APPLICATIONS

FIELD OF THE INVENTION

[0001] This invention relates to the fields of liquid fluid pumping technology, net zero emission engine and power generation technologies, combustion and solar thermal heat energy recovery, and in particular it relates to new methods and systems utilizing simultaneously and or sequentially applied pressure differentials to perform work.

[0002] Disc compressors known to be capable of efficient fluid transfer are herein preferred for utilization in applications wherein the strategic combination of evacuation and compression potentials synchronously and or sequentially applied enables the specification of new methods and systems for: the efficient transfer and or lift of liquid fluids to elevation, and; closed loop and semi-closed loop systems wherein the confinement of high pressure gaseous fluid availing substantial conservation of the energy of compression in combination with applied evacuation and compression potentials employed may provide remunerative measures of work concurrent with energy conservation, and; engine designs also providing pressure energy conservation which may be capable of leveraging the ratio of liquid vs. gaseous working fluid viscosities employed to provide enhanced energy conversion relative thereto said ratio in cooperation with disc turbines configured for energy extraction there-from said fluids, and; the utilization of ambient atmospheric pressure as a cooperating source of energy by which the continuous extraction of gravitational energy may be availed from celestial bodies possessing a suitable atmospheric pressure, liquid fluids of suitable viscosity thereon and a suitable gravitational field strength to assist in providing renewable power generation according to the invention.

BACKGROUND

[0003] It is well known that large motors are required to drive liquid fluid pumps tasked with raising large quantities of liquid fluids to elevation, which requirement may be attributed in part, to the prior art liquid fluid pumping elements' immersion in the liquid fluid to be pumped, which liquid fluid, water for example, is very dense and very viscous in comparison to gaseous fluids (or vacuum) and prior art pumping devices of said liquid fluid are greatly limited in their performance by the effects of cavitation, and which liquid fluid pumping is meanwhile affected by local gravitational field strength imposing a different head pressure (back-pressure) and therefore performance characteristic upon said liquid fluid pumps according to their type under different pressures of operation, and which combination of parameters requires large scale energy expenditures globally to perform the requisite displacement of liquid fluids to elevation en-mas se.

[0004] Prior art engine and power generation technologies (hybrid and electric drives aside) utilize pressurized masses of gaseous fluid (combustion products) to do work against engine components and a drive-train to provide useful output work, however, in the process, said gaseous products of combustion are typically expelled to the atmosphere where the pressure energy provided by said combustion process is constantly dispersed.

[0005] Hydro-generated pressure differentials, while providing clean energy supply through their conversion, similarly release higher pressure potentials through the work conversion process, and whereas humankind may continue to dam rivers to avail further renewable pressure differential for work generation at the expense of the environment, pressure differential obtained thus may be volatile in the face of climate change.

[0006] In light of the prior art methods wherein liquid fluids are moved to elevation by liquid fluid pumps operating with noted restrictions, and other systems limited by their operation on the basis of single-usage of high pressure potentials and or those systems which utilize the ambient mediums (which on Earth are required to support life) as a sink for said systems' pollution, heat, and pressure losses, there is great need for new methods and systems which may reverse this trend by employing ambient medium(s) in capacity as sources of energy, and other systems which may provide remunerative re-use of captive high pressure fluids to cooperate with energy generation and pumping systems to provide greatly needed conservation lacking in the prior art. SUMMARY OF THE INVENTION

[0007] An object of the present invention is to provide a system for raising liquid fluids to elevation in cooperation with the atmospheric medium, which system utilizes sub-atmospheric (or vacuum) reference pressures applied in opposition to said atmospheric pressure substantially across an intervening liquid fluid column (or lift-leg) by which to convey liquid fluids hither or thither. In accordance with an aspect of the present invention, there is provided a system for pumping liquid fluids to elevation comprising: one or more multi-stage Tesla-type disc compressors acting to evacuate gaseous medium, from; one or more vacuum compatible capacities alternately filled with and thereafter emptied of; said gaseous fluid provided by the ambient atmospheric medium according said capacities' gaseous pressurization and subsequent substantial evacuation, by way of; one or more gaseous fluid valves and conduit means there-for permitting atmospheric ingress without requirement for continually energized pressurization means (such as a compressor), and; one or more further gaseous fluid valve(s) communicating gaseous fluid from said capacities (sequentially) to the axial inlet of said Tesla-type compressor, and; at least one liquid fluid valve respective to each capacity such as check valves or controlled valves permitting the ingress of liquid fluid there-into said capacity concurrent with its gaseous evacuation, and; at least one liquid fluid valve and conduit means there-for respective to each capacity such as check valves or controlled valves permitting the discharge (and transfer) of liquid fluid there-from said capacity concurrent with its re-pressurization; whereby the entry of liquid fluids temporarily contained in said vacuum compatible capacities upon their gaseous evacuation may be subsequently followed by the expulsion of said liquid fluid and the movement thereof to another location or to elevation if desired by permitting the atmospheric medium to enter said capacities and act upon the liquid fluid interface surface therein.

[0008] A further object of the present invention is to provide a method for the transfer of liquid fluids to elevation utilizing the system of sequentially applied sub-atmospheric pressures (or vacuum potentials) and atmospheric pressure potentials previously discussed, and further described herein at length, to provide an efficient method of pumping liquid fluids which does not suffer the disadvantages of prior art liquid fluid pumping methods. [0009] Another object of the present invention is to provide a system for raising liquid fluids to elevation which does not require communication with the atmospheric medium, but which system utilizes vacuum and or low gaseous system reference pressures applied in opposition to high gaseous system reference pressures substantially across an intervening liquid fluid column (or lift-leg) by which to convey liquid fluids hither or thither. In accordance with an aspect of the present invention, there is provided a system for pumping liquid fluids to elevation comprising: one or more multi-stage Tesla-type disc compressors acting to alternately evacuate and pressurize; volume(s) of captive gaseous medium of preferably light density and low viscosity, from; one or more liquid fluid receiving vacuum compatible capacities filled with liquid fluid concurrently with said capacity's active gaseous fluid evacuation, and; one or more alternate liquid fluid sourcing pressure compatible capacities discharging liquid fluid upon said capacity's active gaseous pressurization, whereby; the alternating of the gaseous pressurization and gaseous evacuation potentials of said one or more Tesla-type disc compressors distributed across a system of vacuum-and-pressure-compatible capacities may concurrently drive liquid fluid from one capacity (under active gaseous pressurization) to another capacity (under active gaseous evacuation), by way of; one or more gaseous fluid valves and conduit means respective to each of said capacities permitting ingress of the pressurized gaseous fluid providing active (or eventual) compression to drive said liquid fluid (to a capacity under active evacuation or under a lower gaseous reference pressure), and; one or more further gaseous fluid valve(s) and conduit means there-for permitting gaseous fluid egress from each of said capacities under active gaseous evacuation whereby liquid fluid may be drawn into said capacities, through; at least one liquid fluid valve respective to each capacity such as check valves or controlled valves permitting the ingress of liquid fluid there-into said capacity concurrent with its gaseous evacuation, and; whereby the discharge of liquid fluids first received in said capacities (upon said capacities' gaseous evacuation) may be subsequently followed by the expulsion of said liquid fluid and its movement to another location or to elevation via communication of the high system reference pressure (provided by the tangential discharge of said multi-stage Tesla-type compressor(s) into said capacities and act upon the liquid fluid interface surface therein.

[0010] Another object of the present invention is to provide a method for the transfer of liquid fluids to elevation utilizing the system of simultaneous and sequentially applied low (or vacuum) reference pressures and high system reference pressure potentials previously discussed and further described herein at length, to provide another method of transferring liquid fluids which does not suffer the disadvantages of prior art liquid fluid pumping methods.

[0011] A further object of the present invention is to provide a system and method for raising liquid fluids to elevation in cooperation with the application of atmospheric medium pressures and sub-atmospheric (or substantial vacuum) pressures as discussed which may avail remunerative measures of energy generation there-from in cooperation with Tesla-type turbines configured for energy extraction there-from said fluids which upon said liquid fluid reaching an upper elevation of the system, or at a later time, may be permitted to fall there-from said elevation at a flow-rate largely equal to the rate of liquid fluid flow provided by the system to said elevation(s), and in which system over the period of operation of consideration, the system's total uplift of liquid fluids to elevation may be largely configured to be equal or greater than the total release of liquid fluids from all elevations of consideration so that while energy generation may occur on a continuous or scheduled basis, storage capacity of liquid fluids at elevation may also be provided by the system for later use.

[0012] Yet another object of the present invention is to provide a system for raising liquid fluids to elevation which does not require communication with the atmospheric medium, but which system utilizes vacuum and or other low system reference pressures applied in opposition to captive volume(s) of high gaseous system reference pressures substantially across an intervening liquid fluid column (or lift-leg) by which to convey liquid fluids hither or thither by which remunerative measures of energy generation there-from may be availed in cooperation with Tesla-type turbines configured for energy extraction there-from said fluids which upon said liquid fluid reaching an upper elevation of the system, or at a later time, may be permitted to fall there-from said elevation at a flow-rate largely equal to the rate of liquid fluid flow provided by the system to said elevation(s), and in which system over the period of operation of consideration, the system's total uplift of liquid fluids to elevation may be largely configured to be equal to or greater than the total release of liquid fluids from all elevations so that while energy generation may occur on a continuous or scheduled basis, storage capacity of liquid fluids at elevation may also be provided by the system for later use. [0013] Still another object of the present invention is to provide systems which may both sequentially as well as simultaneously apply captive volume(s) of high gaseous system reference pressures in opposition to system vacuum and or other low reference pressures whereby liquid fluid may be driven from one vacuum- and-pres sure-compatible capacity to another in substantially closed loop by way of said liquid fluid passing through work generation or conversion means such as a Tesla-type disc turbine to provide energy recovery from the system in proportion to the flow of liquid fluid through said turbine, the axial distance of separation of adjacent turbine discs, and the viscosity of the liquid working fluid driven through said liquid fluid turbine by said gaseous pressure differential developed by one or more multi-stage Tesla-type disc compressor(s) tasked with maintaining high system reference pressure in a regulated high pressure supply reservoir while concurrently providing evacuation of gaseous fluid from one or more other capacities, and in which system(s) the flow-rate of liquid working fluid through said liquid fluid turbine is configured to be sufficient to drive a load, and the run-time replenishing high gaseous fluid reference pressure is always available for application to the liquid fluid interface surface above a source of liquid communicating with said turbine, while the vacuum potential of multi-stage compressor ever-communicates with the discharge side of said liquid fluid turbine whereby the system's gaseous fluid of greatly lesser density and viscosity may be configured to drive the liquid fluid flow circuit at the required flow-rate over the period of operation of consideration by said gaseous fluid requiring less energy to move, and the pressure of which may be largely conserved in operation.

[0014] Yet another object of the present invention is to provide systems utilizing sequentially and simultaneously applied high and low (or vacuum) gaseous system reference pressures which in many embodiments do not require communication with ambient external environments, and by nature of the resistance of Tesla-type turbines to wear, said systems may therefore provide dual service in wastewater treatment processes by which energy generation may be a beneficial by-product of said service.

[0015] Still another object of the invention is to provide a system and method for energy recovery from combustion processes so as to minimize the environmental heat loading and pollution caused thereby said combustion processes. In accordance with said object, a system is disclosed which comprises: a multi-stage Tesla-type compressor, the intake (low pressure) with an axial inlet and a discharge (compression pressure), which axial low pressure inlet potential of said Tesla-type compressor is directed unto communication with a source of combustion flue gases, and; said higher pressure outlet potential of said Tesla-type compressor adding heat of compression to said (compressed) flue gas is directed unto communication with one or more conduits equipped with check valve or controlled isolation valve means, whereby; compressed combustion flue gases entering said conduits may be communicated into one or more isolated heat exchangers which may be submerged in or otherwise communicate heat into; a heat recovery fluid further communicating said received heat energy to; a load, by way of; further conduit means, and; return conduit means returning said heat recovery fluid to said heat exchanger from said load in combination with; a liquid fluid circulation means; with said compressed heat recovery fluid remaining captured in said heat sink means for a configured period of time (permitting substantial extraction of heat energy from said combustion) by a further check valve or controlled valve respective to each heat exchanger branch, prior to said compressed combustion exhaust being ejected by; a subsequent charge of compressed combustion exhaust similarly captured for a period of time, with said first charge of compressed and cooled combustion exhaust either being ejected to; atmosphere, or said first charge of compressed and cooled combustion exhaust alternately passing through; a coalescing filter, and further valve means into; a carbon capture conduit, which carbon capture conduit may communicate with the axial inlet of; a larger capacity Tesla-type compressor amplifying said carbon capture conduit pressure to greater pressures required for insertion into carbon sequestration vaults.

[0016] Another object of the invention is to utilize the simultaneous and or sequential application of pressure differentials to cooperate with all liquid fluid pumping applications so as to reduce the energy consumption required to operate said systems. In accordance with said object, liquid fluid pumping applications abound which may utilize the various embodiments of the invention disclosed for the transfer of liquid fluids which include: solar thermal energy collection systems, well systems, irrigation systems, municipal water pumping, and other heat transfer systems.

[0017] A further object of the invention is to provide the active evacuation of building envelopes as a centralized service component of residential, community, commercial as well as large constructions so as to provide exceptional thermal resistance to heat-loss (insulation value) by utilizing the excess vacuum capacity offered by: Tesla-type disc compressors or other serviceable compression means, to; maintain a high degree of evacuation (extremely low pressure, or rarefaction) in one or more large capacity vacuum compatible reservoir(s) which may be communicated; thermal resistance diminishing gaseous fluid from said; active evacuation building envelope panels, segments or arrayed systems thereof, by way of; vacuum compatible isolation valves and conduit means where-through said gaseous ingress into said active evacuation building systems may be further communicated to the axial inlet of said large capacity Tesla-type disc compressor(s) of high evacuation potential through; a further vacuum compatible valve and conduit means, when the pressure sensed by; a pressure control means responding to a configured high pressure limit controls said valve to open.

[0018] Yet another object of the invention is the recovery of energy from the pressure differential reversals and fluid flow operations required of the method, which in various embodiments may permit either or both gaseous fluid and or liquid fluid turbines to be employed to this purpose.

[0019] Equation 1, below generally states the relation for power in given cross sections of fluid which may be referred to regularly during application design and when modelling the efficiencies required and or realized from energy conversion turbines utilized in various locations of embodiments of the invention in relation to the energy actually present in the flow as given in Equation 1.

[0020] Equation 1:

Power in a Given Cross Section of Moving Fluid = '/2 x p x A x v ³

Where: P = power p = density

A = cross-sectional area v = velocity

BRIEF DESCRIPTION OF THE FIGURES

[0021] In drawings illustrating embodiments of the invention, Figures Ia and Ib illustrate the utilization of vacuum potential and the atmospheric medium to provide liquid fluid pumping work in a sequence of side views illustrating a multi-stage and runner disc vacuum-compression means employed so as to develop a serviceable sub- atmospheric pressure at a higher elevation to effect efficient liquid fluid transfer thereto from a lower elevation capacity whereupon the ambient atmospheric medium is applied as a motive pressure source, which sequence of side views providing a single 50% duty cycle approach to liquid fluids transfer; Figures Ic and Id illustrate a further sequence of side views utilizing the approach provided in respect to Figures Ia and Ib in a system offering redundancy of like components and cooperative usage of conduits and other components to largely provide a 100% duty cycle transfer of liquid fluids to elevation utilizing the atmospheric pressure as a motive pressure source provided over multiple lift-legs to elevation; Figures Ie and If illustrate a further sequence of side views employing a Tesla-type compressor (or vacuum-compression means) wherein both its vacuum and compression potentials may be simultaneously utilized to achieve liquid fluids pumping to elevation or elsewhere, wherein said vacuum-compression means generates and maintains a serviceably high gaseous control fluid pressure for application to the surface of lower elevation capacities through the evacuation of said gaseous fluid pressure from upper capacities whereto liquid fluids may thereby be conducted through larger lift legs if designed there-for; Figure Ig provides a side view illustrating a 'top- down' application of captive system-generated high reference pressures wherein larger capacity conduits and dedicated vacuum-compression means at each lift station offers large capacity 'pumping', with said figure also incorporating pressure recovery turbines to recover energy from the transfer of gaseous pressurization control fluid; Figure Ih illustrates a 'side-to-side' system side view wherein gaseous pressurization control fluid is transferred between adjacent lift station capacities thereby expressing a differential pressure at each elevations' lift station concurrently controlled to be largely 180° out of phase with successive elevation lift station(s)' expressed pressure differentials whereby opposite polarity gaseous pressure differentials are produced across vertically communicating liquid fluid interface surfaces causing liquid fluids to be substantially pushed to a higher elevation on the one hand, while liquid fluids are drawn there-into adjacent lift station capacities, said figure also illustrating further work conversion means recovering energy from the transfer of gaseous fluids during energy conserving gaseous fluid pressure-shunting events permitting the recovery of a substantial portion of the energy expended to operate the system; Figure Ii provides a side elevation view of a rotary pressure reducing valve apparatus discussed in respect to Figure Ih providing synchronization of cycles of pressurization, evacuation and shunting with a rotary valve operator, which during shunting operations occurring each lift-cycle permits energy recovery via said high pressure fluid transfer passing through a disc turbine mounted for rotation there-within said pressure reducing valve assembly permitting the further recovery of the energy utilized to operate such systems, and; Figure Ij illustrates a further side view of an embodiment of the invention discussed in terms of higher gaseous pressure references than atmospheric pressure, including that of Figure Ik disclosing a design for an actively evacuated building envelope panel which may provide superior thermal and moisture barrier performance greatly exceeding the prior art. Figure 2 illustrates the extended application of simultaneous and sequentially applied pressure differentials whereby a primary goal of the system is the generation of power in conjunction with large staged energy extraction vortices and a design for permanent magnet power generation means there-for. Figure 3 provides a four-part sequence of side views illustrating another captive high-pressure application of the invention put to the task of liquid fluids pumping and energy recovery there-from. Figure 4 provides an eight-part sequence of side views illustrating the operation of an embodiment of a Viscosity Vacuum Engine in which the energy of compression may be substantially conserved and power output may be proportionate to liquid vs. gaseous fluid viscosities ratio. Figure 5 provides an eleven-part sequence of side views illustrating the operation of an alternate embodiment of a Vacuum Viscosity Engine in which compression energy is largely conserved and power may be proportionate to the viscosity ratio of liquid and gaseous working fluids. Figure 6 illustrates a part side and part sectional view of a further embodiment of a Viscosity Vacuum Engine in which the introduction of a timing mechanism synchronizing rotation of a slotted valve-plate may simplify the operation and minimize the complexities and parts required for utilization of such machines, with its engine operation explained in conjunction with a sequence of timing mechanism 'valve states'. Figure 7a provides primarily a side sectional view illustrating the application of simultaneous evacuation and compression potentials of Tesla type disc compressors to the recovery of heat energy from residential and (by extension) other combustion exhausts, meanwhile pre-compressing, cooling, filtering, de-watering and capturing combustion flue gas emissions (CO ₂ ) in carbon capture conduits for furtherance to central compression plants while providing energy extraction and return on investment from the capture of sequestered CO ₂ , and; Figure 7b provides a side elevation view of an application of simultaneously applied pressure differentials according to the invention applicable the transfer of liquid fluids for solar thermal energy collection and other general purpose pumping tasks. Figure 8 illustrates a partial sectional view showing the employment of permanent magnets in an automatic disc spacing sub-system for disc compressor, pump, turbine and vacuum pump means. Figure 9a provides a chart of the vapour pressure of carbon-dioxide, while Figure 9b and 9c provide charts of the Vapour Pressures of Hydrocarbons and Phase Diagrams of Ethane-Methane Mixtures, respectively, as background information in regard to Figure 7a, and Figure 9d provides a reference chart of atmospheric pressure with respect to altitude in consideration of embodiments of Figures 1 and 2 wherein the atmospheric pressure is utilized as the high-pressure reference.

DETAILED DESCRIPTION OF THE INVENTION

Disc Turbines and Compressors

[0022] Disc turbines, pumps, compressors and vacuum pumps largely disclosed by Dr. Nikola Tesla (1, 2, 22) in the earlier part of the twentieth century and researched in depth (28, 30-33, 37-40, 42) are known to be effective fluid energy receivers utilizing boundary layer adhesion, viscous shear stress and serviceable disc separation (forming channels or gaps between discs) to develop torque upon axially spaced disc surfaces generally having tangential inlet and axial outlet holes in turbines, and utilizing the same principles substantially in reverse, torque applied to a driven disc device having axial inlets and tangential outlets (ie: to and from said inter-disc channels or gaps) may provide an effective fluid energy transmitter through which torque applied to turn said compression, pump and or vacuum pump disc runners causing rotation thereof may result in the transfer of shear stress from the boundary layer fluids (adhering thereto the rotating disc elements) defining opposite walls of said channels, with said shear stress causing the fluid present in the disc gap to be acted on according to its viscosity and the angular momentum of said rotating discs whereby a velocity gradient produced in said inter-disc fluid (in disc runners having effectively spaced discs) reaching a maximum in the central region of the disc gap also results in the development of a radial pressure gradient increasing toward tangential fluid expulsion from the inter-disc channels owing the centripetal force applied by the boundary layer 'stationary' fluids on the fluid set in motion in the disc gap further resulting in the tangential discharge of pressurized fluids propelled thus. [0023] As disclosed by Tesla (2, 22), disc compressors make highly efficient compressors and vacuum pumps when these devices are provided disc spaces which under the particular fluidic and angular velocity conditions of operational service may provide a laminar flow character permitting working fluid received at axial inlets formed by one or more concentrically arranged holes in each of (typically) a plurality of axially spaced apart discs, fluid may be drawn there-into the channel under the radial pressure gradient imposed, and thereafter be transferred through the (plurality of) inter-disc gaps and be expelled from the periphery of the disc runner (through tangential channel outlets) with a minimum of turbulence.

[0024] Since the conditions of proposed service for disc-compressors (vacuum- compression means as later referred to) disclosed herein shall impose dynamically changing pressure and also temperature conditions, it may be understood that the fluid viscosity of the gaseous pressurization control fluid being communicated between respective pressurization reservoirs shall significantly change from the start through completion of said gaseous fluid pressure differential reversals. While the property of dynamic viscosity is substantially independent of pressure, it may be understood that since according to Equation 2 (below) it is the kinetic (or kinematic) viscosity of the working fluid (largely air in this case, except at very low pressures where water vapour may dominate the gaseous mixture composition, and require that disc spacing appropriate there-for be provided for optimal 'pumping' action during low pressure operation) which is utilized to derive the ideal disc spacing for service in disc device applications, it follows, therefore that the kinetic viscosity which is pressure dependent (since it relates to the ratio of dynamic viscosity to the density of the working fluid, which fluid density is directly dependent upon the pressure of service) shall along with the temperature of service also be changing at a particular rate throughout run-time system operation, and therefore that dependent upon the ultimate pressures of service required, that fixed disc spacing disc compressor devices may not be capable of providing the required level of service.

[0025] Accordingly, it is foreseeable that the disc spacing appropriate for the initial stage of pressure reversals, or fluid transfer, (wherein temperature and pressure and density at the axial inlet are highest and temperature, pressure and density of the gaseous fluid at the discharge are lowest) may be significantly different than the disc spacing appropriate throughout the gaseous fluid transfer (wherein the temperature, pressure and density of fluid at the axial inlet are decreasing while the temperature, pressure and density of the gaseous fluid at the discharge are increasing) and said appropriate or ideal disc spacing may continue to change until termination of the fluid transfer / pressure differential reversal (whereupon the temperature, pressure and density of fluid at the axial inlet are at a minimum while the temperature, pressure and density of the gaseous fluid at the discharge are at a maximum), that a dynamic disc spacing apparatus would assist embodiments of disc compression devices utilized in the invention (ie: vacuum- compression means discussed at length herein) to better conduct the working fluid provided under the dynamically changing kinetic viscosity conditions of service.

[0026] Adjustable and dynamically adjusted disc spacing (ie: disc separation automated to be controlled by a control system) has been previously suggested for use in disc turbines (18), however, the conditions of service which may be prevalent in compression type systems as well as more detailed description indicating the requirement for said adjustable disc spacing features as component to disc compression devices was not previously specified as provided herein. While the kinetic viscosity of higher pressure gaseous fluids may be small in comparison to the kinetic viscosity of rarefied (low pressure) gaseous fluid and this in turn may require that in observance of the relation specified in Equation 2 that the required disc spacing be much smaller at higher pressures of operation than during lower pressure operation, it may also be stated that at the start of pressure reversals discussed herein when the pressure differential is a maximum, that it may be most serviceable instead to initially set up the disc spacing to provide for an intermediate disc gap spacing in anticipation of an operational pressure to be realized post opening and subsequent closure of one or more high volume valves communicating between pressurization reservoirs which may most rapidly equalize the pressure between reservoirs and therefore most rapidly and efficiently apply a serviceable pressure for pumping purposes, upon the liquid fluid replete reservoir's liquid fluid interface surface, where-after said equalization period the disc spacing set may most effectively communicate the gaseous fluid, with modulation of disc spacing being controlled to be proportionate to kinetic viscosity thereafter.

[0027] In any case, it may be understood that the transfers of gaseous pressurization control fluid specified herein under dynamically changing conditions of operation applications may be significantly advantaged through the employment of vacuum- compression means equipped with an adjustable disc spacing mechanism so as to provide automatic adjustment of the disc gap so that under varying working fluid conditions of pressure, temperature, and co-related fluid viscosity, and or rotor angular velocity, said discs in conjunction with a controller and control algorithm there-for may be positioned to provide effective disc spacing in accordance with or in approximation of the relation defined in Equation 2, in further cooperation with a control actuation means there-for effecting the disc spacing commanded by said controller. A representative dynamic disc spacing sub-system is provided later herein.

[0028] Also disclosed by Tesla (1) and further discussed herein with respect to energy extraction from gaseous and liquid fluid flows, disc turbines comprise axially spaced apart discs mounted normal to a shaft forming a symmetric body of rotation, with at least one of said discs having one or more openings near its centre through which to discharge working fluid. Disc turbines utilized in the various applications herein are provided a housing oriented so that enhanced velocity working fluid flow is guided unto tangential approach with the perimeter of the discs whereby the mass-flow of fluid provided is guided unto full admission about the perimeter of said turbine runner and substantially parallel to the planes defined by the discs thereof so that working fluid is provided only one path of potential flow (ie: largely tangentially) into the spaces, or channels, between co-rotating discs of the disc turbine runner, whereupon a combination of inwardly acting radial pressure gradient forces and outwardly acting centrifugal forces exerted on the fluid due to the rotation of the disc runner cause fluids to follow a spiral path toward the one or more central openings in communication with a lower pressure communicating with said central discharge opening(s) defining the turbine's axial outlet. Fluids spiralling toward the central openings through advantageously spaced discs develop viscous shear-stress there-between fluid layers which may further communicate shear-force to the two or more discs through the boundary layer of working fluid fixedly attached via adhesion to the surfaces of the two or more discs, further developing torque and rotation of the disc turbine. Optimally spaced and operating in a laminar flow regime, a maximum amount of shear-force may be communicated to the discs, which may result in greater torque and rotation there-from.

[0029] As discussed, inter-disc spacing is a critical factor affecting successful torque development in disc turbines, and also affects the successful propulsion of fluids in disc compressors later disclosed herein, therefore the runners of any disc device specified herein is understood, if not specifically specified, to be equipped with an adjustable disc spacing sub-system so that the adjacent discs of disc turbine and compression runners may all be spaced an advantageous axial distance of separation apart for the given viscosity and angular velocities conditions of service, so as to provide optimal disc spacing to approximate laminar flow, instead of non-optimal disc spacing which may otherwise impose efficiency losses due to turbulent flow (spacing too wide) or choking of the flow (spacing too tight) between discs.

[0030] Equation 2: d = π x sqrt(V/ω)

Where: d = optimal disc spacing

V = kinetic viscosity of the fluid ω = angular velocity of the rotor

[0031] Equation 2 (28, 30, 42), above, shows the relationship for the optimal channel width (disc gap, or inter-disc spacing) in disc turbines and compressors, which increases with working fluid kinetic viscosity and decreases with rotor angular velocity. This relation is important to consider for optimal transfers of gaseous pressurization control fluids through vacuum-compression means discussed herein, since it is known that air compression systems may develop significant heat in operation, and while Tesla-type compressors may impose less shock during gaseous fluid compression than piston type compressors, it is nevertheless pertinent to note that over a possible air temperature range of operation (ie: from system start-up on a cold day at 0 ⁰ C whereat the kinetic viscosity of air is 1.32xlO ^"5 m ² /s, through a steady state 'warmed up' compression sequence run-time temperature, which may vary dependent upon the invention application under consideration or a particular stage thereof, however, which steady state temperature may exceed 70 ⁰ C running (whereat the kinetic viscosity of air is 1.97xlO ^"5 m ² /s) whereby over said temperature range, the kinetic viscosity of air increases about 49% which would affect the ideal disc spacing of the vacuum-compression means as well as energy recovery disc turbines specified for use in the system requiring a significant increase of separation in the provided disc spacing of said vacuum compression and turbine means by a considerable margin (according to the relation of Equation 2). [0032] Disc turbines specified for use in liquid fluid energy conversion herein are widely recognized to offer cavitation-free performance enabling them to operate without this significant efficiency limitation suffered by other prior art liquid fluid energy extraction and liquid fluid propulsion means. It has already been stated that liquid fluid pumps (which the present methods of the invention may obviate) are also greatly limited by cavitation, and while Tesla-type disc pumps may also act to provide pumping, action, it is foreseeable that the presently disclosed invention may provide more effective fluid transfers. It is also recognized that rotary engines (of which the Tesla-type turbine is an example) can be much more efficient that piston based engines since there are no connecting rods, linkages and other appurtenances thereby greatly limiting the significant friction suffered by much prior art energy conversion machinery in use today.

[0033] The invention will now be described with reference to specific examples. It will be understood that the following examples are intended to describe embodiments of the invention and are not intended to limit the invention in any way.

[0034] Referring now to Figure 1, the extended application of disc devices as vacuum pumps, compressors and turbines are presently expounded upon which may avail the novel application of disc turbine technology to the elevation and transfer of liquid fluids (without operating in the liquid fluids) so that liquid fluids such as water may be raised from lower elevation to higher elevation more efficiently than hitherto availed with liquid fluid service pumps, and which may thereby effect a great conservation in energy expenditure required to perform the same work as compared to present day liquid pumping methods in such applications.

[0035] Whereas enormous measures of work are done in municipal water pumping processes including: treatment and pumping thereof to elevated storage towers and other reservoirs; wastewater pumping; pumping of cooling water, steam feed- water and heavy water for thermal energy generation requirements of both coal and nuclear operations; irrigation of farmlands; and other industrial and commercial processes in combination implicating vast global energy consumption, financial cost and deferred environmental burdens associated therewith the carbon footprint there-for said pumping of liquids by conventional means known to be susceptible to the limiting effects of cavitation to pump said heavy and viscous water at high pressures upwardly against the force of gravity through pipes into elevated storage reservoirs and elsewhere, the presently disclosed method by contrast need only apply alternating pressure differentials of serviceable pressure to top-side gaseous fluid pressure connections communicating with liquid fluid interface surfaces therein a series of sequentially higher-elevation pressure and vacuum- compatible conduits and or transfer tanks of suitable capacity, where-into and where- from finite masses of air and of evolving water vapour alternately pressurizing and being evacuated through said top-side gaseous fluid connections of the various reservoirs proposed may communicate desirously large pressure differentials across liquid fluids contained therein said conduits or capacities in order to cause their flow from lower elevation (whereat a higher gaseous fluid pressure is exercised) through intervening vacuum-compatible liquid fluid transfer conduit to a higher elevation liquid fluid capacity referenced to a very low or substantial vacuum pressure thereat, while said liquid fluids pass en-route through check valve means keeping liquid fluids thus moved at the higher elevation realized under given lifts caused by the provided gaseous differential pressure (and volume thereof) application. Alternation of pressures subsequently applied thereto said series of sequentially higher elevation elements may then cause movement of the contained liquid fluids in the (upward) direction yet again, and again, and so on, to great height if desired, although with decreasing height differences per 'lift' with increasing elevation gain, due to the reduction in atmospheric pressure with elevation (if the atmospheric pressure is utilized as the high pressure reference). With well-sealed vacuum conduit means preventing ingress of the atmospheric pressure into largely evacuated process lines throughout embodiments of the system, and with the assurance of vacuum-compression means provided by a multistage Tesla-type vacuum-compressor with effective labyrinth seals, substantial voids in the ambient atmospheric medium may be strategically created and maintained in said conduits and reservoirs when required to maximize the pressure differentials required for efficient liquid fluids 'pumping' where-into said reservoirs liquid fluids induced by the favourable pressure differential created may be thereby caused to enter there-into said voids due to the imbalance of forces availed through operation of the system and thereby gainfully effect the upward conveyance of liquid fluids to elevation.

[0036] In cooperation with controller means such as a PLC, with key operating parameters of the system defined, including but not limited to: anticipated differential pressures across high and low pressure sections; mean liquid fluids transfer time constant under the maximum and average pressure differentials possible; the gaseous pressurization and evacuation time constants for the conduit sizes and reservoirs utilized; the number of conduit sets, and reservoirs utilized; and automated valve and check valve sizes and numbers required to satisfy downstream demand, and the cracking pressures (opening pressure resistance) thereof; and the throughput capability of the enabling multi-stage compression means utilized, herein preferred to be a Tesla-type disc compressor of large capacity (but which may be another type of centrifugal compressor), a process control strategy which may largely comprise scheduled pressurization and de-pressurization (ie: evacuation) event sequences alternately applying pressure and or vacuum to the gaseous pressure control connection points of said conduits or capacities, which also need to be sized to permit the gaseous enabling throughput required to cause the required liquid fluid flow to be effected to sequentially elevated conduits and or capacities at largely the design time constant (to ensure a timely schedule is kept), and in combination with further feedback from analog and discrete pressure, level and flow metering and monitoring devices which may also desirously be incorporated into the control strategy to ensure optimal utilization of the capacity offered by the system and meanwhile afford alarming and safety and interlock information where required.

[0037] Liquid fluid filling into upper-elevation conduits and or capacities are accomplished via the application of sufficiently low vacuum pressures to top of liquid- fluid conduit or reservoir gaseous fluid pressurization and evacuation connection points concurrent with the application of sufficiently high gaseous pressurization control fluid to bottom of lift-leg connection points also located on or close to the top of respective reservoirs and or conduits so that gaseous pressurization control fluid communicated from or to the vacuum-compression means by way of control valves or slow-acting shut- off valve means may always act upon the liquid fluid interface surface of the to be conveyed to (and or received at) higher elevation. An enabling feature of the invention being the advantageous density difference between liquid fluids (ie: water in this terrestrial application) causing the liquid fluid to be ever confined by its density to always occupy the bottom region of said reservoirs even up to extremely high pressures of gaseous fluid captivity (beyond those pressures contemplated for use with the invention).

[0038] Said favourable density difference also cooperatively maintains that references to partial vacuum, low and high pressures including and beyond the atmospheric pressure by way of said top-of-reservoir connections discussed in the various embodiments of the invention ensures that the gaseous pressurization and evacuation control fluid ever of lighter density than said liquid fluid (hence being communicated from above in the various embodiments) is always segregated from the fluid to be raised to elevation or otherwise transferred.

[0039] Since the gaseous and liquid fluid circuits of the invention are separate, the only 'pumping element' of the invention (ie: said vacuum-compression means, hereinafter referred to as VCM or VCM 2000) responsible for developing pressure differential and thereby 'pumping action' in the methods discussed may be located, as discussed, outside of the liquid fluid circuit completely which offers step change advantage to maintenance services required compared to liquid fluids pumping in the prior art. With said pressurization control fluids being applied to the reservoir volume above the liquid fluid interface surface within said capacities, being of greatly less density than the liquid fluid co-occupying the same conduit, said gaseous pressurization control fluid remains on top of the liquid surface while exercising potentially great contiguous downward pressure and force upon the full surface thereof said liquid fluid expanse so that providing one or more outlets communicating with the bottom of said pressurization reservoir(s), said downward force application and resultant push in the downward direction results in fluidic egress via said liquid fluid conduit outlets at length communicating through check valve means to higher elevation (or elsewhere), as discussed, where a substantial vacuum pressure (or another serviceably low pressure) is exercised, thereby drawing and forcing the liquid fluid medium down and out of said capacity, and thereafter upward to the low pressure at an upper elevation.

[0040] Post exhaustion of liquid fluid from the lower elevation capacity, a subsequent operation may commence following the closure of a check valve or another back-flow preventing means whereby the elevated liquid fluid may be isolated from the lower elevation fill-conduit in preparation for said subsequent fluid movement operation. Once separation of the respective 'lift' horizons (or lift stations) has been effected after the flow toward the upper elevation slows or terminates, a pressure-equalization event may be triggered.

[0041] Pressure equalization events providing the first step in reversing the differential pressures required to convey liquid fluid received to an upper elevation reservoir may be effected by controlling the appropriate valve positions isolating the liquid fluid interface surfaces from the application of vacuum pressure via first closure of the vacuum conduit valve followed by restoring the atmospheric or other serviceably high pressure to the surface of said liquid fluid interface in said liquid fluid replete capacity as by opening an atmospheric or other high pressure ingress valve, and with said liquid fluid providing a perfect seal about the full cross-section of the capacity, ingress of the atmospheric or other high gaseous pressure fluid may apply great pressure and concurrent force to the liquid level surface in said capacity tank or conduit without leakage owing the favourable density difference discussed between said gaseous an liquid fluids.

[0042] The extended transfer of liquid fluids from lower elevation to higher elevation may be continued via the application of vacuum pressure to a reservoir at a higher elevation communicating with said (previously stated) reservoir in process of being restored to higher pressure (considered for purposes of discussion to be located at lower elevation) whereby the capacity (or reservoir) under the higher gaseous pressure at the lower elevation may provide liquid fluid to liquid fluid conduits and thence to elevation when a favourable differential pressure exists following the opening of vacuum valve means thereafter communicating pressurization control fluid by way of valve and conduit means (and or by way of common headers which may also be employed) the communication of low vacuum pressure unto the interior of said subsequent vacuum capable capacity may thereby substantially evacuate contained air and or liquid fluid vapour (ie: water vapour) where-after said capacity substantially evacuated to very low pressure and thereby offering no backpressure against the atmospheric or other higher pressure applied at lower elevation substantially across the intervening 'lift-leg' (ie: the liquid fluid conduit representing a liquid column separating reservoirs by an elevation difference) may then permit the conveyance of said liquid fluids toward the upper elevation, by way of conduits comprising piping of preferably very large diameter to minimize frictional losses while allowing large or great volumetric flow-rates to be readily achieved, which large diameter liquid fluid conduits may further employ guide blades and other contrivances as disclosed by Schauberger (23, 24, 25) to permit faster and generally freer movement of the fluid through said conduits to further reduce the effective friction observed through said conduit means.

[0043] Due to its light density and serviceable pressure the energy of the atmospheric medium alone may suffice to push heavy liquid fluids 'up-hill' against the force of gravity providing for the expression of a substantial vacuum or vacuum-like pressure applied above the upper-elevation reservoir's liquid fluid interface surface (ie: at the top of the lift-leg) so that a sufficient differential pressure is expressed across the lift-leg to elevation which exceeds the head-pressure in the liquid fluid when the liquid fluid level in the lower elevation is lowest and the liquid fluid level in said upper elevation reservoir is highest (dependent upon the conduit configuration of given embodiments). By design, the very density of liquid fluids (ie: water) affords their substantial segregation from the lighter gaseous pressurization fluids employed in the method, so that even if charged with excessively greater pressure than proposed lift-leg height- respective pressures, said gaseous fluids will always remain substantially segregated. Along with their serviceably high viscosity and suited adhesion characteristics causing them to always occupy the bottom and remain in adhesive adjacency with lower wall portions of said conduits and capacities, liquid fluids may thereby create a contiguous fluidic seal there-about the inner perimeter thereof said reservoir(s), and in similar case in point to the atmospheric pressure being capable of causing the 'up-hill' movement of said liquid fluids in single-lift fashions illustrated in respect to Figures Ia and Ib, said same method may be extrapolated upon to provide multi-lift-leg service as illustrated in Figures Ic and Id, and the application of higher pressure system references than the atmospheric pressure affords is illustrated and described in respect to Figures Ie, If, Ig, Ih, Ii, Ij may preferably provide higher gaseous pressurization pressures via reciprocation of higher pressures maintained in captivity within the fixed system volume disclosed. For example, upon expulsion of a given lower elevation conduit's liquid fluid contents (through a check valve preventing its return), via gaseous ingress and pressurization there-into said lower elevation conduit or capacity, higher pressure gaseous fluids there-forced-into said lower elevation conduit, may, via valve cycling and pressure shunting there- within said fixed system volume, which may also include its passage into and eventually through an intermediary pressure capacity tank (not shown in the figure), be provided to the axial intake of the disc 'vacuum-compressor' (providing the high pressure within the system wherefrom the system shown in the pair of figures may further provide an elevated high pressure within the high pressure capacity tank shown in the figure, and may thereby provide the mass at extended pressure required for subsequent vacuum-pumping 'lifts', since as shown, the elevated pressure feed source may be reciprocated throughout the limited volume of the system at will (in conjunction with appropriate valve cycling and with the further prudent employment of pressure regulation means with which to minimize the shock of pressure cycling and the accordant stress implicated thereby within the disclosed system helping to provide great system longevity between failures). Re-stated, and therefore, as the gaseous pressurization fluid is thus withdrawn (or, evacuated as by said gaseous disc 'vacuum-compressor') from the lower of the two liquid fluid conduit(s) in any given lift- leg of consideration, a reversal of valve positions at an appropriate period in time (thereby avoiding the overwhelming of piping and capacity components with shock) may then cause the (gaseously) evacuated conduit (now) replete with liquid fluids, to become pressurized, so that said liquid fluids previously drawn through an open check valve at lower elevation, now cause the same check valve to close, and with increasing gaseous pressurization of the given capacity or conduit beyond the head pressure of the given lift-leg of consideration now considered the lift leg comparatively above the capacity under consideration, these same liquid fluid contents may then push open the check valve there-disposed between said pressurized (now lower) conduit or capacity, and thereby permit the relocation of said (now-) pressurized liquid fluid contents to the upper elevation.

[0044] Note that depending upon the system capacities at different pressures in effect, it may be recommended to employ slow opening pressurization valves or gaseous fluid dispersion elements inside the gaseous control pressure application points to prevent jettisoning pressurized gaseous control fluid into the depths of the liquid fluid near the liquid fluid egress point from the conduit or capacity especially at the beginning of pressurization events when the differential pressure is a maximum (which may generate high velocity, potentially violent gaseous fluidic in-rush into the largely evacuated yet liquid-filled conduits) possibly instigating a 'loss of prime' event which may trigger the collapse of the vacuum-maintained head at elevation by significant pressurized vapour and or air ingress into and upward through vertical 'lift- legs' with potentially some time elapsing with accordant reverse-liquid-flow occurring before closure of the check valve may occur since for a time the pressure differential may be maintained through the open check valve while heavier liquid fluids acting in accordance with gravity may fall and equi-pressurized gaseous fluids taking their place in the fluidic column may rise. While effects during such events as minimal as water hammer may be anticipated should such hydraulic tunnelling be generated within said conduits, in general, embodiments of the disclosed invention designed adequately with safety in mind may feature gaseous pressurization application points at opposite ends of conduits and capacities from liquid fluid egress points such that (any) rapid air ingress penetrating the surface of the liquid fluid may substantially return to the gaseous domain above the liquid surface safely away from the liquid fluid egress path from said conduit or capacity means.

[0045] In such systems it may be stated that upon substantial evacuation of air from given system piping segments, that naturally evolving vapour will attempt to express a pressure which may largely correspond to the given liquid fluid's equilibrium vapour pressure at given temperatures, and depending upon: the strength of the vacuum applied by the vacuum-compressor provided and the distance and intervening free path therefrom the control-point of application at which it is applied; the effectiveness of the vacuum (ie labyrinth and other) seals employed; and the assistance there-for provided by the other vacuum-producing appliances to be discussed, said exhaustion may be effected to lower pressure than even said vapour pressure, or may be limited thereto. For example, upon exhaustion of the limited air from within a given conduit or capacity either largely or partially filled with liquid fluid (ie: water) at 10 ⁰ C whereat the corresponding vapour pressure of water is about 1.23 kPa, or about 1.2% of atmospheric pressure, once the liquid fluid is moved from said conduit via the combination vacuum- pressurization method proposed, provided good vacuum seals, the liquid level may be maintained thereat rest indefinitely, should the given lower and upper pressurization and vacuum respective valve positions be also maintained.

[0046] It is widely recognized that liquid fluids may only be 'vacuumed' to an elevation of 33 feet (or slightly more, depending on factors including the type of vacuum pump employed and the effectiveness of the liquid-gaseous fluid seals thereof employed), yet to date a system and method which takes such a scheme into beneficial practice on a grand scale of service far in excess of 33 feet, so far as is known to the applicant, has not been achieved. Notwithstanding this fact, the capability of such a system approach concept has already been validated (albeit the example provided avails, as suggested, only a single elevation 'lift-leg' height of service) and was recently witnessed in operation as a high-lift capacity pump priming mechanism in a municipal water treatment plant wherein a startlingly-tiny capacity lobe vacuum pump operating at slow RPM for about four minutes readily evacuates the air from three large diameter water (suction) conduits, and thereby raises water therein said lift-legs from the clear- well below through a distance of some fifteen feet or more, where-after said time, the pumps may remain primed indefinitely with good seals intact, thereby confirming that a very small work expenditure is required to cooperate with the atmospheric pressure so as to induce it to do great work.

[0047] With the air in such a system largely evacuated, it may be stated that while vapour evolution may be limited to the small fractions of atmospheric pressure discussed, that the location and orientation of check valves in such systems may determine the extent to which cavitation may play a part of 'normal' system operation. Accordingly, with check valve means responsible for preventing the gravity return of said liquid fluids conducted to higher elevations, depending on the relative elevation of their installation within given 'lift-leg' segments, vertical check valve installations oriented so as to permit flow in the upward direction, while producing checking action, may also implicate cavitation upon stoppage of flow and check valve closure since the weight of the water acting downward (upon changing pressure conditions effected by the changing of valve states at the lower elevation conduit or capacity) underneath well sealed check valve(s) may readily develop the vapour pressure accordant the temperature of the medium, which may lead to earlier check valve failure(s). Therefore, check valves may preferably be installed in ever-flooded segments of lift-legs below the bottom of the capacity tanks in general (to avoid or minimize the degree of cavitation of the fluid generated within the piping arrangement), and concurrently they should also be mounted above the level of sediment build up, and preferably isolation valves (to permit sediment removal and cleaning of valve-seats) may be provided in their vicinity where line sizes employed do not permit manned or autonomous cleaning thereof said sediment build-up.

[0048] Whereas Figures Ia and Ib illustrate a means for the evacuative filling of a water tower or other elevated storage tank, wherein said means provides a single, however, discontinuous path for the upward atmospherically pushed (or, siphoned) flow of fluids and thereby affords intermittent, albeit reduced energy consumption conveyance of liquid fluids from lower elevation to higher elevation (for example, to fill a water tower), with said single-path method being appropriate for lower demand regions, Figures Ic and Id illustrate a similar, however, more sophisticated and where required, redundant series of elements largely comprising identical elements to those of Figures Ia and Ib wherein vacuum capable capacity tanks, liquid fluid conduits and check valves and at least one large control valve of suitably large flow capacity cooperating with a separate, however, intermittently connected vacuum line comprising further elements of vacuum capable conduits which may be smaller in diameter than the liquid fluid conduits, control valves or slow-acting shut-off valves and a multi-stage disc vacuum-compressor capable of operation with heterogeneous fluids, as may be provided by a multi-stage Tesla-type disc device. Said arrangement depicted in Figures Ic and Id provide largely the continuous conveyance of liquid fluids similarly provided access to the open, submerged ends of preferably larger diameter liquid fluid conduits commencing at lower elevation in either open-to-atmosphere liquid fluid reservoirs, or alternately from another pressurized source, (with other provisions) required (to be discussed in respect to Figures Ie and If). With said liquid fluids induced thus to enter and migrate there-through the conduit beginning at lower elevation (under atmospheric or other suitable pressure) and being further referenced to a lower pressure at an upper elevation (as expressed via the application of vacuum-like pressure above the liquid fluid surface at the upper elevation) the significant atmospheric (or other suitable) pressure may be enabled to provide a large enough differential pressure there-across the upper versus lower elevation gaseous/liquid fluid interfaces (utilizing the intervening liquid fluid to be conveyed as a largely incompressible, elastic, and motive pressure transmitting medium) so that when the head pressure (and extendedly, the force) represented by the height of the liquid fluid column within the conduit is exceeded, in accordance with first principles of Newton, in response to the greater pressure and force at the lower elevation, the liquid fluids may then be caused to move through said conduit to the upper elevation wherefrom a fall into a large capacity reservoir may contain the liquid fluid for a period of time either under or in the absence of significant pressure. And in this manner, one or more simple, effective vacuum pumps may induce the atmospheric medium to do great work to cause liquid fluids to be continuously pushed and pulled to higher elevations via the design and construction of systems incorporating two or more similar or identical vacuum-compatible conduits and associated elements which while working to exhaust comparatively weightless and low viscosity finite amounts of air and vapour, may do away with the need for devices expending much more energy to work in and move greatly heavier and sometimes hundred-fold more viscous liquid fluids such as water.

[0049] Whereas avoidance of liquid fluids entering the vacuum line is normally advisable, and should be addressed accordingly, Tesla-type turbines and compressors are not significantly adversely affected by condensation during fluids pumping, since in operation there is virtually no impingement upon the surfaces of the rotor occurs, however, drainage ports in the bottom of turbine housings are advisable, and are contemplated herein to account for condensate build-up implicating great fluid drag on the normally 'unloaded' runner should a liquid level be high enough within the turbine casing to touch the moving disc turbine runner(s), and either discrete or analog level control means are also contemplated to prevent liquid fluids entering the 'vacuum line' in operation to further prevent such parasitic loading and system efficiency losses.

[0050] With reference now to Figure Ia, with valves in the figure series understood to be schematically illustrated and flow arrows showing the path of fluids transiting particular conduits of concern, an embodiment 1 of the method offering the capacity to raise liquid fluids to the elevation of a transfer tank elevation with a minimum of energy expenditure is presented, wherein a liquid fluid conduit 2 arriving from a source such as a water treatment plant passes through check valve 33 largely preventing its backflow therein said conduit. As shown, flow 3 through a vertical lift-leg height passes thereinto transfer tank 4 whereto vacuum or other substantially low pressure is applied thereto via vacuum compatible valve means 5 (and meanwhile atmospheric pressure valve 6 is closed), whereby a differential pressure there-across check- valve 33 causes the check valve to remain open, and with sufficient pressure differential existing as expressed by combinations of atmospheric or other pressure existing on the surface of the liquid conducted through conduit 2 (at its remote end not shown in the figure) and head pressure (if below the level of the source pressure), and the comparative sub- atmospheric pressure in capacity 4, liquid fluids may flow quickly or slowly there-into capacity 4 accordantly to develop liquid level 36. During this time period, check valve 33 at the elevation of the bottom of capacity 4 remains closed, since atmospheric pressure applied through valve 26 thereto upper capacity tank 23 (supported upon stand 22) and passing through port 25 to act upon the liquid surface within conduit 21 in combination with the head pressure in vertical leg 21 significantly oppose the vacuum pressure in capacity 4, thereby keeping said tank-4 adjacent check valve closed during said vacuum-pressurization fill operation. As shown, vacuum valve 36 communicating said vacuum pressure (or other low pressure, hereinafter simply referred to as vacuum) via conduit 7 by way of conduction of flow 8 communicating the gaseous fluid contents of capacity 4 to a VCM comprising a driving means 9 to drive the shaft 10 of a multi- stage vacuum-compressor advantageously provided by the disc device shown wherethrough larger disc spacing providing a large volume impetus for gaseous fluids to enter said multi-stage fluid pump are succeeded by successive stages of centrifugal acceleration at the end of which accelerating sequence, the vapour and air contents expelled at high velocity from rotating disc runner 11 of comparatively tight disc spacing in the direction indicated 12 may then pass through conduit 13 as a compressed discharge flow which by design of conduit 14 tangentially approaches turbine 15 within an enclosed casing to derive rotation 16 of a secondary shaft en route to being expelled to atmosphere as flow-stream 17. Since rotation may be developed upon said secondary shaft via the shear stress, shear force, and torque communicated thereto it by the compressed fluid in accordance with known operational characteristics of disc turbines, a portion of the power required to operate the VCM used to induce gaseous fluids to push liquid fluids to elevation may thereby be recovered concurrently as by generator 18.

[0051] As shown at the upper elevation in the figure, vacuum valve 27 is meanwhile closed, and with atmospheric pressure valve 26 open concurrently with capacity valve 31 being open, the contents of vacuum compatible upper transfer tank 23 may simply fall through valve 31 and thence through port 30 into the main portion of the distribution tower. Always acted upon in this example by atmospheric pressure applied by way of vent 32, liquid fluids are able to falls through stand-pipe 34 as flow 35 to supply demand there-for as normal. Note that a further atmospheric valve 6 may communicate with the vacuum pump should rapid vacuum relief be required or for other reasons such as maintenance, whereas otherwise housing 19 completely isolates said VCM largely comprising multi-stage compressor 11 from the atmospheric pressure and is therefore very strong and comprised, for example, of thick-walled stainless steel pipe with flanged connection ports where required. Note that based upon the premise that this method provides a means to greatly minimize the energy requirement to move liquid fluids to elevation, and said series of figures respects this goal by assuming that only a minimal head pressure plus atmospheric pressure acts on the system at inlet conduit 2 and its check valve, depending upon particular integrations of this method, a shut-off or control valve may well require installation in conduit 2 in place of or alongside check valve 33 to isolate the energy-minimizing segments of the overall distribution system where required, with logic accounting for said integration not being addressed herein for brevity. [0052] Referring now to largely identical Figure Ib, When liquid level 36 of capacity 4 is largely filled (as at the end of the transfer tank filling operation depicted in Figure Ia), vacuum valve 5 closure may then be effected on either scheduled basis, or desirously in response to a level control feedback circuit comprising either discrete or analog level monitoring instrumentation information provided to a PLC via pneumatic, electric or electronic signal means with said PLC frequently analyzing said information and further issuing a control signal to said valve means 5 to effect said valve's closure (with similar valve operations to be more briefly described, however, considered to pass through a similar information loop through to valve actuations for sake of brevity). With the closure of valve 5, whether on cue or via PLC time based algorithm atmospheric valve 26 is also closed, which isolates vacuum in capacity 4, and atmospheric pressure in upper transfer tank 23 when capacity valve 31 is similarly closed. With the goal being to raise the liquid fluid from the lower transfer tank to the upper transfer tank 23, vacuum valve 27 at the upper elevation is open, which then allows communication of the gaseous contents of upper capacity 23 into vacuum line 7 wherefrom the VCM within vacuum-tight shell 19 works to first reduce the pressure within said capacity 23, and then to fully evacuate same. Largely concurrently with the opening of vacuum valve 27, atmospheric valve 6 of capacity 4 may be opened to allow the previously largely evacuated capacity to breathe, and then normalize to the atmospheric pressure, after which time significant pressure differential develops which may at a particular time exceed the combination of head pressure in conduit 21 and pressure remnant in capacity 23, at which time flow 20 in the upward direction may then result.

[0053] Note that during the period of the upper capacity 23 filling operation, with capacity valve 31 being closed, atmospheric continues to act upon the surface thereof the liquid in the standpipe contents as per typical water distribution practice. Also, with atmospheric pressure acting upon interface surface 36 making a seal thereabout as it distributes pressure largely equally there-across to develop flow 20 through conduit 21 to the upper elevation, liquid level 36 decreases, availed by the closure of capacity valve 31, upper capacity 23 's liquid level rises as liquid falls there-into said capacity 23. At low level in capacity 4, valve 6 of controlled to close by control means disclosed largely concurrently with the closure of vacuum vale 27 at the upper elevation removes the upwardly positive pressure differential causing said upward flow, at which time check valve 33 adjacent capacity 4 shall close isolating the liquid fluid in lift- leg 21. Meanwhile, with atmospheric pressure acting there-across capacity 4's liquid level surface 36 and by extension also acting upon the surface of the liquid fluid column in conduit 2, in further combination with the liquid fluid column providing a head pressure which head pressure may largely be designed to approach yet be advantageously less than atmospheric pressure significant back-pressure expressed thereby upon check valve 33 of conduit 2 may keep it closed during the filling of the next-upper elevation capacity.

[0054] With reference now to Figure Ic, taking the premise of Figures Ia and Ib further, the figure illustrates how the pumping of fluids via the method presently disclosed may substantially continuously move liquid fluids to elevation via the arraying of groups of liquid fluid capacities, and liquid and gaseous fluid conduits and valves in stages. The primary components being reiterated and therefore known from the previous parts of Figure 1, a sequence of operation may now become evident which when developed may allow liquid fluids to be filled at a given elevation concurrently with their discharge to higher elevation there-from the same elevation, which, while happening from separate points, may nevertheless be multiplexed via conduits where possible into an amenable system which may cost more in raw materials to construct, however, with the anticipated long-term power and cost savings as well as carbon footprint reduction and beneficial effect from all of the above elements when multiplied by the global effect thereof, the disclosed elements properly learned, assembled and maintained may provide a valid path forward in many industries to lower energy consumption there-for, and wherein largely constant 'up-hill' flow may be availed by combinations and duplicity of elements where required so as to provide the capacity to utilize common liquid fluid lift- leg conduits and common vacuum (low pressure) conduits, and where possible avail the common employment of larger valves so as to reduce costs via the further employment of headers and or simply increasing diameters of conduit (for example, in the case of multiple vacuum conduits being joined to the same conduit bound for induction points and or the VCM of the system).

[0055] In the figure, first lowest conduit 45 is shown to bring flow 46 from a lower elevation source such as a terrestrial lake or reservoir in a water treatment plant, or which may be from another source elsewhere, such as a liquid ethane lake on the surface of Titan, or even from a deeper source such as from the liquid water ocean thought to exist there-beneath Titan's surface as conducted through a heated network comprising said groupings of capacities and or conduits and valves extending to warmer depths, with said heating energy being provided by means further disclosed in reference to Figure 2 on a large scale, or which may for a time be provided by the high-wind mountain-top wind-turbine illustrated in cross-section in the figure. Whichever being the case, lift-leg heights considered largely from the bottom of a lower elevation capacity to the top of a higher elevation capacity are provided, with said lift-leg heights being limited in magnitude to serviceably less than the distance related to: ((Atmospheric Pressure - (Fluid's Vapour Pressure + Check Valve Cracking Pressure Rating + Conduit Frictional Pressure Loss))/(Liquid Fluid Density x Gravitational Acceleration) at given elevation lift-legs under consideration so as to enable a satisfactory 'uphill' flow-rate. Notably, Figure 9d illustrating the terrestrial atmospheric pressure profile with elevation shows that due to the significant gravitationally abetted pressure rise with depth, the presently disclosed method may become significantly more efficient at depth, instead of being more energy-consumptive as compared to typical present day practice (recently comparatively described by a water treatment plant operator to be "like pushing water uphill with a pointy stick").

[0056] Meeting a junction in the conduit, the flow is diverted to the right, since with capacity 39' s atmospheric valve 6 being closed the vacuum pressure applied therethrough open vacuum valve 5 of said capacity 39 may largely evacuate the air and continuously evacuate fluid vapour there-from said capacity 39 into said vacuum line 7 as extended flow 8 inexorably bound for the capable VCM removed there-from. Whereas one might assume that with the air removed from such an enclosed system that the water vapour may replace it, and while volumetrically true, the equilibrium vapour pressure curve of water, for example, shows that the pressure attempting to be re-created above the liquid fluid surface of such an evacuated fluid is but a fraction of the atmospheric pressure, for example, at a temperature of 10 C water will attempt to provide 1.23kPa wherefore it may be readily surmised that provided the height of first lift- leg 45 is not greater than ((Atmospheric Pressure - (Fluid's Vapour Pressure + Check Valve Cracking Pressure Rating + Conduit Frictional Pressure Loss))/(Liquid Fluid Density x Gravitational Acceleration), that flow there-into and there-through said first lift-leg 45 and upward to the evacuated capacity 39 may be initiated and continue until either: the favourable head in the lower elevation capacity (ie: lake or constantly filled reservoir, not shown) becomes too low to support continued 'uphill discharge', or until such time as the PLC (hereinafter assumed to be controlling each of the plurality of level filling operations of the desirously extensive system) should close vacuum valve 5, and with said vacuum valve 5 closed, the flow there-into capacity 39 may stop largely immediately in response to the reduction of differential pressure with which to sustain said flow, or the flow may stop in sync with the closure of the check valve in extended conduit 37 which may also abruptly close due to the reversal in net pressure differential applied there-across the conduits and respective capacities at largely opposite ends of the single-lift segment under consideration, wherein the head pressure may rapidly become the dominant pressure (ie: force acting downwardly) thereby closing said check valve and halting said filling operation of capacity 39. Notably, the liquid level 40 of capacity 39 during this time period rises due to the ingress of liquid fluid as flow 38, through conduit 37, however, owing to the system design no disadvantageous head is applied to the lift-leg conducting liquid fluid from the elevation below since the liquid fluids simply fall into an open void with no means of 'spillage' there-from.

[0057] Meanwhile, during the fill operation of capacity 39, check valve 33 below capacity 39 remains closed since firstly, the vacuum pressure in said capacity acts to close the valve, and also since as shown, a high pressure exists in the common discharge line communicating therewith the discharge side of both discharge check valves such that said higher pressure also acts to close the discharge check valve 33 of capacity 39' s discharge conduit to isolate the filling operation and help seal there-in the application of vacuum. Also concurrent during said fill operation, the atmospheric pressure applied therein capacity 41 (to be discussed) acts to close fill check valve 33 there-adjacent capacity 41 in (its) fill conduit 44 so as to contain the high (atmospheric) pressure for application as shown, in the lift of capacity 41' s liquid fluid contents to the next higher elevation. Note that for simplicity sake capacity 41' s fill check valve 33 is drawn in the figure as a vertically oriented, which may operate for a time satisfactorily, however, with accumulation of particulates or even debris over time being not uncommon in operation of large piping networks, it may well be anticipated that such fouling may eventually degrade the system efficiency by not only allowing pressurized atmospheric air to migrate through 'failing' check valves and subsequently act to reduce the beneficial vacuum applied to the opposite capacity (ie: during filling operations) due to the influx of said moderated pressure air in the desirously evacuated region, but it may thereby also extendedly affect the efficiency of the whole system due to loading common vacuum lines with added base pressure at a rate which may be faster than the design capacity of the system VCM may accommodatingly remove effectively. Therefore orientation, location, and especially scheduled maintenance cleanings of said check valves need be considered in such systems, and isolation valves on both sides of all check valves in the system are therefore recommended (however not shown) to avail ready access for said regular maintenance cleanings.

[0058] Concurrent with the filling of capacity 39, capacity 41 is shown to be accompanied by closure of vacuum valve 5 preventing connection to the vacuum line, and an open atmospheric valve 6 such that atmospheric pressure is applied therein said capacity, which, while largely forcing fill check valve 33 in capacity 41' s fill conduit 44 closed, in applying said atmospheric pressure fully there-across liquid fluid surface 42, a great combined force is there-applied-to said liquid fluid interface which may readily exceed the designed lift-leg head pressure in second conduit 45 leading upward to the second evacuation-compression pumping elevation of the figure, whereat the left-most capacity 41 is shown to be filling with its vacuum valve 5 in the open state, and its atmospheric reference valve closed. Whereby liquid fluid flows there-into without recourse but to fall thereinto and remain until its valve positions are reversed, and flow is permitted at yet a further upper elevation by a cooperating set of valve states.

[0059] As will be apparent from a cursory or detailed analysis of the figure, liquid fluids may herein be enabled to be received in one capacity at elevation A concurrently with their alternate discharge from another capacity at elevation A to higher elevation B, and so on, so as to permit the sustained flow of liquid fluids via said low energy consumption requirement method to elevation, with two check valves per capacity and with inlet check valves opening toward destination capacities and discharge check valves opening away from the supply capacity, as may be anticipated.

[0060] At upper right in the figure a large diameter disc turbine operates as a wind turbine (ie: at elevation and location where high winds may be typical such as through a mountain pass) whereat approaching ambient winds 54 forced to circumnavigate large mountain features may cooperate to generate flow conservation enhanced fluid current 55 velocity substantially seeking the path of least resistance to the other side of the mountain, and in combination with further ambient wind approach and a conducive mountain profile, a resultant EVFES 56 may be driven while largely drawn toward and over volute directional lip 66 by the viscous drag applied thereto it by the rotating turbine runners' production of low pressure in the region of its perimeter by a combination of factors not the least of which being the expression of desirously low pressure by the fluid extraction device upon turbine discharge ports 69 and the rapid rotor velocity arcing away there-from on a divergent course en route passing inner surface 57 of volute collector 58 adding further mass-flow to the turbine feed- stream, being supported by pivoting volute support arms 59 fixing said volute collector 58 to ground support features 64 of turbine 61 rotating as indicated 62 to turn shaft 63 as by shear-stress, shear-force and torque applied thereto by the vorticing EVFES fluid current entering the wide open inlet sector of the disc turbine runner disposed windwardly owing the pivoting action of the volute collector having spring or otherwise-returning guides 60 causing said volute collector 58 to largely self align in bi-directional wind vectors. With ground support features 64 as well as the ground-contacting girth of partial-housing 67 being fixedly attached to bedrock 65 and with shaft 63 freely turning in bearing means further fixedly mounted to said ground support features 64, and with venturi induction slots at either end of every disc turbine runner (not shown) being so positioned so as to provide a dynamic vortex flow system which may be further controllable under any flow condition via active disc spacing means already discussed which while setting the axial distance of separation between adjacent disc members to provide more or less separation, may thereby also effect a greater or lesser degree of free-vorticing, more or less shear-stress and shear-force, and thereby also effect control of the torque applied to shaft 63.

[0061] The run-time generation of electric and or hydraulic compression energy implied herein to be capably produced via coaxial multi-stage compression of a suitable hydraulic fluid at run-time and provided to a disc-turbine hydraulic in order to turn the VCM of the invention in real-time, or which hydraulic energy production from wind or other locally available renewable energy source may rather be stored as in a high- pressure compatible storage means near the point of use wherefrom the run-time working fluid energy requirement of said hydraulic motor to power the vacuum pumping method may be withdrawn at run-time as through a pressure regulator set to provide adequate fluid throughput under pressure to said disc-turbine hydraulic motor attached to the shaft of said VCM to develop the required rotation thereof shaft 10 of said VCM, where- after being expelled from the turbine, remnant energy left in the working fluid may be used to carry said fluid through a suitable diameter conduit to elevation where it may be pooled to provide flooded priming of the hydraulic compression components of the system for the compression work to immediately resume upon the return of suitable velocity winds. Alternately, as shown in the figure, electrical energy derived at runtime via permanent magnet generation means (not shown) and or stored in another form which may include the raising of further water or other liquid fluids to elevation (via the presently disclosed VCM for anticipated maximum benefit there-from said energy expenditure) for storage and subsequent release as through a suitable elevation drop unto a turbine for deferred generation of such power requirement (and which may, for example, utilize the method for power generation disclosed in respect to Figure 2 with sustained power generation being one of possibly many benefits afforded thereby the addition of the required elements there-for said alternate power generation lift-chain comprising multi-tiered lift-legs to elevation such as those described herein respect to Figure 1). Alternately, power-conditioned ultra-capacitor banks may be utilized to receive the large anticipated charges and electrical currents developed by such large disc-turbines at runtime in significant winds, and with substantial arrays of such disc turbine vortex energy conversion embodiments at elevation, significant power generation in conjunction with said power conditioning elements (not shown) as well as devices to be later disclosed in reference to Figure 2 may offer a very low net power consumption to effect pumping of liquids to elevation.

[0062] With reference now to Figure Id, the same figure from Figure Ic is presented, which for sake of brevity shall not be described in detail with the respective sequencing now established, save mentioning that the figure generically presents reversed flow conditions compared to Figure Ic so as to show the alternate capacities being filled at respective elevations, while the co-alternate capacities thereat the same elevation previously filling, are herein provided appropriate valve states so as to effect liquid fluid transfer to a next elevation capacity and continue to endow the system of largely continuous liquid fluids being raised to elevation, even as some capacity rather pools thereat said elevation in preparation for a subsequent valve-cycling to effect their discharge to elevation.

[0063] Notable in the figure is the reversal of prevailing wind 54 applied to the Tesla- type wind turbine embodiment, with volute collector 58 assuming an opposite directional sense as guided thereto by guiding appendage 60 or another appendage catching the wind (not shown) to thereby provide collection of the EVFES approaching from said opposite sense and thereby develop torque-producing turbine rotation 62 of reversed direction concurrently with renewable power generation. Pertinent, however not illustrated, it may be stated that the presently disclosed system also permits the filling or discharging of both capacities at the same elevation simultaneously (ie: both in a state of filling or the converse), which although in a conservatively specified system such as the one illustrated is not anticipated to increase the volumetric flow-rate to elevation significantly due to the bottlenecking effect of commonly utilized lift-legs for economic reasons, said duality of functionality at given horizons may nevertheless be a useful service capability to equalize or sync the respective lift-legs to the schedule or cycle as appropriate (such as may be desirous following planned or unplanned maintenance)

[0064] With reference now to Figure Ie, a similar system is illustrated so as to expound upon the method of vacuum-compression pumping of liquids to elevation to include the employment of higher than ambient system-generated high reference pressures with which to load the liquid fluid surfaces of capacities to further enable greater height lift-legs to be utilized as may be required under various special circumstances which may permit the method to be utilized for example on other celestial bodies having lesser atmospheric pressures, greater gravitational acceleration constants, or where otherwise greater density liquid fluids are to be moved to elevation by the method.

[0065] In the figure, the vacuum-compression system instead of exhausting through a multi-stage disc power generation turbine to a 'free' exhaust in the atmospheric medium (as in Figures Ia to Id), Figure Ie rather illustrates a single stage work generation turbine harvesting the kinetic energy of motion imparted to the centrifugally accelerated working fluid (pressurized gaseous control fluid) and may thereby be stated to employ the disc turbine along with its housing and containment thereof in capacity as a dynamic to static pressure recovery unit there-within the enclosed system high pressure reservoir, or which may alternately be mounted externally to said high pressure containment with bypass valve means to put it in service or remove it there-from the path of fluids subsequently utilized for the gaseous pressurization control fluid of the system in place of atmospheric pressure. Depending upon the pressure achieved by the VCM (as delivered to the high pressure reservoir) the system illustrated may be adequately sized for the small total lift depicted, however, larger systems, greater lift-leg heights, greater gravitational acceleration constants and greater liquid fluid densities thereof to be conveyed to elevation may necessitate higher pressure containment, larger volume thereof the high pressure containment, or a combination of both.

[0066] With common elements and their function described previously, unique features of the figure-pair Ie and If shall now be discussed. Pressure regulator 1997 installed between the high pressure reservoir and the point of use high pressure control valve 1996 may help system capacity tanks experience less pressure-induced shock, when once full of liquid fluids and largely at a vacuum or vacuum-like pressure, they are subsequently isolated from said vacuum via closure of vacuum valve 5 (ie: of capacity 4 in the figure) and may then be thereafter opened unto the high pressure communicated from said high pressure reservoir, whereupon a rapid or even high velocity influx of gaseous pressurization control fluid may take place, thereby possibly rapidly pressure cycling said capacity. Notwithstanding this possibility, said pressure regulator 1997 which may reduce said shock potential may not be required since if the capacity tanks or other reservoirs are not completely full when the gaseous pressurization control fluid valve is opened, then the volume of unfilled capacity alone may buffer the effects of said possible rapid ingress of gaseous control pressure fluid via dispersion of same causing an initial degree of depressurization thereof said control fluid upon entry there-into the capacity, and via instrumentation and control, said degree of 'unfilled capacity' may be automated to a desired level so as to achieve a buffered gaseous control pressure entry profile with time. Also, the use of said pressure regulation means may slow the time constant of the capacity discharge cycles (forcing the liquid fluids to higher elevation) depending upon the Cv of said regulating means. As illustrated, in such a system configuration, the gaseous pressurized control fluid may largely be a fixed volume, except where a final requirement is to provide an atmospherically pressurized liquid fluid, in which case cycling of vacuum pressure valve 27 would bring atmospherically pressurized gaseous fluids into the system in addition to the fixed system volume. This eventuality is accounted for in Figure Ie and If via the inclusion of a further isolation valve 1999 which when opened, provides a path for the high pressure reservoir to communicate as through pressure regulator 1998, with the atmospheric pressure, whereby and where-through said pressure regulator 1998 may provide the function of relieving said added (gaseous atmospheric) fluid ingress from the total system volume intermittently. Although intermittent, depending upon the location and requirement for absolute conservation, and pressure differential between said atmospheric pressure and the high pressure of the system, it may be advantageous to install an end-of-line turbine to extract energy from said discharges. Thus in larger systems as may be surmised, a substantially fixed system capacity may be largely maintained in a constant state of flux between liquid fluid capacity tanks in states of fill and discharge, gaseous control pressure conduits, the system VCM, and the high pressure reservoir, thereby largely directly transferring the gaseous control pressure fluid capacity as required, without adding extra load upon the system VCM to minimize the work required to move the greatly more heavy and viscous liquid fluids to elevation.

[0067] With reference now to Figure If, with atmospheric valve 26 closed, capacity valve 31 closed, and vacuum valve 27 of upper capacity 23 open, said capacity 23 is thereby subject to the vacuum pressure extended there-from the intake of the system VCM, and so gaseous pressurization control fluid is thereby withdrawn there-through vacuum line 7 as depressurizing flow 8 communicated to the axial receiving intake of the VCM subsequently re-compressing the same media via multi-stages of coaxial compression resulting in its communicating an elevated pressure gaseous fluid product 13 through interconnecting conduit 14 to the single stage work generating turbine as discussed acting as a dynamic to static pressure (and power) recovery device ultimately communicating said higher pressure gaseous fluid to the high pressure reservoir of the system. Meanwhile, with vacuum valve 5 and control pressurization valve 1996 of capacity 4 open, capacity 4 is subject to the high pressure extended there-from the high pressure reservoir, which as long as said high system reference pressure exceeds may be largely any pressure above that defined by the limiting relation ((System High Reference Pressure - (Fluid's Vapour Pressure + Check Valve Cracking Pressure Rating + Conduit Frictional Pressure Loss))/(Liquid Fluid Density x Gravitational Acceleration) required to exceed the significantly high

[0068] In all embodiments of the basically illustrated system shown, a gaseous fluid check valve suited to application with the given liquid working fluid's vapour as well as to the atmospheric gases thereat may advantageously be installed in the system so as to provide isolation of a preferably large volume vacuum conduit or capacity further separated from the intake of the system VCM by yet another similarly suited gaseous fluid check valve (both being readily capable of preventing backflow as well as of passing the rated system throughput) so that when the VCM is shut-down for maintenance or another reason, the work done to achieve the respective unique system pressures thereby provided, may be conserved.

[0069] Referring next to Figure Ig, an embodiment of the gaseous-liquid fluidic lift system is presented which while similar to the earlier embodiments of Figure 1 in principle, in contrast rather provides larger volume pressure-compatible conduit and reservoir means (said reservoir means comprising extended length horizontally lain pressure and vacuum compatible pipes of preferably large diameter) permitting more rapid liquid fluid communications there-through for faster service by the invention, provides a distinctive piping strategy as well as an arrangement for mounting disc VCM (VCM) 2000 within said high volume conduit means, provides greater detail pertaining to pressure energy recovery turbine 200(s) work extraction means proposed for recovery of a substantial portion of the energy expended to run VCM 2000(s) (and therefore recover a significant portion of the energy expended to run the system), and also illustrates a multi-tiered fluidic lift system approach wherein arrayed iterations of VCM 2000(s) cooperate to effect dedicated and more rapidly achieved compression and evacuation of respective elevation pressurization reservoirs 330.

[0070] In contrast to earlier embodiments of the gaseous-liquid fluidic lift system(s), the presently disclosed embodiment requires no communication with the atmospheric pressure, and as implied, both high pressures as well as vacuum and or low pressures of operation may be utilized in practice, thereby offering the potential for a very widely configurable apparatus. Further, the present embodiment contemplates the use of significant pressures up to or exceeding those utilized by the prior art in liquid fluids pumping (provided appropriately rated conduits therefore) to enable the height of respective lift legs to be great if desired, or alternately so that a more rapid fluidic lift system may be provided in operation owing the pressure differential utilized. For example, a given system pressure differential (expressed so as to represent a given height of liquid fluid head) applied to liquid fluid lift-legs designed to represent significantly less head pressure than the system pressure differential offered, thereby offering a significant surplus of differential pressure may develop a greater velocity of liquid fluid flow to higher elevation through said larger diameter piping providing less head loss than systems offering a smaller differential pressure and smaller conduit means therefore, and with fewer 'lift-elevation stations' being required as availed through the employment of said higher differential pressures of operation, the cost of such systems may also be more immediately economically feasible.

[0071] Multiple lift-stages are depicted in the figure to illustrate the intended reversals of liquid fluid reservoir-occupation from one elevation to the next which may balance the weight load implicated by larger systems wherein an extensive mass of liquid fluid such as water is to be desirously lifted, with said largely equalized weight distribution being of concern in the operation of such systems whereby successful management of said weight distribution may permit a wider variety of ground conditions and or structures of differing integrity to support proposed applications of the technology with minimized risk of ground and or structural failure. The system illustrated permits said liquid fluid position-reversals through arrangement of its vacuum/low pressure gaseous pressurization control conduit means 1984 and bifurcated extensions thereof (both of larger size than indicated in previous embodiments of Figure 1) so as to provide shorter overall conduit runs thereby offering comparatively freer communication path(s) for gaseous pressurization control fluid 1978 to pass from presently liquid fluid receiving pressurization reservoir(s) 330 to and through vacuum/low pressure isolation valve(s) 1986 as vacuum/low pressure gaseous extraction fluid flow 1985 to the axial intake(s) of respective elevation VCM 2000(s) effecting the required gaseous pressurization control fluid evacuation(s) there-from said liquid fluid receiving reservoir(s) 330 at run-time. VCM 2000(s) driven as in previous embodiments via electrical motor mean(s) are disposed, as illustrated, between vacuum/low pressure gaseous fluid 'extraction' conduit means 1984 and high pressure gaseous fluid 'filling' conduit means 1994(s) permitting communication of VCM 2000(s)' pressure amplified final-stage tangential discharge flow 1995 to and through high pressure isolation valve(s) 1996 and thence into presently sourcing liquid fluid reservoir(s). En-route to the population of said presently liquid fluid sourcing reservoir 330, said VCM 2000(s)' pressure amplified discharge flow 1995 is caused by said high pressure piping arrangement there-for to supply the tangential admission working fluid flow of a work extracting pressure energy recovery turbine 200 which may be located within or alternately outside of said liquid fluid pressurization reservoirs 330 so long as said turbine's discharge outlet is thereafter communicated as by further pressure compatible conduit means there-into said presently liquid fluid sourcing reservoir 330 to load same with said pressure amplified gaseous pressurization control fluid. [0072] Said work extraction (pressure energy recovery) turbine 200(s) may be provided by various embodiments of the presently described invention in a single turbine at respective lift-elevations either directly or at length receiving said pressure amplified tangential gaseous discharge as working fluid input and thereafter directing its axial discharge flow 1995 as by gaseous high pressure fluid valve 1996(s) and conduit means 1994 there-for arranged so as to then communicate said discharge flow 1995 into said presently liquid fluid sourcing pressurization reservoir(s) 330, or as illustrated in the figure, a bifurcated high pressure discharge conduit means 1994 may be provided with dedicated high pressure gaseous isolation valve(s) 1996 commanded to open by PLC or other controller means (to load said pressure-amplified tangential feed flow 1995 into the desired pressurization reservoir 330), whereupon said gaseous pressurization control fluid 1978 thus communicated through valve(s) 1996 may be provided to one or more reservoir-dedicated pressure energy recovery work extraction disc turbine 200(s). Said work extraction disc turbine 200(s) are contemplated to be capable of being driven at high angular velocity during at least a significant portion of said gaseous pressurization control fluid loading into said presently liquid fluid sourcing pressurization reservoir 330, and as such, may be utilized to provide shaft work thereby which may for example drive a co-rotating disc compression means at equal angular velocity to provide a degree of gaseous pressurization control fluid pre-compression, or may alternately (as contemplated by the figure) provide significant rotation of permanent magnet means embedded in the outer surfaces of both thick end discs of said disc turbine 200(s), said permanent magnet means thus rotating at significant angular velocity adjacent the open ends of stator cores mounted upon said work extraction turbine's housing normal thereto the plane of said turbine's rotation wherein toroidally arranged windings filling the annular region defined by the circular array of said cores arranged so as to position said opens ends at common radii with said permanent magnets, said cores having largely equivalent widths and arc lengths as permanent magnets means discussed, said cores separated by arc-lengths (of space) matching the arc lengths of said permanent magnet means so that said permanent magnet means arranged adjacent each other at given radii are mounted from one to the next in opposing polarity, said permanent magnet means thereby causing the rapid near- saturation of said cores with common flux vectors so that while the polarity of flux passing into cores to develop electrical potential in said windings changes, said alternating polarity of said flux passing sequentially across said cores (relating to a changing vector of induced electromotive force in individually considered windings) may thereby induce a regularly alternating voltage potential within each winding, and provided sufficiently large gauge conductor and number of turns thereof within in each of said windings, said electrical potential developing thereby may supply a proportionate electrical current flow when provided to rectification and power conditioning means (not shown) which may provide a significant energy recuperation which may be further connected to a storage means and or load.

[0073] As indicated in the figure, said work extraction turbine(s) 200 are supported by freely turning bearing means supported in rigid pipe section means further supported by and within a rigid housing means which may comprise the conduit means itself. Notably, except for the requirement of such a pressure recovery turbine to have said cores and windings mounted normal and in close proximity to the faces thereof said disc turbine(s) end disc(s) such a work extraction unit may not require a traditional full housing, but mat rather simply provide a case ring of involute or circular cross-section permitting gaseous high pressure working fluid provided tangentially thereto to only enter said disc turbine at its perimeter, with discharge being availed through axial egress provided by said disc turbine(s)' discharge(s) into the presently sourcing pressurization reservoir 330.

[0074] The opening and closing of vacuum/low pressure isolation valve(s) 1986 as well as high pressure isolation valve(s) 1996 to cause appropriate fluidic communications in the presently discussed embodiment are contemplated to be made by a data-aware PLC or other controller means in response to a system control algorithm based upon combined level information provided by level switch(es) LSH 1933 and LSL 1934 at the respective lift-elevations, and or via independent analog level transmitter means(s) 1930 feedback alternately in conjunction with feedback from pressure transmitter(s) 1989 information communicated from pressurization reservoirs 330 of the system.. Alternately, said actuation may be effected on a time-based schedule (when qualified by feedback from said level and pressure transmitters indicating that no significant pressure or liquid fluid losses have occurred from the system, which may adequately indicate that the system is intact and therefore that the schedule may continue to be followed until such time as, for example, one or more of the low pressure switches LSL may remain tripped during normal system operation, or a low pressure exists where a high pressure should, or other conditional system interlocks). [0075] A narrative of system operation commences with the system as shown in the figure ie: in process of largely vertical liquid fluid transfer operations through open liquid fluid check valve(s) 290, said transfer being caused by the differential pressure expressed there-across largely contiguous lift-leg column(s) maintained between respectively considered lower and upper lift-elevation(s)' isolated liquid fluid surface(s), said liquid fluid surfaces alternately communicating with higher pressure gaseous pressurization control fluid (applied to lower elevation liquid fluid surfaces) and vacuum/low pressures (concurrently and concomitantly applied to upper elevation liquid fluid surfaces), said high and vacuum/low gaseous pressurization control fluid pressures being substantially trapped there-within said pressurization reservoir(s) 330 owing the favourably large density difference between the gaseous pressurization control fluid and liquid fluid being transferred to elevation, said density (weight) difference ensuring that gaseous pressurization control fluid ever-occupies the top region of said pressurization reservoir(s) 330 (ie: region of said reservoirs opposite the local gravitational acceleration vector) and liquid fluid occupying the same pressurization reservoir 330 ever-occupies the bottom region of said pressurization reservoir(s) 330 (ie: region of said reservoirs closest the source of the local gravitational acceleration) whereat an inversion 1947 in the liquid fluid piping circuit permits only the liquid fluid in successfully designed and controlled gaseous-liquid fluidic lift systems to access said horizontally lain capacities 330 under the contemplated pressures of operation.

[0076] With the isolated loading of high pressure gaseous pressurization control fluid (denoted PHP in the figure) onto the liquid fluid surfaces at lower elevation (said high pressure being concurrently applied to the isolated liquid fluid surfaces within all such diagonally opposite liquid fluid pressurization reservoirs 330 communicating with the high gaseous outlet pressure provided by upper elevation VCM 2000(s) as indicated in the figure), and meanwhile with pressurization reservoir(s) 330 there-above as well as there- adjacent the aforementioned reservoir(s) 330 being concomitantly drawn to lower pressure provided by VCM 2000(s) adjacent said reservoir(s) at given lift-elevations (lift horizons), a resultant differential pressure is produced across the liquid fluid column(s) extending between respective lift-horizons thereby developing liquid fluid flow from said lower elevations (at higher pressure) to said higher elevation lift-horizon pressurization reservoirs 330 (at vacuum/low pressure) when the magnitude of the pressure differential expressed (ie: when (Lower elevation's higher pressure) - (Upper elevation's lower pressure)) exceeds the observed head between said lower and upper pressurization reservoirs (said head expressed in terms of a density-respective pressure), and further that the observed differential pressure is also greater than the sum of (Check Valve Cracking Pressure Rating + Conduit Frictional Pressure Loss), at which time said flow shall migrate so as to fill said upper elevation pressurization reservoir until such time as the differential pressure condition no longer exceeds the discussed combination of variables.

[0077] Note that although gaseous fluid pressurization and evacuation ports are also provided on top of said pressurization reservoir(s), liquid fluid is not permitted to enter these ports in normal system operation owing its greater density, and a main function of the data-aware PLC or other controller contemplated for service therewith the invention is to cause the cycling of high and vacuum/low gaseous control pressures at an appropriate time prior to said liquid fluid level rising to said height on the one hand, while concurrently preventing the egress of gaseous pressurization control fluid through said lower elevation piping inversion 1947 on the other.

[0078] As gaseous pressurization control fluid is withdrawn from presently liquid fluid receiving pressurization reservoir(s) 330 facilitating their being filled with liquid fluid from below through said piping inversion 1947, and gaseous pressurization control fluid withdrawn there-from said pressurization reservoir(s) 330 is concomitantly compressed and loaded into presently liquid fluid sourcing pressurization reservoir(s) 330 at next- lower lift-horizon(s) so as to force the discharge (flow) of the latter(s)' liquid fluid content first down, then out of said piping inversion(s) 1947 with said flow being prevented from downward migration by liquid fluid column(s) held in-situ by closed check valve(s) 291 there-below, liquid fluid is thus only provided a path upward through the indicated vertical conduit to elevation through which to reach pressure equilibrium with the applied gaseous pressurization control fluid differential pressure across said liquid fluid column(s), which gaseous pressurization control fluid trapped within pressurization reservoir(s) 330 by said conduit inversion(s) 1947 and control strategy is thus enabled to effect the lift of masses of liquid fluids without ever contacting said dense, viscous liquid fluid, and owing the ever-segregated isolation of said gaseous pressurization control fluid there-from said liquid fluid said method of raising liquid fluids to elevation shall never require auxiliary priming means as is typically provided for prior art liquid fluid pumps, thus permitting said gaseous-liquid fluidic lift system to remuneratively utilize largely fixed masses of pressurization control fluid in a closed system so as to effect the lift of said liquid fluid through lift-legs provided by conduit means which may in practice be provided at largely any desired inclination.

[0079] Said respective intra-system pairings of liquid-fluid-transferring pressurization reservoir(s) 330 in due course of approaching the completion of said liquid fluid transfer operations occurring at a point in time dependent upon the (integrated sum of) liquid fluid flow-rate discharged there-from and also dependent upon the volume represented by 'full' and 'empty' levels of pressurization reservoir(s) utilized by the system for control purposes, (diagonally opposite) liquid fluid sourcing pressurization reservoir(s) 330 eventually reaching a maximum gaseous control pressure while concomitantly being substantially emptied of liquid fluid (ie: the liquid fluid level therein may near the physical bottom of said horizontally-lain pressurization reservoir(s) 330, or alternately said liquid fluid level may approach a permissible bottoming level as triggered by either low pressure switch(es) LSL 1934, or as may otherwise be determined by a PLC receiving real-time feedback from level transmitter(s) LIT 1930 and comparing said level to control set-point(s) there-for), with said alternate pressurization reservoir(s) 330 there-opposite the aforementioned reservoir(s) at respective lift-horizon(s) being the concomitantly drawn down to a minimum pressure(s) availed by VCM 2000(s) while concurrently being substantially filled with liquid fluid, shall cause thereby an eventual decline in the achievable outlet pressure of gaseous pressurization control fluid discharged from VCM 2000(s) owing said (compressed) discharge fluid being drawn from a substantially rarefied (gaseous environment) liquid fluid receiving pressurization reservoir(s) 330 of diminishing gaseous pressure which may at thereafter cause check valve(s) 1962 in the high pressure VCM 2000 discharge line 1994 to close, subsequently isolating the presently liquid fluid sourcing pressurization reservoir(s) 330 from further gaseous pressurization fluid loading (note that said isolation may also be provided by a PLC control algorithm when the system provides an operational differential pressure significantly higher than the head-respective pressure difference implicated by the lift- leg height between lift-horizons). Isolated thus from further pressurization control fluid loading, the stagnation of the differential pressure (in lower pressure systems) there- across the liquid fluid column extending to the next upper lift-horizon (or in an alternate control algorithm case, with the cycling of high and vacuum/low pressure valves effecting a rapid decrease in the pressure within said pressurization reservoir(s) 330), the closing of open liquid fluid check valve(s) 290 accompanied by the stoppage of liquid fluid flow to upper elevation lift-horizon(s) shall be caused, which stoppage in flow may be signalled by: the incorporation of one or more position switch(es) mounted on either liquid fluid check valve(s) 290/291 or gaseous fluid check valve(s) 1962; or alternately via flow switch(es) positioned so as to indicate flow in lift-leg conduit(s); or as may otherwise be indicated by the inactivity of liquid fluid levels in the pressurization reservoir(s) 330. Upon detection by said PLC or other controller means of the flow, level and pressure stagnations which may largely concurrently occur (the latter primarily dependent upon the selected operational pressure range), said PLC or controller may then change the state of high pressure isolation valve(s) 1996, and also change the state of vacuum/low pressure isolation valve(s) 1986 to effect the redirection of VCM 2000(s)' evacuation and compression effects into alternate pressurization reservoir(s) 330 which as shown in the figure may thereafter cause liquid fluid to fill previously emptied overlying liquid fluid reservoirs 330, meanwhile cause the emptying of previously filled liquid fluid pressurization reservoir(s) 330.

[0080] The present embodiment of the invention illustrates the employment of disc turbine(s) 200 to provide pressure energy recovery from the very process which may exceed the prior arts' capabilities in liquid fluid 'pumping', wherein requisite transfers of gaseous pressurization control fluid through said turbine(s) 200 into presently or subsequently liquid fluid sourcing pressurization reservoir(s) 330 where-into said gaseous control fluid is driven by design may provide energy extraction which may be the greater (during at least part of said fluid transfer operations) through the addition of pressure as well as velocity energy by and through VCM 2000(s) en-route to said reservoir(s) 330. Notwithstanding VCM 2000(s)' potential service in this regard, it may be stated that at the time of changes of state of low 1986 and high pressure gaseous isolation valve(s) 1996 (ie: at or near the completion of a particular pressurization reservoir's liquid fluid sourcing period caused by said gaseous control fluid's pressurization/ loading of same), that since the energy of compression loading the respective pressurization reservoir(s) 330 remains (pressure energy is not destroyed or lost), that a high differential pressure shall therefore exist between adjacent pressurization reservoir(s) independently of additional energy which VCM 2000(s)' further evacuation and compression potential may avail. Thus it should be recognized that a significant period of pressure equalization may be provided (without additional work performance by VCM 2000s) during each lift-cycle owing said pressure differential discussed, which pressure equalization may be approximated to occur in a time period proportionate to factors including: the varying pressure differential observed; the varying viscosity of the gaseous pressurization control fluid employed; the temperature through which the transfers are effected; with the resistance (R) to the passage of said gaseous fluid flow there-between said pressurization reservoir(s) 330 owing pipe frictional losses of conduit means provided, as well as; the volume of said pressurization reservoir(s) 330 employed and the changing volume of liquid fluid fill there-within said reservoir(s) throughout the transfer period providing (the net capacity C), resulting in an effective R-C time constant of said gaseous fluid transfers. Whereas the invention discussed contemplates large cross-section piping and other foreseeable provisions to desirously decrease the conduction time required to effect said gaseous fluid transfers to increase the speed of service of (all embodiments of) the gaseous-liquid fluidic lift system discussed, it may be stated that said pressure differential and equalization period discussed may be designed to cooperate with the invention to reduce the net energy required to operate such systems.

[0081] In keeping with this goal, provisions may be made so as to accommodate both energy conservation (which may be provided via shutdown of VCM 2000(s) during said pressure equalization periods - made permissible since pressure will equalize between inter-communicating reservoirs naturally without aid of VCM 2000(s), and will do so without liquid fluid loss to lower lift-horizons owing the holding capacity of closed liquid fluid check valve(s) 291), as well as energy extraction as through the provision of (un-illustrated): auxiliary pressure equalization conduit(s) top-mounted on each pressurization reservoir or sharing the low pressure conduit illustrated (with further accommodations for isolation and alternate fluid transfer routing being required in such cases) of preferably large diameter through which to conduct high-volume gaseous fluid flow from pressurization reservoir(s) 330, past; auxiliary work extraction turbine discharge return flow ports, to; isolation valve(s) in said pressure equalization conduit(s), and; further conduits leading there-from said valve(s) unto tangentially arranged rectangular cross section expansion nozzle(s), feeding; one or more auxiliary pressure energy recovery dual exhaust disc turbine(s) 200, having; one or more large volume check valve(s) and preferably large diameter conduit(s) there-between said turbine(s)' axial exhaust outlet(s) and said auxiliary pressure equalization conduit(s) so as to conduct said equalization pressure flow with a minimum of frictional loss to the respective destination pressurization reservoirs), so that as gaseous pressurization control fluid pressure equalizes between cross -communicating pressurization reservoir(s) 330 (which may in due course begin to raise liquid fluid to elevation in said alternate fluidic lift-leg(s) dependent upon the pressure differential availed therein and the height of respective lift-legs to the next higher lift-horizon), said equalization process may thereby permit energy recuperation during each lift cycle while functionally preparing each pressurization reservoir for its next stage of liquid fluid sourcing or receiving, whereupon approaching the end of said pressure equalization phase(s) as may be determined by a PLC or other controller's time based analysis of real-time pressure information provided by pressure transmitter(s) 1989, said respectively opened isolation equalization valve(s) shall be closed to isolate said respective equalization conduit leg(s) and auxiliary turbine(s) 2000 as VCM 2000(s) are re-energized and the appropriate opening of low pressure 1986 and high pressure gaseous pressurization isolation valve(s) 1996 as previously discussed (in the case of illustrated system operation) shall be effected, substantially causing the system to assume a state largely equivalent to that shown in the figure, however, with all respective pressurization control valve states, fluid flow vectors and applied pressures illustrated being rather offset vertically by one lift-horizon (however, with the respectively indicated liquid fluid levels of pressurization reservoir(s) being reached only after a period of time).

[0082] Alternate means of energy recovery (requiring neither the shutdown of VCM 2000(s) nor additional conduits and valves there-for) may be provided with the operation of a tertiary energy recovery disc turbine (not illustrated), located for example between vacuum/low pressure valve(s) 1986 and vacuum/low pressure conduit(s) 1984 or preferably at the convergence of both of said conduit(s) 1984 and VCM 2000(s) intake pipe for at least a portion of the high velocity flow period between reservoir(s) 330 post commencement of the inter-reservoir gaseous fluid transfer event(s). With conduit means 1984 leading directly into tangential inlet(s) to said tertiary disc turbine(s) by design providing the only (allowed) path of egress for fluid flow from pressurization reservoir(s) 330 (since the only other 'open' egress point is through the piping isolation inversion 1947 through which the lighter density pressurization control fluid is barred from exit thereby the gravitational acceleration causing it to remain ever-on-top-of said liquid fluid being transferred to elevation) and disc turbine(s) providing axial egress into VCM 2000(s) axial intake the transfer of gaseous pressurization control fluid from one reservoir to the next may thereby provide greater energy recuperation there-from said regular discharges. The provision of the dynamic disc spacing functionality of the invention in said tertiary energy recovery disc turbine would afford the capability of said turbine to better provide torque control there-through the passage of gaseous pressurization control fluid possessing variable transport properties as previously discussed, not the least of which being the fluid's density largely varying during said fluidic transfer.

[0083] While successful implementation of the system may call for the provision of sufficiently large or effectively large diameter piping (ie: which may be provided by a plurality of smaller diameter, respectively communicating conduits of suitable pressure rating) to minimize the effect of negatively imposing frictional pipe losses on the conduction of liquid fluids to elevation, and restrictions in said liquid fluid conduit(s) beyond those implicated by liquid fluid check valve(s) 290/291 are in general to be avoided, that notwithstanding these considerations the viscosity of the liquid fluid when considered alongside the desirously great volumes thereof intended to be raised to elevation in combination with the great possible ranges of pressure differentials of service which variations of the system may provide (which operational pressure range may require either more or less stages of gaseous fluid compression than illustrated in VCM 2000(s) of the figure to effect the required liquid fluid conductions through lift- horizons separated by lift-legs of various heights) together may permit the further integration of liquid fluid disc turbines in the liquid fluid conduits to avail further increased energy recovery from the motion of said liquid fluids to elevation.

[0084] The application of high pressure by VCM 2000(s) to the gaseous fluid medium in the illustrated system (herein contemplated to be air which through a reference temperature range of operation between 20°C and 80°C may have densities of 1.205 kg/m3 and 1.000 kg/m3 respectively at 1 bar atmospheric pressure) is limited by the density of the liquid fluid being raised to elevation since the selected liquid fluid medium (herein contemplated to be water at about 997 kg/m3 average density, at about 25 °C) prevents egress of said gaseous pressurization control fluid through said inverted piping section(s) 1947 as discussed. Therefore the maximum limiting value of gaseous fluid density must remain less than said 997 kg/m3 (liquid fluid density) in order to maintain said gaseous pressurization control fluid ever-on-top of said liquid fluid as is required for successful system operation, and it may thereby be stated that said gaseous pressurization control fluid which may be compressed by 56 to 67 or more times (dependent upon the temperature of compression yielded) before said captivated gaseous pressurization control fluid might thereafter become more dense than the liquid fluid (water) barring its egress. Conveniently, 56 times compression relating to 56 bar (or 823PSI) is far in excess of the contemplated pressures required for successful system operation, which pressure may more realistically be in a range between 1 (or less) and 20 bar dependent upon conduit strengths employed. With 20 bar relating to a head of over 600 feet, it should be recognized that the pressure differential of service contemplated may offer significant fluid velocities through smaller lift-legs of operation.

[0085] Since pressure energy is neither destroyed nor lost in successful system embodiments of the invention but is rather forced to be communicated between liquid fluid receiving and sourcing pressurization reservoir(s) 330, with total masses of gaseous pressurization control fluid captivated at respective lift-horizons sufficient to provide a minimum pressure in the lower pressure pressurization reservoir 330 (ie: near the time of cycling of the high pressure 1996 and low pressure 1986 valve(s) redirecting the application of VCM 2000(s)' vacuum and pressurization potentials) which may be largely at or below the head pressure in the lift- leg of liquid fluid extending to the next higher lift-horizon, and the concomitantly provided higher pressure applied to concomitantly communicating pressurization reservoir(s) 330 raising liquid fluid to next higher lift-horizon(s) may be permitted to reach pressures greatly exceeding said lift-leg respective head pressure, meanwhile creating desirously great pressure differentials for service in the method. While understanding that the integration of liquid fluid disc turbines to provide energy recovery from the motion of liquid fluid passing upward through the system may cause some pressure energy loss in transit to said upper elevation lift-horizon(s) largely materializing as work output, said pressure loss is by design created in a secondary loop (the liquid fluid circuits) of the system where said transitive pressure energy loss is by comparison, expendable, whereas the premise of the invention to utilize remuneratively redistributed captive gaseous fluid loads (in primary, gaseous fluid circuits) permitting the conservation of pressure energy which while being neither lost nor destroyed, but rather redistributed to create successions of pressure differentials capable of great work, and said secondary fluid circuit anticipated pressure losses may thereby warrant said liquid fluid disc turbine integration.

[0086] Since the torque achievable by Tesla type disc turbines is proportionate to the square of their radius as previously discussed, integrations of Tesla type disc turbine(s) in the liquid fluid circuits of the invention may therefore desirously provide larger diameter disc turbines than the diameter of liquid fluid conduits to elevation, with said discharge cross sectional area of said turbine(s) being largely equal to the diameter of said lift-leg conduits, and with check valves being installed there-above said disc turbines or alternately with upper thick end disc(s) thereof said disc turbine(s) (rotating in the horizontal plane) having upwardly opening chamfered inside diameter(s) and o- rings seated within annular grooves therein said chamfered surface(s) as well as guide(s) vertically extending upward there-from whereupon said guide(s) rigid plug means providing positive shut-off may thereby permit said disc turbine to provide both energy extraction as well as the function of a built-in liquid fluid check valve via the action of said plug(s) under the influence of acting pressure differentials causing said plug(s) to either rise and permit flow to elevation through said disc turbine(s), or be caused to seat and seal the upwardly opening turbine discharge region with said check-action plug(s) riding along said guide(s) (with said plug means providing said positive shut-off in conjunction with chamfered or conic surfaces matching the angle of said aforementioned chamfered disc surfaces and having o-ring or gasket means embedded therein one or more annular recesses in said conic or chamfered surface(s), with said plug means while rigid, may be made light by the inclusion of gaseous medium within a cavity thereof, and where employed, said check-valve action turbine(s) necessitating the provision of sizeable axial load bearing means there-for). In contemplation of liquid fluid turbine integration as discussed, disc turbine housing(s) may be mounted between flanges positioned in the indicated check valve 290/291 position(s) or may be located elsewhere in the lift-leg conduit(s), with said housing(s) or flange(s) appurtenances providing multiple tangential disc turbine(s) inlet(s) to said large diameter disc turbine(s), said lower housing or disc turbine lower blanking end-disc further providing a conic or contoured surface providing a degree of acceleration to the liquid working fluid upon approach and entry into said tangential disc turbine inlets and subsequently into the spaces between said disc turbine disc(s) so as to enable enhanced energy recovery from said pressure differential of said secondary liquid fluid circuit. [0087] Electrical energy extraction by the presently discussed invention embodiment may be contemplated to be provided in many fashions, including: standard generation means attached to the shaft of said disc turbine(s) and turning in an enclosed space or turning externally to the pressurization reservoir; the employment of Tesla type disc runner(s) turning a shaft to drive a co-rotating magnetic coupling component to further drive a secondary shaft in an isolated fluid circuit raising the pressure of closed loop hydraulic fluid further supplying working fluid to drive an external Tesla type disc turbine operating in capacity as a remotely stationed hydraulic motor which may further drive a co-rotating electrical generator, or; which electrical generation means may alternately comprise a toroidal generation means of similar design to that disclosed in Figure 2.

[0088] As may be surmised, the presently disclosed system illustrates a 'top-down' gaseous flow network wherein gaseous pressurization control fluid collected and charged into the system's second highest (and subsequently lower) elevation lift-horizon pressurization reservoir(s) 330 causes liquid fluid charge(s) thereat said second highest (and subsequently lower) elevation to be sequentially moved to the highest elevation lift- horizon in the manner previously discussed. In contrast to previously illustrated embodiments, however, uppermost elevation lift horizon pressurization reservoir(s) need never be subjected to sub-atmospheric pressure application for successful conduction of liquid fluid thereto elevation, provided sufficient differential pressure with respect to atmospheric pressure is applied in said second-highest (and subsequently lower elevation) pressurization reservoir(s) 330. Different means may be provided with which to satisfy said requirement for high pressure 'initial' charge(s) of said gaseous pressurization control fluid which may include the axial intake of VCM 2000 being (protected from debris ingress, however) left open to full atmospheric pressure gaseous ingress, thereby providing maintained pressure amplification through VCM 2000 for application to said second highest elevation pressurization reservoir(s) 330 further permitting the uppermost elevation liquid fluid receiving reservoir to be left open to atmosphere (preferably one large reservoir with sufficient capacity valve(s) communicating there-with same to permit the discharge of ample liquid fluid for the required purpose into a further atmospherically pressurized capacity or capacities such as a water tower or stand-pipe of water distribution grid, or alternately into another process commencing at elevation (with one such process, power generation, being subsequently disclosed in respect to Figure T). In this way, a fresh charge of atmospheric air may be provided to maintain adequate oxygenation thereof said liquid fluid conducted to elevation where this is of concern. Alternate configurations of largely the same embodiment may instead provide admission of another gaseous pressurization control fluid at elevation or may provide readmission of the same gaseous pressurization control fluid which may be re-conducted from bottom-most pressurization reservoir(s) having previously sourced liquid fluid to elevation, where-after said liquid fluid sourcing period(s) said gaseous pressurization control fluid medium may be communicated to the axial intake of uppermost VCM 2000 (where relative distance thereto is sufficiently short) through a dedicated pressure compatible conduit (not shown) equipped with isolation valve(s) and associated header means, or may be conducted thereto by way of one or more iterations of said dedicated conduit means augmented with further dedicated VCM 2000(s) means (where said distance to uppermost elevation lift- horizon's VCM 2000 is excessive) whereby normal system operation via closed-loop recirculation of said gaseous pressurization control fluid there-from alternating lowest elevation pressurization reservoir(s) 330 in sequence to said upper elevation VCM 2000 may alternately be provided. Application of the latter-mentioned closed-gaseous-loop embodiment of the invention may be contemplated for waste-water conduction and or treatment processes since said high pressure gaseous fluid reservoir may facilitate collection of methane there-from (provided motors 265 of VCM 2000(s) are isolated from the process and explosive pressure and gas concentration limits are avoided in operation) provided appropriate off-gassing valves to conduct said gas unto containment, compression, and or combined heat and power combustion turbines, which may also be disc turbines if desired, utilising pulse combustion techniques developed there-for.

[0089] As shown in the figure, condensate line(s) as well as isolation valve(s) 1972 are provided so as to drain away liquid fluid which may otherwise pool within the lower flanges of VCM 2000(s)' housing during the compression processes. Owing the fact that in the proposed multi-stage configuration, wherein blanking end-discs are provided (at the bottom of each respective stage of compression as indicated in the figure) opposite axial intakes, it is foreseeable that only a limited amount of condensate may accumulate therein, since condensate developing shall be conducted through the rotor and with a thoughtfully constructed discharge, may find egress through the gaseous high pressure discharge port and check valve thereof to pass by way of pressure recovery turbine(s) 200 into the next lower pressurization reservoir currently being charged with gaseous pressurization fluid where-the anticipated amount of condensate shall not pose significance to the system's operation. A notable characteristic setting disc turbines apart from other bladed types of turbines is that masses of liquid fluid condensate propelled there-into disc turbines may cause no appreciable degradation in performance of said disc turbines, whereas bladed prior art gas turbines may be destroyed thereby depending upon the speed of operation due to blade fragility. In any case condensate accumulating in the housing of VCM 2000(s) must be permitted egress so as to prevent parasitic loading thereof should accumulated liquid come into continuous contact therewith said VCM contemplated to turn at considerable angular velocity for successful system operation. The requirement of isolation valve(s) 1972 becomes evident when considering closed loop gaseous operation of such systems wherein the communication of said condensate may most effectively be accomplished (with a minimum degree of disturbance owing cross-pressurization gaseous flow) while said conduit 1971 is at gaseous pressure equilibrium with both the condensate line issuing from VCM 2000(s) as well as the pressurization reservoir into which said condensate is communicated (which may be isolated by further isolation valve means) which due to the variability of the discharge pressure of VCM 2000(s) over the normal cycle of operation (owing the first high pressure, and thereafter largely continuously declining pressure in pressurization reservoir(s) 330 from which said VCM 2000(s) draws gaseous pressurization control fluid at run-time) is not normally the case except for brief periods of time during each cycle, wherefore pressure monitoring in said conduits may be advantageous to ensure pressure equilibrium at the time of condensate communication.

[0090] While differential pressurization is the greater theme of this embodiment, it will be understood that with the inclusion of further appropriately placed valve means, such as would permit atmospheric pressure gaseous fluid (air) to enter the second stage of VCM 2000 compression or low pressure conduit 1984 once a sufficiently low pressure has been achieved in the liquid fluid receiving pressurization reservoir at run-time (which gaseous pressure there-from said pressurization reservoir may be received by the primary compression stage's axial intake during this same time period), that the atmospheric medium may then permit the extended supply of high pressure into liquid fluid sourcing pressurization reservoir(s) and thereby continue to increase the pressure and volume of liquid fluid pushed to elevation even as gaseous pressurization control fluid is depleted in the lower pressure liquid fluid reception pressurization reservoir, which capability may significantly aid system performance should a nuisance leak develop in a system conduit which cannot be rectified readily.

[0091] Referring now to Figure Ih, a preferred embodiment of the gaseous-liquid fluidic lift system is presented in which a plurality of liquid fluid lift-horizons and lift- legs extending to elevation comprising parallel network(s) of preferably large effective diameter pressurization reservoirs 330 and liquid fluid: conduit(s) 1946; conduit invert section(s) 1947 and check valve(s) 290/291 put to the task of high volume liquid fluid 1977 transport there-through as forced by differentially applied gaseous fluid 1978 pressures developed by multi-stage Tesla-type disc runner vacuum and compression means VCM 2000(s) communicating with vacuum/low pressure gaseous fluid conduit(s) 1984 as well as high pressure gaseous fluid: conduit(s) 1994; check valve(s) 1962 and isolation valve(s) 1996 to develop intra-lift-horizon pressurization reservoir 330 gaseous fluid transfers as required to create said differentially applied gaseous 'control fluid' pressures at run-time. A cylindrical multi-aperture valve 1966 intermittently rotated within low pressure conduit 1984 unto alignment(s) commanded by a system- wide controller avails first pressure equalization between pressurization reservoir(s) 330 where-through power may be generated by an integral-to-valve power generation disc turbine 200 (see Figure Ii for detail), and unto secondary alignment thereafter providing VCM 2000(s)' axial intake(s) with gaseous fluid input for compression and transfer into alternate pressurization reservoir(s) 330 at respective lift-horizon(s), with said controller means controlling the appropriate phasing of intra-lift-horizon respective differential pressures so as to produce the inter-lift-horizon differential pressures required to conduct desirously large volumes of liquid fluid to elevation through the remunerative utilization of pressure energy in closed loop, and with energy recuperation availed upon communication(s) of said gaseous pressurization fluid and liquid fluid, kinetic energy recovery availed by gaseous and liquid fluid disc turbine(s) 200 of the system (previously discussed in respect to Figure Ig) may minimize the total energy consumption required and carbon footprint incurred to raise liquid fluids to elevation. With the indicated functional similarities between the two figures' embodiments being largely understood, the significant differences between the two designs shall presently be discussed. [0092] Whereas the previous system embodiment provides top-down communication of gaseous pressurization control fluid in an open or closed loop fashion as suiting particular applications, the presently described figure illustrates a substantially closed loop piping/conduit arrangement providing generically indefinite isolation of fixed masses of gaseous pressurization control fluid at given lift-horizons, which depending upon the configured height of lift leg, may represent a considerable savings in materials cost of the low and high pressure piping which in the present embodiment may be greatly minimized. Fixed masses of gaseous pressurization control fluid captivated by and reciprocated between intra-lift-horizon pressurization reservoir(s) 330 through the action of dedicated VCM VCM 2000(s) turning at preferably high angular velocity to rapidly effect said transfer of gaseous fluid contents creates a surplus of gaseous molecules in a destination pressurization reservoir concurrently with a scarcity of same in a source pressurization reservoir, relating to an increasing pressure in one reservoir concurrent with a decreasing pressure in the other, where-after a time period (required to cause a sufficient liquid fluid transport) pertinent isolation valves may be cycled or rotated on a scheduled basis by said system-wide controller means such as a PLC capable of changing the state of said valve(s) so as to effect the redirection of lift- horizon respective VCM 2000(s)' vacuum and compression potentials to further produce inter-lift-horizon respecting (in addition to the pressurization reservoir respective) cyclically reversing differential pressure oscillation(s) of controllable base pressure and oscillation intensity through VCM 2000(s)' withdrawal of gaseous pressurization control fluid mass from one of said lift-horizon capacities with concomitant loading and pressurization of same gaseous control fluid into alternate lift-horizon respective pressurization reservoir(s) 330, whereby the liquid fluid surfaces therein said respective capacities are thereby caused to be acted upon by either high or low (or vacuum, if desired) gaseous control fluid pressure(s).

[0093] With said PLC commanding the actuation of reservoir respective high and low pressure gaseous fluid valve(s) at successive lift-horizons so as to cause the liquid fluid surfaces in successive liquid fluid communicating pressurization reservoir(s) 330 (ie: those reservoirs indicated as being vertically above/below each other in the figure) to be acted upon by gaseous pressurization control fluid pressure(s) peaking largely 180° out of phase with the gaseous control fluid pressures applied to liquid fluid communicating pressurization reservoir(s) at said successive lift-horizon(s) (noting that system operation is functionally equivalent regardless of whether said successive iteration lift-horizon(s) are located at extended elevation difference, horizontal distance, or along a slope distance there-between said successive reservoir(s) of concern), sufficiently strong differential pressures may be developed there-across the liquid fluid surfaces of said liquid fluid inter-communicating pressurization reservoir(s) that liquid fluid replete pressurization reservoirs 330 at lower-paired elevations being comparatively pressurized with captive high pressure gaseous pressurization control fluid in respect to liquid fluid depleted pressurization reservoirs 330 at upper-paired elevations being comparatively evacuated of gaseous pressurization control fluid while the liquid fluid lift-leg extending there-between the two permit communication of said liquid fluid by way of liquid fluid check valve(s) 290 opening only in the upward direction, liquid fluid may thereby be forced to elevation under a favourable pressure differential which may be tailored by system design parameters to provide a balance between cycle time, volume of liquid fluid transfer, and conduit cross-sections in light of the design pressure differential employed.

[0094] While the gaseous pressure energy provided through the operation of VCM 2000(s) may be nether lost nor destroyed in the present method, it may, however, be anticipated that (depending upon a variety of factors including: selected gaseous and liquid fluid mediums' miscibility and rate of dissolution of the given pressure gaseous fluid into given liquid fluid, and how the process may damp or alternately increase this by; the degree of agitation caused by the character of gaseous fluid entry into pressurization reservoir(s) - which agitation may be greatly reduced by the integration of indicated pressure energy recovery turbines 200 providing greater lateral pressure dispersion of entrant gaseous pressurization control fluid, whereas in said turbines' absence said same entrant gaseous fluid may substantially be jetted into the liquid medium, which may greatly disturb the liquid gaseous boundary layer, increase the surface area of contact as well as include small bubbles of gaseous control fluid medium in said liquid fluid in process of exiting said reservoir - which may comparatively significantly increase the rate of gaseous medium mass loss over time especially if said gaseous fluid direct entry were arranged close to the liquid fluid invert sections; gaseous compression temperature; liquid fluid temperature; and residence times at the given operational temperatures and pressures of application) some fundamental degree of gaseous pressurization control fluid mass may be carried through to discharge or merging with gaseous fluid in upper elevation lift horizons owing factors described above, which may therefore over time result in a degree of diminished total mass of said gaseous pressurization control fluid captive at the various lift-horizons further leading to a diminished maximum pressure capacity at respective elevation lift-horizons which may be observed over time, and therefore a means of replenishing said gaseous pressurization control fluid mass loss need also be included for long-term system operation consideration (which may be provided, for instance, in the form of one or more open to atmosphere - if the gaseous medium is air - auxiliary isolation valve equipped conduit(s) connected to low pressure conduit 1984 or otherwise communicating directly with VCM 2000(s)' axial intake so that during a given cross- pressurization cycle, said auxiliary valve of the pressurization reservoir 330 where-from gaseous fluid is being withdrawn may be opened when the pressure in said low pressure pressurization reservoir 330 reaches atmospheric pressure at which time a period of atmospheric medium ingress (into VCM 2000(s) intake) sufficient to replenish the mass of gaseous fluid lost may be provided followed by closure of said valve and the system being returned to a normal operational state).

[0095] The presently described system provides closed loop gaseous fluid communication wherein gaseous pressurization control fluid is captive at the various lift-horizons of the system in operation. While an observer may state that the system must move comparable volumes of pressurized gaseous fluid in order to provide the transport of equivalent volumes of liquid fluid, the lower power requirement to move said gaseous fluid owing its greatly lighter density and viscosity may provide the present invention significant advantage over the prior art in liquid fluid pumping, and in combination with energy recuperations described from the intra-lift-horizon pressure equalizations and gaseous pressurization process(es) occurring during each cycle and which may endure for significant periods of time related to the pressure differential availed and in light of the fact that VCM 2000 may be shut down for a period of time during each cycle while recovering energy from the process, it may be said that significant opportunity for energy conservation may be provided by the present method of liquid fluid 'lift'.

[0096] In general the design of piping systems for incompressible flows is a well established art in which the Darcy-Weisbach equation (see Equation 6 below) may be utilized to approximate the systems' required liquid fluid circuit(s) physical configurations to permit the conductance of large volumetric flow-rates of liquid fluid to elevation in requisite periods of time. Although the illustrated figure may indicate sufficient conduit diameter(s) to permit the design volumetric flow-rate to be achieved, it must be considered that since at the time of pressurization reservoir changeovers when a given reservoir's liquid fluid has been sent to elevation and the adjacent pressurization reservoir replete with liquid fluid becomes the 'active liquid fluid sourcing reservoir' that at this time, were it not for the check valve in the liquid fluid column, there would be full negatively applied pressure differential inclusive of negatively imposing liquid fluid head pressure applied to said pressurization reservoir at said lower elevation, and therefore it must be understood that VCM 2000(s) shall take time to: firstly reverse the relative gaseous pressure differential applied across the liquid fluid communication reservoir pair(s) under consideration, and; thereafter produce sufficient excess differential pressure so as to exceed the head pressure between liquid fluid surfaces respective to overcome said head pressure of said lift-leg(s) of concern (and thereby commence flow to said higher elevation) (even though VCM(s) 2000 at both lift- horizons of concern may forthwith work to overcome the same negatively imposing pressure considerations, whereby: VCM 2000 at the lower elevation may set about increasing said pressure in said first lower elevation pressurization reservoir 330 utilizing a source of gaseous pressurization control fluid already at high pressure, which should greatly aid said process' time constant, and; upper VCM 2000 at said upper - or subsequent - lift-horizon may set about reducing said pressure in said upper - or subsequent - pressurization via discharge into a pressurization reservoir offering little initial resistance to loading. Regardless of the favourable initial cross-pressurization conditions offered by said co-lift-horizon-resident pressurization reservoirs during the initial period of time subsequent to said 'changeover' of active liquid fluid sourcing reservoir therefore, a decided lag-time shall exist before fluid flow at significant rate develops which may cause the 'peak flow-rate' requirement imposed by the presently described system to significantly exceed the sustained integrated value of volumetric flow previously stated to comparatively provide the same normalized flow volume in equivalent time periods, which greater peak flow-rate may be limited by the diameter of conduit illustrated, and therefore it may be necessary to provide one (or more) auxiliary lift-legs to elevation which may comprise like-capacity components discussed already and auxiliary flange connection / conduit invert section(s) 1947 not shown) through which to provide greater effective diameter conduits to permit the requisite total flow during the peak flow period(s).

[0097] Equation 6: h _f = f ^• L - V ²

D - 2g

Where: hf = Head loss, L = Length of conduit, V = Velocity of fluid, average

D = Diameter of conduit, and/= Friction factor, further dependent upon fluid: density, velocity, viscosity and conduit diameter

[0098] Since the disclosed system is not a constant pressure application owing the cyclic oscillations of differential pressure across liquid fluid lift-legs responsible in the method for causing the conduction of liquid fluids to elevation, it may be anticipated that the system's base load of gaseous pressurization control fluid (captivated at the various lift-horizons) may require adjustment at the time of system commissioning owing variations in the performance of key system elements of concern. For example, the effectiveness of vacuum and pressure seals used throughout the system are of particular concern wherein seals in the gaseous fluid circuit - including labyrinth seals 244/246 about VCM 2000(s)' multiple compression stage axial inlets; sealing means within check valves 1962, and; seals 248 within and about cylindrical valve 1966 preventing disadvantageous fluid bypass - although foreseen to remain ever-clean and serviceable owing permanent non-contact with liquid fluid transfer processes may in any case over time require service. Seals in the liquid fluid circuit(s) by contrast comprising: pressurization reservoir(s) 330 and other conduit means flange and blind flange connection(s) which must provide effective sealing over a varying pressure range of service (which may include vacuum pressure) said seals requiring gaskets there-for, and; liquid fluid check valve(s) 290/291 seats which may be foreseen to become fouled over time and therefore requiring intermittent maintenance cleaning in order to maintain their effectiveness (which cleaning may take the form of scale or debris removal dependent upon the liquid process fluid of concern, which cleaning may be facilitated by the employment or development of self-cleaning check valves, or which cleaning may alternately be achieved via manned SCUBA equipped inspection/cleaning crew(s) where permissible in fresh or salt water applications, for example, while the particular system lift-leg is in a maintained nodal state at atmospheric pressure, or which cleaning may alternately be accomplished during system run-time via guided un-manned dextrous manipulation craft capable of such inspection and cleaning tasks and of being inserted in an access hatch (not shown) under atmospheric pressure, subsequently travelling to the work-site to perform said inspection and maintenance unaffected by pressure swings of operation and returning later to the same or alternate access egress hatch). Further variation in gaseous fluid base load may be anticipated due to temperature (where uninsulated conduits are utilized), and may be significantly offset by the dynamic disc spacing function performance which may change the effectiveness of VCM 2000(s) capability to adhesively 'grip' the gaseous fluid for purposes of centrifugal acceleration and centripetal pressure increase, and also; seals 248 employed by said dynamic disc spacing apparatus, which in combination may significantly affect the gaseous pressure differentials achieved in operation - and by extension the pressure differential applied across liquid fluid surface(s) and lift-leg(s), and therefore the liquid fluid flow-rate by extension;

[0099] The utilization of the dynamic disc spacing functionality foreseen to be requisite and or avail advantage in each significantly pressure-variant working fluid condition of service throughout the figures of the present application is especially contemplated for service herein the gaseous and liquid fluid turbines 200, as well as gaseous vacuum and compression VCM(s) 2000 configurations of the presently described gaseous-liquid fluidic lift system, wherein with particular reference thereto said VCM(s) 2000, it must be recognized that the base-load mass of captive lift-horizon respective gaseous pressurization control fluid should be provided in a measure which cooperates with given VCM(s) 2000 configurations such that in system operation through maximum and minimum gaseous pressure swings of service (ie: the pressure- differential oscillations responsible for conducting liquid fluids to elevation in the method), said gaseous service pressures (and temperatures of compression and evacuation) may cause a wide range of gaseous fluid kinetic viscosities to act upon the working surfaces of the machines disclosed herein which may further require that VCM(s)' 2000 employed disc spacing method provide a range of achievable dynamic disc spacing to at length provide optimal or near optimal disc separation for advantageous operation which may be characterized by or approximate laminar flow conditions where appropriate. It should also be recognized that dependent upon the disc spacing employed, the maximum static pressure achievable by a given VCM 2000 configuration turning at a given angular velocity may be achieved in practice by appropriately spaced discs, whereas inappropriately spaced discs ie: those too loosely spaced, may not realize the possible maximum pressure owing an inability to sufficiently grip the whole mass of working fluid in order to fully accelerate it, and conversely discs too tightly spaced may rather choke the flow of gaseous working fluid flow through VCM 2000, which function of the invention to tailor the disc spacing so as to better 'grip' the working fluid between the discs may thereby afford better performance to VCM 2000 under the widely varying gaseous pressures of service contemplated. As previously discussed, said spacing may very pertinently point to the optimal employment of the dynamic disc spacing in all versions of the gaseous-liquid fluidic lift invention to better approximate ideal disc spacing (highly dependent upon the kinetic fluid viscosity of the working fluid) under cyclic as well as long term operation, whereby said dynamic disc spacing functionality may also provide for advantageous service over time as the base load pressure in said pressurization reservoir(s) may decline for various reasons including leakage, and which disc spacing functionality may thereby also provide for fine adjustment of system operation over extended time periods between service (wherein typical system service may in part involve re-setting or re-filling the base load pressures to a consistent mass in all pressurization reservoirs throughout the system).

[00100] The system further contemplates the independent application of the dynamic disc spacing function to each respective compression stage runner of VCM(s) 2000 so as to achieve control over the full span of compression provided, and while the maximum pressure rise achievable by each stage may largely remain proportional to the disc diameter and rotor angular velocity in runners exhibiting optimal or near optimal disc spacing, the service of the dynamic disc spacing functionality may optionally be exercised so as to permit VCM(s) 2000 to be configured to function more-so as blower(s) if desired by substantially opening up the spaces between the discs to permit both greater volume gaseous fluid axial ingress as well as tangentially expelled fluid egress there-from (which functionality may at the time of changeovers to 'subsequently liquid fluid sourcing pressurization reservoirs' permit more rapid transfer of gaseous pressurization control fluid of potentially significantly higher pressure into neighbouring co-lift-horizon-resident gaseous 'transfer pair' pressurization reservoir(s) 330 with less implicated load upon VCM(s) 2000 employing said purposefully set wider disc spacing offering greater runner freeness of motion through given medium(s). Accompanying the service of the dynamic disc spacing in effectively manipulating the fluid passing through the spaces between the discs must be a means to prevent negatively imposing reverse 'back-pressure' gradient (leakage / backflow around VCM(s) 2000), since the advantages secured by the dynamic disc spacing function as well as compressors and vacuum apparatus in general are moot if there is leakage there-into or there-out of evacuated or pressurized containers (respectively). The present invention therefore also contemplates the employment of labyrinth seals in order to prevent gaseous fluid from passing around disc compressor stage runner(s), which labyrinth seals comprising raised and or channelled annular appendages milled, moulded or otherwise affixed to one or more end-disc(s) and also to the housing component there-adjacent said end-disc(s) depending upon the application, said labyrinth seals which may be of a type described by Letourneau (17) or of another functional type.

[00101] Notwithstanding the above considerations, once a basic system configuration and control strategy has been decided upon (which control strategy may preferably take into account the peak flow design requirement discussed as well as taking into consideration VCM(s) 2000s' anticipated performance), a preliminary valve cycling and rotation configuration schedule respecting these system parameters may be approximated which may provide appropriate time constants of evacuation and cross- pressurization with which to facilitate the system providing the required gaseous differential pressure oscillations and design flow of liquid fluid throughput to elevation (and or distance). In any case, configurable and variable performance features of the system may combine to result in deviation from said preliminary schedule's performance measurably owing variables discussed previously as well as below, which deviation may require an accordant revision in said schedule at the time of system commissioning. For example should said preliminary valve cycle and rotation configuration be too brief in duration to develop a serviceably high gaseous differential pressure, only limited liquid fluid flow to elevation may be achieved; or if alternately said valve configuration is too long in duration which while providing serviceable pressure differential and completing the liquid fluid transfer, may waste the power expended to operate VCM(s) 2000 by needlessly extending said cycle period beyond that required to conduct the required quantity of liquid fluid to elevation. It may be foreseeable that the most efficacious valve schedule may be derived at the time of system commissioning while pressure-differentially loading lift-horizons with liquid fluid from a source at a base elevation under said preliminary valve schedule, and with each successive lift-horizon's filling, thereafter modify the valve cycle periods and analyze said gaseous cross-pressurization time constants between pressurization reservoir(s) under varying differential pressures in order to determine the most favourable conditions of operation. Alternately, as long as the system functions in the correct sequence(s), the basic control strategy, largely comprising said basic valve schedule and disc spacing(s), may be conditioned as by level and or pressure feedback from transmitters 1930 and 1989 respectively, as well as high 1933 and low level switches 1934 illustrated, as required, to cue to required valve cycling(s) in conjunction with programmable timers as required to trim the cycle times duration.

[00102] The illustrated system may also lend itself to augmentation of performance through adaptations (not shown) such as the provision of auxiliary pressure compatible gaseous fluid reservoir(s) at each lift-horizon with which to temporarily store the VCM(s)' 2000 discharge product resulting from compression of remnant vacuum/low pressure in a liquid fluid receiving pressurization reservoir, said reservoir supported with first isolation valve 1996 and conduit means there-for providing an inlet communicating with VCM(s)' 2000 final compression stage discharge, as well as second isolation valve with conduit communicating with the axial intake of VCM(s) 2000 providing outlet from said auxiliary reservoir. A contemplated sequence of operation follows, wherein, for sake of convention components of concern shall be referred to in the plural form in consideration of a system comprising a plurality of lift-horizons wherein each of the components and sequences discussed are repeated throughout, and wherein said first named valve(s) may be commanded to open (permitting redirection of VCM 2000 discharge and compression of same there-into said auxiliary previously largely evacuated reservoir) which valve opening may follow the closure of check valve 1962 (said closure condition signalled to said PLC or other controller operating the system via the further provision of a limit switch actuated by said check valve, or in another manner such as by a pressure switch), said check valve closure occurring with declining VCM(s)' 2000 outlet pressure, which post-peaking, may no longer keep said check valve in an open state (due to the greatly diminished source fluid pressure and limitation of pressure amplification across VCM(s) 2000. With said first named valve 1996 open and said second named valve closed, remnant gaseous pressurization control fluid 1978 may be withdrawn from 'liquid fluid receiving' pressurization reservoir(s) 330 by VCM(s) 2000 resulting in the further lowering of pressure therein while concurrently enhancing the differential pressure across the liquid fluid lift leg(s) under consideration, thereby availing an enhanced rate of conduction of liquid fluids 1977 to elevation. When 'liquid fluid receiving' pressurization reservoir(s) 330 are considered replete (as may be decided by said controller's reception of LSH 1933 high level switch state change information upon liquid fluid level(s) reaching said target level(s), the closure of auxiliary isolation valve(s) 1996 may then be effected to isolate said auxiliary reservoir(s) now considered at intermediate pressure. With the subsequent: closure of gaseously pressurized liquid fluid depleted pressurization reservoir 330(s)' high pressure isolation valve(s) 1996 (to prevent gaseous loading thereof said 'next-to-be-evacuated' pressurization reservoir(s) 330 during the subsequent operation), followed by the; rotation of rotary valve 1966 to a nodal position (ie: intermediate its current VCM sourcing position and the 'equalization valve state' whereby VCM(s) 2000 axial intake(s) may be isolated from both pressurization reservoir(s) 330), while; said auxiliary reservoir(s)' second mentioned isolation valve(s) are opened (to permit the ingress of said auxiliary reservoir(s)' mid-pressure gaseous pressurization control fluid into VCM(s)' 2000 first stage(s) of compression), concurrently with the; dynamic spacing of VCM(s)' 2000 inter-disc spaces of respective compression stages to reflect the kinetic viscosity changes of the working fluid undergoing pressure (and therefore density) as well as temperature changes at run-time, while; the opening of liquid fluid replete pressurization reservoir 330(s)' high pressure isolation valve(s) 1996 (to permit loading said auxiliary reservoir(s)' gaseous fluid content into said 'next-to-source liquid fluid' pressurization reservoir(s) 330 as an initial step toward liquid fluid sourcing through VCM(s) 2000 put to task in blower configuration initially for rapid gaseous fluid transfer purposes, and thereafter with a tighter disc spacing aiding the evacuation of said auxiliary reservoir) said gaseous pressurization control fluid delivered by way of work extraction turbine 200, said gaseous fluid transfer continuing until substantial exhaustion of said auxiliary reservoir, before; closure of said auxiliary reservoir(s)' second named isolation valve (thereby isolating said reservoir from VCM(s) 2000 while at substantially very low pressure in preparation for its next serviceable filling), and further; rotation of valve 1966 to the pressure equalization position, whereupon VCM(s)' 2000 drive motor may be powered-down to conserve energy while power generation may be sustained for a period of time via gaseous working fluid passage through valve 1966(s)' integral turbine 200, (ie: wherein reference to Figure Ii, largely full differential pressure may be initially applied across pressure energy recovery turbine 200, with said differential pressure decreasing during said equalization period(s), with high pressure from the previously 'liquid fluid sourcing' pressurization reservoir entering disc turbine inlet 256 bounded between solid separation plates 558 providing egress for said equalization flow only through turbine(s)' 200 closely spaced discs, its central upper exhaust port, and thereafter through rotary valve bypass outlet port 1969 providing access to the alternate reservoir 330). Returning now to the discussion of Figure Ih, it may be stated that owing the markedly decreasing differential pressure there-across turbine 200 on approach to completion of the pressure equalization process and with said pressure equalization time taking longer with decreased pressure differential, that a prolonged period of time may elapse before true equalization may occur, and that even with the benefit of the dynamic disc spacing functionality the achievable rate of rotation and accordant torque and work output there-from turbine 200 through the latter stages of a hypothetically extended period of equalization may require that the requirement for swift system operation take precedence over the work generation process at some point, at which time, the; liquid fluid replete pressurization reservoir(s)' intake isolation valve 1996 shall be opened, as; VCM(s) 2000 are reenergized, and; rotatable valve is rotated through any intervening nodal arc to the position whereby port 1967 (of Figure Ii) is positioned to permit gaseous fluid ingress there-through from the previously liquid fluid sourcing pressurization reservoir, said gaseous fluid finding egress there-from through rotating valve component(s)' isolation plate 1982 holes 1983 and stationary low pressure/vacuum isolation plate(s)' 1987 holes 1988, where-through said; gaseous fluid may further source gaseous working fluid to VCM(s)' 2000 compression sequence, with the output thereof as discussed loading into the presently 'liquid fluid sourcing' pressurization reservoir 330 substantially bringing the discussion to a point of reiteration of the aforementioned process which shall not be repeated for purposes of brevity, however, being understood to be the same, however in reverse relation to the respective reservoir(s) wherefor the process was previously discussed.

[00103] Note that throughout periods of pressurization reservoir 330 as well as auxiliary reservoir compression, evacuation (and or expansion) that the disc spacing of VCM(s) 2000 (as well as work extracting disc turbines) is anticipated to undergo gradual change by the dynamic disc spacing function to reflect the change of kinetic viscosity of the gaseous fluid supplied thereto VCM(s) (and work extracting disc turbines) as working fluid, and in accordance with the successful tracking of kinetic viscosity (owing the effect of said compression and expansion and evacuation potentials to increase and decrease the temperature of the fluid undergoing said processes accordingly) the further requirement of analog temperature measurement as well as angular velocity (or shaft rotation speed, where the given turbine or compression device is variable speed) representation for input into the dynamic disc spacing control algorithm to better effect said dynamic disc spacing control function at run-time are also contemplated.

[00104] For successful system operation the provided base-load mass of gaseous pressurization control fluid loaded into lift-horizon(s) respective pressurization reservoir pair(s) must be capable of furnishing the oscillating differential pressures required in a reasonable amount of time, and while a controlling valve schedule may manage the vacuum and compression potentials of VCM(s) 2000 to successfully segregate said base-load mass into high and low pressures of (generically) two isolated containment reservoirs provided at each lift-horizon, depending upon the volume of liquid fluid to be lifted to elevation per cycle (note the break-lines in pressurization reservoir(s) shown indicating indefinitely defined pressurization reservoirs which may provide great capacity) and the cycle time required to achieve a desired throughput, that the system may require more than one VCM 2000 per lift elevation in order to achieve a desired system throughput with a control strategy and valve schedule providing operation (which may be conditioned with level and or pressure feedback from transmitters 1930 and 1989 respectively as well as high 1933 and low level switches 1934 illustrated), which system desirously availing serviceable time constant(s) of liquid fluid conduction to elevation through successive lift-horizons (to achieve said desirable liquid fluid throughput) need respect variables including: selected liquid and gaseous fluid temperatures and densities; VCM configuration and angular velocity; valve sizing; liquid fluid lift-leg height; pressurization reservoir 330 capacities; liquid fluid check valve 290/291 cracking pressures; and liquid fluid conduit pipe frictional pressure losses.

[00105] The oscillating pressure differential(s) produced by the system via system- wide intra-lift-horizon valve actuations during run-time operation of VCM 2000(s) imposing serviceable differential pressures across respective liquid fluid lift-legs places two-fold reliance upon both VCM(s)' 2000 evacuation and compression potentials (both synchronously required to provide benefit in the production of said inversely applied gaseous pressure differentials, which gaseous pressurization load components thereof remain ultimately trapped (in successful applications of the method, by liquid fluid occupying open piping inversions 1947 owing the difference in gaseous and liquid fluid densities observed throughout low and high pressures of system operation whereby said gaseous pressurization control fluid remains ever-on-top of said liquid fluid and thereby remains substantially captive therein).

[00106] In general, open isolation valve(s) 1996 provided in VCM 2000(s)' high pressure stage outlet(s) permit high pressure gaseous pressurization control fluid to enter and thereby pressurize 'presently liquid fluid sourcing' pressurization reservoir(s), while closed valves 1996 prevent said higher pressure gaseous fluid discharge from being re- circulated back unto entry into the 'liquid fluid receiving' pressurization reservoir where-from said gaseous pressurization fluid is extracted (to supply said high / increasing pressure in the alternate pressurization reservoir 330) by way of low pressure conduit 1984 and VCM 2000(s)' axial intake, said desirously low gaseous pressurization control fluid pressure in said 'liquid fluid receiving' pressurization reservoir(s) 330 inducing a faster flow-rate of liquid fluid there-into said liquid fluid receiving pressurization reservoir(s) 330 advantageously approaching very low or vacuum pressure when nearly replete with liquid fluid just prior to changeover of the actively liquid fluid sourcing reservoir.

[00107] While as discussed gaseous fluid check valve(s) 1962 indicated in high pressure conduit 1994 shall close as VCM(s) 2000 output pressure peaks, said check valve(s) may also serve to prevent undesirable gaseous fluid back-flow or loss, which in the event of a line break in said discharge conduit(s) 1994 or failure of VCM 2000 or simply during energy conservation and or pressure equalization cycles when gaseous pressurization control fluid may be permitted to flow for an undetermined duration of time prior to the closure of isolation valve(s) 1996, said check valve(s) may obviate the requirement (or provide failsafe system performance alongside) further measures to detect and correct problematic operational situations whereby monitoring by a supervisory control and data acquisition (SCADA) system and or operator, or via programmable interlock(s) based upon gaseous fluid charge time and or pressure and or liquid levels or rates of change thereof, or upon optional reverse flow switches or differential pressure measurements appropriately tied-in, the further timely closure of valve(s) 1996 may be effected. In extreme pressure loss potential situations, the temporary halting of system service via appropriate valve(s) reversal may remove gaseous pressurization control fluid effectively from a failing lift-horizon capacity to prevent its escape to atmosphere (where an atmospheric medium such as air is employed) until such time as service may be performed). Alternately, changing the local pressure oscillation amplitude(s) may permit a crippled reservoir to be bypassed for a period of time, or where putting a given lift-leg out of service until reparations are made is acceptable the operational pressurization reservoir 330 may be caused to communicate with the aforementioned auxiliary reservoir, in which case the system may continue to operate (albeit at diminished capacity) in the absence of a given pressurization reservoir's 330 service for a period of time until said repairs may return the affected pressurization reservoir to service.

[00108] While continuing the discussion of Figure Ih, specific reference shall now be made to Figure Ii detailing the operation of one possible form of cylindrical rotating valve mechanism 1966 substantially replacing the functionality of a plurality of valves and conduits with a single motor-driven cylinder serving as a window through which two (or more, in alternate embodiments) sequential gaseous fluid transfers may be conducted, namely: first major intra-lift-horizon gaseous fluid transfer (ie: lateral cross- pressurization indicated in the figure between co-lift-horizon resident pressurization reservoir(s) 330 through ports 1967 and 1983 of said valve 1966 when port(s) 1988 of stationary isolation plate 1987 are in alignment with aforementioned holes 1983 permitting said gaseous pressurization control fluid flow egress there-through to source VCM 2000 further loading 'next to liquid fluid source' destination pressurization reservoir(s) 330. It must be understood that the fluid transfer being discussed commences subsequent to the equalization process (described next), which post- equalization gaseous fluid pressure providing the initial intra-reservoir cross- pressurization loading pressure is contemplated to retain a high percentage of the maximum pressure of the normal system pressure oscillations (since the percentage of liquid fluid fill in the destination reservoir may occupy a large percentage of the destination pressurization reservoir(s)' volume thereby leaving a comparatively small void and further limiting the transfer volume required to fill said void which at length may keep the volume-weighted pressure of gaseous pressurization control fluid at the close of said pressure equalization transfer period substantially high) and therefore the loading of gaseous pressurization control fluid into said destination reservoir by way of VCM 2000 amplifying said pressure en-route there-to may therefore have a ready effect upon the transfer of liquid fluid to elevation owing the exchange of higher and lower pressures applied thereby across liquid fluid surfaces of inter-lift-horizon pressurization reservoir(s) 330 separated by lift-legs of distance, elevation, or both, and; second minor intra-lift-horizon pressurization reservoir(s) 330 pressure equalization through ports 1968 and 1969 by way of turbine 200 (during which isolation plate hole(s) 1983 of rotating isolation plate 1982 are out of sync with stationary isolation plate 1987 hole(s) 1988 thereby isolating VCM 2000 from the intra-reservoir gaseous fluid transfer process, said VCM 2000 contemplated to be de-energized during said pressure equalization period while rapidly exhausting gaseous fluid communicating there-through its multiple stages and substantially forming a massive fly-wheel may thereby turn freely for an extended period of time in the evacuated space, with said time duration contemplated to outlast the pressure equalization time period so that the subsequent reenergizing of motor 265 indicated adjacent the high pressure stage shall draw significantly less power, and meanwhile said co-lift-horizon reservoir(s) may thereby be prepared for the subsequent alternation (reversal) of higher or lower pressures application therein as permitted by alignment of said function specific ports of said rotating valve 1966 cylinder aligned for appropriate fluid communications by the passing of a brief measure of electrical energy through positioning motor Mθ located non-invasively to said fluid transfers.

[00109] Rotary valve- 1966-integral energy recovery disc turbine 200 mounted on an overhung shaft may develop significant torque during pressure equalization event(s) when said valve 1966 is aligned by motor Mθ so that smaller port 1968 sized to supply turbine 200' s inlet 256 with a full cross-section of high pressure gaseous fluid flow is positioned within a supply aperture of θ degrees of arc in source 'low pressure' transfer conduit 1984 with said inlet 256 feeding gaseous pressurization control fluid as working fluid by way of an involute housing (or other housing form which may as shown in the figure be provided by a circular housing arching unto tangency with the periphery of a centrally located disc turbine with the aid of a rigidly fixed tangential fluid guide 548) said working fluid thus admitted into disc turbine 200 preferably outfitted with a required-span capable dynamic disc spacing apparatus to manage the optimization of disc spacing under anticipated pressure swings of service (affecting the kinetic fluid viscosity of said working fluid as discussed), said turbine 200 via shear stress developed between viscous fluid layers applied through the adhesion of zero speed boundary layers to disc turbine disc surfaces of great combined surface developing significant shear force, torque, and rotation thereof said disc turbine 200 and shaft upon which it is mounted, said working fluid (gaseous pressurization control fluid) thereafter discharging through outlet 259 of preferably greater cross section than inlet 256, with said outlet 259 further communicating with a destination pressurization reservoir 330 through a larger area outlet port 1969 permitting elevated pressure gaseous pressurization control fluid (in the form of VCM 2000 throughput) to be provided to the destination 'liquid fluid sourcing' pressurization reservoir 330 (which may not source liquid fluid until the subsequent cross-pressurization event is in progress due to the higher gaseous pressure in the pressurization reservoir 330 there-above the liquid fluid lift-leg separating said lower and upper pressurization reservoirs) said valve 1966' s outlet port 1969 also providing an aperture of θ degrees of arc while concurrently positioned adjacent a discharge aperture of largely matching dimensions in alternate 'low pressure' transfer conduit 1984 (which alternate conduit 1984 contemplated to comprise an opposite leg of a precision manufactured union-cross of large diameter in which valve 1966 may rotate freely in the centre region thereof while being sealed therein by lightly compressed high durometer lubricated o-rings inset about its perimeter kept under contiguous seal by preferably at least two circumferential bearing means ensuring parallelism between the outside diameter of said valve cylinder 1966 and the inside diameter of said union-cross or other suitable pressure-compatible containment, thereby favouring seal longevity as well as service under wide ranging pressures of application) said alternate conduit 1984 illustrated diametrically opposite the aforementioned conduit 1984 requiring that valve 1966 inlet port 1968 also be arranged opposite outlet port 1969 and port 1967 being positioned at right angle with respect to the former ports to permit conducive isolation / blanking zone(s) between adjacent port(s) by which counter-productive cross- pressurization(s) and de-pressurization(s) may be controlled as required whereby turbine 200' s throughput may be communicated into the lower (however increasing toward equalization) pressure of destination pressurization reservoir 330 permitting loads such as mechanical or electrical work generation means (which may be mounted there-below in stationary cavity 219) to be driven by torque developed by turbine 200. [00110] It should be understood that contemplated embodiments may incorporate valve 1966 inlet and outlet port configuration(s) reflecting different angular layout as well as different numbers of ports to permit multiple simultaneous operations if desired, for example, permitting pressure equalization between two or more pressurization reservoirs while another one or more pairs of pressurization reservoirs may concurrently be undergoing cross-pressurization(s), depending upon the size, capacity, angular velocity and or number of VCM(s) 2000 provided. Meanwhile it must be understood that the invention may in other embodiments prefer to provide equivalent-to-rotary-valve-1966 functionality through the alternate incorporation of more traditional valve and conduit arrangements facilitating similar fluidic communication(s) between appropriate intra- lift-horizon pressurization reservoir(s) 330 of concern and also provide intervening lag- time between valve operations when required to maintain the isolation of respective capacities of fluids and thereby prevent disadvantageously affecting cross- pressurization(s) and de-pressurization(s).

[00111] Alternately supporting turbine 200 between upper and lower bearing set(s) as indicated in Figure Ih (wherein an upper bearing mounted in the bottom of a rigid central shaft support element extending downward from the underside of rotating valve 1966's uppermost isolation plate 1982 and a further bearing means located in or attached to bottom isolation plate 558) may provide greater support for a vertical shaft. Should horizontal mounting of said shaft, turbine and work generation elements rather be preferred, said elements should not appreciably extend beyond upper isolation plate 558 so as to maintain minimal resistance to previously mentioned primary cross- pressurization process flow passing through the same intra-valve region. In general dual turbine exhausts are preferable to enhance the discharge area and therefore expansion ratio attainable for better work generation efficiency through disc turbines, which advantage may be favoured by the horizontal mount discussed. As illustrated in Figure Ii, however, said shaft supported by freely turning bearing means positions turbine 200 between isolation plate(s) 558 comprising a lower element having both condensate and central shaft through-hole(s) with bearing mount there-for (hidden in the view behind tangential fluid guide 548) and an upper element having a preferably tapered through- hole of turbine discharge diameter concentrically located with turbine 200 so as to permit the pressure equalization process flow driving turbine 200 to freely discharge through pressure equalization outlet port 1969 and subsequently to produce electrical energy via the additional incorporation of a generator which may comprise low profile MultiTAP generation method appurtenances, to be discussed in greater detail, in lower compartment work generation mounting cavity 219.

[00112] With lift-horizon respective liquid fluid pressurization reservoir(s) 330 and conduit/piping inversion(s) 1947 (barring the egress of lighter density gaseous pressurization control fluid from said reservoir(s) as in the previous figure - which gaseous fluid may be pressurized to many atmospheres of pressure if required to conduct liquid fluid through great lift-leg heights - without said gaseous pressurization control fluid escaping through said piping inversion(s) 1947 owing said large gaseous versus liquid density difference) interconnecting with other like lift-horizon components by and through lift- legs comprising liquid fluid check valves 290/29 land liquid fluid conduits 1946, large volume liquid fluid flow conduits to elevation may thus be embodied. Dedicated gaseous pressurization control fluid hardware comprising: low pressure conduit(s) 1984; combination low pressure transfer / pressure equalization rotating valve/turbine 1966 (with integral energy recovery disc turbine 200 recuperating a portion of the energy of compression respective to each gaseous differential pressurization of reservoir(s) 330 during pressure equalization periods occurring in each cycle); high pressure conduit(s) 1994 and valve(s) 1996; as well as gaseous fluid check valve(s) 1962, all work in conjunction with VCM VCM(s) 2000 at respective lift- horizon^) to permit the withdrawal of gaseous pressurization control fluid from first pressurization reservoir(s) 330 and the concomitant loading of same into second pressurization reservoir(s) 330 at the same lift-horizon(s), at length developing low pressure in the former reservoir(s) and a high pressure in the latter pressurization reservoir(s) 330, respectively, where-through said cross-pressurization process(es) recuperation of a substantial portion of the energy expended to operate the system may be recuperated by way of further pressure energy recovery turbine(s) 200 positioned to receive the fluid propelled by VCM 2000 through high pressure conduit 1994 and valve 1996 as a tangential input developing shear stress, torque, and rotation of said turbine(s) via disc turbine principles discussed previously, said energy recovery disc turbine(s) acting in function as dynamic to static pressure energy converter(s) permitting a significant measure of work output there-from concurrently with each major stage of the gaseous-liquid fluidic lift (hereinafter referred to as the GASLift process) - whereby energy consumed by motor 265 to drive VCM 2000 may concurrently yield electrical work generation (with appropriate provision(s) 271 there-for, contemplated to comprise the multi-phase toroidal planar - heretofore referred to as MultiTAP - electrical generation means detailed later herein with respect to Figure 2 which is contemplated to provide a cost-effective small footprint electrical generation technology to cooperate neatly with the compactness of form and local manufacturability traits represented by disc turbines in general).

[00113] A brief discussion of a typical liquid fluid conduction to elevation is herein provided wherein "positive pressure differential" is understood to imply greater pressure in lower elevation lift-horizon pressurization reservoir(s) 330 with respect to lesser pressures of gaseous pressurization control fluid application in upper elevation lift- horizon pressurization reservoir(s) (ie: those communicating through the same liquid fluid lift leg). The system shall be discussed commencing with an initial 'system state' in which a segment of the system (ie: a given liquid fluid communicating pressurization reservoir pair) comprising a first liquid fluid replete pressurization reservoir 330 at a first (lower elevation, for purposes of discussion) lift-horizon communicating through a liquid fluid lift-leg to elevation with a second liquid fluid depleted pressurization reservoir 330 at a second (higher elevation, for purposes of discussion) said segment under a considerable negative pressure differential owing the higher gaseous pressurization control fluid pressure in said second upper pressurization reservoir compared with the initially lower pressure in said first lower pressurization reservoir (with no incumbent liquid fluid flow there-between said reservoirs owing the check valve in said liquid fluid line preventing back-flow downward from the higher elevation). With a discrete rotation of valve 1966 through largely 90° of arc as generally illustrated in Figure Ii (while understanding that another specified angle of arc may be designed to facilitate a greater number of reservoirs and or number of operations to be undertaken at given lift-horizons), the subsequent pressure equalization event discussed is commenced through which event the pressurization reservoir 330 under the higher gaseous pressurization control fluid pressure discharges a component of its gaseous fluid into an alternate pressurization reservoir 330 under lower gaseous control fluid pressure at the same respective lift-horizon (by way of energy recovery disc turbine 200 generating power through said pressure re-distribution), said pressure equalization event bringing intra-lift-horizon system pressurization reservoir(s) 330 closer to pressure equilibrium with one another (and by extension also closer to pressure equilibrium with inter-lift-horizon pressurization reservoirs 330, since by design, the system causes the pressures in successively liquid fluid communicating pressurization reservoir(s) at successive lift-horizon(s) to substantially inversely mirror those at other successive lift- horizons), however there shall be no incumbent liquid fluid flow during this time period since there remains a lack of sufficient positive differential pressure with which to drive liquid fluid to elevation through the lift leg under consideration. In process of said intra- lift-horizon pressure equalization process as the gaseous fluid pressure differential tends toward equalization, the system shall command the further discrete rotation of valve 1966 and cycling of appropriate high pressure discharge valve(s) so as to begin the cross-pressurization event wherein the liquid fluid replete (initially lower pressure) pressurization reservoir 330 is loaded with VCM 2000 discharge flow received by way of pressure recovery disc turbine 200 (driving further MultiTAP electrical energy generation appurtenances 271), said VCM 2000 discharge flow providing turbine 200 with a tangential working fluid feed of high velocity substantially matching the peripheral velocity of the disc compressor runner (in appropriately spaced disc runners) contemplated to be spun at high angular velocity. During the early stage of this process the gaseous differential pressure there-between intra-lift-horizon pressurization reservoirs 330 reverses, and a net positive inter-lift-horizon gaseous pressure differential may thereby develop as the rising pressure in the lower liquid fluid replete pressurization reservoir 330 becomes less and less opposed by the gaseous pressurization control fluid pressure (in process of evacuation to an alternate pressurization 330 reservoir thereat said upper lift-horizon) at said upper lift-horizon, yet in the absence of sufficient net positive gaseous pressurization control fluid differential pressure to exceed the head pressure in the liquid fluid lift-leg between liquid fluid surfaces of said successive lift- horizon pressurization reservoir(s) 330, no incumbent liquid fluid flow shall develop. Continued transfer and ingress of intra-lift-horizon gaseous pressurization control fluid there-into first liquid fluid replete pressurization reservoir 330 (in combination with the identical process at the successive upper elevation lift-horizon inversely depressurizing the pressurization reservoir 330 there-in-liquid-fluid-communication with said first liquid fluid replete pressurization reservoir 330) increasing the relative application of positive inter-lift-horizon pressure differential through and beyond that magnitude required to exceed the sum of the effective liquid fluid head pressure, check valve cracking pressure (or opening pressure requirement) and liquid fluid lift-leg conduit frictional losses shall in due course cause said liquid fluid check valve to open and upward flow to commence slowly at first, and with greater and greater positive pressure differentials, faster flow-rates thereto the upper elevation lift-horizon shall be caused and in due course causing the decided volume of liquid fluid to be transferred to said upper elevation lift horizon. While it may be accurately pointed out that the head pressure between said upper and lower liquid fluid level interfaces shall increase throughout the cross-pressurization process, the utilization of horizontally lain pressurization reservoir(s) of greater horizontal dimension than vertical shall cooperate with embodiments of the system to limit the negatively imposing head pressure rise throughout the process (as compared with reservoir(s) of similar volume having proportionally greater vertical height dimensions). Regardless of said head pressure rise, the differential pressure rise through latter stages of the cross-pressurization process may be anticipated to be of significantly greater magnitude than the observed head pressure rise, and duly increasing flow velocity to elevation with time may also be anticipated, which depending upon the form of pressurization reservoir utilized, wherein for example the variable cross sectional area of horizontally-lain circular cylindrical or other reservoir forms with height may result in a varying rate of liquid fluid level increase in said pressurization reservoir 330 at said upper elevation lift-horizon which need be considered in cases where the decided control strategy may include conditional interlocks based upon rates of change of liquid fluid level with pressure and or time (since the diminishing rate of change (increase) of level as the wide midpoint of a cylindrical reservoir is reached may be construed by a data-aware application as a system leak scenario). As the pressure in second liquid fluid receiving pressurization reservoir 330 at the lower elevation declines through continued concomitant VCM 2000 cross-pressurization of gaseous fluid into the co-lift-horizon-resident presently liquid fluid sourcing pressurization reservoir 330, the discharge pressure attainable by VCM 2000 may at some point peak and the pressure differential availed there-between said first and second pressurization reservoir(s) 330 shall largely concurrently peak also. However, it is anticipated that in successfully operating system embodiments, that in order to provide a serviceable overall liquid fluid throughput flow to elevation, that the base-load pressure of gaseous pressurization control fluid provided (ie: the nominal equalized pre-loaded pressure in each pressurization reservoir(s) 330 irrespective of evacuation and compression capacities offered by VCM 2000) shall be at least equal to the head pressure in liquid fluid lift-legs, and may preferably be multiples of same which under fully realized maximum differential pressures may reach the pressure rating of the utilized conduits and reservoirs. Pre-loaded thus therefore capable of a achieving a maximum VCM 2000 differential pressure(s) which may significantly exceed the head pressure of said liquid fluid lift-leg(s) to elevation with a given VCM 2000 configuration, said upper elevation pressurization reservoir 330 may thereby be brought to be full of liquid fluid in advance of the VCM(s) 2000 evacuation and compression capacities bringing the inter- lift-horizon pressure differential to the maximum, which may permit the system to change and rotate respective valve states (to begin the pressure equalization event) as the liquid fluid level is rising at said upper elevation, whereby substantial pressure equalization may be controlled to occur as the liquid fluid level at elevation reaches the replete designation level as demarcated by level switch LSH 1933 or level transmitter LIT 1930 (whereby it may be stated that the system may generate energy - through said pressure equalization event and turbine 200 operation thereby - as liquid fluid is conducted to elevation under the impetus of a positive differential pressure while the prime mover of the system (motor 265 driving VCM 2000 are de- energized). When once the pressure equalization period is completed as determined by said high LSH 1933 and or low LSL 1934 level switch(es) or analog transmitter process value compared against a set-point, or alternately upon a pressure set-point in relation to the current process (pressure) value provided by pressure transmitter 1989, the system may command the subsequent cross-pressurization event to begin. As may now be evident the properly sequenced system may cause the realization of substantial pressure equalization to coincide with the maximum liquid fluid level realization in said upper elevation pressurization reservoir(s) by utilizing the pressure equalization event to substantially stop the flow of liquid fluid to elevation while concurrently preparing the system for the subsequent cross-pressurization operation to substantially minimize the system' s cycle time constant.

[00114] The present invention embodiment may also contemplate the employment of liquid fluid energy recovery disc turbines which while imposing a degree of added backpressure (flow opposition) during liquid fluid conduction to elevation may in any case help to reduce the net energy consumption expended to operate the system wherein anticipated flow-rates of liquid fluid to elevation may provide laminar liquid fluid flows for energy extraction purposes.

[00115] In similar fashion to the previous embodiment, the present embodiment of the gaseous-liquid fluidic lift system utilizes differential pressurization as its means of liquid fluid transport to elevation and in well balanced systems with no leaks may operate successfully in the absence of real-time interface with the atmospheric medium pressure, it will be understood, however, that with the inclusion of further appropriately placed valve means (which may in any event be required to provide the initial fill surplus of gaseous pressurization control fluid charge to pressurization reservoirs at respective lift-horizons) capable of communicating a requisite throughput of atmospheric pressure gaseous fluid (air) to the second stage axial compression inlet of VCM 2000 or alternately into the primary stage with an alternate ingress to the primary compression inlet while the liquid fluid receiving pressurization reservoir may be isolated concurrently as by the inclusion of isolation valve means in low pressure conduit(s) 1984 or alternately with further port(s) connection(s) in as well as there-to rotating valve means 1966 concurrently while isolating both pressurization reservoirs once a sufficiently low pressure has been achieved in the liquid fluid receiving pressurization reservoir at run-time, that the atmospheric medium may then (isolated from said liquid fluid receiving reservoir) permit the extended supply of high pressure gaseous pressurization control fluid into the liquid fluid sourcing pressurization reservoir and thereby continue to increase the gaseous pressure there-within as well as cause the more rapid and or the more voluminous lift of liquid fluids to elevation thereby, even as the liquid fluid differential pressure exercised by respective lift-leg(s) becomes comparatively adverse with the liquid fluid level rising in upper pressurization reservoir(s) and concomitantly becoming lower in lower pressurization reservoir(s), and meanwhile the gaseous pressurization control fluid may be further depleted in the lower pressure liquid fluid receiving pressurization reservoir via continued admission into the primary VCM 2000 stage. As discussed such access to the atmospheric medium may then significantly advantage system performance should a nuisance leak develop in a system conduit or pressurization reservoir that is not readily rectifiable, or which functionality may be required over time to replenish the mass of gaseous pressurization control fluid escaping respective lift-horizon(s) via dissolution into the liquid fluid proportionate to temperature and other factors discussed.

[00116] With reference now to Figure Ij, an alternate embodiment of the gaseous liquid fluidic lift (GASLIFT) system (with power generation) is shown in which VCM 2000 provided at each lower elevation lift station 1890 are operated so as to alternately effect the evacuation of gaseous fluids from one vacuum-and-pressure-compatible capacity 330 (or, reservoir 330 for brevity) while concurrently charging said gaseous fluid medium(s) into the adjacent (or a nearby) reservoir 330 (through upper elevation gaseous communication ports thereof) - to thereby effectively fill or replenish the evacuating reservoir 330 through a lower elevation port thereof with liquid fluid discharging from power generation turbine 200 liquid fluid collection reservoir 1889 while at the same time pressurizing said adjacent (or nearby) reservoir 330 with higher pressure gaseous fluid through an upper port to expel pre-loaded liquid fluid there-from through a lower elevation liquid fluid discharge connection and valve or check valve communicating with said reservoir 330. With a differential pressure expressed across the leg of liquid fluid extending to elevation through conduit 1946, which differential pressure may be increased via communication of the top surface of said liquid fluid leg (liquid column) with a lower pressure or sub-atmospheric pressure contained within a further pressure-and-vacuum-compatible reservoir 330 expressed above the liquid fluid surface in an upper elevation liquid fluid drop station 1891, a suitable said differential pressure may thereby be applied so as to significantly exceed the gravitationally applied liquid fluid head pressure acting in opposition to said differential pressure (which is greater at the lower elevation and lesser at the upper elevation) so that the liquid fluid contained within said lower elevation lift station reservoir 330 by nature of only being provided one path of egress there-from said reservoir 330, is therefore induced to enter into conduit 1946 and be raised to elevation until halted by the diminution of said gaseous differential pressure which may be caused by the programmed or timed or otherwise triggered reversal of lift station reservoir-330s-respective pressures in preparation for the similar raising of the alternate reservoir 330' s liquid fluid to elevation when the liquid level in said first reservoir 330 (discharging liquid fluid) nears the top of said discharge outlet (whereupon the pressure in said reservoir 330 must be decreased to below the head pressure extending to elevation so as to prevent the greatly less dense gaseous medium from finding egress from said reservoir 330 into conduit 1946, which may eventually migrate upward through said conduit 1946 and produce some degree of backpressure to the liquid fluid lifting operation in proportion to said leakage of gaseous It should be realized that while earlier embodiments of the GASLIFT system have been illustrated as operating under atmospheric pressure where gravitationally sourced gaseous fluid pressures ever available for application as the higher system pressure and which atmospheric pressure sets an imposed limit on the height of respective lift- legs to that height (of said lift leg) relating to a liquid fluid head pressure less than the atmospheric pressure which shall permit an acceptable upward migration of liquid fluid through (the necessarily) larger diameter conduit means 1946 and valve means to elevation. By contrast, in system embodiments such as the one presented in Figure Ij wherein the higher system pressure utilized as the system pressure applied to the liquid fluid interface surface of lower elevation reservoir 330s' (ie: applied so as to drive liquid fluid upward) may be largely provided by captive volumes of pressurized fluid shunted and driven by VCM 2000s between chambers, it may therefore be understood that since Tesla type turbo-compressors may provide both extreme pressure and ultra-high vacuum, that the height of respective lift- legs 1892 may therefore be greatly increased beyond that possible with atmospherically driven lift-leg operations.

[00117] Since as previously described, the principle of operation of embodiments of embodiments of the GASLIFT system - including the captive-pressure system presently described in which greater pressure differentials than those of atmospheric pressure are availed - requires that the higher gaseous system pressure applied to the liquid fluid interface surface at the lower elevation of respective lift-leg(s) 1892 be maintained substantially captive thereat the lower elevation (ie: in reservoirs 330), it is therefore evident that the greater is the higher system pressure reference (and consequently the gaseous differential pressure availed to be applied as a liquid fluid lifting motivator) the higher is the effective height of lift legs through which liquid fluid flow may be driven by such systems and similarly may the velocity and or volumetric flow-rate of the system be configured to greater magnitudes. While ultimately limited by the angular velocity and other parameters of VCM 2000s creating and sustaining enhanced differential pressures for application, the system's greatest lift leg height may out of cost consideration or practicality be decided by the pressure safety rating of components utilized throughout the system, the cost factor of which may markedly increase with greater pressure ratings there-for.

[00118] In demonstration that the system is not physically limited in principle by the employment of high system pressure (and therefore high or extreme differential pressures and lift leg heights of operation), an analysis of the density of the gaseous fluid medium employed in such systems is requisite. At a gaseous fluid operating temperature of 140 ⁰ F as an example, the density of air is about 4.6 Ibs/ft3 at 1000 PSI, so it is apparent that the use of air as the gaseous fluid medium (even at pressures well in excess of anticipated system operation pressures) would be physically possible in such systems since even at extreme pressure, the low density of air in comparison to that of the liquid fluid (ie: water with a density of nominally 1000kg/m3) would cause it to remain on top of the liquid-air interfaces of the system and would thereby satisfy the system requirement of gaseous fluid captivity.

[00119] Since Tesla type disc compression means may provide discharge pressures greatly exceeding the pressure rating of water transmission conduit systems in operation today wherein pressures may be typically less than 150 psig, the present system methods may therefore be adapted to existing water transmission systems, forwardly looking, to reduce energy consumption and provide power cogeneration as a by-product of system operation. While not physically limited to present day water transmission pressures, with stronger vessel pressure ratings in preferably larger diameter reservoirs 330 and conduit means 1946, the presently described system may be applied to very large lift legs and or much larger flow-rates of liquid fluids to elevation than currently practical with traditional liquid fluid pumps required to directly push liquid fluids in opposition to the force of gravity and act against the density and therefore inertia of the liquid fluid, and also act at a disadvantage inhibited in pumping action by the comparatively great viscosity of said liquid fluids.

[00120] In cooperation with advantageous features of the GASLIFT system proposed in other embodiments of the system, the presently described embodiment furnishes further appurtenances to the VCM (VCM) 2000 wherein housings are equipped with port selection means capable of routing the communication of high, medium and vacuum/low pressures of the system to the appropriate stages of VCM 2000s whereby the conservation of higher pressures as well as the maintenance of vacuum/low pressures may be maintained where required via routing of the respective pressure potentials of the various stages of VCM 2000 to effect or assist in cooperatively producing the differential gaseous fluid pressurizations required with a minimum of energy losses. For example, the rotary cylindrical valve and operator 1966 illustrated in respect to Figure Ii may also be employed in the presently discussed system as well with an alternate valve- cylinder having various possible opening configurations which may further provide triangular or other opening leading edges which may assist in minimizing shock in the system to prolong component service life. Said valve operator upon rotation may synchronize particular pressure levels of reservoir(s) 330 under various states of compression or decompression with appropriate pressure stage of VCM 2000 compression. Adjustable disc spacing mechanisms previously discussed may be automatically controlled based upon angular rotor velocity and run-time inlet fluid pressure and temperature (and viscosity) conditions to provide enhanced utility in generating differential gaseous fluid pressures most efficaciously.

[00121] For example, the timing or sequencing device discussed in conjunction with a rotary cylindrical valve actuator may schedule evacuation and concurrent compression system events to cooperatively program said actions with a controller whereby largely continuous liquid fluidic lift may be provided in cooperation with the alternating pressurization and evacuation of pressure compatible capacities 330 at different elevations' lift 1890 and drop 1891 stations discussed. Through the controlled rotation or axial alignment of one or more of such valve-action cylinders (or a similar event- schedule effected with more-traditional valves), alignment of the high pressure port of said cylinder into communication with the VCM 2000 discharge (ie: to pressurize one capacity 330), and either concurrently, gradually, or sequentially align one (or more) low/vacuum pressure port(s) of said VCM 2000 compression intake(s) with fluid conduits communicating with alternate reservoir(s) 330 (ie: to evacuate same), and or alternate vacuum loads as indicated at right in Figure Ik, wherein an active-evacuation building envelope shell system (to be described subsequently) is shown connected to the present system via vacuum isolation valve 1986.

[00122] While the fundamental operation of the GASLIFT systems has been previously described, it may be stated that the presently illustrated system may be adapted for community power generation purposes valid where local topography provides useful elevation drops capable of supporting the weight of the fully loaded (with liquid fluid) system and providing sufficient height of liquid fluid head with which to develop a satisfactory supply of hydroelectric power with. It is evident upon inspection of the system that substantially the entire conduit and pressure compatible capacity elements of the majority of the system may be provided without an above-ground 'footprint' as by the utilization of existing mine shafts and drift voids of preferably mined-out ore-bodies. The large power distribution facilities, services networks and underground workings availed by mining operations contemplated for use by GASLIFT systems may greatly extend the usefulness and minimize the overall ecologic footprint of underground mining and may thereby provide extended value to mining developments as down- stream power generation facilities, especially where good ground control practices have been employed to ensure the longevity of the tunnel / void system networks provided, which may provide very wide diameter, screened and concrete walled tunnel systems in igneous or metamorphosed rock formations of significant stability which may provide excellent high-pressure containment cavities capable of withstanding extremely high system gaseous reference pressures of service without incurring a high cost for containment vessels since the mining operations have typically already calculated and incurred said development costs for safe mine operation, thereby providing a means to minimize the cost and ecologic footprint of GASLIFT power conversion / generation systems. In further contemplation of factoring in downstream cost recovery which may be availed by GASLIFT power generation systems, in some instances more costly, however, safer or less environmentally detrimental mining methods may be pursued as a means to concurrently produce the parallel or proximate drifts (reservoirs 330) at the same elevation required by GASLIFT systems for concurrent operation while mining operations may minimize tailings on surface by following higher grades of ore at depth with a more selective mining practice performed so as to cooperatively furnish said pressure compatible capacities 330 (cavities) required by GASLIFT systems.

[00123] The system is shown with independent liquid lift conduits 1946 between lower elevation lift-stations 1890 and upper drop-station 1891 horizontally lain elongate reservoir(s) 330, and a common liquid fluid descent conduit 1899 which may be fitted with vortical flow inducing elements as well as air induction ports further discussed in respect to elements 315 of Figure 2a to minimize the effect of boundary layer drag on the descending liquid fluid at the descent conduit wall whereby said descending liquid fluid may reach significant velocity en-route to turbine 200 at length driven by said liquid fluid flow for power conversion purposes.

[00124] In general, the system must be designed to provide on average an equivalent liquid fluid up-lift flow through conduit(s) 1946 to match the volume of descending liquid fluid flow through descent conduit 1899 required for power generation purposes, and accordingly, the system's differential pressure configured for the uplift of liquid fluid must be such that after de-rating the realized maximum flow-rates achieved for process lag times due to requisite gaseous pressure reversals discussed, that the maintainable average system up-lift flow-rate achievable may equal or preferably significantly exceed said required liquid fluid flow-rate to satisfy the power generation requirement so that peak loads may be accommodated by the system preferably designed for excessive load.

[00125] Although the task of VCM 2000s to cyclically reverse the application of gaseous pressurization control fluid pressures (expressed upon the liquid fluid surfaces of lower elevation lift-stations 1890 reservoirs 330) may cause the system up-lift flow through lift-leg 1892 conduits 1946 to lag the incessantly descending power generation working fluid flow 9 for brief periods of time during said pressure reversal periods (said pressure reversal period representing the cyclic lower elevation high to sustained low gaseous pressure transitions required to fill liquid fluid depleted reservoirs with liquid fluid, and the low to sustained high pressure transitions required to pump the liquid fluid from liquid fluid replete reservoirs 330 to elevation) thereby causing a slow-down in the instantaneous volume of liquid fluid moved through lift-leg(s) 1892 to upper elevation drop-station 1891 reservoir(s) 330 generally configured in operation to be under gaseous evacuation when receiving liquid fluid through an open inlet check valve 290 (and conversely configured to release liquid fluid for power generation purposes when placed under atmospheric or another pressure reference while turbine 200' s working fluid supply valve 1956 is open), the aforementioned delay or process lag is not an inhibitor to successful GASLIFT system operation, since the gaseous pressurization control fluid pressures applied in said upper elevation drop-stations 1891 (whether atmospheric pressure or another low pressure is configured (ie: another pressure dramatically less than that of the gaseous pressurization control fluid captive and transferred between lower elevation reservoirs 330 to more-freely permit the release of liquid fluid from drop-station 1891 reservoir(s) 330 while under some pressure, said gaseous fluid pressure cooperating to increase the differential pressure across the power generation turbine) said gaseous pressurization control fluid pressures applied to the upper liquid fluid interface surface of lift-leg(s) 1892 may be configured to be largely always significantly or greatly less than the captive high pressure gaseous pressurization control fluid pressure at lower elevation lift station(s) 1890 thereby ensuring that a high enough pressure (in the form of said captive mass of gaseous pressurization control fluid) is always present and available to be applied to the lower elevation liquid fluid interface surfaces of lift-leg(s) 1892 (ie: without needing to develop said fluid motivating pressure at the time of liquid fluid 'pumping', which in prior art systems requires the expenditure of large amounts of energy every time liquid fluids are to be pumped owing disadvantages already outlined there-with said prior art) so that in the presently disclosed method, there is in effect substantially always sufficient pressure energy placed on reserve (as by the capture of said pressure energy within said lower elevation pressurization reservoirs 330) which then need only be allowed into communication with the liquid fluid interface surface of a liquid fluid replete reservoir 330 to begin the GASLIFT of liquid fluids through lift-leg 1892 to elevation.

[00126] Since said captive lower elevation pressure energy (re-distributed during each lift-cycle by VCM 2000s as discussed) once delivered is not destroyed or significantly lost in system operation, but remains ready in captivity in close proximity to its subsequent application destination (ie: the adjacent or nearby reservoir 330 where-into VCM 2000 configured by way of valve or valve-action means may rapidly deliver said gaseous pressurization control fluid) it is therefore evident that upon execution of gaseous pressure equalization event (which may alternately be designed to occur through a sufficiently large capacity shunt-conduit to control gaseous fluid entry velocities into the alternate reservoir, or may alternately be configured to enter the alternate reservoir by way of a work conversion turbine configured for compressed gaseous working fluid - not illustrated in the figure - where-after said pressure equalization event, VCM 2000 compression discharge and evacuation inlet port communications may be reversed to redirect the vacuum and compression potentials of VCM 2000 as by valve or cylindrical valve-action means which may be axially or rotationally driven as discussed, after which time a rapid transfer of gaseous pressurization control fluid may be effected into the alternate reservoir 330, or alternately into an intermediary gaseous pressure transfer reservoir not shown whereby or where-through a rapid application of the captive high pressure gaseous pressurization control fluid may be continuously applied to the volume above the liquid fluid interface surface of the counterpart reservoir 330, which in either case, properly sequenced, although said high system reference pressure may be slightly diminished in intensity initially owing the initially increasing volume into which said gaseous pressure is transferred, as soon as the gaseous differential pressure expressed across lower and upper lift leg 1892 liquid fluid interface surfaces exceeds the total resistance to the upward migration of liquid fluid, that the liquid fluid in said liquid fluid up-lift conduit 1946 shall begin to flow, and shall continue to flow through the period in which VCM 2000 and the given system's control strategy maintains an excessive differential pressure across the liquid fluid column extending to elevation, which it may do by transferring to near exhaustion the greatest part of the gaseous fluid mass into said counterpart reservoir whereupon said captive pressure remains available for its subsequent iteration of remunerative re-use.

[00127] While the upward resistance to flow in the system is largely comprised of: the liquid fluid head pressure imposed by the Earth or other system-hosting celestial body's gravitational acceleration through its attraction of the relatively dense liquid fluid toward said celestial body's centre of mass, and; pipe wall friction - which friction may be minimized through the employment of large diameter conduits to form lift-leg 1892 conduits 1946, and; check valve 290 opening resistance (ie: cracking pressure), and; other valve pressure drops if employed and or other intermediary conduit means pressure loss(es), and; further pressure loss which may be imposed across auxiliary upward-flow liquid fluid power turbine means which may further increase the energy conversion of the system should a sufficiently high pressure be accommodated by system design, it may be stated that further resistance, if temporary in nature, may be imposed during drop-station 1891 reservoir 330s gaseous control pressure reversals during which period of time a back-pressure shall be placed upon liquid fluid up-lift through lift-leg(s) 1892 prior to the evacuation of gaseous medium there-from the liquid fluid receiving reservoir(s).

[00128] Although the aforementioned resistances may represent substantial physical limitation and continuous power drain upon prior art liquid fluid pumping systems tasked with the displacement of large volumes of liquid fluids to elevation owing disadvantages already discussed with said prior art methods, by contrast, the design of GASLIFT systems permits the remunerative use of captivated volumes of high pressure gaseous control fluid to drive liquid fluid to a position of rest at lower pressure which by design is configured to be at extendedly higher elevation. Conveniently, said gaseous control fluid pressures may greatly exceed the required high pressure component of the lift- leg differential pressure required to cause the rapid flow of liquid fluid to elevation, and which high pressure gaseous control fluid once created may remain substantially indefinitely available for repetitive communication between one vacuum and pressure compatible pressurization reservoir 330 and its adjacent or proximate counterpart - and while in the absence of an 'air barrier' quantities of said gaseous control fluid may be dissolved into the liquid fluid at a greater rate with higher temperatures, GASLIFT systems may further be equipped with full surface area lightweight floating membranes, bladders or bellows-like sub-systems designed to rest on top of the liquid fluid interface surface and conform to the cross-sectional profile of given pressurization reservoir 330 profiles so that by isolating the liquid fluid from the gaseous pressurization control fluid, said liquid fluid may be insulated from temperature increase owing the effects of the repetitive singular-stroke reservoir-to-reservoir 330 gaseous fluid transfer cycle of the method, and meanwhile said segregation of gaseous and liquid fluids by said floating insulating membrane (or other functionally equivalent sub-system, not shown in the figure) may also prevent the mass loss of said gaseous pressurization control fluid into the liquid fluid which over time may otherwise result in potentially significant pressure loss, thereby ensuring longevity of pressurization control fluid service. In systems not employing such air barrier means, or where pressure loss may occur owing leaks in the system, replenishment of the gaseous pressurization control fluid to make up for said losses may be provided by the opening of an atmospheric pressure ingress valve (not indicated) which may directly communicate atmospheric or another similarly pressurized or alternately an highly pressurized gaseous medium into an appropriate stage of VCM 2000 to be further elevated in pressure if required and directed to the appropriate reservoir largely without interruption of system operation.

[00129] Understanding that GASLIFT systems may trap high pressure gaseous pressurization control fluid substantially indefinitely within the system and that through the simple action of transferring said highly compressed medium from one reservoir 330 to another (which a large capacity Tesla type disc runner - configured with compressor / pump type inlets for minimized fluidic shock in operation - may do very effectively) the system may thereby manipulate stored energy reserves with a limited requirement for new energy expenditure in order to enable it to move requisite volumes of liquid fluid to elevation without need of developing new pressure energy by which to effect said lift of liquid fluid. Since the gaseous pressurization control fluid medium's captive high pressure and large volume may greatly exceed not only the high pressure component of the differential pressure required for said large-volume liquid fluid uplift(s), but also greatly exceed the backpressure caused at elevation by short-period drop-station 1891 pressure reversals discussed already (applying a cooperating pressure to the upper surface of lift-leg(s) 1892 to facilitate fluid up-lift operations), it should be further understood that the backpressure of atmospheric or other alternately moderated pressures at said upper elevation drop-station 1891 reservoirs 330 may present only a minimally inhibiting effect upon the systems fluidic lift operation, so that whether the system is operated as shown with drop-station 1891s (sequencing the alternating application of pressurized and rarefied pressures thereat to serviceably decrease the back-pressure on the liquid fluid uplift operations and concurrently augment the differential pressure across turbine 200), or whether said drop-stations 1891 are completely removed from the system in favour of either a pumped storage system at elevation under atmospheric pressure where-into said liquid fluid up-lifted through lift- leg 1892 conduit 1946 may be delivered and remuneratively re-delivered for later utilization, for example during peak load periods, it may then be understood that whether a pumped storage system at elevation is employed at atmospheric pressure, or whether the illustrated system is provided with back-pressure to overcome owing said pressure reversal events, that said back-pressure may be configured through system design to substantially only reduce the upward flow of liquid fluid to elevation, and not halt said flow beyond the halted period of upward liquid fluid flow owing lift- station 1890s gaseous pressurization control fluid pressure reversal, which as discussed, may be brief. With upper elevation drop-station 1891 reservoir(s) 330 operated between atmospheric pressure and sub-atmospheric (ie: vacuum) pressures, as may be provided with a system of cooperating valves 1896 and 1986 generally embodied at upper right in the figure which may in practice be preferably located directly adjacent VCM 2000 and reservoirs 330 to directly communicate VCM 2000 expelled gaseous medium to atmosphere or alternately add pressure to a particular pressurization reservoir 330 as required through conduit means extending thereto (during liquid fluid reception process) and alternate atmospheric ingress valve(s) communicating atmospheric pressure thereinto reservoir(s) 330 may in various embodiments be closed following drop-station 1891 liquid fluid sourcing (to turbine 200)and thereby cooperate to minimize the overall resistance to the upward liquid fluid flow as well as provide a minimized resistance to the downward flow (fall) of liquid fluid into turbine 200, or in alternate embodiments with higher pressure operation in drop-station 1891 reservoir(s) 330, pressurization of said turbine liquid working fluid may significantly add to the differential pressure across turbine 200 to enhance work generation thereby.

[00130] At the lower left lift-station 1890-A/B in the figure no liquid fluid is entering either of horizontally elongate reservoirs 330-A or B owing the orientation of liquid fluid check valves 291 forced unto closure at the inlets thereof due to both reservoirs' present containment of gaseous pressurization control fluid medium at captive pressures considerably in excess of the pressure applied by liquid fluid exhausting from power generation turbine 200 and collected in liquid fluid collection reservoir 1889 and at length communicated thereto said check valve 291 port(s) to await entry and conveyance to elevation.

[00131] Counterpart lift-station 1890-E/F's reservoir 330-F at lower right in the figure, by contrast, is shown to be actively receiving liquid fluid through permissive liquid fluid check valve 290 post exhaustion of the greater mass of gaseous pressurization control fluid there-from said reservoir 330-F (by VCM 2000 receiving said gaseous fluid at its axial intake and centrifugally accelerating same unto discharge there-from) and having been depressurized unto a remnant gaseous pressure therein expressing less pressure than the total pressure applied by the liquid fluid discharge of turbine 200 communicated to the external port of said check valve(s) by way of an extension of collection reservoir 1889, liquid fluid is therefore drawn into said reservoir through low cracking pressure check valve 290. While exhaustion of the larger part of said gaseous pressurization control fluid is required to receive liquid fluid into given lift-station 1890 reservoirs 330, the flexibility of system design allows said fluid to be concurrently moved into counterpart reservoir 330-E or alternately into an interstitial gaseous fluid pressurization reservoir 330 - not shown - serving as a pressure buffer capacity to permit VCM 2000s to readily exhaust gaseous pressurization control fluid from one reservoir 330 while concurrently permitting a high throughput of said gaseous fluid into said alternate reservoir or both said alternate reservoir as well as reservoir 330-E as through a further port communicating high pressure gaseous fluid there-from) so that while said pressurization reservoir (330-F in the discussion) may imminently realize a sufficiently low control fluid pressure above the liquid fluid interface surface therein to permit its reception of liquid fluid, while at the same time high pressure gaseous control fluid pressure may be rapidly stored as well as applied to the liquid fluid interface surface of reservoir 330-E to permit it to begin sourcing liquid fluid to elevation as quickly as possible in cooperation with a significantly lower pressure expressed above and upon the liquid fluid interface surface in pressurization reservoir 330-B of drop-station 1891-A/B to assist in the development and sustaining (in further cooperation with VCM 2000) of the required pressure differential to effect the lift of substantially a pressurization reservoir 330' s volume of liquid fluid to elevation. [00132] The specification of a workable design-mass of captive gaseous pressurization control fluid capable of serving as the high pressure reference for gaseous fluid distribution operations in lower elevation lift-station 1890 may be based upon information including but not limited to: pressure vessel safety ratings by which to set ultimate pressure safety limits on the system; the power turbine 200' s liquid fluid throughput and head pressure requirements; work generation means conversion efficiency at the rated power output (said work generation means generically indicated by stator core(s) 270 adjacent power turbine 200, however, which work generation means may take the form of another variety of coaxially rotating work conversion outputs already discussed); the pressure differential required to cause at least the design volume of liquid fluid to be lifted at a cooperating average flow-rate to elevation so as to match said turbine through-put requirement while overcoming system pressure losses including those due to said head rise at the maximum height of the variable-height liquid fluid column represented by lift-leg 1892 and other head losses incurred by various valves utilized throughout the system herein stated to be preferred as full port valves; application of the Darcy-Weisbach equation (Equation 6) to formulate pressure loss information and cooperate to derive appropriate pipe dimensions (diameter), type and or characteristics to satisfy the decided upon system flow-rate; application of Charle's law (Equation 7 PV=nRT) to derive the base charge (mass) of gaseous pressurization control fluid required to provide substantially one pressurization reservoir 330 volume at preferred design pressures (to supply the correct high pressure component of the differential pressure required to drive upward liquid fluid flow to elevation); upper elevation drop-station 1891 (if employed) pressurization reservoirs pressures of operation as these shall affect the differential pressure achieved at run-time across the liquid fluid column (ie: lift leg 1892) to elevation, and or local barometric base pressure and nominal variability thereof also affecting the differential pressure across the lift-leg 1892 to elevation; liquid fluid density as this may dramatically affect the requisite differential pressure required to drive said liquid fluid to elevation, and; forwardly looking to extra-terrestrial applications of such GASLIFT systems where the ambient atmospheric pressure and available gaseous medium for utilization as the gaseous pressurization control fluid as well as the liquid fluid density available and both of these fluids' viscosities and temperatures of intended operation must all be considered, as must the local gravitational acceleration greatly influencing the differential gaseous fluid pressure required to effect the lift of the requisite quantity of the available species of liquid fluid employed in such systems.

[00133] It is an important consideration and salient feature in support of the installation and usage of GASLIFT systems for both retro-fit as well as new installations in water treatment or hydroelectric power generation facilities or in largely any commercial, industrial or other process in which high volumes of liquid fluid must be pumped owing the substantially cavitation-free operation offered by the liquid fluid motivation means, VCM 2000, and methodology employed. While it has been stated that GASLIFT systems may be configured to operate over a wide range of pressures, extension of this capability unto applicability in effect means that GASLIFT systems may therefore be configured to substantially match the operating characteristics of many or largely any process and thereby provide energy savings vs. prior art pumping systems, and it may be stated that with the further configuration of additional automatic control means to provide proportional, integral and derivative control responses where required, that with appropriate placement of liquid fluid control valve means and or gaseous fluid pressure regulation means and actuators and feedback control loops effecting their control, that the pressure variances of operation (anticipated in the basic system presented in the figure as stated in respect to pressure reversal events) may be largely smoothed out to thereby provide substantially steady state flows in operation.

[00134] Advantage over present day liquid fluid pumping means is provided via the fast time constant of application of largely the full captive pre-pressurized gaseous pressurization control fluid pressure (for example upon pressure reversals in between lift-station 1890 pressurization reservoirs 330) as by VCM 2000s rapid transfer of said pre-pressurized gaseous control fluid to the adjacent pressurization reservoir 330' s extremely large working surface area represented by the entire liquid fluid interface surface area of reservoirs 330) which understandably may vastly exceed the working surface area of any known prior art pumping system limited to the liquid-contacting surface area of its impeller and limited further by disadvantages already discussed. While it is known that liquid fluid pumps are limited by the cavitation of liquid fluid into vapour causing prior art pumps to be significantly limited in efficiencies at higher rotational velocities, the presently described system offers a means to utilize turbo machines operating in the gaseous fluid medium environment to great advantage to completely avoid the efficiency and throughput limiting effect of cavitation and thereby dramatically increase the 'pumping' action thus obtainable, as by the utilization of Tesla type turbo-compressors and turbo-vacuum pumps (or which in other system embodiments may comprise axial flow turbo compressors or vacuum pumps of the bladed variety preferably offering as large a working surface area and as high an angular velocity specification as possible). Said VCM 2000s comprised of turbo machines operating at very high angular velocity, or alternately comprising very large disc diameter runner(s) or multi-stage runner(s) so as to provide serviceably high peripheral velocity of operation in combination with large area axial inlet(s) to permit high-volume throughput through one or more runner(s) at a more moderate rotational velocity. Thus, with cavitation-free liquid fluid pumping provided for - the system is enabled to perform work upon the liquid fluid to move said fluid to significant elevation in single lifts (or alternately to extended distance) as implied by the current configuration, or may alternately be configured for multiple lift operation as discussed in respect to previous embodiments of Figure 1.

[00135] While intelligently sequenced, GASLIFT systems may be designed to apply a pressure of gaseous pressurization control fluid configured to moderately exceed the combination of total upward flow resistances previously discussed to permit a moderated average flow of liquid fluid to elevation which may suffice for smaller communities' water storage systems or other processes, it is instructive to note that since GASLIFT systems may (with higher pressure rating) captivate and apply two (or more) times the pressure differential required to rapidly drive the required volume of liquid fluid to elevation (to satisfy the volume of liquid fluid required by particular applications), it is clear that given pressurization reservoir(s) 330 capable of safely containing a high volume of fluids at required pressures of operation discussed, that with or without the alternate inclusion of auxiliary buffer reservoir(s) 330 (not shown, but which may in combination with isolation valves and pressure regulation means, or alternately in combination with said previously mentioned array of varied pressure rating check valve(s) provide alternate egress to reservoir(s) of varied pressure with may take part in subsequent pressure equalization and reversal operations through said same means provided a control system capable of sequencing the process effectively to cooperate with said actions and means) it is evident that the system may in any case be capable of applying sufficient gaseous pressurization control fluid in conjunction with VCM 2000 vacuum and compression potentials to achieve serviceable system operation under various heights of lift-leg(s) 1892 to elevation.

[00136] As previously indicated, VCM 2000s may preferably be equipped with a dynamic disc spacing system in order to provide further benefit to the system by limiting the disc gap in a particular 'compression' - centrifugal acceleration - stages so that as the gaseous fluid in particular pressurization reservoir(s) 330 becomes significantly pressurized or de-pressurized as the case may be (or both, in the case of direct transfers from one to another reservoir 330, that the automatic run-time adjustment of disc spacing made possible with the various embodiments of the dynamic disc spacing subsystem and a control system there-for may modulate the disc spacing effectively so as to preferably ideally match the working fluid conditions of intake and discharge 'containers' communicating with said VCM 2000, whereby changing viscosity, pressure and temperatures of operation in said containers may be best accommodated in conjunction with said control systems' automatic control capability which in combination with isolation vales and pressure regulation means communicating with the discharge outlet of VCM 2000, fluidic communication with one or more intermediary pressure gaseous pressurization reservoirs at various pressure benchmarks may be employed as discussed to more rapidly prepare lower elevation lift-station 1891 reservoir(s) 330 to achieve the vacuum / rarefaction pressure required to receive liquid fluid while at the same time permit full largely the full high reference pressure to be rapidly applied for purposes of liquid fluid uplift. With the further service of inlet and outlet three way valves communicating with said auxiliary pressurization reservoirs or a combination of isolation valves permitting the suction and expulsion potentials of VCM 2000 to be routed between intake(s) and outlet(s) thereof and at length transfer sufficient of said pressurization fluid at controlled pressure between liquid fluid receiving and sourcing pressurization reservoir(s) 330, a more serviceable and controllable system operation may be afforded.

[00137] While VCM 2000s at lower elevation lift stations 1890 are required to exert high pressure upon the liquid fluid interface surface in reservoir(s) 330 at that elevation in order to effect the requisite liquid fluid lift, there is less importance placed upon said same VCM 2000s to achieve and apply ultra low system pressures (in the system presented in this figure, where no subsequently lower elevation fluidic lift is required), except that the pressure in said reservoir(s) 330 at the time of their filling with liquid fluid must be at a reduced pressure compared to liquid fluid collection reservoir 1889 so that liquid fluid may be permitted to flow there-into the reservoir 330 under gaseous evacuation until replete with liquid fluid. In contrast to the high pressure discharge requirement of lift station 1890-A/B and 1890-E/F VCMs 2000 at the lower elevation of lift leg(s) 1892, the main requirement of VCM 2000s at upper elevation drop stations 1891-A/B and 1891-C/D (again, if said drop-station(s) are employed in the given system embodiment) is to provide and maintain low pressures above the liquid fluid interface surface in reservoir(s) 330 which are significantly less than the pressure applied at the lower elevation so as to cooperate to increase the pressure differential with respect to that pressure captivated and or being supplied to the liquid fluid sourcing reservoir 330 at the lower elevation lift-station so as to more effectively realize a larger or more consistent average ascending system flow through conduit 1946 to equal or exceed that of the descending flow 9 through descent conduit 1899, which may be facilitated through the use of large diameter ascent conduits and a large pressure differential between the bottom and top of lift leg(s) 1892, which as discussed, is feasible for such systems, and in practice GASLIFT systems are contemplated for use over a large range of pressures.

[00138] While check valves are illustrated at the liquid fluid inlets and outlets of the various reservoirs 330 it must be realized that while not shown to avoid clutter at the scale of the figure, that check valves or controlled isolation valve(s) in the gaseous fluid conduits communicating with said VCM 2000 are herein implied so that, for example, since liquid fluid as illustrated may be concurrently pushed into both pressurization reservoirs 330-A and 330-B of drop station 1891-A/B, that without said valve means to prevent liquid fluid from entering a port of VCM 2000, that with liquid fluid in the housing of same, the parasitic drag of liquid fluid would represent a very high load upon said VCM 2000 to the point that the efficient gaseous fluid transfers and evacuation potentials relied upon by the system may be greatly compromised. In operation therefore check valves may be provided on the discharge outlet of VCMs 2000 independently of an isolation valve satisfactorily prevent liquid fluid ingress, while conversely in respect to the suction inlet of VCMs 2000, while check valves may be utilized to guard the low/vacuum pressure potentials realized against unanticipated gaseous high pressure ingress which may cause the relocation of a certain mass of gaseous pressurization control fluid further causing an inconveniencing slow-down in the uplift of liquid fluid realized which at length may further result in delayed and or reduced power conversion, the recommended employment of preferably automated isolation valves is therefore contemplated for GASLIFT systems to prevent said possible inadvertent gaseous pressurization control fluid displacements. Also, depending on the cracking pressure of liquid fluid check valves employed in the system, it may be stated that since different control strategies with respect to lift stations 1890 and drop stations 1891 may be conceivably employed while still providing serviceable pressure differentials for operation, that in alternate system embodiments, automated valves may instead or in addition to liquid fluid check valves 290 / 291, with the understanding that a sequencing means such as may be provided by one or more programmable controller(s) employed to advantage to serve in myriad functional configurations possible for such systems.

[00139] For example, a strategy may be provided wherein drop station 1891 reservoirs 330-A/B may be filled with liquid fluid concurrently as by evacuating gaseous medium from both via their simultaneous communication with the low pressure intake of VCM 2000 of that station (which gaseous medium may be expelled to atmosphere as through a compressed air turbine coupled to a work generation means) and at a later time (assuming drop station 1891-C/D adheres to the same strategy) whence drop station 1891 reservoirs 330-A/B are replete with liquid fluid, one or more atmospheric pressure isolation valve(s, not shown) communicating with the top of said reservoir(s) 330 and also said station's power turbine liquid fluid supply valve 1956 may be opened to permit liquid fluid there-from to supply power turbine 200 to further drive work conversion/generation means (implied by the partial array of stator cores 270), while concurrently or sequentially, drop station 1891-C/D's power turbine liquid fluid isolation valve 1956 may be closed and the pressure potentials of that station's VCM 2000 be reversed to similarly evacuate said reservoirs' gaseous fluid to thereafter fill said station 1891-C/D's reservoirs 330 with liquid fluid in continuance of the cycle. In this strategy the atmospheric pressure gaseous medium admitted to reservoir(s) 330 to permit liquid fluid to fall readily through descent conduit 1899 may be augmented as by the reception of a higher pressure gaseous pressurization control fluid so as to augment the pressure differential across the falling which may thereby provide a greater differential pressure of operation across turbine 200 to drive work generation means at greater angular velocity or under a greater load. In either case, at the termination of the turbine working fluid supply reservoir' s liquid fluid sourcing period, when said gaseous pressurization control fluid must be expelled from said reservoir, the combination of valve(s) and the vacuum and gaseous compression (expulsion) potentials of VCM 2000 inlet and outlet ports may effect the required pressure inversion to effect the requisite subsequent operation ie: when evacuation of said gaseous medium is required.

[00140] While as discussed, the lift leg 1892 at left is presently engaged in the up-lift transfer of liquid fluid under the influence of a pressure differential even though VCM 2000 need not create new pressure energy to effect said lift, since said pressure energy is not destroyed and is ever present is substantially always capable of uplift of liquid fluid requiring only that VCM 2000 cooperate to direct said compressed energy to the appropriate location in a reasonable (required) period of time, it may be understood that with the system of valves discussed, that said vacuum and expulsion potentials may readily direct said compressed fluid appropriately to enable and effect the functional liquid fluid up-lift required by the system.

[00141] While no liquid fluid is entering lift-station 1890-A/B reservoirs 330-A or 330- B as discussed (hence the stationary liquid fluid indicated between reservoir 1899 and inlet liquid fluid check valves 291) since said reservoirs are in a momentary period of gaseous pressure reversal, the control strategy illustrated nevertheless permits the uplift of liquid fluid during said pressure reversal event as indicated by arrows flowing through the discharge region of said reservoirs to elevation. During the pressure reversal event, re-direction of VCM 2000 intake and outlet port potential permits the rapid exhaustion / expulsion of gaseous fluid there-from the previously liquid fluid sourcing reservoir 330 and applies said gaseous pressurization control fluid to the subsequently - or presently - liquid fluid sourcing reservoir. So whether the upper elevation drop- stations are in a state of pressure reversal (ie: alternating low and high pressures from one to the other drop station 1891 reservoirs 330) which dependent upon the instantaneous pressure in the respective reservoir 330 may result in a greater or lesser flow rate and or pressure drop across turbine 200, fluid uplift may occur here-into (while liquid turbine 200 working fluid sourcing valve 1956 is in the closed state so as to not interfere with the pressure differentials expressed thereat). Considering that the discharge of turbine 200 as shown may be placed under atmospheric pressure as by the actuation of atmospheric isolation valve 1896, or may alternately be placed at substantially a vacuum pressure as by communication of the evacuation potential of VCM 2000 by way of valve 1986 (which may alternately be provided by a pressure regulating control valve controlling reservoir 1889 pressure based upon demand load or another system parameter) to diminish/control the pressure at the turbine discharge, said discharge pressure control capability being further availed in cooperation with an extended height of discharge fluid collection reservoir 1899, altogether this results in a further capability of the presently illustrated system to accommodate peak load and load variance. Providing an effectively modulated head pressure in combination with the physical elevation drop between the liquid fluid surface in reservoir 330 "C" and turbine 200, a wide variety of load capacities may be accommodated.

[00142] Turning next to a discussion of Figure Ik, an active evacuation section of a building envelope is presented which may be considered to be portrayed in vertical or horizontal cross section. In the name of sustainability and energy efficiency, global efforts are underway to provide net zero energy consumption 'green buildings' which may provide a greatly reduced environmental footprint than comparable buildings of the current day. One of the mandates of LEED and other sustainable infrastructure mandates is that required in the domain of insulation in building. While homeowners and businesses take advantage of cost savings and incentives which improving the R- value of insulation in their respective buildings may provide, new insulations are under development which are far superior in terms of R-values provided for comparable thickness, said new insulations being engineered to provide a significant degree of vacuum therein. In general, vacuum envelope insulations have shells into which enveloped materials are placed when evacuated and sealed is capable of resisting the compressive (ie: crushing) forces applied by the atmospheric pressure gases. In use vacuum envelope insulations must be carefully installed into cavities in building envelopes so as to avoid puncture which would destroy the high R-value rating of said insulations which would then become less effective than standard insulations.

[00143] While it is anticipated that vacuum envelope insulation research shall continue and may develop robust packaging material which will not be susceptible to damage, the presently discussed figure rather discloses a means by which the vacuum capabilities of VCM 2000s featured in the discussions of Figure 1 may during extended periods of pressurization reservoir 330 evacuation cooperate with sustainable communities and building envelope design to provide a means to fantastically increase the thermal resistance (R-value) of building envelopes as by the provision of actively evacuated building envelope 'wall' segments illustrated in the presently discussed figure.

[00144] As indicated in the figure, framing elements 800 which may comprise standard framing lumber in typical use today secures rigid vacuum compatible U-channels 830 having a compressive strength permitting their exposure to pressures greater than the atmospheric compression (for safety factor purposes) while said envelope is evacuated by VCM 2000.

[00145] It is instructive to note that the large capacity evacuation potential of VCM 2000s of largely all embodiments of the present invention may provide extended evacuation potential useful to provide active evacuation potential for generic domestic or industrial use between said pressure reversals discussed, since with good seals, said evacuated building envelopes shall place no load or limited load upon said dedicated (to other tasks) VCMs 2000. In other fashion for larger community service, said evacuation potentials may be provided active evacuation potential on a continuous basis if said systems are equipped with large capacity independent VCM 2000s dedicated to active evacuation service, so that by way of appurtenances which may include (but not be limited to) vacuum isolation valve(s) 1986, vacuum draw-down check valve(s) 1894, conduit(s) 836 and connector 838 means together providing a gaseous fluid evacuation path by which gaseous fluid medium infiltrating vacuum encapsulation sheath 806 and sealing means 804 or 828 may be expelled as by further communication with the axial intake ports (ie: the vacuum pump intake - when at low pressures of operation) of VCM 2000, the building envelope segment shown in the present figure may be remuneratively drawn down to low pressure to increase the thermal resistance of said envelope segment.

[00146] A plurality of fully dressed mounting bolts 802 equipped with recessed o-ring or other type of gasket means (not indicated at the present scale, 825) forming a continuous seal between the heads and washers of said bolts while transmitting largely the full fastener force afforded via threaded engagement of said bolt 802 with structural element 830 (providing lateral vacuum containment in the envelope system) to rigid perimeter compressing vacuum seal component pressure plate 834. At largely full engagement of said bolts 802, both said fasteners' through holes through pressure plate element 834 as well as said fasteners' through hole passages through vacuum encapsulation sheath 806 are sealed since rigid pressure plate 834 forming part of the vacuum encapsulation system envelope applies largely even pressure to further o-ring type seals 835, standard neoprene type gasket sealing means 829, or a two part vacuum seal sub-system comprising a continuous rigid raised-perimeter-edge component 826 which may be comprised of one or more co-parallel triangular profile stainless steel ridges engaging a softer gasket material 827 such as copper which seal arrangement is in common use in vacuum systems, in any case in combination forming a gas barrier preventing the transmission of the atmospheric medium there-through said sequence of sealing means and thereby forming a full-perimeter vacuum seal in combination with vacuum encapsulation sheath 806 further compressing a vacuum encapsulation sheath gasket 804 or o-rings 828 or yet another set of raised-perimeter two-component sealing means 826/827 so as to form a largely complete vacuum encapsulation shell in combination with mating u-channel structural elements 830 preferably made of a rigid low-heat- conductive material which may be moulded or cast to provide a continuous lateral containment shell in combination with previously stated sealing means whereby an integral vacuum envelope is produced.

[00147] With vacuum evacuation means VCM 2000s availed by varied service applications disclosed herein, and with said evacuation means and systems cooperating therewith providing on-demand or on-schedule evacuation capacity, it is apparent that with quality vacuum seals being provided by the arrangement discussed or one providing similar functionality, that the illustrated building envelope segment and systems derived there-from may provide service in a highly evacuated state of vacuum for extended periods of time without placing any significant load on VCM 2000 means discussed.

[00148] In normal operation vacuum isolation valve 1986 may remain in the closed state for extended periods of time to most effectively isolate VCM 2000 and the processes they serve from interrupted or degraded service owing excess external load. Whether due to internal off-gassing of the selected material components or a degradation of the vacuum sealing of the system, when pressure indicating controller 1880 senses a pressure increase within the vacuum encapsulation shell, it may control vacuum isolation valve 1986 to be opened to evacuate the gaseous ingress from said building envelope shell segment or zone (and provided a data-logging system, may also be configured to flag and data-log zones frequently experiencing atmospheric ingress, for maintenance reasons). Should the pressure in said building envelope segment not drop sufficiently after a configurable time period, the system may close said vacuum isolation valve 1986 so as to prevent unnecessary load upon VCM 2000 and its primary process which may be different than building envelope evacuation, and the system or controller may further flag said zone or specific segment for immediate maintenance).

[00149] As illustrated in the figure, at least one gaseous egress hole is provided in u- channel 830 to permit off-gassing gaseous fluids and or other unwanted gaseous ingress to be actively withdrawn from the evacuated building envelope segment or zone by way of connectors 838, pipe or tube fitting 839 (which as indicated may be a tee or another fitting type including a header permitting the simultaneous evacuation of gaseous fluid from multiple evacuated building envelope segments concurrently (as indicated by secondary evacuated building envelope segment 840 also communicating through fitting 839, evacuation conduit 836 and valve means, which in simple systems may comprise one check valve per evacuated building envelope segment so as to prevent ingress in other segments from destroying the extremely high R- value of the evacuated segments, while permitting said unwanted ingress to be evacuated on demand when vacuum isolation valve 1986 or a manually operated valve (not shown) may be opened to permit communication with the axial intake of VCM 2000 means or alternately a previously evacuated auxiliary vacuum compatible container of preferably large volume and structural integrity under vacuum pressures, which while permitting unwanted gaseous fluids to move from the ingress pressure arrived at, unto the lower pressure of said auxiliary vacuum compatible capacity (not shown) and thereby return the said building envelope segment(s) or zone(s) to a significant degree of vacuum until such time as the full evacuation potential of VCM 2000 may be communicated as by further vacuum isolation valve 1986. Notably, channel 831 of u-channel structural element 830 is shown to be receiving evolving and or ingress gaseous fluids 832 at length communicated exhausted through conduit connector 838 and associated conduit and valve means previously discussed.

[00150] The materials selected for utilization in evacuated building envelope segments and systems should ideally incur zero or substantially zero off-gassing volume, should provide thermal insulation value, and should be in a form capable of safely withstanding continuous compression under the intended vacuum pressures of operation. Materials may also be selected which would provide opportune re-use such as environmentally contentious automobile, truck and large equipment tires which cannot be re-treaded, however, which may be shredded to provide a component of matrix 816 or 822 which may also comprise glass beads or spheres, dried, aged and pre-evacuated for a period of time natural materials, recyclable materials and or other materials which may be effectively prevented from internal re-distribution due to gravitational effects or building sway expressed on building structures under extreme wind conditions as by the use of internal material- segregating / support barriers 818 and perforated or porous mesh 820 and rigid perforated barrier 824 which may have perforations or pores of smaller cross- sectional area than the smallest diameter of contained matrix materials, and capable of supporting the weight of the internal matrices and other elements while providing points of attachment for various internal elements which may assist in maintaining the spatial relationships of said internal components so that under adverse pressurization conditions which may tend to cause outward bulging of the vacuum encapsulation shell material, that said internal matrices and other elements may not be unduly disturbed from their original configuration permitting the vacuum encapsulation shell to return to its original state of flexure subsequent to the return of said building envelope vacuum encapsulated segment to vacuum pressure. A plurality of sets of centrally disposed and non-centrally disposed non-aligning and preferably non-heat-conductive expansion restricting cross- support elements 842 (one set of which is illustrated in the figure) are shown as a further provision against the potential negatively connoting effect of unwanted atmospheric ingress which upon said ingress would prevent the internal matrix materials from "loosening up" owing the reduction in compressive forces thereupon said components caused by the reduction in pressure differential between the external atmospheric medium and the preferably high vacuum (caused to be low or no vacuum in times of severe system leakage) of the interior of the evacuated building envelope segment(s).

[00151] The system designer may further contemplate that vacuum encapsulation shell element 806 material may be provided by a heat conductive material offering high compressive strength resistance. In this case, an air gap 810 adding some thermal resistance is produced in conjunction with an exterior glazing 670 preferably having Fresnel-lens type of relief impressed at temperature, embossed or adhered upon said glazing, or alternately cut or scored there-into (to reduce reflective losses) may be utilized in place of typical exterior sheathing on South, East, and West faces of building envelopes (in the Northern hemisphere) so that while heat is absorbed into the vacuum encapsulation building envelope segments, means there-for the capture of said heat influx is also provided by the system in conjunction with heat conductive solar thermal energy (heat) capture conduits 812 and heat conductive envelope element(s) 808 indicated as corrugated material in the figure both adding compressive resistance to the overall assembly as well as providing thermal bridging points whereby said heat influx sourced by said heat conductive vacuum encapsulation shell material 806 may be passed into said heat capture conduit(s) 812 as by thermal communication at 814 and also at each corrugation of 808 where coming into contact with conduit 812 walls. While liquid fluid may be passed there-through said conduits 812 to collect said heat energy, a forced air heat recovery system may also be provided through said conduit means, with a disc blower (a single stage Tesla-type compression runner) providing circulation means to drive said forced air flow circuit which may thereafter be provided to heat exchange means of various kinds comprising hydronic, domestic hot water pre-heating and or air- to-air heat exchange. If liquid fluid is desired to be drawn there-through a cooperating system of conduits may also be provided such that the larger portion of the heat energy influx may be 'sunk' into the conduits 812 and fluid passing through said conduit(s), with said heat energy being extracted in an integral or external heat recovery sub- system there-for.

[00152] The designer may also note that interior room temperature conditioning may also be provided through a secondary (interior to building envelope side, as at left in the figure) heat communication sub-system as the one described which may thereby heat extraction (air conditioning) in the summer months in conjunction with a modest geothermal array which may provide cooling of fluids thereafter re-circulated to said conduit means 812 located at left in the figure, may thereby absorb heat energy fro the living quarters in the summer, and may alternately cooperate with a heat pump in the winter months to warm the walls thereof said living quarters and thereby permit said actively evacuated building envelope segments and zones to maintain a high or extreme R-value rating while actively participating in heat transfers to provide added service. In other system embodiments the designer may alternately substitute the outer shell assembly discussed for a flat plate heat exchanger shell system having ready connections for liquid fluid communication (ie H. P. and L. P. ports).

[00153] Referring now to Figure 2, said method of utilizing the ambient atmospheric medium (or another greater gaseous control pressure) as a higher pressure source of pressure differential concurrently with the use of a vacuum-compressor to achieve a desirous degree of lower pressure or of vacua applied to upper elevation components of lift-legs which may have in previous arts individually reached to limited height, are herein suggested to be capable of being combinedly joined together in various forms proposed herein so as to be therefore extended to great height in conjunction with the application of disc VCM as well as other vacuum-producing contrivances with which to impose lower pressures upon isolated gaseous/liquid fluid interfaces at the higher elevation of the individual lift-leg segments of such as system, and accordingly, since such extension thereto great height may be accordantly further combined with the employment of greater diameter piping, conduits and or capacities for such service so that the volume of liquid fluids brought to great height thereby said means of liquid fluid pumping with limited power input, it may be stated that a great volumetric flow-rate may be sustained thereby. In further consideration of the capacity to effect movement of such great quantities of liquid fluids at minimal energy expenditure to great elevation, it may naturally be contemplated that said great volumetric flow-rate of heavy liquid fluids may be advantageously directed so as to fall there-from to lower elevation unto liquid fluid power generation turbines so as to win a great wealth of electrical and or other forms of energy output from such liquid fluid turbines, and Figure 2 illustrates such capacity as relates to said method's application to new means for power generation.

[00154] The atmospheric pressure is significant and as already discussed, is capable of pushing against the head pressure of fluids occupying vacuum-compatible conduits up to a distance limited by the pressure differential existing between two capacity tanks or conduits separated by elevation, and accordant the density of the liquid fluid to be conveyed, a limiting height to which the liquid fluid may be 'drawn' under such conditions may be defined. Whereas the presently disclosed method may make use in some cases of elevation differences approaching this limiting value, the anticipated rates of flow there-through produced also may be limited due to pipe frictional losses as well as the requirement for check valves or other valves in the method which may implicate further differential pressure loss even while open. Accordingly, to ameliorate the anticipated flows to be realized by the method, head pressures observed between the outlet of lower elevation capacities and inlets of upper elevation capacities need be appropriately matched to the control pressures and conduit-sizes utilized to permit acceptable design flow-rates, with fill-times of upper capacity tank(s) being such that the 'one (or more) line(s) on fill / one (or more) line(s) on discharge' overall system- approach flow-rate achieved produces a largely steady, high volume flow for discharge from the upper-most elevation capacity tank(s) unto release into the power-generation circuit.

[00155] It is pertinent to point out that while Zotloterer (26) employs vortex technology for beneficial natural stream aeration, the presently disclosed method also contemplates that since it may be capable of re-cycling liquid fluids remuneratively from bottom of power generation circuit to elevation over and over ad infinitum if desired (with some obvious loss of fluid mass to evaporation and leakage requiring occasional replenishment), it is contemplated that the presently disclosed method may accomplish advantageous water and or waste-water treatment processes concurrently with power generation since advantageous agitation aeration as well as convenient mixed chemical addition points there-for are readily availed which may further afford water treatment processes break-up of solids, mixing and residence time. It is also contemplated that by said method, energy may be produced from the operation of at least part of said water treatment processes employing said method, instead of the currently great energy consumption required to perform said treatment. Of course said method is not limited to energy production by containment of wastewater alone, since seawater for example, may equally be utilized, as may fresh water, or contaminated water which may hereby and herein be sequestered for extended periods of time while also being utilized thus for energy production fluid which may also provide valuable decomposition residence time thereby. It may further be surmised that provided an isolated and contained location, even radioactive wastes comprising strongly ionized and finely disseminated particles might also be carried through such a system (provided a suitable flocculant to keep it in suspension) which may well avail such wastes of energy production longevity through the addition of stages of magnetohydrodynamic energy conversion which may be carried out in the method due to the rapid fluid descents afforded the falling liquid fluids, whereat venturi-throat entrances to power generation vortices (as well as about 'pipes' leading fluids there-into) high flux-density permanent magnets largely positioned about quadrant surfaces may generate a continuous direct current flux (in response to the passage of the strongly ionized radioactive particles in suspension) in large pick-up coils appropriately positioned about opposing quadrant surfaces in the high-velocity regions of the power generation chute or venturi entrance throat. [00156] With power generation circuits comprising economically feasible iterations extending to significant height comprising arrangements of: the elements disclosed with respect to Figure 1 (and may preferably employ the particular features discussed in respect to Figures Ie and If when lift-legs may necessarily or desirously be extended) with which to raise liquid fluids from lower elevation at the source of the liquid drive fluid of the power generation circuit, to higher elevation at the commencement elevation of the power generation 'falling' and or storage circuit components, by the vacuum- pumping method previously described, wherein significant gravitational potential energy may be added to the liquid fluids at the limited expense of running one or more vacuum- compression pumps largely to remove intermittently strategically allowed ingress of gaseous pressurization fluids (ie: atmospheric pressure, or higher pressure control pressurization gaseous fluids); and the subsequent release of liquid fluids unto significant elevation drop(s) through suitably engineered conduit lengths allowing liquid fluids to reach a desirous velocity (with preferably many iterations of elevation drop(s) and velocity development(s) being availed by the 'total elevation drop' provided by the system's 'total lift' capacity) with respective stages of either enclosed or open-to-air descent-chutes being designed accordantly with ancillary purposes of the system (ie: should added vacuum generation be desired to minimize load on the system disc vacuum-compressor, gaseous fluid induction into the falling liquid fluid stream may be readily accomplished, however, would require enclosed descent conduits as well as additional appurtenances to be further discussed; while water treatment goals may be preferably be done in open-to-air chutes for aeration aspects provided, except in freezing climates).

[00157] As indicated in Figure 2a the elevation drop induced momentum provided by the heavy falling liquid fluids in conjunction with appurtenances disclosed by Schauberger (23, 24, 25) which may dramatically increase the velocity of descent through given diameter conduits, with said velocity-enhanced gravitationally energized liquid fluids further caused to enter there-into a terminating venturi throat which may further enhance the velocity of the falling liquid fluids prior to being delivered unto stationed, large diameter and capacity (and upon reflection of Equation 1 - great power density) liquid fluid vortices and in-situ Tesla-type disc turbine(s) of large proportion dimensioned accordingly to develop angular velocities permitting laminar flow based upon continuous peripheral fluid velocities supplied thereto from the falling liquid fluid. With the advantageous employment of a variable disc- spacing method previously disclosed (18) which may similarly be applied to all energy recovery turbine runners of the presently disclosed invention embodiments of varied form, said grand-scale Tesla- type disc turbine discs may be axially-spaced apart largely ideally to receive the enhanced velocity liquid working fluid input provided to the turbine located within and rotating within the fullness of the height and breadth of the anthropogenically staged vortex, to provide large moment arm torque development further utilizing the full cross- section of the vorticity of fluids caused to enter into the spiralling fluidic vortex engine(s), and may thereby permit that a great percentage of their kinetic energy from 'the fall' be converted into fluidic shear-stress between layers, shear-force application through boundary layers to the surfaces of the discs, and torque applied to the shaft thereof said large diameter turbine, whereupon sustained rotation, large scale torque, power, and long-term clean energy supply by said method may be provided for distribution from a mechanical coupling or PTO extending above-ground, or alternately via electrical tension developed independently at each vortex power station, coupled with other conditioned power outputs of other such generation means and thereafter provided for distribution so as to provide serviceable energy product from the 'falls of liquid fluids' through the staged- vortical-descent fluidic power circuit illustrated.

[00158] In consideration of said evacuation-compression (or pressure-differential) lifting of liquid fluids to elevation, it may be stated that this method may be enabled to work (to great height) wherever natural landforms permitting the support of required structures are present for single or iteratively staged assemblages to serviceable elevation or depth, wherein permutations of the method may be enabled via submersion of system components in calm waters, with system fabricated of heavy concrete capable of long term differential pressure cycling with further tethering and floatation support where required to substantially support the required elements of the system.

[00159] As implied, the disclosed invention method may form part of new energy production means for application on other planets beyond Earth which are known to have concentrations of both liquid as well as gaseous fluids of serviceable pressure located either on their surface, or which liquid fluids may exist at depth, such as in subsurface fissures or beneath icy surfaces of significant. The present method of power generation may be suggested for utilization wherever the required elements are present such as at the surface of Saturn's moon Titan where lakes of liquid ethane (of the same order of magnitude in mass density as that of liquid water) concentrated by a local gravitational acceleration also conveniently providing an atmospheric pressure similar to that of Earth may set the stage for applications of the presently disclosed method of power generation elsewhere than on Earth to assist in providing remote power reserves for inter-planetary exploration which do not require combustion processes, and therefore the presently disclosed method of power generation is also contemplated to be applicable throughout the universe wherever liquid fluids of suitable density and viscosity may be found in proximity to significant gaseous atmospheric pressures and significant enough local gravitational acceleration constants.

[00160] In general, said evacuation-compression lifting of liquid fluids to elevation is enabled due to the maintenance of substantial voids (or otherwise, of suitable pressure differentials) within the enclosed conduits and or capacities of the system, with said voids being controlled to cycle sequentially with higher gaseous fluid pressures and those alternately applied gaseous control pressures being further applied amongst paired intercommunicating higher and lower elevation liquid fluid conduits; with said paired liquid fluid conduit elements being capable of further identical intercommunications with other, like, higher and lower elevation liquid fluid conduits equally able to intercommunicate; and further, that a favourably enabling density difference between liquid fluids to be conveyed and the gaseous pressurization mediums employed must exist, whether the atmospheric pressure or another largely fixed volume higher pressure medium is utilized (ie: in the latter case enabling an increased height of each successive 'lift-leg'). And whereas at the terminus of the largely vertical or inclined fall component(s) of the system, whereupon the gravitational potential energy added to the fluid in staged lift-legs may be released into significant fluid velocity energy availing the advantageous conversion thereof into work reclaimed by the vortical energy harvesting means disclosed, a comparatively small amount of input energy is herein implicated to be required to maintain the voids (or other suitable pressure differentials) of fixed volume to thereby enable the lift of said liquid fluids to elevation, since great energy is already freely provided by the substantially limitless power of the gravitational acceleration, which, by compressing (in the first case) the atmospheric medium against gaseous-liquid surfaces there-exposed to said atmospheric pressure more than provides the energy required to push the fluids down, across and upward toward an evacuated (or other zone of lesser pressure), and thereby the present method of serviceable fluids pumping to elevation may be capable of inducing the atmospheric pressure to perform great work wherever sources of liquid fluids may be found or be engineered to be found in the presence of significant gaseous fluid pressures. It may also be stated that should lift-leg elevations per stage out of necessity or advantage be desirously increased via the employment of greater pressure gaseous pressurization fluids in the method, it remains the gravitational acceleration which has collected these fluids for use, and which has equally provided a functional base pressure from which the employment of the method enables the relinquishment of gravitationally availed clean energy.

[00161] As may be anticipated, although with increased elevation the effectiveness of the utilization of the atmospheric compression alone as the gaseous pressurization source becomes diminished, as discussed, utilization of the alternate fixed- volume differential pressure system approach as expressed in respect to Figures Ie and If may be required for the method to work at higher elevations. Accordingly, even with great elevation, the gravitational acceleration in concert with the presently disclosed method may enable suitable gaseous fluid pressures to be cycled in conjunction with substantial voids, and by extension, more generally via application of pressure differentials of required magnitudes to overcome desired liquid heads so as to effect the raising of liquid fluids to great elevation in order to work at humankind's behest to satisfy its growing demand for clean renewable energy through the subsequent release of the energy potential stored therein the liquid fluids raised to elevation unto the pull of the gravitational acceleration to remuneratively release gravitational potential energy through the fall of liquid fluids which may therefore be largely and indefinitely if desired sequestered for utilization as fluidic input to said wholly new vortex energy extraction systems featuring disc turbines of large scale availing the efficient production of energy there-from new hydroelectric power generation methods utilizing greater cross-sectional areas of vortical fluid movements to advantage than hitherto achievable.

[00162] An evacuation and compression energy generation system capable of being initiated by renewable energy generation means of the system or external to the system which may feature vortex energy conversion capabilities operating either within the liquid fluid circuits of the system or without, wherefrom electric, hydraulic and or pneumatic compression energy produced and or stored by said renewable energy generating means may be either directly or indirectly applied to the shaft of; a liquid fluid elevating system gaseous VCM providing a serviceably large differential pressure there-across its inlet maintained at vacuum or other low pressure via strong suction there-into, and its outlet maintained at higher pressure via the multi-stage coaxial compression of the inlet fluid, wherefrom said inlets and outlets, pressure-compatible conduits and or capacities communicating said substantial vacuum or other serviceably low system pressure, as well as alternate conduits communicating the higher system pressure of said VCM may be extended there-from to provide the differential pressure required to effect the strategic, sequential, and largely fixed-capacity application thereof one or both of said generated system pressures to the liquid fluid elevation circuit(s) of the system wherein potential energy may be added to liquid working fluids raised to elevation by said gaseous control pressure fluids there-utilized to effect the flow and raising of said liquid fluids in stages via the sequencing of valve states where-through the capable differential pressures developed by the system VCM may be communicated appropriately so as to cause ingress of fixed volumes of higher pressure gaseous pressurization fluids into lower elevation liquid fluid conduits or capacities (ie: as provided by either the external ambient atmospheric pressure entering through open-to- atmosphere actuated valves, or as may otherwise be provided via application of said higher pressures availed by the VCM similarly entering actuated valves) concurrently with the egress, or evacuation thereof (previously admitted gaseous control pressure) fluids from upper elevation capacities via said capacities' opening thereunto the vacuum or other low pressure of the system such that liquid fluid surfaces there-within lower elevation capacities are acted upon with an excess of force exceeding the sum of forces acting there-in-opposition-to said lower elevation pressure (ie: largely equivalent to the sum of the weight of the net column of liquid fluid disposed between the lower and upper elevation capacities, the force required to overcome frictional losses incurred by the check valve and conduit, and the additional force expressed by the upper elevation vapour pressure or other net low pressure remnant acting downward upon the fluid column at the upper elevation) so that an imbalanced net force results across the liquid fluid column thereby caused to flow upward toward and spill there-into the upper capacity until such time as the pressure differential causing the imbalance of forces is removed, at which time liquid fluid check valves arranged so as to permit only unidirectional flow toward successively higher elevation capacity tanks by way of further conduits may prevent backflow of liquid fluids to the lower elevation, whereafter cycling of control pressure valve states causing a reversal of vacuum or lower pressure application with higher pressure application as applied through top-of-capacity gaseous fluid pressure control ports communicating with the topside of liquid fluid interfaces at respective elevations, said alternate pressure-cycling at respective elevations as may be applied through individual valves on a common line or a common large valve with pressure header(s) feeding multiple conduits at appropriate times, the outflow of liquid fluids from lower elevation capacities (where liquid fluid level may approach but is controllably prevented from entering into the liquid fluid conduit to any significant degree) with the concurrent filling of liquid fluid capacities at upper elevations may result, and with secondary and optionally tertiary, quaternary and other similar sequences of liquid fluid conduits, capacities and valves with accompanying gaseous control pressure valves and conduits iteratively being arranged to provide multiple communicating paths to elevation, a significant and largely continuous volume of liquid fluid flow may be established substantially via the maintenance of small volumes of vacuum or of vacuum-like voids or via other suitably low system pressures affording a suitable system differential pressure readily maintainable via the system VCM disclosed if suitably sized, with; optional storage means for liquid fluids at elevation with which to start the power generation process again at another time, and; valve means in the discharge and power generation chute means beneath power- extraction horizon generation means with which to hold fluids at elevation (ie: keep the system primed), and; supply means with which to supply, filter and isolate the liquid fluids entering the power generation system, and; either aerated open-to-atmosphere or alternately totally enclosed power generation chutes which may employ flow-enhancing appurtenances inducing a degree of vorticity there-within said chute to enhance the velocity of descent in said descent chutes advantageously sized to pass the same volumetric flow-rate at high velocity as that lesser velocity flow designed to be raised at equivalent volume upward to elevation, said power generation chutes extending therefrom the uppermost lift-leg elevation to a power-extraction horizon elevation there- below which may be an intermediary horizon, or may be a final horizon elevation depending upon the system design wherein lesser numbers of iterations and or heights thereof respective fluidic lifts provided may avail a single power-extraction horizon, or may avail preferably great numbers of power extraction horizons, whereat power generation chutes upon entering there-into the inlet of a large-diameter anthropogenically engineered vortex are passed through a venturi flow restricting nozzle-like throat section to further increase the velocity of fluidic ejection there-from upon entry into; said vortical flow system wherein a centrally located discharge where- through a vortex line expressed to lower elevation concurrently provides impetus for the tangentially inlet power generation chute flow to travel a largely vortical path and increase its flow velocity through to said centrally located discharge chute, with; a large diameter Tesla-type turbine largely concentrically located within said vortex flow system, and riding upon horizontally freely turning bearing means which may comprise circular train or train-like wheels with accompanying annular train track means at one or more radii in such fashion as to fully support the weight of the large rotor and weight of the liquid fluid flow comprising said vorticity, or may alternately employ large scale fluidic bearings, magnetic bearings, roller or ball-bearings or other bearing means evidently suited to heavy service over a wide cross-sectional area while implicating a bare minimum of vibration and run-out, and be so gasketed thereabout its perimeter that while not substantially touching the wall surfaces of the volute there- surrounding the turbine's girth, a substantially effective fluid seal may be provided therewith so that while some leakage flow may occur there-through, a very high component of the energy of the power generation flow energy is available to act upon the discs of aid large diameter Tesla-type turbine thereby made freely turning and able to be dragged by largely the full energy of the falling fluid while not being exposed to the fluid drag of the viscous liquid fluid either above the level of the active discs thereof or there-below in the region of its freely turning bearing means thereby largely eliminating counterproductive fluidic drag thereupon said large scale rotor provided by the Tesla-type turbine further comprised of discs designed to optionally, however, advantageously endowed with means to effect the variable spacing function of the invention at run-time via the incorporation of bladders there-within said discs spaced apart by a base axial distance of separation and anchored and sealed thereat against the surfaces of the through bolts (provided by rigid tubing of large diameter having holes therein at appropriate locations median to the intersection of the disc deflated-thickness along said through-bolt tube such that according to temperature, angular rotor velocity and variability of working fluid media employed affecting the resultant fluid viscosity thereof, the variable disc spacing function may as discussed avail largely ideal disc separation during start-up, during variable fluid velocity conditions or in other circumstances which may require a more immediate stoppage of the massive inertia represented by such a device, and; with the optional connection of gasketed ports in the power generation chutes via piped connection to the vacuum or other low pressure gaseous fluidic control pressure service line employed by the system by way of large volume valves such as control valves, with said piped connection lines being connected to the appurtenances within said power generation chute(s) s that as the velocitous downward fall of fluids is effected through said chutes, along with their beneficial effect upon the flow velocity, gaseous control fluid may be inducted there-into said downwardly falling fluid so that a further siphon is placed upon the vacuum or low pressure line of the system to relieve the load upon the system VCM and enhance its ability to produce higher states of vacua whereby the system may operate more efficiently.

[00163] A numerically substantiating description of operation is presently provided to relate system operation to the common experience that but a small amount of energy need be expended in order to effect the evacuation of a conduit such as a straw submerged thereat lower elevation in a source of liquid fluid (provided the liquid fluid surface external to said straw or conduit is open to the atmospheric pressure - or another serviceable pressure) whereupon the ambient external-to-conduit pressure constantly applying great force to the liquid fluid surface may readily push said liquid fluid of acceptably slight viscosity to a higher elevation (ie: within the straw) accordant to the pressure differential thereby applied, and further, and that should said pressure differential be maintained and providing further appurtenances in the form of equally evacuated capacity (or capacities) at said higher elevation, that liquid fluids may continuously be forced through the conduit (climb the straw) and advantageously fall there-from into said evacuated capacity (or capacities) until such time as the pressure differential is disadvantaged or the capacity is filled.

[00164] Whereas human-kind from infancy knows how to employ a contiguous air-tight seal so as draw liquid fluids from their source to a zone of lower pressure whether this be at lower, higher or another location by applying a degree of vacuum-like differential pressure, it has not to date employed this technique on a grand scale. The difference in energy expenditure (to be discussed herein) by the application of vacuum to the task of liquid fluids pumping on a large scale as compared to the methods of the present day wherein globally contemplated, energy is exhausted at an exaggerated rate to effect the conduction of liquid fluids such as water to elevation utilizing liquid fluid pumps prone to the effects of cavitation - ultimately and greatly limiting their efficiency in performing this task - to push said heavy liquid fluids uphill against the force of gravity to cause said liquid fluids to be stored at elevation (which also places liquid fluid service pumps at odds with the greater flow-inhibiting viscosity of said liquid fluids and also pits said pumping means against the force of the gravitational acceleration while attempting to force said liquid fluids to elevation) may be tremendous by comparison.

[00165] Whereas it is recognized that prior art methods by comparison to the methods disclosed herein operate at significantly disadvantaged efficiency, future-oriented sustainable economies seeking to seriously invest in timely ideas are herein offered and provided a method by which liquid fluids may be efficiently 'pumped' to elevation whether on this planet or largely any other hospitable place in the universe where we might wish to conduct liquid fluids from a lower elevation to an higher elevation, whether for consumption purposes, or for power generation purposes, or both. It is not under debate that present-day liquid fluids pumping methods must over-power the resistance of liquid fluid to its passage through smaller diameter conduits and must oppose the force of gravity in pumping liquid fluids to elevation. A small town (of about 8,000 for example) may utilize a plurality of 200+ HP motors to drive respective liquid fluid pumps capable of pumping 15,000 m ³ /Day, and while a scheduled rotation of pumps may be utilized and the pumps may not run all day, a great deal of energy expenditure is nevertheless implicated to effect said (limited though serviceable) liquid fluid lift to elevation while directly 'pushing' said heavy, viscous, and bulky water to elevation.

[00166] By contrast, the presently disclosed method may utilize lesser HP motors to drive lift-leg respective VCM which may advantageously operate completely outside of the liquid fluid to be pumped, and in never needing to come into direct contact with the heavy, viscous, bulky and sometimes nasty liquid fluids to be pumped, great servicing and operational advantages may be afforded not the least of which being prime mover VCM being kept largely in a permanently clean state through everlasting non-contact with the liquid fluid to be 'pumped' , which in such cases as the pumping of waste- water, or contaminated liquid fluids, or boiling or cryogenic liquid fluids obviously are desirously availed characteristics not currently afforded maintenance personnel needing to clean and service present-day liquid fluid service pumps (albeit the latter requiring further pressure regulation and elevation or suppression of system low and or high pressures and potentially special gas -concentration - re: explosive limits - detection and control, and other temperature related considerations appropriate to particular liquids operating at and or near their boiling point temperatures in such cases). [00167] The philosophy or control strategy of said vacuum-compression (gaseous-liquid fluidic lift) method of pumping, then, is not to attempt to overpower and force liquid fluids through comparatively smaller diameter conduit means to elevation, but is rather to provide as large an effective diameter and volume of pressure-compatible array of liquid fluid conduits, capacities and valve (and or check valve) means extending to a feasible elevation, and then in a sequential fashion, schedule pairings of upper-elevation and lower-elevation capacities which may thereby permit liquid fluid to be communicated through said liquid fluid conduit and capacity array's isolated segments via the application of appropriately timed or otherwise controlled inversions of gaseous fluid control pressures administered by a network of gaseous high and vacuum pressure valves, conduits and capacities also operating external to the liquid fluid to be conducted to elevation so as to communicate gaseous control pressures with said liquid fluid capacities through ports typically in, adjacent, or near their 'tops', whereupon an application of greater pressure gaseous control pressures to lower elevation capacities (contiguously across the top of the liquid fluid surface therein) concurrently with the application of vacuum, vacuum-like or other suitably low-pressure gaseous control pressures above upper elevation capacity liquid fluid surface(s) such that the pressure- differential thus referenced there-through the liquid fluid to be conducted to elevation is sufficiently large as to exceed the head pressure existing in the liquid fluid column between the capacity fill-openings at the upper elevation (or liquid fluid level there- within said upper elevation capacity where dependent upon fill-conduits' position, orientation and capacity) and the liquid level at the lower elevation whereupon the higher pressure gaseous control pressure acts to distribute force evenly across the complete liquid fluid interface.

[00168] System VCM (VCM) continuously evacuating the gaseous fluidic load (delivered to its axial inlet without energy expenditure by the gaseous medium's inherent pressure causing it to flow automatically to said VCM inlet providing said vacuum or vacuum-like pressure) either directly in the case of capacity-mounted VCM, or by way of further gaseous control pressure conduit means in the case of remotely stationed VCM which may thereby operate between multi-capacity-horizons if desired, are thereby enabled to effect evacuation concurrently with centrifugal acceleration and compression thereof said air and or vapour conveniently delivered by the remnant air and or vapour pressure present there-within said upper-level liquid fluid capacity. Via extraction thereof the gaseous-fluid content of said upper liquid fluid capacity concurrently with its conduction elsewhere by said multi-stage compression means (ie: in the case of atmospheric pressure utilization as the high system pressure reference, back to the external atmospheric medium, and; in the case of a higher-pressure system generated pressure being utilized as the high system pressure reference, directly to the top of the next lower capacity or thereto by way of a high pressure capacity) a rapid relocation of compression energy from said upper liquid fluid capacity may be provided through its own gaseous exhaustion by said VCM, and with system-wide pairings of capacities concomitantly valved to provide gaseous exhaustion concurrent with liquid fluid filling in upper-elevation capacities (the goal of the method), and liquid fluid exhaustion concurrent with high-pressure gaseous control-fluid pressurization in lower elevation capacities, transfer of liquid fluids may thus be effectively moved through an elevation difference respecting the pressure differential extended there-through said liquid fluid, and with the liquid fluid levels and pressures in respective higher and lower elevation capacities being prepared at the completion of each lift-stage for a subsequent lift-stage requiring only simple inversions of controlling high- and low- system pressure valves, the method thereby provides an advantageous means with which to effect the lift of liquid fluids to further elevation.

[00169] In support of the method, and thereby relate that by not acting to implement such a method, human-kind thereby consumes vast amounts of energy for no reason at all other than 'it has always been done this way' (water and windmill pumping excluded) it may be proven (if it is not already recognized) that it is far easier and should therefore require greatly less energy to move or evacuate a given volume of air or vapour from a capacity to atmosphere or alternately and especially into an evacuated capacity at lower elevation (as is implied herein, where said evacuated capacity is further located within a reasonable distance from said pressurized capacity) than it is to effect the conductance of a similar volume of heavy liquid fluid (ie: water) to a capacity at a higher elevation, especially when we have at our disposal an efficient turbo-machine (or turbo- vacuum pump in this case) with which to produce said vacuum pressure via centrifugal acceleration and multi-stage compression capabilities which may readily move both lightweight and light-viscosity fluids (in contrast to the current state of the art in liquid fluids pumping practiced today, wherein as discussed, said cavitation-prone water pumps fighting great weight density, gravitational acceleration, pump inefficiencies, and liquid fluid viscosity, force said liquid fluids through a smaller diameter pipe to higher elevation).

[00170] For example, a typical means of priming 'low-lift' as well as 'high-lift' water pumps in water treatment and distribution systems is availed by employing a vacuum pump which may be no bigger than a kitchen bread-box and which need not operate at significant speed to evacuate the air from large diameter pump intake conduits descending unto submersion and openness in sources of open-to-atmosphere liquid fluids (water) which may be typically 15 feet below. Said tiny vacuum pump may readily evacuate said intake lines causing the water to be lifted through said lift-leg height (ie: 15 feet) whereupon the pumps are primed, and with the liquid fluid (water) subsequently 'climbing' higher into the vacuum line, a pressure switch or check valve there-in may be actuated and the vacuum pump shut down, after which said the pumps may remain primed at said lift-leg elevation indefinitely (according to the seals employed) - just as everyday human experience with a straw would and should lead us to practice on the grander scale proposed herein.

[00171] In substantiation of the proposed method, it is a matter of documented historical fact that Dr. Nikola Tesla produced a disc-blower device operating upon the shaft of a 75HP motor, which at 3450 RPM was capable of developing airflow of 10,000 CFM. With the knowledge that the present invention seeks to transfer captive volumes of high pressure fluid between pressurization reservoirs, those familiar with Tesla turbo- machinery and vacuum pumps will recognize that with serviceable vacuum seals (ie: labyrinth seals) and an adequate angular velocity that a multi-stage Tesla-type vacuum- compressor of modest diameter and proper disc spacing may serve as a largely ideal vacuum pump which may produce high vacua (22). With minimal modification and suitable housing means said same 10,000 CFM blower may be modified into a multistage vacuum-compressor tasked with evacuating gaseous air and or vapour from vacuum-compatible conduits of 10,000 ft ³ capacity submerged at their base in and open at depth in an open-to-atmosphere liquid fluid source, upon energizing said VCM or otherwise opening it unto the vacuum pressure of the system as by a vacuum valve communicating with the top of said conduit, in one minute's time henceforth we may consider that a largely complete evacuation of the air and substantial vapour from said vertical conduit ("lift-leg") will be achieved, and that concurrent with said evacuation, the atmospheric pressure will simply and effectively push a head of water upward 'behind the evacuating gaseous medium' to a height not greater than the differential pressure created across the liquid fluid column by the VCM. Although liquid-vapour will be evolved concurrently during this evacuation time period so as to attempt to maintain the particular liquid-fluid's vapour pressure, for water at 10 ⁰ C for example, this vapour pressure is only about 1.23kPa, or about 1% of the atmospheric pressure, which may not significantly affect the functionality of the method proposed herein.

[00172] Letting this stage be considered as an initial liquid fluid column 'priming stage', and meanwhile considering that once 'primed', the priming charge liquid fluid column may remain substantially at rest in an elevated state due to the maintained pressure differential exercised through the liquid fluid column by the gaseous control pressures without further energy input other than that constantly supplied by the gravitational acceleration through the atmospheric pressure energy, provided that the vacuum or vacuum-like pressure is maintained upon the upper surface of the liquid fluid column as shall require the appropriate use of sealing gaskets and o-rings where applicable about the sealing surfaces of check valves and within actuated valves as required (notwithstanding it may be assumed that large liquid fluid check valves shall be employed to ensure that catastrophic head loss is not possible in operation) and with said rest-elevation being such that the pressure in the bottom of said liquid fluid column due its height, density and gravitational acceleration thereat being largely equal to the pressure difference expressed by the VCM vacuum or vacuum-like pressure upon the upper elevation liquid fluid surface as referenced against the atmospheric or other serviceably higher pressure applied to the gaseous-liquid fluid interface surface at the lower elevation. It may also be considered herein for all intents and purposes of this exercise, that the expressed 10,000ft capacity may alternately be 10,000,000 ft if desired (with accordant ground- support structure capable of supporting such a weight- load being requiem) and there would be no difference implicated in the example (except for the initial charge period required), so that in considering the following description offered, it may be considered that the ever-present atmospheric pressure may constantly push any desired quantity of liquid fluids to elevation spontaneously that we might care to provide appropriately sized and differential-pressure-rated conduits and capacities there-for in order to effect beneficially large conductions of liquid fluids to desirous elevations economically, and all man-kind need do is enlist the substantially limitless and ever present power of the atmospheric pressure conveniently provided by the gravitational acceleration in such a way as to push isolated and evacuated containers, or "buckets" if you will, full, and in doing so, simply allow nature to work on humankind's behalf wherever possible.

[00173] For purposes of brevity, let it be considered that a succession of vertical 'lift- legs' have been primed so that the continuity issue may be addressed (since the conditions required to effect the priming thereof given isolated liquid fluid conduits and capacities have already been established). Therefore: with said array of system lift- leg(s) (liquid fluid columns) replete with liquid fluids having substantially negligible vapour pressure acting there-across the top surface area thereof, and; with check valve means provided at the base thereof lift-legs to 'hold-the-prime' (so as to prevent catastrophic head losses), and; with the top region of lift-leg volumes communicating either into the bottom or alternately spilling-over into the side or through the top of said capacities provided thereat said upper elevation in variations of the method) through liquid fluid through conduits, valve and or check valve means or a plurality thereof (normally closed during lift-leg priming operations) of similarly sized or advantageously larger volume vacuum or otherwise-specified differential-pressure-compatible liquid fluid capacities (let us say for purposes of discussion, represented by horizontally elongate capacities having topmost ports for application of the stated gaseous and vacuum control pressures thereto, and having further large receiving ports for liquid fluid entry as from the top region of said liquid fluid column conduit-lift-leg, which liquid fluid entry port(s) being located below the liquid fluid lift elevation respective to the pressure-differential offered at run-time by the system VCM thereby permits the filling of horizontally lain capacities when significantly high differential pressures are applied there-through system lift-legs) ... we may now state that said (array of) horizontally lain capacities represent the only requirement for evacuation and compression filling (pumping) purposes hence-forth in the discussion, since the vertical lift-legs remain ever-primed.

[00174] Beginning at T = 0, then, when said vacuum-compressor-generated vacuum or vacuum-like low system pressure is communicated to a first horizontally lain capacity at an upper elevation so as to begin its evacuation, and with said capacity's further egress pathways being closed as by valve and or check valve means so that said capacity is completely otherwise isolated, and following a requisite evacuation time-span given in the example to be about one minute, when once nearing a significant degree of evacuation and the valve or check valve means or plurality thereof commonly communicating between the vertical conduit and the horizontal capacity shall open or be opened (if utilized), liquid fluids within and near the top of said first vertical lift- leg conduit may then simply spill or flow there-into the largely evacuated horizontally lain capacity (according to said interconnecting conduits' position and orientation). With spillage or flow of said liquid fluids there-into said capacity representing a head-loss in the vertical lift-leg (or alternately a head-increase delay, again dependent upon the position, orientation and capacity thereof said interconnecting conduit means), a happy conundrum is thereby permitted by this method and system and is thereby availed to be played upon, wherein the continuous imbalance of forces distributed across the standing liquid fluid column due to the gravitationally-energized atmospheric pressure's capability of moving the easily deformable liquid fluids under such isolated circumstances (ie: in the discussed case of liquid fluid lift-legs being evacuated there- above) until such time as a head of liquid fluid should be produced which pressure equally opposes the differential pressure exacted by the system, wherein such cases said atmospheric pressure shall therefore continuously cause liquid fluids to rise (flow) upward through said vertical lift leg so as to attempt to nullify the pressure differential with a correspondingly equivalent head pressure. However, by design and by provision of a suitably large capacity (or capacities), we may prevent the atmospheric pressure from accomplishing this in an instant, or in a minute, in an hour, or desirously even in an eternity through appropriate design of the system to achieve particular time-constants of operation and by desirously providing secondary, tertiary and or more multiplexed paths to elevation so that preferably great volumes of capacities shall be there- situated at respective elevation-horizons so as to receive said eternal lift-leg pressure-differential balancing flow continuously (ie: in such a fashion that one or another capacity is at all times being filled with great volumes of atmospherically-pushed upwardly-directed liquid fluid flow) where-into said capacities the flow or fall of liquid fluids may thereby continue ad infinitum at given horizontally lain capacity-elevation-horizons in properly designed systems.

[00175] Meanwhile one or more other preferably great capacities at the same elevation- horizon may be continuously prepared for subsequent filling via their emptying (of liquid fluids) through the concurrent application of atmospheric (or other suitable control) pressurization so as to push liquid fluid contents down and out of said horizontally lain capacities and thence upward through subsequent vertical (or other inclination) lift-legs to yet higher elevation, so as to achieve a constant upward multiplexed flow of liquid fluids to elevation which, although segmentally-considered may be cyclically governed by capacity-respective empty and fill time-constants, from a system- wide process-perspective however, said process may be continuously enabled and therefore largely need never be halted but for servicing of lift-segments which may be taken off-line at will with or without halting the overall system function. To achieve this goal it may now be stated that liquid fluid check valve(s) at the base of system lift- leg(s) permissively allowing liquid fluids to flow to elevation but not down-hill therethrough said lift-legs, as well as those check valves between lift-leg conduits and horizontally lain capacities at upper elevations (if utilized in particular embodiments) doubly serve the important purpose of preventing the application of high system reference gaseous control pressures from passing down-hill through the liquid fluid conduit pathways. With said liquid fluid check valves oriented so as to allow liquid fluid flow through said liquid fluid conduits and capacities in the uphill-seeking direction only, with the cooperation of liquid level monitoring and control means such as discrete level- sensing floats operating within said capacities and activated upon rising and falling liquid fluid levels near the top and bottom of said capacities (such that, for example: upon a liquid level approaching the bottom of said capacity, a change in float orientation may effect closure of the atmospheric pressure ingress valve so as to halt the discharging of liquid fluid from the capacity at an advantageous level and thereafter cue via timer or PLC based algorithm, the opening of the vacuum valve so as to then commence the evacuative filling sequence when a lower elevation capacity should be opened unto the atmospheric pressure causing a serviceable pressure differential to exist there-between the two capacities so as to effect such a conduction of liquid fluids to elevation, and; an alternate float operating at the top of said capacity which may upon detecting a liquid fluid level there-approaching the top of said capacity instead effect closure of the vacuum pressure valve so as to halt the filling of said capacity and which may thereafter cue, as by a timer or PLC based algorithm, the opening of the alternate atmospheric or other high system pressure valve so as to begin the discharge phase anew), automation of such a system may be readily accomplished. With the 'emptying' of horizontally lain capacities significantly below their bottom being prevented by said level control means, said liquid fluid may thereby be utilized to seal the gaseous pressurization fluid by way of the density difference between the two fluids, and with vacuum valves closed within said first vertical conduit and horizontal capacity, and with the further opening of gaseous high pressure control pressurization valve(s) there- communicating the ambient atmospheric pressure there-into said first horizontally lain capacities by way of further valve or valves (preferably located in the top of said first horizontally-lain capacities, which may now be considered as a lower elevation capacity in the discussion in regard to the presently described conduction of liquid fluids from first horizontally lain capacities upward to the filling of yet higher elevation second horizontally lain capacities) so as to cause said atmospheric pressure by way of its acting upon the liquid level fluid interface surface there- within said first horizontally-lain capacities to thereby distribute force equally there-across the complete surface area thereof the liquid fluid within said first horizontally-lain capacities to effect said atmospheric push of said liquid fluid contents to the higher elevation.

[00176] At this point the advantageous density difference between the gaseous control pressurization fluid utilized and the liquid fluid to be 'pumped' must be emphasized, since it is the magnitude of this naturally provided property difference which allows the system to be readily designed to prevent the gaseous pressurization fluid from simply passing through the liquid fluid in said capacities and through check valve means and further rise through the liquid fluid column to constantly load the VCM (which would defeat the system concept). Instead, said favourable density difference permits the application of gaseous control pressures spanning a wide range, advantageously allowing atmospheric pressures through very great high-pressure system reference control pressures to be employed in the method if designed for such application of higher pressures, since the density difference between air and water is very great (ie: over 800 times at STP) so that the disclosed method of raising liquid fluids to elevation may also permit the raising of fluids in greater height lift-legs than those availed by the 'free service' provided by the atmospheric pressure alone, as in differently arranged embodiments of the invention disclosed in a pending patent application) and which desirous density-difference may thereby ever-cause said gaseous control pressure fluids to remain 'on-top' if carefully applied thereto the liquid fluid surfaces so as to contiguously distribute pressure energy across the full surface of said liquid level interfaces without jettisoning control pressurization fluid there-into the depths of said liquid fluid (further ensuring no catastrophic head loss conditions are created during runtime operation). [00177] By way of further liquid fluid valve or check valve means in a conduit or conduits there-communicating said first horizontally lain liquid fluid capacity as through its bottom into a second vertical (or alternately inclining) liquid fluid lift-leg conduit extending to a second higher elevation wherein the liquid fluid level (having been previously primed) is at such a level as to permit liquid fluid to fall or flow there-into said second upper similarly arranged horizontally lain capacity upon its evacuation to suitably low pressure, with the application of said vacuum or vacuum-like pressure there-at-the-top-of said second horizontally-lain capacity, and with its substantial evacuation being approached and subsequently being further opened there-unto said second vertical lift-leg replete with elevated liquid fluids as through a further valve or check valve means or plurality thereof as previously discussed, and with atmospheric pressure acting across the complete surface area of the gaseous-liquid fluid interface at the lower elevation effected through an appropriate valve or valves actuation, the pressurized liquid fluid contents of the first horizontally-lain capacity thus referenced to the vacuum pressure at the second higher elevation both at the top of the second vertical lift leg as well as within said second horizontally-lain capacity thereby shall be pushed through the second vertical or inclined lift-leg to the second higher elevation owing to the imbalance of forces substantially acting across said second vertical lift-leg, and so long as said imbalance of forces exists, liquid fluids may simply and effectively be pushed upward through second vertical lift-legs and into second horizontally-lain capacities until they too are replete with liquid fluids whereupon level control means may effect a changing of valve states so as to alternate the pressures appropriately to cause further sequential raisings of liquid fluids to elevation, and so on, and so on, and so on, to any desired elevation in accordance with maximum heights per lift which individually considered lifts may be limited to heights largely defined by the relations:

[00178] In the case of the atmospheric pressure being utilized as the high pressure source:

((Atmospheric Pressure - (Effective Remnant Fluid Vapour Pressure + Check Valve Cracking Pressure Rating(s) + Conduit Frictional Pressure Loss))/(Liquid Fluid Density x Gravitational Acceleration); and or

[00179] In the alternate case wherein a system-generated high pressure reference is rather utilized as the high pressure reference source: ((System High Reference Pressure - (Effective Remnant Fluid Vapour Pressure + Check Valve Cracking Pressure Rating(s) + Conduit Frictional Pressure Loss))/(Liquid Fluid Density x Gravitational Acceleration)

[00180] Since it is already known that piping conduits built for liquid fluid (water) conduction at high pressures (as previously discussed herein with respect to 14" and 16" water treatment plant conduits observed) are already suitable for vacuum application at lower differential pressure, and also because the Tesla- turbine technology may be readily mass-produced and may in doing so may greatly decrease the cost of the already- cheapest-of-all-turbines-to-manufacture even further. Therefore it is desirous that the world utilize this less costly to construct, power and maintain method to avail an important opportunity to reduce the environmental footprint of said electrical energy (excess) expenditure and also reduce the extended carbon footprint of said operation as compared to the way we are currently performing this service.

[00181] Recalling now Dr. Nikola Tesla' s 10,000 CFM blower, and considering it to be the 10,000CFM multi-stage VCM implied in the above system description, a more numerically oriented analysis of a 'single-lift- leg- volume' shall be provided, assuming the 10,000ft / minute evacuation of said horizontally lain capacities may translate to water conduction to elevation of equal volumes in an equivalent time period (ie: 1 minute) and where ... 10,000ft ³ = 283.168m ³ .

[00182] Assuming 100% up-time of said VCM disclosed then, and that in properly designed systems said vacuum-compression function shall be effected continuously at given capacity-horizons (alternately applying via control pressure valve cycling its evacuation capacity between two capacities thereat the same capacity-horizon, whereat a rotating schedule of operation amongst a plurality of said units may permit run-time system service 24/7 as well as longevity of respective VCM), then ... 24 hours = 1440 minutes; 1440 minutes x 283.168 m ³ = 407,762 m ³ of evacuation capacity may be availed by said single 75HP evacuation means, and consequently over that same time period, 407,762 m ³ of concomitantly atmospherically pushed (pumped) liquid fluids may be raised to elevation to fill the horizontally-lain evacuated capacities provided thereat. [00183] Following through with a work calculation then, wherein 407,762.59 m of water moved over the span of the day of operation to higher elevation represents 407,762,590 kg of water, which further represents a weight of water = 407,762,590 kg x 9.8 N/kg = 3, 996,073, 391N, and this weight of water in the example is lifted through 10m doing work (where work = force x distance) on the water lifted through the (10m) elevation of 3,996,073,391N x 10m = 39,960,733,910 J.

[00184] Over the course of a day, this addition of gravitational potential energy to the fluid represents a Power of 39,960,733,910 J / 86,400 sec = 462,508 Watts, or 462.5 kW (since power = work (J) / time (s)).

[00185] Comparing this to the 75HP motor given = 55.95kW = 55,950W = 55,950 J/sec = 55,950J/sec * 86,400sec/day = 4,834,080,000 J ... it is found that 4,834,080,000 J may be expended to induce the atmosphere to do 39,960,733,910 J of work over the course of a day to push said liquid fluids (water in the example) to higher elevation.

[00186] Though un-conditioned by efficiency numbers of the discussed vortex energy extraction method the raw Work Out / Work In ratio representative of the energy utilization vs. energy requirement to raise said liquid fluids to elevation in the provided example: 39,960,733,910 J / 4,834,080,000 J = 8.26 shows that 8.26 times the work expended to induce the atmosphere to push liquid fluids to elevation, is done (by the atmosphere) on the fluid there-pushed to elevation, thereby availing dramatically reduced energy consumption to drive liquid fluids to elevation which may be concurrently rewarded with an accordant energy surplus (ie: providing energy storage beyond the pumped storage volume) in the fluid moved to elevation by the method.

[00187] While based upon the information provided above the invention contemplates 're-writing' the manner in which liquid fluids are pumped to elevation globally so as to avail a great conservation of energy concurrently with splendid reductions in carbon emissions relative thereto in step with the economic capacity for conversion to such systems, it is a further goal that the cooperation of a plurality of lift-legs operating in parallel through myriad elevation-capacity-horizons may in every corner of the globe be utilized to induce the continuous lift of preferably vast volumes of liquid fluids to elevation for purposes of hydro power generation without need of damming, with said liquid fluids being advantageously provided by waste-water, waste-water bypass, industrial waste-water, contaminated liquid fluids and or other desirously sequestered liquid fluids so that in said state of constant sequestration and reciprocation from bottom to top of flow circuits, said liquid fluids may be availed of concurrent process residence time, aeration, agitation as well as venturi-based chemical-addition to further minimize energy consumption normal to said treatment processes, and which over a designated duration in said sequestered service may effect the purification to a desirous degree of contaminated liquid fluids.

[00188] With a concurrent goal of the method being to avail new power generation, whence liquid fluids are induced to said upper-most elevation of the liquid fluidic lift systems, liquid fluids of enormous volume may then supply one or a plurality of power generation chutes of smaller diameter than the effective diameter of conduits utilized to bring the atmospherically driven fluids to elevation. Since liquid fluids falling through said power generation chutes largely under the influence of the gravitational acceleration may attain great velocity, said liquid fluid capacities raised to elevation shall be 'consumed' thereby at a greater velocity than the capacity of said liquid fluids raised at a substantially slower rate thereby necessitating the difference in effective conduit cross- sections (or diameters). In falling there-through said power generation chutes of smaller diameter conduits or therein (where said chutes may comprise open channels) to lower elevation said fluids may attain greater velocity through the action of appurtenances disclosed by Schauberger (23, 24, 25) which may cause the velocity of the fluids in the descending core flow to exceed the velocity which might normally be prescribed to a falling fluid through a pipe and by attributing lesser bulk frictional losses may thereby release greater gravitationally availed velocity energy to said 'falling' liquid fluids to an extent in accordance with the gravitational potential energy added to the liquid fluid through its being raised to elevation in stages. Alternately, said descending power generation flow chutes may be permitted to flow down surface landforms in open channels or waterfalls to provide aeration and depending upon the liquid fluid employed, aesthetic appeal.

[00189] Further, said descending power generation chutes may be provided with induction conduit connections at intervals there-through gasketed ports machined or molded or otherwise provided by said Schauberger appurtenances having bases designed to mate there-with said gasketed ports and with leeward down-slope-facing discharge ports therein may thereby cause said fast-descending liquid fluids to drag greatly upon gaseous control pressure fluids communicated there-into the falling liquid fluid of significant viscosity and velocity inducing a natural vacuum-draft as well as a largely vorticing liquid fluid flow profile (through the employment of said Schauberger appurtenances) and thereby said falling liquid fluid may fall yet faster due to the relative discontinuity between the liquid fluid wetted boundary layer at the pipe-wall provided by the introduction of the greatly less viscosity gaseous fluid in that region (with said gaseous control pressure fluids being communicated thereto via connection between the vacuum conduit networks of the system either in the presence or absence of a vacuum- pressure regulating means), where-through said appurtenances gaseous fluid induction may thereby afford further 'naturally-engineered' system vacuum through said Schauberger appurtenances such that load upon the system VCM of the system may be substantially relieved to the point that said VCM may operate satisfactorily at lower RPM and thereby consume less energy to induce said gravitational acceleration provided atmospheric pressure energy to effect system operation.

[00190] Reaching the bottom of said power generation chutes and being further accelerated through a venturi nozzle-throat, said rapidly driven fluid flow enters into power generation vortices largely expressing their full energies through tangential approach and entrance there-into the spaces between the discs of truly grand- scale Tesla turbines built to be driven by largely the full vorticity of said vortex and designed to ever-after be contained and continuously rotate due to the great, constant, inertial influx of mas s -flow entering the power generation vortex through said venturi at preferably excessive velocity so as to generate great power in cooperation with a mechanism provided for the optimal disc spacing of the disc elements in such turbines operating to develop great shear-stress, shear-force, torque, rotation and power from fluids in motion, and being mounted upon bearings which are not within the liquid fluid vorticity but are fully exterior to same and indeed are within an atmospheric or other low-pressure gaseous medium wherein greatly less viscous attachment is implicated upon the bearing means thereof said large-scale disc turbines therein moving in harmony with, yet not significantly influenced by negatively imposing fluidic drag offering this cavitation-free hydro-electric power generating process yet larger power generation returns from nasty substances in sequestration, if desired, long into the future.

[00191] It should be stressed that with said Tesla turbine devices operating at such large cross-sectional areas contemplated (ie: 100', or 30.48m diameter) these may be foreseen to be very efficient since the complete energy flow of the vorticity must pass through the large-scale disc turbine having fluid energy conversion channels operating at up to 95% efficiency between adjacent discs when operating in stream-lined laminar flow conditions, and which therefore may avail the conversion of a great portion of said gravitationally provided energy storage which may be significantly in excess of the power required to raise said liquid fluids to elevation. Meanwhile, post discharge of liquid fluids from said power generation vortices, the liquid working fluid may be constantly returned to the system to become the first-lifted liquid fluids at the lowest elevation capacity-horizon thereby providing also a largely closed-loop power generation method and system capable of producing great power from the fall and acceleration thereof full cross-sections of said liquid fluids atmospherically pushed to elevation, which method may thereby provide said energy without need of pen-stock, damming or water diversion of any kind from natural ecosystems (save for the amount respective to the base system-fill and evaporation-losses thereafter, which 'fill' being alternately provided from wastewater treatment plants or their bypasses, or other contaminated source waters such as municipal dump leaching fluids or other liquid fluids which may also be advantageously sequestered and treated in such systems as the one herein proposed).

[00192] For example, utilizing the equations provided for the derivation of torque and power in such machines, we may find an anticipated power realization by such a 100' diameter Tesla turbine machine, assuming that the liquid fluid (water at 5°C, in this case) falls from a 3-stage atmospheric pressure lift system of largely 100' (or 30.48m) unto said disc turbine (having assumedly frictionless bearing means for purposes of discussion):

[00193] With a power generation chute drop of 100' = 30.48m, we may use Torricelli's Theorem to compute an anticipated chute efflux velocity, where:

Equation 5 Torricelli's Theorem = (2 • g • (hi - h2)f ²

= (2 • 9.8 • (30.48)) ^1/2 = 24.44 m/s

[00194] Whereas quantifiable test data with which to accredit additional velocity increase to the Schauberger appurtenances (23, 24, 25) is wanting, their usage in combination with venturi throats at the bottom of the power generation chutes wherethrough power generation vortex working fluid is provided may together avail a modest increase in velocity, which may thereby provide a vortex entry velocity of 30m/s, which may avail a rotational velocity of largely 18.8 RPM in advantageously spaced discs of the discussed diameter, and an average velocity across the (great) disc surfaces of 15m/s, and with a fresh-water temperature = 5°C a dynamic viscosity of μ = 1.519xlO ^~3 Ns/m ² may be provided. With sufficient water falling through the power generation chute to sustain said largely 30.48m diameter vortex of arbitrary height 2m wherein said discrunner having a horizontally lain runner comprising thick end discs of appropriate gauge to support the weight of said runner plus the mass of water upon guiding track means 540 such as circular railway or like tracks and wheels and or upon other minimal friction load bearing means 536 which may include ball, roller bearing or magnetic suspension means, any of which or combinations thereof being arranged at one or more radii concentric with produced vortex rotation and being largely free to support rotation thereof said liquid fluid vortex while providing service in a region of gaseous fluid to minimize the effect of negatively imposing fluid drag upon said runner as generally indicated in Figure 2g, with said runner further comprising up to 125 fixed or dynamically spaced apart intermediary discs of about 0.5cm thickness (giving about lcm of separation for purposes of discussion) with central discharge apertures of 5m radius (optimal disc number and spacing for large runners may in operation be found and configured at run-time to be another advantageous distance of separation in conjunction with an adjustable disc spacing sub- system whereby a representative device power capacity operating in and cooperating with said vortex may be calculated as previously approximated (18):

Equation 3: Torque per disc:

T _DΪ SC = 2(3 u YB π r (r? ² - rτ ² )) h

= 2( 3 x l.519xlO ^"3 N- s/m ² x l5m/s x 3.1415 x 15.24m x ((15.24m) ² - (5m) ² ))

0.5 x 10 ^"2 m

= 271 316.1 N- m

^Total / Turbine Runner — 126 X T Disc

= 126 x ( 271 316.1 N m) = 34 185 830 N m, or 225,229,142.5 ft-lbs

Equation 4: Power Turbine = Torque speed

5252 = 25,229,142.5 ft-lbs x (18.8) rev/min

5252 = 90,309.95 HP or 67.37 MW

[00195] Forwardly looking it may be advantageous to design water treatment plants (and other industries currently moving great quantities of liquid fluids via present-day pumping methods) around the liquid fluidic lift systems proposed or similar to the one disclosed herein to avail the harvest of significant power generation capacity from processes which may even utilize waste fluids to develop significant power.

[00196] Restated in yet another fashion, a method for generating power from the gravitational acceleration of the Earth or other celestial body is herein provided wherever liquid fluids of significant density and sufficiently low viscosity, as well as gaseous fluids of significantly less density and sufficiently great pressure may be present or be caused to be present in close proximity, wherein an evacuation and compression energy generation system utilizing machines capable of being initiated by renewable energy generation means of the system or external to the system which may feature vortex energy conversion capabilities operating either within the liquid fluid circuits of the system or without, wherefrom electric, hydraulic and or pneumatic compression energy produced and or stored by said renewable energy generating means may be either directly or deferably applied to the shaft of; a liquid fluid elevating system gaseous VCM providing a serviceably large differential pressure there-across its inlet maintained at vacuum or other low pressure via strong suction there-into, and its outlet maintained at higher pressure via the multi-stage coaxial compression of the inlet fluid, wherefrom said inlets and outlets, pressure-compatible conduits and or capacities communicating said substantial vacuum or other serviceably low system pressure, as well as alternate conduits communicating the higher system pressure of said VCM may be extended there-from to provide the differential pressure required to effect the strategic, sequential, and largely fixed-capacity application thereof one or both of said generated system pressures to the liquid fluid elevation circuit(s) of the system wherein potential energy may be added to liquid working fluids raised to elevation by said gaseous control pressure fluids there-utilized to effect the flow and raising of said liquid fluids in stages via the sequencing of valve states where-through the capable differential pressures developed by the system VCM may be communicated appropriately so as to cause ingress of fixed volumes of higher pressure gaseous pressurization fluids into lower elevation liquid fluid conduits or capacities (ie: as provided by either the external ambient atmospheric pressure entering through open-to-atmosphere actuated valves, or as may otherwise be provided via application of said higher pressures availed by the VCM similarly entering actuated valves) concurrently with the egress, or evacuation thereof (previously admitted gaseous control pressure) fluids from upper elevation capacities via said capacities' opening thereunto the vacuum or other low pressure of the system such that liquid fluid surfaces there-within lower elevation capacities are acted upon with an excess of force exceeding the sum of forces acting there-in-opposition-to said lower elevation pressure (ie: largely equivalent to the sum of the weight of the net column of liquid fluid disposed between the lower and upper elevation capacities, the force required to overcome frictional losses incurred by the check valve and conduit, and the additional force expressed by the upper elevation vapour pressure or other net low pressure remnant acting downward upon the fluid column at the upper elevation) so that an imbalanced net force results across the liquid fluid column thereby caused to flow upward toward and spill there-into the upper capacity until such time as the pressure differential causing the imbalance of forces is removed, at which time liquid fluid check valves arranged so as to permit only unidirectional flow toward successively higher elevation capacity tanks by way of further conduits may prevent backflow of liquid fluids to the lower elevation, where-after cycling of control pressure valve states causing a reversal of vacuum or lower pressure application with higher pressure application as applied through top-of-capacity gaseous fluid pressure control ports communicating with the topside of liquid fluid interfaces at respective elevations, said alternate pressure-cycling at respective elevations as may be applied through individual valves on a common line or a common large valve with pressure header(s) feeding multiple conduits at appropriate times, the outflow of liquid fluids from lower elevation capacities (where liquid fluid level may approach but is controllably prevented from entering into the liquid fluid conduit to any significant degree) with the concurrent filling of liquid fluid capacities at upper elevations may result, and with secondary and optionally tertiary, quaternary and other similar sequences of liquid fluid conduits, capacities and valves with accompanying gaseous control pressure valves and conduits iteratively being arranged to provide multiple communicating paths to elevation, a significant and largely continuous volume of liquid fluid flow may be established substantially via the maintenance of small volumes of vacuum or of vacuum-like voids or via other suitably low system pressures affording a suitable system differential pressure readily maintainable via the system VCM disclosed if suitably sized, with; optional storage means for liquid fluids at elevation with which to start the power generation process again at another time, and; valve means in the discharge and power generation chute means beneath power-extraction horizon generation means with which to hold fluids at elevation (ie: keep the system primed), and; supply means with which to supply, filter and isolate the liquid fluids entering the power generation system, and; either aerated open-to-atmosphere or alternately totally enclosed power generation chutes which may employ flow-enhancing appurtenances inducing a degree of vorticity there-within said chute to enhance the velocity of descent in said descent chutes advantageously sized to pass the same volumetric flow-rate at high velocity as that lesser velocity flow designed to be raised at equivalent volume upward to elevation, said power generation chutes extending there-from the uppermost lift-leg elevation to a power-extraction horizon elevation there-below which may be an intermediary horizon, or may be a final horizon elevation depending upon the system design wherein lesser numbers of iterations and or heights thereof respective fluidic lifts provided may avail a single power-extraction horizon, or may avail preferably great numbers of power extraction horizons, whereat power generation chutes upon entering there-into the inlet of a large-diameter anthropogenically engineered vortex are passed through a venturi flow restricting nozzle-like throat section to further increase the velocity of fluidic ejection there-from upon entry into; said vortical flow system wherein a centrally located discharge where-through a vortex line expressed to lower elevation concurrently provides impetus for the tangentially inlet power generation chute flow to travel a largely vortical path and increase its flow velocity through to said centrally located discharge chute, with; a large diameter Tesla-type turbine largely concentrically located within said vortex flow system, and riding upon horizontally freely turning bearing means which may comprise circular train or train-like wheels with accompanying annular train track means at one or more radii in such fashion as to fully support the weight of the large rotor and weight of the liquid fluid flow comprising said vorticity, or may alternately employ large scale fluidic bearings, magnetic bearings, roller or ballbearings or other bearing means evidently suited to heavy service over a wide cross- sectional area while implicating a bare minimum of vibration and run-out, and be so gasketed thereabout its perimeter that while not substantially touching the wall surfaces of the volute there- surrounding the turbine's girth, a substantially effective fluid seal may be provided therewith so that while some leakage flow may occur there-through, a very high component of the energy of the power generation flow energy is available to act upon the discs of aid large diameter Tesla-type turbine thereby made freely turning and able to be dragged by largely the full energy of the falling fluid while not being exposed to the fluid drag of the viscous liquid fluid either above the level of the active discs thereof or there-below in the region of its freely turning bearing means thereby largely eliminating counter-productive fluidic drag thereupon said large scale rotor provided by the Tesla-type turbine further comprised of discs designed to optionally, however, advantageously endowed with means to effect the variable spacing function of the invention at run-time via the incorporation of bladders there- within said discs spaced apart by a base axial distance of separation and anchored and sealed thereat against the surfaces of the through bolts (provided by rigid tubing of large diameter having holes therein at appropriate locations median to the intersection of the disc deflated-thickness along said through-bolt tube such that according to temperature, angular rotor velocity and variability of working fluid media employed affecting the resultant fluid viscosity thereof, the variable disc spacing function may as discussed avail largely ideal disc separation during start-up, during variable fluid velocity conditions or in other circumstances which may require a more immediate stoppage of the massive inertia represented by such a device, and; with the optional connection of gasketed ports in the power generation chutes via piped connection to the vacuum or other low pressure gaseous fluidic control pressure service line employed by the system by way of large volume valves such as control valves, with said piped connection lines being connected to the appurtenances within said power generation chute(s) s that as the velocitous downward fall of fluids is effected through said chutes, along with their beneficial effect upon the flow velocity, gaseous control fluid may be inducted there-into said downwardly falling fluid so that a further siphon is placed upon the vacuum or low pressure line of the system to relieve the load upon the system VCM and enhance its ability to produce high vacua wherefrom the system may operate more efficiently by said system developing greater power from the fall of the liquid fluids it may capably raise to elevation via said means to maintain substantial or comparative voids (or suitable pressure differentials) within enclosed conduits and or capacities of the system, such that with said voids being likewise controlled by provided valve means to alternate sequentially with higher and lower elevation gaseous fluid pressures applied through gaseous pressure control ports communicating with the top of liquid fluid interfaces, combinedly causing the desirously isolated intercommunication of pressures and mediums within and some through higher and lower elevation liquid fluid conduits with capacities; and with said paired liquid fluid conduit elements being capable of further identical intercommunications with other, like, higher and lower elevation liquid fluid conduits equally able to intercommunicate at appropriately sequenced times; and further, with said a favourably enabling density difference between liquid fluids to be conveyed and the gaseous pressurization mediums employed, whether the atmospheric pressure or another system fluid volume at higher pressure is utilized to enable increased lift-heights in lift-legs, and whereas at the terminus of the largely vertical or inclined fall component(s) of the system, whereupon the gravitational potential energy added to the fluid in staged lift-legs may be released into significant fluid velocity energy availing the advantageous conversion thereof said potential energy into kinetic energy and work thus reclaimed by the vortical energy harvesting means disclosed, and a comparatively small amount of input energy is herein implicated to be required to maintain the voids (or other suitable pressure differentials) of fixed volume to thereby enable the lift of said liquid fluids to elevation, since great energy is already freely provided by the substantially limitless power of the gravitational acceleration, which, by compressing (in the first case) the atmospheric medium against gaseous-liquid surfaces there-exposed to said atmospheric pressure more than provides the energy required to push the fluids down, across and upward toward an evacuated capacity (or other zone of lesser pressure); and thereby the present method of serviceable fluids pumping to elevation may be capable of inducing the atmospheric pressure to perform great work wherever sources of liquid fluids may be found or be engineered to be found in the presence of significant gaseous fluid pressures; and it may also be stated that should lift- leg elevations per stage out of necessity or advantage be desirously increased via the employment of greater pressure gaseous pressurization fluids in the method, that it remains the gravitational acceleration which has collected these fluids for use, and which has equally provided a functional base pressure from which the employment of the method enables the relinquishment of gravitationally availed clean renewable energy. [00197] Referring presently to Figure 9d, a curve of terrestrial atmospheric pressure vs. elevation with respect to sea level is provided for reference to the method of vacuum- compression pumping of liquid fluids to elevation, which in particular shows that a serviceable degree of pressure is available for utilization (ie: with which to develop naturally-provided lift-legs of serviceable height) up to 3000 m above sea level or more, and that successful utilization of the method may be advantaged in regions such as the Dead Sea, which in being located in a significant depression may be provided greater naturally-provided lift-legs through inducement of said gravitationally created atmospheric pressure energy to do work.

[00198] Referring now to Figure 3, a system is illustrated which may effect the transferral of pressure energy from a gaseous fluid to a liquid fluid to be displaced to elevation without utilizing inefficient present-day liquid fluid pumping methods, with said energy transfer being caused so as to enable largely continuous 'pumping' action while affording substantial conservation of the energy expended to effect said conduction of liquid fluids to elevation, and which system may further be utilized interchangeably with means disclosed in respect to Figure 2 to enable the more-direct communication of liquid fluids to greater elevation concurrently with availing greater remunerations of power generation beyond that previously discussed due to said conservation of energy afforded by the system presently discussed. Through distribution of this embodiment's compression energy-product ever-confined within the system and meanwhile directing the expression of the system's vacuum pressure so as to prime the system with liquid fluids by inducing the atmospheric pressure energy to do so, while not permitting ingress of said atmospheric medium into the system (except as desired in terrestrial air-filled systems to initially load the gaseous fluid charge and or to thereafter make up losses in the gaseous fluid charge's mass due to its dissolution into the liquid fluid medium), through confinement and shuttling of a largely fixed charge of pressurized gaseous fluid (which pressure energy is largely conserved) always within the confines of the system, said largely conserved pressure energy may be re-used over and over again to effect a great many conductions of fantastic volumes of liquid fluids to elevation.

[00199] While the presently disclosed system differs from other examples of vortex energy extraction discussed herein, commonalities with the general theme of the invention's features and functionalities are nevertheless evident in: (liquid) fluid collection devices provided by pressure-compatible capacities 330 subjected to vacuum or vacuum-like pressures which may be filled by enhanced velocity efflux fluid flows developing there-into by the pressure of the ambient atmospheric medium causing liquid fluids to enter there-into submerged liquid fluid ingress ports in largely evacuated capacities; fluid extraction devices taking the form of further capacities 330 with further submerged liquid fluid egress opening(s) largely orthogonal or 'leeward-facing' compared to the gaseous control pressure communication ports and liquid fluid ingress ports of said capacities which when subjected to positive pressure differential via the application of high system- generated gaseous fluid reference pressures therein in the presence of check valve means ensuring their energies only cause the discharge of liquid fluids through said leeward-facing openings resulting in fluidic egress in a direction through which gaseous fluid escape is prevented by a contiguous liquid fluid seal and suitable head of liquid fluid; free-vorticing working fluid flow flows; one or more work extraction disc turbines driven by said vorticing fluid flows caused to tangentially approach optimally-spaced discs of same within a housing having discharge outlets placed in fluidic communication with the inlet to a vacuum producing device capable of exacting low pressure upon the vortex line of the disc turbine's vortex flow concentrically rotating coaxially with said work-extracting disc turbines so as to develop increased tangential velocity and greater shear-stress, shear-force, torque and power there-for.

[00200] Referring in particular now to Figure 3a, at left a large fluid collection device (FCD) 330 is subjected to a vacuum or vacuum-like pressure reference expressed therein through open vacuum isolation valve 1986 thereby causing liquid fluids (assumed to be water in the example) to be pushed there-into said capacity by the externally acting atmospheric pressure due to the observed pressure differential across the (accordantly) open liquid fluid check valve 290, resulting in the liquid fluid level rising therein said capacity. Meanwhile, application of the higher system reference pressures developed by interposing VCM (VCM) 2000 may either cooperate with a low pressure application at an upper elevation, or may push liquid fluids to elevation through a height respective to the gaseous pressure exercised by VCM 2000 upon the liquid fluid within capacity 330 while referenced against atmospheric (or another) pressure exercised upon the liquid fluid outlet at an upper elevation. With said VCM 2000 comprising a three-stage 283, 284, 285 vacuum-compression disc device operating to evacuate gaseous high pressure control fluid from one pressure compatible capacity 330 while concurrently loading said control fluid - post pressure-homogenization by said multi-staged compression thereof - into a cooperating pressure-compatible capacity 330 (or capacities) by way of high- pressure 1994 and vacuum- (or low) pressure 1984 compatible conduits and appropriately energized and de-energized high-pressure 1996 and vacuum- (or low) pressure 1986 isolation valves), it may be seen that there are no external outlets available through which the pressurization energy applied to said gaseous control pressure may be lost, and therefore except through dissolution into the liquid fluid, said pressure energy may be largely conserved. With a possibly great volume of pressurized gaseous control fluid available in the 'currently-pumping' capacity, upon changeovers to pumping from the alternate capacity replete with liquid fluids, said great volume of already-pressurized gaseous control fluid may readily be applied to the alternate capacity via a shunting isolation conduit or conduits ny way of valve or valves 298, and during the 'shunting period the VCM may simply be de-energized until such time as the pressures between the capacities approach toward equalization as may be sensed by a differential pressure switch or a flow switch positioned so as to sense such conditions 'in' the shunt conduit. It may be readily understood therefore that with the VCM (pumping means) being enabled to be shut down while pumping continues in said manner, that this arrangement may conserve great measures of energy beyond present- day pumping methods employing cavitation-prone pumps required to run when pumping is required and which fight gravity, great weight density and liquid fluid viscosity in order to effect said pumping.

[00201] Returning now to the discussion, at a particular liquid fluid level as controlled by a discrete level sensing device such as upper float 289 (with an electrical contact) said particular liquid level in causing an orientation change in the float may thereby trip said electrical contact to its alternate position-state, whereupon as indicated in Figure 3b, a de-energization of VCM 2000 may be effected, a bypass (shunt) valve 298 may be opened so as to allow high-pressure gaseous fluids to be communicated from the right hand capacity 330 to the left-hand capacity 330, and at some point in the 'wind-down' period of VCM 2000, for example after a timer effected count period, closure of the high pressure gaseous control fluid supply conduit valve 1996 as well as vacuum communication valve 1986 may be effected. While a wind-down may not be required per se, and should said valves be closed immediately said Tesla-type VCM may readily exhaust the limited gaseous control fluid within vacuum conduit 1984 and simply act as a flywheel (provided substantially frictionless bearing means and ade-coupling of implicated load by the motor is availed) and in which case the Tesla-type VCM device may yet be running at a substantial angular velocity when the shunt period has elapsed at which time re-energization may be accomplished with reduced energy consumption.

[00202] During the shunting period the high-pressure high volume gaseous control fluid in migrating to the left hand capacity in the figure effects an opening of check valve 290 permitting liquid fluids to be conducted to elevation via conduit 1954. As indicated, since a higher-than ambient pressure gaseous control pressure is utilized, there may be a period during the overall shunting period when liquid fluids from both capacities are at a pressure significant enough to effect their communication to elevation dependent upon the height of lift-leg implicated. As discussed when pressures approach equalization and the flow there-through the shunting conduit and valve 298 diminish, and in a properly configured system cuing (which may be effected via an alternate float position orientation change) may effect or provide information in the form of a signal further utilized by a controller which may then effect: closure of shunt valve 298 concurrently with; an opening of high pressure gaseous control fluid supply valve 1996 causing high pressure control fluid to add pressure energy to left-hand capacity 330 to cause it to 'pump' the liquid fluids contained therein at a greater rate to elevation, while; and thereafter cause opening of vacuum application valve 1986 of the right hand capacity 330 concurrently with; the re-energization of VCM 2000 so as to resume the electrical- energy-consuming portion of the pumping cycle wherein the pumping of liquid fluids to elevation is continued from left-most capacity 330.

[00203] After a period of time in this state and as the pressure in right hand capacity 330 is diminished further, at some point the combined pressure afforded by atmospheric pressure plus the pressure due to the external liquid fluid column (that head effectively above the height of the liquid fluid surface level within capacity 330) may exceed that sum of pressures afforded by the head of liquid plus remnant gaseous control pressurization fluid pressure within said capacity 330, at which time liquid fluid supply check valve 291 as shown in (and now turning the discussion over to reference to) Figure 3d may open changing its state to be open check valve 290 subsequently permitting ingress of liquid fluids there-into said capacity 330 to effect its filling until such time as a similar change of state in a discrete level detection device 289 may effect a similar changing of control states respecting: VCM shut-down; isolation of VCM at an appropriate time via; high-pressure gaseous reference control valve 1996 closure and; vacuum valve 1986 closure, which may then continue the pumping of liquid fluids to elevation in an 'un-powered' portion of the system cycle wherein liquid fluids are continued to be pumped to elevation from said right-most capacity 330 until a further right-hand capacity discrete level detection device orientation change or another type of level detection equipment may directly or by way of a signal to a controller such as a PLC, effect closure of the bypass (shunt) valve 298, as well as a subsequent re- energization of VCM 2000 and change of valve states already discussed to complete yet another 'powered' displacement o fliquid fluids to elevation.

[00204] Not shown in the figure, however implied herein by way of example and subsequent discussion, a further work extraction means may be driven via utilization of the pressure differential between the capacities 330 communicated through bypass (shunt) valve 298 where-through a preferably large volume of gaseous pressurization control fluid may be passed twice per (effective, two-capacity-considered) cycle for approximately half of the overall cycle time. As may become evident, then, with the VCM 2000 shut-down during this time period, and said alternate work-extraction device (such as may be provided by yet another disc-turbine with optimally spaced discs producing electrical energy generation during the velocitous transfer of gaseous control fluid from one capacity 330 to the other 330 may recover a substantial portion of the energy required to effect subsequent 'powered phase' pumping cycles, to further reduce the consumption of electrical or other energy required by such systems pumping liquid fluids to elevation.

[00205] The tangential discharge of gaseous control pressurization fluid from VCM 2000 provides a desirously energized working fluid emission at a velocity which may be proportionate to the angular velocity of said VCM as well as the diameter of the discs utilized therein, provided approximately optimal disc spacing is provided. While the purpose of said energized working fluid is to load pressure-compatible capacities 330 so as to act upon liquid fluid surfaces to effect the conduction of said liquid fluids to elevation, since the system affords a degree of conservation of said compression energy, and since dynamic to static energy conversion is required, it may be foreseeable that said high velocity gaseous pressurization control fluid may be optionally utilized as a fluidic coupling there-between shafts so that as shown in the figure, a separate disc turbine mounted within an interposing high-pressure compatible capacity may provide service as a dynamic to static pressure recovery apparatus which while slowing down the energized working fluid through viscous energy communication with the disc surfaces thereof said auxiliary disc turbine, may concomitantly avail recovery of a portion of the kinetic energy of motion delivered to the gaseous pressurization control fluid through centrifugal-viscous acceleration thereof said working fluid while through VCM 2000 thereby providing even further minimized energy consumption to effect the conduction of liquid fluids to elevation.

[00206] With reference now to Figure 4 in conjunction with an understanding of the practical service advantages, energy conservation, and power generation which may be offered in respect to the application of said evacuation-compression 'pumping' method (discussed in relation to Figures 1, 2 and 3) it may be surmised that this concept should lend itself to alternate applications and scalar functionalities in myriad smaller and beneficially greater forms which may desirously provide new large scale clean power- plant operations, engines for automobiles and other forms of transportation, as well as remote and or point-of-use electrical generation means. Such an extrapolation in the context of a low power consumption, high torque output engine design is herein provided in conjunction with the ten-part figure describing a typical sequence of events for its operation and of which an acronymic name for said technology "VIVE" for "Viscosity Vacuum Engine" is heretofore utilized both for abbreviated purposes but which may also be suggestive of its comparative potential benefit on this planet and elsewhere in the extended context of clean engine technology for the future.

[00207] Based upon the same general premise, while taking particular advantage of the version of the method in which high gaseous control fluid reference pressures are provided internally to the system as in the latter examples of Figures 1 and 3, the presently discussed system and sequence of figures avails run-time engine operation independent of communication with the atmospheric medium, and may therefore be contemplated to avail operation wherever significant enough gravitation or rotational energy (as may be provided on a space-station where artificially simulated gravitation) is present with which to permit the continuous segregation of liquid fluids from gaseous fluids for serviceably continuous operation as by the maintenance of a largely contiguous gaseous-liquid fluid interface level within capacities employed by the system, which by this definition may permit its operation largely anywhere in the universe governed by the traditional 'laws' of physics.

[00208] The presently disclosed system pits the lightness of density and dynamic viscosity as well as the compressibility of air (or of another preferably inert - or in combination with a provided liquid fluid, non-reactive - gaseous fluid medium, whether heterogeneous or homogeneous in nature) into service with a multi-stage Tesla VCM (VCM) tasked with the evacuation of gaseous pressurization control fluid from gaseously pressurized liquid-fluid-depleted capacities and the concomitant application of gaseous control pressurization fluid into alternate liquid-fluid replete capacities strategically-paired at run-time by a suitable controller with analog and discrete input and output capabilities which in conjunction with feedback received from sensor information in the form of level, pressure, flow and other system state information may monitor and also control, through valve cycling and or via manipulation of regulation means set-points, the operation of the system serving to permit the continuous transfer of gaseous pressurization control fluid throughout the system in such a fashion as to cause the transfer of liquid fluids from one capacity to another through a disc turbine configured for liquid fluid service, and thereafter cause secondary capacity-pair(s) to in contiguous fashion effect largely identical communication(s) of another mass of liquid fluid while said first-named capacity pairs' liquid fluid is in the mean-time prepared - via intra-system gaseous fluid pressure conservation measures - for re-communication of said first-paired liquid fluids back to the originally replete capacity of the 'pair', or elsewhere if programmed and designed for such service.

[00209] With said VCM comprising a multi-runner 201 disc compression means disposed between low 1980 and high 1990 pressure reservoirs so as to enable amassing the larger portion of the gaseous control fluid mass of the system in said high pressure reservoir 1990, and with the system being further capable via valve means to direct the application of a regulated discharge of said gaseous pressurization control fluid within the system between paired pressurization-reservoirs (capacities) wherein said liquid fluids occupy a concomitant portion of said capacities, and wherein high and vacuum (or other low gaseous system reference pressures) may thereby be expressed at opposite 'ends' of given pairings of conduits and capacities through a controlling set of intercommunicating valves (and conduits). A liquid fluid work extraction or conversion prime-mover means (herein contemplated to be a Tesla-type disc turbine optionally having run-time-optimized inter-disc spacing as provided by the invention, but which may be another prime mover or variation of same) receiving the flow of intra-system- confined liquid fluids developed via temporary application of a desirously large gaseous control-pressurization differential pressure substantially across the gaseous-liquid fluid interface surfaces (levels) at opposing 'ends' of said liquid fluid 'circuit' may cause the development of shear-stress, shear force application, torque and shaft rotation of said prime mover applied to the plurality of disc surfaces comprising the preferred disc turbine, whereby a fairly viscous liquid fluid (herein contemplated to be water, but which may be largely any suitable viscosity liquid fluid) may develop work in proportion to the dynamic viscosity thereof said liquid fluid through the work done there-upon (in causing said liquid fluids to pass through said liquid fluid configured turbine 200) by said gaseous control pressure fluid of substantially lesser density and viscosity.

[00210] Before proceeding with the following description, it must be understood that: the application of shear-stress and shear force by VCM gaseous fluid compression discs wherefrom radial pressure gradient developed is additive in accordance with the centrifugal acceleration effect of said runner(s) and thereby serves to increase the pressure at each stage of outlet, and; the greatly lower viscosity of the gaseous control pressure fluid (ie: air in the example given herein) implicates less load upon said compression means which may thereby operate at significant angular velocity as a largely unloaded system of revolution (22) and may therefore be very efficient. For satisfactory system operation high pressure reservoir 1990 may be sized two or more times the capacity of individual pressurization reservoirs 330 of the system and may further be maintained at a pressure significantly in excess of liquid fluid pressure regulator 1953 (ultimately controlling liquid fluid turbine 200 working fluid pressure and throughput in conjunction with pressure controller 1938 setting the position of said regulator based upon, for example, output shaft speed feedback information received from shaft speed indicating transmitter 1931) so that the declining (by design) liquid fluid level therein the actively sourcing pressurization reservoir 330 implicating a gaseously occupied zone of increasing volume in which the gaseous pressurization control fluid must provide largely constant pressure upon the liquid fluid surface to at length allow liquid fluid pressure regulator 1953 to provide a steady application rate of liquid fluids through said liquid fluid turbine 200 at run-time to extendedly permit regulated output power from the system. An optional, however desirous feature of the system may provide for pressure regulator 1997 to be remotely adjustable as by the application of a control signal from a controller means (not shown) so as to dynamically adjust the gaseous pressurization control fluid set-point at run-time if required, for example, due to a leak in the system, or a system in need of maintenance which may include dirty or clogged pipes.

[00211] In said liquid fluid circuit, significant differential pressure developed via the application of high and low or vacuum gaseous control pressures to 'opposite ends' of said liquid fluid circuit may thereby apply a desirously motivating high gaseous system pressure across the surface thereof a liquid fluid replete pressurization reservoir 330 while concurrently providing a minimization of or alternately a lack of back-pressure in a liquid fluid depleted liquid fluid pressurization-reservoir 330 to which said liquid fluid may thereby be conducted with a minimum of opposition at run-time, which liquid fluid is communicated so as to pass through a nozzle such as a de-Laval type nozzle increasing the velocity of said conducted liquid fluids to achieve substantial efflux velocity for further application (en-route to said to said liquid fluid depleted pressurization reservoir) to a disc turbine 200 configured for liquid fluid service. With a desirously high dynamic liquid fluid viscosity as may be surmised by inspection of Equation 3, a great shear stress, shear force and torque may therefore be applied to the shaft 202 of liquid fluid turbine 200, and which in turning at a lower angular velocity than the VCM, may therefore minimize the effect of negatively imposing radial pressure gradient opposing work generation in disc turbines.

[00212] With the energy of compression largely conserved by the system wherein pressurization control fluid and the evacuation thereof may be advantageously applied as discussed to create favourable liquid fluid pressure differentials, and wherein pressurization control fluid may also be shunted through a plurality of pressure-stepped paths so as to minimize the energy expenditure required to re-assimilate lower gaseous fluid pressures back into the higher pressure reservoir 1990, and wherein power may therefore be withdrawn from the system largely in proportion to the ratio of viscosities of the liquid working fluid forced to pass through turbine 200 in relation to the viscosity of said gaseous working fluid substantially effecting the 'pumping' of said liquid fluids there-through said liquid fluid turbine 200 means, it may be stated that an efficient system for the generation of work may be represented hereby wherefrom a portion of the power withdrawn may be utilized to run a motor such as the one contemplated to effect the required continuous compression of finite quantities of gaseous pressurization control fluid of greatly less absolute viscosity than the liquid fluid of the system.

[00213] At the heart of the system, isolated high-pressure reference capacity 1990 provides a source of gaseous control fluid replenished at run-time by the system's VCM. An accompanying pressure-management sub-system comprising a plurality of normally- isolated and independently-regulated shunt-conduits permitting gaseous control fluid entry only into particular stages of the multi-stage VCM at about the respective stages' outlet pressure may thereby permit the gaseous control fluids (post liquid-fluid compression- stroke) to be re-compressed to the high system reference pressure with a minimum of implicated load upon the system, ensuring that the energy of compression conserved within the system is readily re-availed for the system to make use of again in as short a time-span as possible so as to enable a regular work output, and also works to system advantage by never 'flooding' the first lowest pressure stage of said VCM with undue volumes of high through low pressures helping to thereby ensure that the 'vacuum' conduits of the system are maintained at a largely consistent low pressure for further application to the low pressure side of the liquid fluid turbine through the continuity of communication provided through the liquid fluid.

[00214] While the pressure in said high pressure reference capacity 1990 may ultimately be governed by the VCM' angular velocity, disc separation and disc diameter as well as by other factors to a lesser degree, for purposes of discussion herein, let it be assumed that said sizing may permit the high-pressure system reference to be maintained at a pressure about twice that of power generation turbine 200' s demand pressure as set by pressure regulation means 1953 or 1957 so that over the time-constant of the power cycle during which one pressurization-reservoir 330 volume of liquid fluid may be displaced by an equivalent volume of pressure-regulated gaseous control fluid (substantially effecting the 'push' of said liquid-fluid to and through turbine 200), that with the continuous replenishment of said gaseous control fluid into the high pressure reference capacity 1990 by said multi-stage VCM in combination with pressure regulation offered by pressure regulation valve (PRV) 1997 prior to application to pressurization-reservoir(s) 330, that a largely constant regulated-high-pressure reference with a minimum of pressure disturbance in operation may thereby be availed under varying load conditions for application to said pressurization reservoirs 330. [00215] While in the presently disclosed system two pairs of liquid fluid pressurization reservoirs 330 are employed and therefore it may be stated that the permissible time- constant of re-assimilation for gaseous control fluid issuing from high-pressure system capacity 1990 to be returned there-into - post said gaseous control fluid's cooperative service in forcing a pressurization reservoir 330 volume of liquid fluid through turbine 200 - in general may be stated to be largely equal to or less time than the duration of the liquid fluid power cycle 'liquid fluid push' discussed in order for the system's high pressure reservoir 1990 to maintain ample high pressure pressurization control fluid to sustain system operation, it must be considered that owing to the high degree of conservation of pressurization energy provided by the presently disclosed system wherein pressure energy is distributed but not expelled (lost) to atmosphere and minimum-energy-of-recompression paths (through valves 297 and 1999, herein considered as pressure-management shunting-conduits) are provided to facilitate said gaseous pressurization control fluid return to said high system pressure with a minimum of work and time thereby minimizing the input energy required as well as time required for said re-assimilation process, that a workable time constant for said re-assimilation (ie: the amount of time before a given quantity of gaseous pressurization fluid may actually need to be 're-issued' from capacity 1990 for similar 'power cycle push' purposes) may be designed to be greater than the aforementioned singular liquid fluid 'power cycle push' time constant, since: high pressure capacity 1990 which may comprise a reservoir 'charge capacity' multiples in excess of the per pressurization volume 330 throughput requirement, while pressure regulator 1997 supplying gaseous pressurization control fluid to the liquid fluid circuit for temporary use may be operated with a set-point pressure-multiples above power turbine pressure requirement, which may permit gaseous pressurization control fluid a degree of residence time in pressurization reservoirs 330 (before reservoir 1990 would 'run below' its design high pressure capacity and pressure) especially if more than two pairs of liquid fluid pressurization reservoirs are employed which may remove the urgency for gaseous pressurization control fluids' evacuation and recompression which may permit delayed, however nonetheless required re-pressurization of said gaseous control fluids; and since the power turbine's delivery rate of liquid fluid controlled by pressure regulating valve(s) 1953 or 1957 may be set so as to deliver said liquid fluid at a minimum rate in accordance with the dynamic viscosity of the liquid working fluid; and since disc turbine 200 in turn utilizing a plurality of parallel, co-rotating, optimally spaced apart discs may offer minimized flow channels (inter-disc gaps) with which to provide the desirous condition of streamlined, shock-free, laminar flow which may in turn minimize the working fluid throughput requirement for desired power outputs while concurrently extending the re-assimilation time constant requirement; therefore it may be stated that the transformation of any given pressurization reservoir 330' s volume of gaseous charge to smaller volume at higher pressure in reservoir 1990 may alternately be accomplished over a greater period of time providing at least the turbine throughput mass-flow is in a state of flux thereto, if provided by a plurality of pressurization reservoirs and pressure management paths concurrently

[00216] While the system VCM must be capable of re-assimilating the pressurization reservoir 330 volume of gaseous control fluid at or above design (liquid fluid) turbine working fluid pressure in a time period equal to or less than the cycle time of said liquid fluid 'push' stroke in order for the system to sustain power turbine output, and whereas the discussed pressure management tactics may advantage this goal, the further provision of one or more other coaxially rotating gaseous compression stages (as illustrated in respect to Figure 5) which may operate either in parallel with and or alternately in isolation there-from the first stated VCM so that as secondary, tertiary or other capacities are being prepared for their next service by being 'taken down' toward and to evacuation (or other serviceably low) pressure required for service, said pressure reduction through the shunt-conduits in being provided independent compression path(s) may thereby not unnecessarily pressure-load the ongoing evacuation-process requiring constant application of as low a system-provided pressure as possible in order to derive an optimized efflux velocity of liquid fluid by the currently-serving evacuation- compression 'pair' (of pressurization reservoirs 330) into and through liquid fluid turbine 200.

[00217] As discussed, it may be advantageous for such a system to operate its high pressure reference capacity 1990 with a capacity preferably twice or more that of specified liquid fluid pressurization-reservoirs 330 in order to supply as well as minimize the effect of load-variance-induced working-fluid requirements, which may require exceeding the nominal throughput requirement in order to sustain the operation of said liquid fluid Tesla turbine (or other suitable liquid fluid prime mover) at over- speed for a required duration. Under such conditions the volumetric requirement of gaseous pressurization control fluid need also be provided in excess of the nominal value, so it may be important to specify the system VCM throughput capacity an anticipatable measure in excess of the proportionate nominal liquid fluid throughput capacity so that the gaseous control pressurization fluid volume required to effect said pushing of over-speed representative capacity liquid fluids through said turbine under excess load conditions may be provided without experiencing a shortage of high pressure gaseous pressurization control fluid.

[00218] While the following statements are applicable to the presently disclosed embodiment, they are equally applicable to Figures 5 and 6 as well. Since the selected liquid fluid (water in this case) should be sufficiently free (ie: be of relatively low viscosity) so as to allow its ready passage through system 'piping' conduits which may advantage the flow-rate of liquid fluids pushed and drawn there-through by being provided at greater diameter than might normally be prescribed for the actual design flow and pressure conditions of turbine operation so as to permit the further incorporation of appurtenances disclosed by Schauberger (23, 24, 25) which may through the development of a central core flow in rotation also provide disruption of the viscous attachment of the fluid at the (pipe) wall boundary layer of said flow conduits which may thereby permit freer flow there-through said conduit(s) so as to at length supply working fluid to power-generation turbine 200 with minimized pressure loss. With the viscosity of said liquid fluid (water in this case) developing power through said liquid fluid power turbine in proportion to the dynamic viscosity of said liquid fluid which may be many-fold times the viscosity of the gaseous fluid generating the pressure energy by which the power-producing liquid fluid is driven unto and through said power-turbine, (ie: 55 x air viscosity at 20 ⁰ C, and 104.5x air viscosity at 0 ⁰ C), it may be apparent that cold engine technology may be advantaged through the employment of disc turbines, and; since Equation 3 equally represents the torque which may be applied by a complement of discs to a fluid (as in the case of the air-compression of the VCM of the system creating the gaseous fluid high pressure reference wherein said torque is dispersed therein as shear-stress in the layers of laminar flow preferred between the co- rotating discs cooperating with the centrifugal acceleration applied through the angular velocity of the VCM), as it does to the torque which may be substantially applied by a fluid mass passing through advantageously spaced-apart discs (ie: in the case of power- producing liquid fluid turbine 200, wherein the shear-stress between layers of laminar flow preferentially channelled by advantageously spaced apart discs of said turbine results in the application of shear- force to largely the full effective surface area of every one of the plurality of discs in such turbines, collectively resulting in turbine torque) except in reverse relation, and; since if one considers the rotation of equally dimensioned turbines at equal angular velocity and working fluid speed, the turbine being driven by the working fluid of greater viscosity will produce the greater torque and therefore power as per Equation 3, above, and; in corollary, if one considers rotation of equally dimensioned disc compressors at equal angular velocity and working fluid speed, the compressor driving the working fluid of lesser viscosity will require less work input to effect a similar compression, and; compressing a gaseous working fluid of lesser dynamic viscosity in order to derive pressure energy utilized to then pressurize and further drive a liquid fluid of much greater dynamic viscosity (instead of a liquid fluid pump being utilized to effect such liquid fluid pressurization, which as discussed may suffer inefficiencies) to generate work may permit affording the multiplication of work done by the engine in accordance with the ratio of relative dynamic viscosities, ie: μ Water / μ Air ; and since the system has by design an excess of high reference pressure gaseous fluid capacity with which to effect the pressurization and 'push' of said liquid fluid unto and through liquid fluid turbine 200 so as to sustain said turbine rotation and generate power thereby at a multiple of the energy input required to effect the compression thereof the 'drive fluid' (air), and; that the concurrent vacuum / low pressure developed by the system VCM through the same compression function utilized to effect the pressurization 'push' of working fluid through power generation turbine 200, which may concurrently act to draw the working fluid into an evacuated liquid fluid depleted pressurization-reservoir 330 minimizing the energy required of developing such separate pressure references for application by providing both in a single operation, then; since in this engine method the high pressure reference gaseous fluid is compressed, cycled, shunted and re-compressed (and is also provided multi-pressure minimized-energy-of-re-compression paths, as discussed, to minimize the energy expended in the implied total recompression), however, in said closed loop is never released (lost) to the atmosphere, it may be stated therefore that largely the whole of the energy of compression expended by what may therefore be an accordantly small VIVE is conserved, and; since said VIVE permits operation with largely any gaseous fluid of preferably light density and viscosity conjunctively with largely any liquid fluid of desirously serviceable through higher dynamic viscosities (in which, preferably, explosion and flammability hazards are not a concern, and which liquid fluids serviceably adhere to power turbine 200 discs thereby permiting energy transfer between the fluid and the disc surfaces), largely any liquid fluid may thereby be utilized to 'run' said VIVE engine including: vegetable oil; hydraulic oil; used motor oil; PCB-laden transformer oil; fresh water; sea-water; waste- water; rain-water; and or other toxic waste fluid preferably availing an advantageous viscosity multiplier with respect to the gaseous pressurization fluid selected, so as to avail accordantly large torque realization therefrom.

[00219] Referring now to Figure 4a, VCM largely comprising housing 214, motor 265 driven multi-stage vacuum-compression runners 201 coaxially mounted for rotation and fixedly attached to shaft 202 turning in high-speed smooth-running bearings 210 supported in rigid bearing mounts 212 non-interfering with the axial intake and tangential egress of inter-stage flow products, which through communication with the system's low (or vacuum) pressure reservoir 1980 at its first axial inlet and communication with the system's high pressure reservoir 1990 path by way of check valve 1962 preventing the return of pressurized fluids, and further provided inter-stage pressure management communication inlet ports through isolation valves 1972 which may be opened as required to effectively isolate or permit strategically shunted compression of gaseous pressurization control fluid from various intra-system locations at run-time, said VCM operating at higher angular velocity (than power generation turbine 200 operating within the liquid fluid circuit of the system) may thereby provide effective compression of multi-pressure inputs at run-time to minimize the total energy of compression required to maintain the volume of high pressure gaseous control fluid in reservoir 1990 while concomitantly maintaining a serviceably low or preferably vacuum-like pressure in reservoir 1980.

[00220] High pressure conduit 1994 communicating high pressure fluid release from reservoir 1990 as flow 1995 communicated through pressure regulating valve 1997 while high pressure system enable valve 1940 is open is further conducted through open high pressure isolation valve 1996 to act upon the surface of the liquid fluid contained within pressurization reservoir 330a (where from left to right in the figure, said reservoirs shall heretofore be referred to in alphabetical order from left to right for purposes of discussion in this and subsequent figures, including those of Figure 5). Previously pressure-managed so as to be pre-loaded with a high gaseous fill pressure, with its intake valve 1948 closed, and with gaseously evacuated pressurization reservoir 330b open to the low pressure reservoir communicating with the intake of said VCM, heretofore referred to as VCM 2000, a serviceable differential pressure is thus placed across the contiguous liquid fluid circuit from liquid fluid replete pressurization reservoir 330a, through open check valve 290, through high pressure conduit 1954 as high pressure flow 1955, through surge tank 1950, through variable throughput pressure regulating valve 1953, through forward isolation valve 1956, through forward feed conduit 1959, through venturi turbine inlet nozzle 262 which may provide an enhanced velocity in the resultant efflux flow of liquid fluid discharged tangentially toward the discs of power generation turbine 200 staged to rotate freely on shaft 202 within housing 214 and which may thereby increase work generation or conversion by said turbine through said increased efflux velocity; through axial exhaust holes 222 and disc turbine outlet 258 as discharge flow 261, through low pressure liquid fluid conduit 1944 as flow 1945, through open low pressure liquid fluid inlet valve 1948b, into pressurization reservoir 330b shown to be under the influence of the vacuum or vacuum-like pressure (as indicated by the arrow above the liquid fluid surface representing exhaustion of said chamber; and with low/vacuum pressure hereinafter simply referred to as 'vacuum' pressure for purposes of abbreviated discussion) with said vacuum pressure being provided via communication through vacuum isolation valve 1986 as exhausting vacuum flow 1985 through conduit 1984, and through further vacuum isolation valve 1986 (normally open in operation) at the inlet to vacuum pressure reservoir 1980. Under said conditions, gaseous control pressurization fluid may be understood to exercise a high differential pressure across said liquid fluid circuit, and may thereby immediately continue (or begin) rotation of work generation turbine 200, as the liquid fluid surface drops in pressurization reservoir 330a and rises in adjacent liquid fluid reservoir 330b as indicated by arrows linked to the surfaces thereof. Note that shunt equalization valve 298c is indicated to be opened to permit pressurization reservoir 330c' s equalization to largely the regulated high system reference pressure as supplied by adjacent pressurization reservoir 330d (in process of pressure reduction) which operation is executed to prepare the previously (largely) gaseously evacuated reservoir 330c replete with liquid fluid for the later continuous (if periodic) application of the system's high regulated reference pressure as supplied by regulator 1997 during a subsequent operation when said liquid fluid of reservoir 330c becomes the active turbine working fluid. [00221] Meanwhile, condensate developed by compression in VCM 2000 and intermittently transferred is discharged from condensate reservoir 1970 through condensate discharge valve 1976 into pressurization reservoir 330 which is shown to be isolated from high pressure application through closure of high pressure isolation valve 1996, as well as isolated from vacuum pressure via closure of vacuum isolation valve 1986, yet opened via equalization isolation valve 298d and shunt isolation valve 297 and further through gaseous pressure conservation valve(s) 1999 and independent shunt pressure regulators 1993 of sequenced pressure set-point and thence through shunt / condensate isolation valve(s) 1972 to supply VCM with inter-stage working fluid which may comprise remnant gaseous pressurization control fluid, and or liquid fluid vapour given off at the equilibrium vapour pressure rate accordant to the temperature of liquid fluid remaining in pressurization reservoir 330d. Note that condensate may freely accumulate at run-time in condensate pot(s) 1970 while pressurized at various pressures respective of the particular stage of compression accessed thereby said condensate conduit.

[00222] With reference now to Figure 4b expressing largely the same valve state conditions, it may be seen that the liquid fluid of pressurization reservoir 330a is in process of transfer to reservoir 330b with liquid and gaseous fluids in the fluid circuits responsible for developing power following the same paths as in Figure 4a. Valve 298c has been closed, however, indicating that the permitted equalization time constant has elapsed and said reservoir in being closed off by all valves there-communicating with it is thereby placed in stasis awaiting application of the full high system pressure reference to place it into service as the active turbine liquid fluid supply source. Notwithstanding, pressure conservation effecting the re-assimilation of gaseous pressurization control fluid from pressurization reservoir 330d is shown to be still in process, however, the pressure therein said reservoir is indicated to be reduced since (rightmost) highest gaseous pressure conservation valve 1999 is closed, and leftmost lowest pressure conservation valve 1999 has been opened permitting a minimal pressure gaseous fluid feed to pass through low set-point pressure regulation means 1993 into the vacuum/low pressure system reference capacity 1980, which although loading the low pressure reservoir and increasing the back-pressure upon the liquid fluid power generation process to a degree dependent upon said regulator's set-point, may adequately deplete the pressure in next-to-receive liquid fluid pressurization reservoir 330d which is duly prepared thereby. Note that to offset this temporary backpressure increase, either regulation means 1997 or 1953 might be automatically controlled to have an equally temporary pressure set-point increase. Also noteworthy is that the final stage of depressurization of reservoir 330d wherein only the leftmost vacuum shunt conduit / pathway is opened so as approach largely complete exhaustion of pressurization control fluid from reservoir 330d.

[00223] Referring now to Figure 4c illustrating an alternate system state post- changeover to pressurization reservoir 330c (indicated by arrows acting downward upon the liquid fluid surface interface therein) actively supplying liquid working fluid to turbine 200 through its open liquid fluid check valve 290 and previously described path through said work generation turbine 200 and common communication conduits already stated, and with the ambient pressure within pressurization reservoir 330d having previously been drawn down ideally to the vapour pressure of the liquid fluid therein and indicated to be placed under vacuum in the figure through vacuum isolation valve(s) 1986, and with its low pressure liquid fluid isolation valve open thereby communicating said vacuum or vacuum-like pressure to the liquid fluid circuit where-through turbine 200 and conduits discussed the high regulated system pressure acting on the liquid fluid surface of adjacent liquid fluid replete capacity 330c as communicated thereto through open gaseous high pressure isolation valve 1996 is thereby referenced, thereby exercising a significant pressure differential across the 'open' ends of said liquid fluid circuit, which being the same differential pressure as the previously applied pressure differential (ie: that exercised across the liquid fluid circuit in the previous two figure parts a and b) an identical efflux velocity, turbine rotation and power output may thereby be maintained, especially in consideration of the control exercised by pressure regulating valve 1953.

[00224] While condensate discharge valve 1976 is closed, condensate pot 1970 is shown to be accumulating condensate delivered thereto through the interposing header conduit connecting therewith the condensate isolation valves 1972 isolating the respective vacuum pressure through full VCM/system high pressure condensate drain conduits through respective condensate pots 1970 integral to each respectively pressure sequenced condensate drain. Condensate removal is important in disc device application since a high angular velocity of the system' s VCM need be maintained for sustainable gaseous component system operation, and runner contact with liquid fluid although not disastrous to a Tesla type disc device, would nevertheless impose significant parasitic drag loading which may implicate a greatly reduced high system pressure reference as well as significantly affected (elevated) vacuum pressure which may prevent proper system operation. In the subsequent figures, a sequence of condensate discharge events is portrayed in which first vacuum pressure, and subsequently mid-pressure, higher pressure, and finally full VCM unregulated system pressure sections of the pressure conservation and reservoir sections of the system are substantially drained into a master condensate pot 1970, and substantially once per system cycle, with individual condensate isolation valve(s) 1972 closed, when the host condensate reception reservoir (shown to be reservoir 330d in the figure) has completed a liquid fluid (power cycle) 'push' and is at a gaseous high pressure, condensate drain valve is opened and left open for condensate to return to the liquid fluid circuit of the system, and through pressure reduction through the stages of pressure conservation, said headered condensate drain line is taken down to vacuum pressure in preparation for the successive cycle of condensate drain events beginning, as discussed, with the vacuum pressure drain event.

[00225] The temporary equalization of pressure from reservoir 330a to reservoir 330b is also illustrated in the figure, which equalization is to be taken as having been completed and valve 298b in process of closing (said fluid pressure equalization and valve 298b' s opening being purposefully short-lived in duration to effect said pressure equalization with the comparatively small volume of reservoir 330b and retain as high a conservation pressure pre-loading as possible in preparation for its later 'active-reservoir' operation), meanwhile post-equalization (however shown on this figure to reduce figure-count) pressure conservation shunt valves 1999 being opened permit the drawing down of reservoir 330a to lower pressure in preparation for its next vacuum-application active- reservoir service. Regarding said equalization, it may be considered that if the pressure set-point of the system's high reference pressure regulator 1997 were raised to be two or more times that of the liquid fluid power turbine regulator 1953 set-point, then the equalization process itself might produce a second power cycle 'push' of liquid fluids from reservoir 330b through turbine 200 and thenceforth to another reservoir 330 under vacuum pressure, however the present system does not contemplate such application and added equipment and conditional considerations would also be necessitated including an extra pressurization reservoir 330, appurtenances and controls there-for. [00226] With reference to Figure 4d illustrating largely the same condition-set of valve states as the previous figure, the liquid fluid transfer is shown in progress as indicated by down-arrows on the surface of liquid fluid in reservoir 330c and up-arrows apparently lifting the liquid fluid interface surface in reservoir 330d. Notable differences between the present and prior figure being: the mid-pressure condensate drain event taking place through open valve 1972 (note that pressure conservation may concurrently continue through adjacent regulator 1993 since the condensate drain line through to master condensate pot 1970 represents an expansion zone for the gaseous fluid exhausting from reservoir 330a since the stated condensate drain line was lastly at vacuum pressure), and; pressure conservation paths have been alternated, with the high inter- stage inlet being swapped for the vacuum inlet indicating pressure has been drawn down below rightmost regulator 1993 set-point.

[00227] Referring now to Figure 4e illustrating largely identical valve states as the previous figure, the present system 'snap-shot' describes conditions at the moment prior to changeover to an alternate reservoir communication-pair. With the liquid fluid surface in pressurization reservoir 330c under the continued influence of high reference pressure gaseous control fluid, said liquid interface continues to be acted upon by greater pressure than the pressure set-point of liquid fluid regulator 1953 and thereby continues to force liquid fluid through the liquid fluid circuit for work production purposes (as indicated by down-arrows on the liquid fluid interface therein), meanwhile its paired complement liquid fluid collection/reception reservoir 330d shown to be nearly replete with liquid fluid (the level of which is still increasing as indicated by up-arrows at the liquid fluid surface) via open vacuum isolation valve(s) 1986 continues to exhaust the temperature-derived vapour pressure of the liquid fluid remaining in reservoir 330d (which for water at 30°C is only about 4% of atmospheric pressure).

[00228] While the final stage of decompression of liquid fluid pressurization reservoir 330a is indicated to be proceeding via equalization valve 298a, shunt isolation valve 297, vacuum pressure conservation isolation valve 1999, vacuum pressure regulator 1993 and condensate isolation valve 1972 thereby drawing reservoir 330a down in pressure to approach the vacuum pressure of VCM 2000, higher inter-stage pressure condensate is released through condensate isolation valve 1972. Note that since the pressure conservation pathway through valve 1999 is closed that it is preferable that upper condensate isolation valve 1972 be closed as well to better conserve the energy of compression by maintaining compression throughput momentum toward high system pressure reservoir 1990 (instead of side-stepping developed pressure into the condensate line, which would otherwise result if lower valve 1972 were left open).

[00229] The changeover process shall now be described (which is applicable in like manner to other changeovers implied herein to occur at the time when the currently sourcing liquid fluid pressurization reservoir runs low on working fluid therein necessitating other pressurization reservoir pairs to become the actively sourcing and receiving liquid fluid capacities) which in practice may occur in the moments of time subsequent to the present figure, however for which no dedicated figure is provided since this may happen over many 'snapshots' in time) wherein once the liquid level in the actively sourcing liquid fluid pressurization reservoir (330c in this case) has reached or become lower than the level permissible by the set-point of low level switch LSL 1934c (the sensor of which in practice would be placed in a region of the reservoir sheltered from the effect which 'sloshing about' may have upon a valid instrument reading which may for example in an automobile application be caused by washboard- like road surfaces), the opening of high pressure isolation valve 1996b (resuming gaseous control fluid pressure loading of pressurization reservoir 330b) may be controlled in preparation for changeover. Note that at this point check valve 291b may open due to the larger liquid head pressure in reservoir 330b compared to that in reservoir 330c while both respective liquid fluid surface(s) are concurrently acted on by the equivalent gaseous control fluid pressure, which may largely halt liquid fluid egress from reservoir 330c concurrently with liquid fluid egress from pressurization reservoir 330b commencing to maintain the liquid fluid throughput through the liquid fluid circuit. In the subsequent instant of time the opening of vacuum isolation valve 1986a largely concurrently with the closing of shunting/equalization isolation valve 298a lowers the pressure on the liquid fluid surface therein reservoir 330a from that of the regulated discharge path to the 'full' vacuum pressure of the VCM and thereby applies the effort of said VCM on the fluid load offered by the vapour pressure of the liquid fluid in reservoir 330a) and further enables reservoir 330a to receive liquid fluid from the liquid fluid circuit (at a shortly-to-be-realized later instant in time) as may be commanded by a controller (not shown, but indicated to be monitoring all process signals shown in the figures as well as providing timers and set-point values for reference and action). When high level switch LSH 1933d is triggered by the liquid surface level rising to or above the level set-point programmed there-respective-to, low pressure liquid fluid inlet valve 1948a may be opened (thereby permitting liquid fluid pressurization reservoir 330a to receive liquid fluid from the liquid fluid circuit (working fluid discharge from work producing turbine 200) and shortly thereafter, vacuum isolation valve 1986d may be commanded closed causing pressurization reservoir to (gently) no longer be preferred by the liquid fluid circuit as 'the place to go' since the path of least resistance (toward the lowest pressure) may be rather found via entering pressurization reservoir 330a into which liquid fluid is thereby caused to flow. After a programmable time-out period, low pressure liquid fluid inlet valve 1948d may then closed to isolate reservoir 330d in preparation for its re-pressurization, where- respective-to the subsequently described figure continues the discussion.

[00230] With reference now to Figure 4f, post changeover (from reservoir pair 330c and 330d being active), reservoir pair 330a and 330b are shown to be actively receiving and sourcing liquid working fluid respectively, and with high pressure isolation valve 1996b open thereby applying high regulated system pressure through regulator 1997 upon the surface of the liquid fluid level interface in reservoir 330b liquid fluid there-from said reservoir is indicated (by down arrows on the liquid fluid surface in said reservoir) as being forced out open check valve 290 to supply the liquid fluid power-deriving circuit, while the liquid fluid level interface in reservoir 330a is indicated to be rising due to receiving the liquid fluid 'push' throughput from adjacent reservoir 330b (as indicated by up-arrows at the surface thereof) and while off-gassing vapour pressure in accordance with temperature as previously discussed, said vapour along with any remnant air or other pressurization control fluid specified is meanwhile exhausted through open vacuum isolation valve(s) 1986.

[00231] Two successive pressure conservation events are illustrated in this figure: firstly indicated is the brief pressure equalization event of liquid fluid replete reservoir 330d obtaining a high percentage of the regulated load pressure of liquid fluid depleted reservoir 330c through equalization valve(s) 298c and 298d (which gaseous load pressure as discussed may be well in excess of the demand pressure set-point of liquid fluid pressure regulating valve 1953, thereby preparing reservoir 330d for a subsequent sourcing operation), and; secondly is the subsequent pressure conservation of said high load pressure applied to reservoir 330, whereby after the equalization event with adjacently-paired reservoir 330d has been completed and valve 298d has been closed, the opening of the pressure conservation paths through rightmost shunt isolation valve 297 as well as rightmost pressure conservation valve 1999 gaseous permits exhaust of the high load pressure of reservoir 330c into VCM 2000' s high pressure stage through which it may be centrifugally accelerated and released from the VCM into a dynamic to static pressure recovery housing region from which it may pass through check valve 1962 directly into the high pressure reference reservoir 1990 of the system with a minimum of energy expenditure..

[00232] Referring now to Figure 4g illustrating largely the same system valve states as the previous figure, the transfer of liquid fluid from pressurization reservoir 330b to 330a is indicated to be in progress through open check valve 290, through work generation turbine 200 for the development of work, through discussed high and low pressure liquid fluid conduits, through adjacent reservoir low pressure inlet valve 1948a and thence into reservoir 330a, as indicated by arrows at the surface of the respective liquid level interfaces. Meanwhile, the de-pressurization of reservoir 330c is shown to be continuing through alternate intermediate pressure conservation valve 1999 and regulator 1993 set to a mid-range set-point which may be about the design pressure of the intermediate compression stage to allow said reduced-pressure working fluid from non-active reservoir 330c to be re-assimilated to higher pressure by the mid-stage compression runner. Also notable is the discharge of condensate from the high system reference pressure reservoir 1990 through alternate high pressure condensate isolation valve 1972 into a common condensate pot 1970 shared with the high pressure compression stage condensate outlet of VCM 2000 which may be isolated during said discharge via its condensate isolation valve normally open during run-time operation of the system to prevent parasitic loading as discussed.

[00233] With reference to Figure 4h in which the liquid fluid levels in pressurization reservoir pair 330a and 330b are shown to be brought full circle in preparation for their re-sourcing of liquid fluid power turbine 200 (in the same directional sense as in Figure 4a), largely the same valve states are in effect as in the previous figure as the high regulated pressure gaseous control fluid loading pressurization reservoir 330b through valve 1996b largely completes the expulsion of the remaining load of permissible liquid fluid there-from through open check valve 290, liquid conduits, liquid fluid turbine 200, low pressure inlet valve 1948a and being deposited into pressurization reservoir 330a as indicated by arrows upon its surface. Also indicated is the discharge of condensate from high pressure condensate pot 1970 through lower condensate isolation valve 1972 falling into a master condensate pot 1970 which was indicated to relieve the total condensate there-from in Figure 4a, however, which may equally be delivered there-into at this point in the system cycle, with a like high pressure already present in reservoir 330d. While discharge into the same reservoir presents an eventual liquid fluid surplus in the 330d / 330c reservoir pair which must be dealt with at some time, it may be readily observed that at many times in the operation of the VIVE there is high pressure in either of said reservoirs while the 330a / 330b pair are actively sourcing, and with a brief high regulated system pressure application through high pressure isolation valve 1996, the extra condensate may simply be forced into the alternate active reservoir pairs' receiving reservoir 330 with largely no system impact especially in light of the liquid fluid pressure regulation occurring down-stream of said gaseous fluid (liquid drop and push) operation.

[00234] The viscosity vacuum engine also contemplates utilization of the dynamic disc spacing functionality offered by the invention in reference to Figure 8 which may be particularly helpful during initial system configuration, during the system start-up period as gaseous working fluid (and the system as a whole) warms up to a steady state operating temperature during which period, as discussed, a varying working fluid viscosity may substantially change the optimal inter-disc spacing for ideal disc turbine and compressor efficiencies. Many variations may also be made to the controls and or logic with respect to this invention without departing from the spirit thereof, such as the replacement of LSL 1934 for analog transmitters and PLC defined valve actuation limits in code as opposed to the electrical contacts of the switching mechanisms shown. Economisations may also be provided, for example, through the employment of a singular liquid fluid pressure controller 1938, pressure regulator 1953, pressure transmitter 1951 and flow transmitter 1952 through the use of a single three way valve directing the outlet flow from the control and measurement elements just named to the alternate forward 1959 or reverse 1960 inlet ports.

[00235] Referring now to Figure 5, a further VIVE engine embodiment is presented wherein a secondary VCM 2000 contemplated to engage the shaft of primary VCM 2000 as required may both enhance the system volume maintainable at high pressure as well as favourably minimize the backpressure applied by cross-pressurizations of pressure management (conservation) functions compared to the service offered in respect to the previous figure wherein the advantageous vacuum pressures provided at run-time may be affected to a degree during limited periods of the cycle. A further pressurization reservoir is added to provide a reservoir always substantially evacuated and ready to receive liquid fluids without imposing backpressure so that as soon as crossover to another 'fresh' liquid fluid sourcing reservoir occurs, the power generation process may thereby be met with no resistance other than that imposed by the work generation / conversion means, and that experienced en-route through the turbine, conduit, and valve means for said work conversion control.

[00236] Referring now to Figure 6a a viscosity vacuum engine (VIVE) embodiment is presented wherein motive, static and reciprocating elements of the system are assembled into a common housing which may be provided by one or more large diameter high pressure rating pipe segment(s) secured as by flanges sealed with appropriate gaskets and hardware adjoining VCM (VCM) 2000, pressurization reservoirs 330, liquid fluid turbine 200, blind flange(s) or other end-covers, and other elements of the system. A slotted valve-plate hereinafter referred to as timing-disk 1900 permitting simultaneous and sequenced isolated fluid transfers through annular channels and holes equipped with seals and bearing means permitting its rotation at run-time forming the heart of a revolving timing mechanism which may replace a great many electrically or otherwise operated valves and other appurtenances and may therefore minimize the cost and footprint as well as simplify the automation of engines of this type compared with the other VIVE embodiments presented in Figures 4 and 5.

[00237] The system' s integral liquid fluid disc turbine 200 located in the system so as to receive and transform into output shaft work a substantial portion of the kinetic energy of pressurized liquid fluid flow driven tangentially thereto its perimeter by a convergent divergent inlet nozzle 262, said working fluid axially discharging into largely evacuated reservoir(s) 330 at run-time, said liquid fluid flow being provided via the substantially constant application of lighter density high pressure gaseous pressurization control fluid to the surface of liquid fluid in one or more liquid fluid sourcing pressurization reservoir(s) 330 while the concomitant evacuation of gaseous pressurization control fluid there-from one or more liquid fluid receiving reservoir(s) developing a strong differential pressure there-cross said work generation turbine 200 causes said liquid fluid to be driven there-between said 'active' pressurization reservoirs paired at runtime. Said paired reservoirs upon transfer of the quantity of liquid fluid from said higher pressure liquid fluid sourcing reservoir to said evacuated liquid fluid receiving reservoir being thereafter filled with liquid fluid and subsequently replaced in active liquid fluid sourcing duty by a second liquid fluid pressurization reservoir transfer pair (prepared in advance for such service while the previously mentioned transfer pair is in process of its liquid fluid transfer) permits turbine 200 to continuously provide work in accordance with disc turbine principles discussed already (ie: adhesion, viscosity, and advantageous disc spacing) through the passage of a serviceably viscous liquid fluid through turbine 200, while an efficient turbo compressor 2000 providing recovery of gaseous pressure energy from non-active previously sourcing pressurization reservoir(s) may simultaneously and sequentially prepare high gaseous and vacuum/low system pressures for remunerative usage as control pressures at length sequenced by timing disk 1900 for application to active reservoirs to develop liquid fluid work generation.

[00238] For the sake of clarity in the figure, some valve and pressure management/regulation means are indicated to be located within upper high pressure gaseous reservoir 1990 which may or may not in practice be acceptable depending upon their construction, therefore these elements may be considered to be located outside said containment 1990 either in front or behind the sectional view presented with appropriate pressure connections provided there-for. With further integration, timing disk 1900 may eliminate the requirement of valves 1999a, b, and c with the provision of further channels and arcuate holes in timing disk 1900, reservoir cover 1911 and upper connections plate 1910 with independent conduit connections being also provided thereto respective VCM 2000 pressure inlet ports shown. Alternately, the sequenced actuation of valves 1999a, b, and c shown may be substantially effected if desired without additional power consumption beyond the energy required to turn timing disk 1900 through its path of minimum opposition normal to the applied gaseous control pressures and magnetic lines of force by magnetic valve actuation means comprising a number of arcuately formed or arranged permanent magnets embedded in or mounted upon timing disk 1900 in a serviceable location which may cooperate with ferromagnetic induction/conduction circuits (not shown) passing magnetic flux through respective valve actuation means for a duration of time set by timing disk 1900 angular velocity. [00239] As illustrated in the figure, multi-stage VCM 2000 driven by motor 265 and shaft coupling 203 at suitably high angular velocity may maintain the gaseous pressurization control fluid 1978 charge in the system's high pressure gaseous fluid reservoir 1990 through the concomitant evacuation of liquid fluid vapour and remnant gaseous pressurization control fluid 1978 from both the actively liquid fluid receiving (filling) pressurization reservoir 330b (with said gaseous fluid being drawn through timing disk 1900, low pressure section 1980 and VCM 2000' s axial intake) as well as via the system's pressure management functions conserving the energy of compression of the gaseous pressurization control fluid present in the previously liquid fluid- sourcing (liquid fluid depleted) pressurization reservoir 330 (note that the inactive reservoir pair is not shown in the figure due to being located in quadrants normal to the sectional view presented). Through rotational operation of the timing mechanism which may comprise an internally isolated standard drive means or as illustrated comprises variable speed timing motor 1901 with rotating toothed shaft appendage engaging toothed annular timing ring 1903 to drive complementing magnetic coupling 1902 outfitted with a plurality of position-fixing permanent magnets set therein or thereon projecting magnetic flux through the circumferential wall of high pressure reservoir 1990 to drive inner timing disk 1900 by way of a secondary plurality of permanent magnets mounted on or set therein about its circumference with said magnets acting in attraction to synchronize the motion of said inner timing disk 1900 with the outer timing ring 1903 magnets, a scheduling of effective valve operations may be availed there-though said timing disk 1900 operation. Annular inset channels 1920, 1922, 1924, 1926 and 1928 on the top side of timing disk 1900 (refer to Figure 6b) largely equalizing the distribution of pressure across the full disk surface permit communication of gaseous pressurization control fluid through holes 1921, 1923, 1925, 1927, 1929 to and from appropriate ports of VCM 2000 as well as to, from and between pressurization reservoirs 330 enable the system to perform requisite gaseous fluid transfers and pressure management operations at run-time. Note that for purposes of discussion, the direction of rotation shall be assumed as that indicated by arrow 1908, or counterclockwise in plan and toward to observer at left and away from the observer at right in Figure 6a sectional view.

[00240] Stationary pressurization-reservoir upper connections plate 1910 separating the high pressure gaseous fluid reservoir 1990 and VCM 2000 from rotating timing disk 1900 and stationary lower reservoir cover 1911 (and other elements of the system) permits simultaneous as well as sequential system operations through said timing mechanism. Loading of a high regulated pressure gaseous pressurization control fluid through stationary system enable valve 1940, pressure regulating valve 1997 and the high pressure fill port of pressurization-reservoir connections plate 1910 permits a regulated feed of gaseous control fluid to pass through revolving timing disk 1900' s high pressure fill channel 1928 and there-through said rotating disk's high pressure fill hole 1929 anywhere in its circular travel while being synchronized with only one given pressurization reservoir by way of pressurization reservoir cover 191 l's high pressure fill hole(s) 1918 permitting said high regulated pressure gaseous fluid to pass therethrough to pressurize the actively liquid fluid sourcing pressurization reservoir (330a in the figure) and thereby drive liquid working fluid through turbine 200 in conjunction with the vacuum/low pressure simultaneously provided in the actively liquid fluid receiving reservoir (downstream of turbine 200' s discharge and pressurization reservoir fill conduit 1912) by VCM 2000 combinedly maintaining a high differential pressure across turbine 200 via the withdrawal of gaseous pressurization control fluid through pressurization reservoir cover 1911 's vacuum/low pressure hole 1914, timing disk 1900's centrally located vacuum/low pressure hole 1921 and channel 1920 and thence through upper connections plate 1910's vacuum/low pressure hole and (VCM 2000's) axial intake.

[00241] While the aforementioned liquid fluid transfer between active pressurization reservoirs 330a and 330b (by way of turbine 200) continues owing the gaseous differential pressure maintained there-across, gaseous pressurization control fluid present in the non-active liquid fluid transfer-couple (comprising the high pressure gaseous fluid existing in the liquid fluid depleted reservoir 330 and the vacuum/low pressure gaseous fluid in the liquid fluid replete reservoir 330) is firstly pressure- equalized through pressurization-reservoir cover 1911 's shunt hole(s) 1915 and timing disk 1900' s shunt hole(s) 1927 by way of shunt channel 1926 so that through the partial decompression of the non-active liquid fluid depleted reservoir, partial gaseous control fluid pre-pressurization of the inactive liquid fluid replete pressurization reservoir (in preparation for its subsequent liquid fluid sourcing operation) may be effected substantially without energy consumption since said operation occurring in sync with timing disk 1900 rotation (through a time-span set by the angular velocity of timing disk 1900 by timing motor 1901 and also by the arc-length of shunt hole(s) 1927) happens as a matter of course upon chamber cross-connection. Thereafter, gaseous fluid withdrawal of the balance of gaseous pressurization control fluid from the non-active liquid fluid depleted pressurization reservoir by way of pressurization reservoir cover 191 l's bypass withdrawal hole 1917, timing disk 1900's bypass withdrawal hole 1925 and channel 1924, and pressurization reservoir upper connections plate 1910' s respective port and conduit 1992 into appropriate ports of VCM 2000 by way of valve(s) 1999 may be effected. Pressure transmitter 1961 (or alternately discrete sensing means) providing integral closure contacts or alternately providing real-time pressure information to a PLC or other controller means (not shown) capable of energizing and de-energizing valves 1999a, b, and c to open or close as required by programmed pressure set-points may thereby direct the depressurization of gaseous fluid most efficaciously into appropriate VCM 2000 stages of compression so as to minimize the energy required to re-assimilate the pressurization control fluid back to the high reference pressure of reservoir 1990, while also minimizing the back-pressure on lower stages of VCM 2000 compression to permit it to maintain the lowest possible vacuum/low gaseous fluid pressure in the receiving liquid fluid pressurization reservoir 330 for optimal differential pressure application across work generation disc turbine 200.

[00242] The annular channels of timing disk 1900 (not indicated in subsequent sequence of operations Figures 6d and 6e to maintain clarity of timing disk 1900's hole positions relative to pressurization reservoir cover 191 l's reservoir holes, however, understood to be present nevertheless) permit the passage of respective gaseous control fluid pressures within and along the top surface of said circular timing disk 1900 at different radii, with said channels and pressures being isolated from adjacent channels and pressures by rotating mechanical seals or alternately by annular o-ring means 1905 indicated in Figure 6a being applied at given radii adjacent the plurality of bearing means 1906 which may evenly distribute pressure-induced force-loads under largely all conditions of operation. Thusly supported by matching bearing sets 1906 on opposite sides of slowly turning timing disk 1900, slightly compressed high-durometer isolation o-ring means 1905 recessed into smooth form- fitting grooved slots in the underside surface of connections plate 1910, top and bottom surfaces of timing disk 1900, as well as the top surface of pressurization reservoir cover 1911 may thereby provide effective inter-channel pressure seals with the provision of appropriate o-ring 1905 lubrication means as may be provided by a vacuum grease or other sealing lubricant compatible with the provided gaseous pressurization control fluid.

[00243] With liquid fluid being forced down and out of the presently liquid fluid sourcing pressurization reservoir 330a via the loading of greatly less dense and comparably in viscid high pressure gaseous control fluid into said pressurization reservoir 330a through system enable valve 1940, gaseous pressure regulating valve 1997, pressurization-reservoir connections plate 1910, timing disk 1900's high pressure fill channel 1928 and hole 1929, and pressurization reservoir cover 1911 's high pressure fill slot 1918, two possible liquid fluid turbine inlet 262 configurations shall presently be discussed. At left, liquid fluid forced as flow-stream 1955 from pressurization reservoir 330a through open check valve 290 (which in variations of the embodiment may be replaced or accompanied by individual shut-off valves in high pressure liquid fluid conduit 1954) and thence through common isolation valve 1949, optional pressure 1951 and flow 1952 transmitters and liquid fluid pressure regulator (not shown, but which may alternately set the efflux velocity of liquid fluid driven through tangential turbine inlet nozzle 262 toward the periphery of liquid fluid turbine 200 for purposes of work generation, which inlet nozzle may take the form of a Tesla variable nozzle or a deLaval type flap-nozzle arrangement. At right in the figure, channel(s) descending through the floor of pressurization reservoir(s) 330 (as indicated in dashed lines below reservoir 330b in the figure) equipped with any or all of high pressure liquid fluid isolation valve(s) 1949 in the flow conduit to provide positive shut-off, standard check valve means, and or normally closed tangential inlet nozzle-flap means opening upon greater pressure existing in the presently liquid fluid sourcing pressurization reservoir 330 while lesser and or controlled pressures present in other pressurization reservoirs causing other like check-valves and or flaps to close (where a plurality of individual inlets are utilized) and seal owing the pressure differential across and or spring return actions provided thereby, liquid working fluid from said actively liquid fluid sourcing pressurization reservoir 330 at high regulated pressure may thereby be caused to pass through said channel to source liquid fluid turbine 200 to provide working fluid feed inlet to turbine 200.

[00244] In either configuration feedback to pressure controller 1938 or alternate liquid fluid pressure regulation means (such as are illustrated in Figures 4 and 5) to set the turbine working fluid pressure may be provided by: speed indicating transmitter 1931, pressure indicating transmitter 1951, flow indicating transmitter 1952, or alternately by a voltage measurement instrument (not shown) measuring the electrical pressure of the conditioned output supplied to load and or storage means. Whatever the chosen configuration, with regulated gaseous high pressure fluid driving liquid working fluid to issue from inlet nozzle 262 at significant efflux velocity tangentially toward turbine 200 while being forced there-through under the influence of an advantageous pressure differential applied there-across owing the vacuum / low pressure applied at length by the axial intake of VCM 2000 and extending there-through low pressure section 1980 opened unto the actively receiving pressurization reservoir 330 (330b in the figure, by way of pressurization-reservoir connections plate 1910 hole(s), timing disk 1900's vacuum pressure exhaust channel 1920 and hole 1921, and pressurization reservoir cover 1911 's vacuum pressure exhaust slot 1914), the liquid fluid column in pressurization reservoir 330a is thus induced by said differential pressure to move through work producing turbine 200 toward the low pressure provided by VCM 2000' s axial intake, however en-route passing through check valve means 290 (illustrated as a swing check valve but which may be provided in many well known varieties) opened due to the differential pressure there-across it, and with said liquid fluid being greatly more dense than the chosen gaseous pressurization control fluid (and the liquid's vapour) said liquid fluid passing through said check valve means falls into pressurization reservoir 330b, where-into it may flow with largely no back-pressure other than that offered by the head in central fill conduit 1912 and remnant gaseous pressure in said receiving reservoir 330b which may be at or below the vapour pressure of the liquid fluid in service at the given temperature of operation depending upon the efficacy of VCM 2000' s evacuation capability .

[00245] The gaseous and liquid fluid differential pressurization closed loop system operation of the VIVE illustrated in the figure provides for electrical energy output to be withdrawn (on wires not shown, however implied to be connected to windings 267 either directly or indirectly in the case of onboard power conditioning) and may alternately or additionally avail other work output with the addition of a PTO in place of or in parallel with electrical energy generation means shown as by the addition of a shaft coupling to other said load(s). Work output may represent the only discharge from VIVE engine embodiments in operation provided sufficient radiant and sonic insulation (not indicated in the figure, however hereby implied to surround the embodiment presented to minimize energy losses from the system), and with the further provision of heat economizing transfer loops with which to distribute heat within the system, VIVE operation may also be enhanced, for example, by providing cooling (removing heat from) liquid working fluid prior to its being supplied to turbine 200 so that the increase in its viscosity afforded thereby may consequently increase the shear stress and consequently the torque and power output of the VIVE since disc turbine 200 shear stress is proportional to the dynamic viscosity of the working fluid.

[00246] By design VIVE engine embodiments provide base-loading of smaller volume gaseous voids at vacuum/low pressure occupying the top of inactive 'subsequently sourcing' liquid fluid replete reservoir(s) 330 as a function of depressurizing and evacuating the gaseous content of the inactive 'previously sourcing' liquid fluid depleted pressurization reservoir 330 containing a complete volume of gaseous control fluid at higher pressure (post completion of said reservoir's liquid fluid sourcing operation), through which pressure equalization both reservoirs undergo the first stage preparation for their subsequent service in which the liquid fluid shall be returned to the pressurization reservoir pair's previously sourcing reservoir. Following said non-active pressurization reservoir pair's pressure equalization and isolation from one another (as the lagging edge of timing disk 1900' s pressure equalization holes 1927 pass beyond the arc length of pressurization reservoir cover 1911 's shunt holes 1915) the previously liquid fluid sourcing pressurization reservoir's gaseous pressurization control fluid is subsequently shunted, as discussed, along paths effecting its staged decompression so as to effect the evacuation thereof said reservoir in preparation for its subsequent (re-)filling with liquid fluid, and is accordingly caused to undergo a pressure management, or conservation, process wherein evacuation of said reservoir's remnant gaseous fluid pressure through VCM 2000' s compression capacity occurs in sync with the rotation of timing disk 1900 which in rotating at an angular velocity defined by timing motor 1901 permits VCM 2000 to remove said remnant gaseous fluid there-from said pressurization reservoir in stages through valve(s) 1999 with: valve 1999a being opened first (post the pressure equalization operation discussed) to feed VCM 2000' s 3rd stage of compression 285 with a narrow yet compatible pressure range of axial feed pressure permitting the re-assimilation of its output to (cooperatively maintain) the high system pressure of reservoir 1990 while valves 1999b and 1999c remain closed, and; valve 1999b being subsequently opened (for example, when the pressure in line 1992 drops below the normal second stage of compression 284 output pressure) followed swiftly in succession by the closure of valve 1999a, and; valve 1999c opening (for example, when the pressure in line 1992 drops below the normal 1st stage of compression 283 output pressure) followed by the swift closure of valve 1999b. Note that valve 1999c may preferably be an analog control valve initially opening only to an extent not causing significant backpressure in the liquid fluid reception reservoir (pressurization reservoir 330b in the figure, so as to not greatly alter the pressure differential across turbine 200 in operation) with said valve thereafter gradually or proportionally opening to fully open inversely with pressure decline in the previously liquid fluid sourcing reservoir under evacuation (ie: becoming fully open only as the pressurization remnant approaches very low pressure).

[00247] By contrast to prior art combustion type engines unfortunately converting fossilized hydrocarbons and life- sustaining oxygen into greenhouse gas exhausts, particulate contamination and heat-loading of the atmosphere causing both environmental concern and chronic health problems, the presently disclosed VIVE invention remarkably distinguished there-from by creating no emissions (other than those implicated to produce the electrical energy required to drive VCM 2000 at the required angular velocity - where electricity is utilized) if desired may recuperate heat generated due to fluid friction therein through said thermal insulation auxiliary heat recovery apparatus. While the heat of compression added to gaseous pressurization control fluid may be retained in the system's high pressure reservoir if adequately insulated, said heat load passed in part via thermal communication with (and thereby there-into) liquid turbine drive working fluid 1977 within pressurization reservoirs 330 (through interface at the liquid-gaseous fluid level boundary therein) in combination with further frictionally-derived heat energy augmentation added to liquid fluid during its passage through turbine 200, may be desirously removed as discussed from the liquid working fluids of the system to enhance the work generation capacity of the liquid fluid turbine 200. In a proposed scenario to accommodate such heat extraction (not illustrated herein), pressure energy developed in a high vapour pressure auxiliary heat recovery working fluid via thermal energy communication there-into (which heat recovery working fluid being liquid carbon-dioxide or another high vapour pressure low boiling point liquid fluid sequestered in closed or semi-closed loop in) high pressure rated heat conductive tube, tube-in-tube, or flat plat heat exchangers formed or arranged so as to provide thermal barriers within and or around the liquid fluid pressurization reservoirs of the system as well as about the inlet nozzle 262 and liquid fluid turbine 200. With said heat absorbing thermal barriers in place and the provision of appropriate conduit and connections to an auxiliary heat recovery disc turbine which may include an expansion nozzle, said turbine driven at speed and further coaxially mounted so as to drive a stage or stages of isolated compression may transform lower system gaseous control pressures into higher gaseous control pressures thereby, where-after said vapour partly cooled and condensed through the work extraction process (by and through said auxiliary heat extraction turbine and or nozzle 262) with the component of said auxiliary heat extraction fluid changing phase fluid back into liquid form being drawn by gravity into a reservoir communicating with the base of said heat extraction turbine's housing through a valve opening on a schedule valve subsequently readmitting said liquid fluid component to the heat extraction evaporator through a second valve, and with further requirement for heat extraction vapour recompression being satisfied by a dedicated compression stage there-for and additional external cooling loops as required), whereby it may be stated that the gaseous pressurization control fluid utilized to force liquid fluid to drive work-generation turbine 200 may be partially pre-compressed through the development of frictional heat load comparatively wasted in prior art engines. With or without said degree of pre-compression of gaseous pressurization control fluid by heat energy extraction means (discussed above) prior to providing same to VCM 2000 for recompression as per the general sequence of operation outlined, VIVE embodiments in any case permit gaseous pressurization control fluid to be remuneratively and substantially indefinitely used in sequestration (provided good seals), and the very fact of said remunerating fluid recompression into the high pressure reservoir 1990 of the closed loop system concurrently providing continuous evacuation of pressure from a vacuum/low pressure part of the system expressed by design upon the discharge of the work generation turbine thus allows the VIVE engine to largely eliminate the operational back-pressure of the system's work generation process while providing remunerative high pressure through an efficient gaseous compression process which in an on-going cycle may thus minimize the requirement for high pressures of operation (by instead extending the operating pressure range of VIVE engines into the sub- atmospheric pressure domain as permitted by closed loop operation). VIVE engines may through their timely deployment provide a means to minimize the emissions from engines of all sizes, through the change of focus from combustion engine technologies radically changing the physical properties of reactants to achieve high pressures of operation, to the presently disclosed invention's technology focus offering a methodology capable of extracting energy based upon the leveraging of fundamental physical properties of fluids without changing their composition as is contemplated by the presently disclosed invention wherein the relative viscosities and densities of gaseous and liquid fluids are employed and manipulated to produce significant pressures of operation and engine torque, and employing an accordantly reduced HP prime-mover (motor) to create said required differential pressure through work done in and on a light, inviscid fluid by comparison to the viscous heavy working fluid thus transmitted to perform work. Also evident is that VIVE embodiments presented herein are absent of mechanical linkages, connecting rods, pulleys, gears and their related appendages and are accordingly devoid of their incumbent frictional losses which in VIVE engines may be limited to the friction of preferably (substantially) frictionless bearings of VCM 2000 and turbine 200 (as well as pipe frictions, nozzle frictions, and eddy current losses of electrical generation means implicated, which are contemplated to be greatly lesser losses than the prior art losses noted above), and thereby VIVE engine losses may be significantly less in comparison to even Stirling type engines.

[00248] The employment of Tesla compressor technology in combination with the dynamic disc spacing functionality offered by the invention may significantly minimize the backpressure imposed on the work generation process by the ongoing pressure management/conservation processes disclosed. By dividing each of the respectively illustrated compression stages 283-285 of VCM 2000 into two independent (ie: primary and secondary) compression stage(s) sharing the same blanking end disc(s) having no axial hole pattern (which blanking end discs are common in multi-stage Tesla compressors, and are implied to comprise the thick top-side end-disc(s) of each compression stage 283-285 shown in Figure 6a) with said isolated paths of compression being supplied pressure management/conservation gaseous pressurization control fluid through relocated valve 1999s' discharge conduit(s) connected to isolated axial intakes thereof said auxiliary stage(s) of compression discharging commonly into the illustrated housing sections. With at least the vacuum/low pressure sections of work generation and pressure conservation paths segregated thus, the elimination of backpressure from disturbing the liquid fluid work generation process may be better provided thereby, and through the configurability of the inter-disc spacing provided by dynamic disc spacing mechanism equipped compression runner(s), variable pressure differentials of discharge across the respective stage(s) of auxiliary compression may be provided so as to largely match the pressure discharge of the primary (adjacent) compression stage(s) as the pressure declines there-through conduit 1992 as a function of the decompression in the pressure-managed/conserved gaseous pressurization control fluid.

[00249] While auxiliary compression stages without the benefit of the dynamic disc spacing functionality may permit the desirous isolation of pressure conservation and work generation pressure differentials to an advantageous degree especially with the employment of analog control valve(s) 1999, the optional integration of said dynamic disc spacing functionality in said auxiliary isolated-inlet stage(s) which may permit the tailoring of the axial separation of the inter-disc gaps under varying stages of depressurization may permit VIVE system embodiments equipped with discrete valve(s) 1999 to also successfully limit the potential influx (and accordant back-pressure) of said pressure-management/conservation fluid (between respective compression stages). Further, through the variation of the inter-disc gaps of dynamic disc spacing equipped Tesla compression runner(s) (functioning substantially as multiple channel control valves) said variation in disc spacing offers variation in shear stress and thereby discharge pressure through the variation in centripetal force applied on the gaseous pressurization control fluid by boundary layer adhesion and fluid viscosity (in the variable channel width) whereupon a radial pressure gradient is imposed. Naturally, VIVE embodiments equipped with the dynamic disc spacing functionality in all stages would offer a great degree of configurability to permit operation with: varied gaseous pressurization control fluids; different liquid fluids having varied vapour pressures as well as dynamic viscosities thereof, and; significant variation in temperature and pressures of operation. Should the aforementioned variables be anticipated to change significantly, a particularly advantageous VIVE embodiment would also provide for the configurability of liquid fluid turbine 200 which may thereby avail better torque control through the incorporation of the dynamic disc spacing functionality.

[00250] The pressure conservation process, understood to be performed on inactive reservoirs (ie: those not currently either sourcing liquid fluid to or receiving same through turbine 200) commences as illustrated in Figure 6d, parts 2, 5, 7, and 10, the pressure equalization of the high volume high pressure gaseous pressurization control fluid from the previously liquid fluid sourcing pressurization reservoir through pressurization reservoir cover 191 l's pressure pre-load shunt/equalization hole 1915, timing disk 1900's pressure pre-load equalization shunt hole 1927 (not shown, off- section in the view however illustrated in Figure 6b) and annular pressure equalization shunt channel 1926, with the inactive pressurization reservoir pair being cross -connected during this time period with gaseous pressurization control fluid passing into the opposite pressurization reservoir 330 through the identical features in reverse order, namely 1927 and 1926 of 1900, and 1915 of 1911. It should be noted that since a great gaseous differential pressure shall exist at the commencement of the pressure equalization operation between the two reservoirs which may therefore cause a great velocity gaseous efflux there-into the liquid-fluid replete reservoir (initially under vacuum/low pressure) for a period of time related to the pressure differential therebetween said reservoirs and the volume of liquid fill in the destination reservoir, that said velocitous fluid transfer presents both an opportunity for pressure energy recovery as well as the reduction of system shock to a degree. Accordingly, said further energy recovery which may be provided through the optional design of timing disk 1900' s pressure equalization/shunt channel 1926 to lead into the convergent section of a deLaval type (preferably variable throughput) expansion nozzle arranged to provide tangential admission of said channel flow by way of the divergent section thereof said nozzle into yet another one or more disc turbine(s) discharging through axial exhaust there-into said destination pressurization reservoir 330 with said turbine being further equipped with coaxially mounted electrical generation or one or more stages of disc compression runner means to minimize the required measure of external energy required to operate the system, with said electrical or compression energy recovery being at length utilized to increase the system's pressure differential producing capacity (of the gaseous pressurization control fluid) through said regular fluid discharge caused as a matter of course of system operation.

[00251] Following said direct pressure equalization whereby gaseous pressurization control fluid in inactive reservoirs are brought to an equilibrium pressure somewhat lower than the desired liquid working fluid turbine feed pressure, it may be understood that in order to prepare the destination liquid fluid replete reservoir for contiguous sourcing of liquid fluid in a subsequent operation (ie: at and after the instant timing disk 1900 passes into the next quadrant of pressurization reservoir cover 1911 thus changing the active liquid fluid transmitting / receiving reservoir pair in operation), further pressure energy must be added to said liquid fluid replete destination reservoir. Accordingly (as illustrated in Figure 6d, parts 3, 6, 8, 11) gaseous pressurization control fluid supplied through pre-load isolation valve 1965, secondary pressure regulation means 1997 and associated connection through pressurization reservoir upper connections plate 1910, timing disk 1900's bypass fill channel 1922 and fill hole, and finally into pressurization reservoir cover plate 191 l's bypass fill hole 1916 may then be directly added to said diagonally opposite liquid fluid replete non-active pressurization reservoir (also not shown) to continue its preparation for its subsequent liquid fluid sourcing operation whereby the required high pressure of the regulated liquid working fluid pressure may be pre-loaded into said liquid fluid replete (inactive) pressurization reservoir without implicating direct loading of VCM 2000 (since said pressure is already present and ready for use in the high pressure reservoir 1990).

[00252] Sequential operations in the presently described VIVE embodiment may be provided with a significant conservation of energy as compared to the embodiments discussed in relation to Figures 4 and 5, since a minimized quantity of power may be drawn by timing motor 1901 to rotate timing disk 1900 on bearings (which may comprise ball bearings 1906 freely running in annular slots milled at common radii in adjacent sides of pressurization reservoir connections plate 1910, timing disk 1900 and pressurization reservoir cover 1911 as appropriate) at low angular velocity, as compared to the plurality of valves requiring concurrent actuation in said previously described embodiments. While the physical dimensions of the fluid transfer holes and channel features milled in as well as pocketed through timing disk 1900 and also pocketed through pressurization reservoir cover 1911 (illustrated in Figures 6b and 6c) may approximate a serviceable complement of representative channels and holes with which to effect successful valve operations, it should be recognized that the actual sizing thereof respective channels and holes shall be dependent upon factors such as: VCM 2000 angular velocity; VCM 2000 configuration in terms of disc sizes, disc quantities per stage, as well as disc spacing; the viscosity of working fluids selected; the desired working fluid pressure of operation; the efflux velocity of and liquid working fluid throughput rate required through turbine 200, and; the timing disk angular velocity required. [00253] With the pressure management/conservation paths for recompression and evacuation of gaseous pressurization control fluid as well as the gaseous and liquid fluid inter-communication relationship(s) between active and inactive pressurization reservoir(s) 330 thereof with respect to VCM 2000 having been discussed, it may be understood that VIVE embodiments (including the one presently discussed), while producing output torque in proportion to the viscosity of the liquid working fluid forced through turbine 200, remuneratively provide at least a portion of said output torque through the economy offered by said pressure management/conservation operations discussed. Further providing operative service requiring both higher as well as vacuum/low pressures both economically provided as a matter of course by said VCM 2000 consuming energy in proportion to the greatly lesser viscosity (and density) of the gaseous pressurization control fluid employed, it may be stated that VIVE systems may produce usable output torque and energy thereby at a rate in proportion to the ratio of liquid and gaseous fluid viscosities utilized.

[00254] Referring now to Figures 6d and 6e providing a sequence of operations for the presently disclosed VIVE embodiment comprised of twelve plan views (subscripted 1 through 12) of superimposed representations of timing disk 1900 (with through-holes displayed empty, and channels there-for absent for purposes of clarity) above pressurization reservoir cover 1911 (having patterned through-holes) it should be recognized that annular o-ring pressure isolation means 1905, bearing means 1906 as well as recessed channels for both are not indicated thereon for better recognition of the discussed features, said features being understood to represent the same features shown in individually respective Figures 6b and 6c.

[00255] Commencing with Figure 6d sub.l, the system is shown in a nodal position which may in practice be quickly passed over via more rapid rotation of variable speed timing disk 1900 so that as the application of pressurization control fluid is removed from a presently liquid fluid sourcing reservoir 330 (thus halting said reservoir's liquid fluid sourcing period) gaseous pressurization control fluid may be quickly and substantially fully applied thereby to a subsequently liquid fluid sourcing reservoir so that little to no significant interruption in liquid fluid sourcing is experienced in operation, which possible interruption contemplated to take the form of a momentary low-pressure irregularity may have limited to no effect upon work generation turbine 200 turning at speed before said subsequently sourcing reservoir has fully assumed liquid fluid sourcing duty. Alternate provision(s) may also be made to largely eliminate said pressure disturbance, for example, through the: angular extension of timing disk 1900' s high pressure fill hole 1929 (beyond its presently illustrated trailing edge) with a similar shift in the angular position of the leading edge of timing disk 1900' s equalization hole(s) 1927 so as to extend the duration of gaseous pressurization control fluid application in the presently liquid fluid sourcing reservoir and also delay the pressure equalization operation of the pressure management process, and the; arcuate extension of the trailing edge of timing disk 1900' s bypass fill hole 1923 with the provision of a temporary increase in the pressure set-point of high gaseous pressure regulating valve 1997b so that as the cross section of gaseous pressurization control fluid throughput admitted to the subsequently liquid fluid sourcing reservoir 330 diminishes as timing disk 1900 rotation thereby draws the pressure management operation to a close (the subsequently sourcing reservoir having already been brought largely to liquid working fluid pressure by the pre-loading of gaseous pressurization control fluid there-into) the restricted gaseous throughput may nevertheless begin the liquid fluid sourcing from said reservoir 330, resulting in liquid fluid being sourced from two pressurization reservoirs concurrently for a brief period of time to maintain the total quantity of liquid fluid throughput largely constant during said changeover period(s). Note that such accommodation also necessitates the arcuate elongation of timing disk 1900's vacuum/low pressure hole 1921 at leading and trailing edges so as to continue the evacuation of gaseous pressurization control fluid from both present and subsequently liquid fluid sourcing reservoirs to facilitate a smooth transition between said present and subsequently liquid fluid sourcing reservoirs 330 to largely eliminate the nodal effect implicated by the configuration shown in the figure and at length maintain a regular liquid fluid flow through turbine 200 even during reservoir changeovers. Notwithstanding the accommodations discussed, as previously indicated (and illustrated in the VIVE embodiments of Figures 4 and 5) the employment of a liquid fluid pressure regulation means 1953 (either alone or in conjunction with a pressure regulating controller 1938 capable modulating its pressure set-point based on information received from a pressure transmitter 1951 in turbine 200' s high pressure working fluid supply line and preferably a secondary pressure indication provided by a transmitter sensing the vacuum/low pressure in the presently liquid fluid receiving reservoir or the pressure at VCM 2000's axial intake in section 1980 - said pressure transmitter not shown in the figure) in the turbine feed conduit may be required to ensure a consistent efflux velocity of liquid fluid applied to turbine 200. By contrast to the regularity of liquid fluid throughput which may be availed by the accommodations discussed, if the system were rather 'frozen' in the state indicated in the figure, the flow of gaseous pressurization control fluid from the high pressure reservoir would be halted, and liquid fluid flow through turbine 200 (as well as work generation availed thereby) would come to a halt following pressure equalization of pressurization reservoir(s) 330 permitted to intercommunicate through liquid fluid check valves provided.

[00256] With reference now to Figure 6d sub.2, the system is shown with high gaseous pressurization control fluid being loaded into the pressurization reservoir of the 4th quadrant (ie: lower right, or South East quadrant) to drive liquid fluid through turbine 200 while VCM 2000 extracts remnant gaseous pressurization control fluid and liquid fluid vapour pressure from the diagonally opposite reservoir of the 2nd (North- West) quadrant. Concurrently, the first stage of the pressure conservation process is shown in progress through timing disk 1900 pressure equalization channel 1926 (heretofore simply referred to as '1926') and hole 1927 (heretofore simply referred to as '1927') and pressurization reservoir cover 1911's pressure equalization holes 1915 (heretofore simply referred to as '1915') between quadrant 1 and quadrant 3 pressurization reservoir(s) . Note that the arc length of said timing disk equalization hole(s) 1927 shown should only be considered as a positional reference, since in practice may be of significantly lesser angular extent owing the anticipated to be 'near full' height of liquid fluid fill in the inactive previously liquid fluid receiving reservoir 330 (at the commencement of said pressure equalization operation) which may therefore require only a short duration of pressurization control fluid influx/application in order to effect said pressure equalization. In turn the smaller arc length of the pressure equalization/shunt hole(s) may permit a greater extent of arc (ie: a greater time period) through which to effect the subsequent stage(s) of pressure conservation and pre- compression of the subsequently liquid fluid reservoir.

[00257] With reference now to Figure 6d sub.3, the system is shown still in process of quadrant 4 pressurization reservoir 330' s liquid fluid sourcing period, with concurrent liquid fluid reception occurring in quadrant 2's pressurization reservoir 330 owing the vacuum/low pressure application therein said reservoir through timing disk 1900' s vacuum/low pressure channel 1920 and hole 1921 and pressurization reservoir cover 191 l's vacuum/low pressure hole 1914 respective to said reservoir of quadrant 2. Meanwhile the pressure equalization of quadrant 3 with quadrant 1 pressurization reservoir(s) shown to have been completed for a period of time is superseded by the concurrent pressure management/conservation processes (previously discussed) causing the pre-pressurization of the pressurization reservoir 330 of quadrant 1 and the concurrent evacuation of gaseous pressurization control fluid from the pressurization reservoir 330 of quadrant 3 respectively.

[00258] It should be recognized that the period of liquid fluid sourcing provided by each pressurization reservoir-pair may be caused by design to be extended significantly with the cooperative provision of greater volume pressurization reservoirs 330 and high pressure reservoir 1990, which added capacities may most cost effectively and practically comprise the addition of a plurality of capacities of suitable pressure rating in the respective system areas which may be more readily available than singular larger capacities which may be very costly by contrast due to the mechanical strength requirement of construction for service with significant pressures of operation

[00259] With reference now to Figure 6d sub.4, the system is shown in a second nodal state which is largely the same as that shown in Figure 6d sub.l, with the exception of the change in the notable quadrants of designation owing the direction of rotation maintained through sequence of subscripted figures referenced previously as being caused by the rotation of timing disk 1900 in the direction indicated by arrow 1908 of Figure 6b (ie: counter-clockwise).

[00260] With reference now to Figure 6d sub.5, the system is shown in largely the same state as similarly described in relation to Figure 6d sub.2 with the exception of the change in the notable quadrants of designation.

[00261] With reference now to Figure 6d sub.6, the system is shown immediately prior to a nodal state as both the liquid fluid sourcing period of quadrant 1 pressurization reservoir 330 approaches and the pressure management/conservation preparation(s) of pressurization reservoir(s) 2 and 4 approach completion.

[00262] With reference now to Figure 6e sub.7, the system is shown in largely the same state as similarly described in relation to Figure 6d sub.2 with the exception of the change in the notable quadrants of designation. [00263] With reference now to Figure 6e sub.8, the system is shown in largely the same state as similarly described in relation to Figure 6d sub.3 with the exception of the change in the notable quadrants of designation.

[00264] With reference now to Figure 6e sub.9, the system is shown in a nodal state as similarly described in relation to Figure 6d sub.l with the exception of the change in the notable quadrants of designation.

[00265] With reference now to Figure 6e sub.10, the system is shown in largely the same state as similarly described in relation to Figure 6d sub.2 with the exception of the change in the notable quadrants of designation.

[00266] With reference now to Figure 6e sub.11, the system is shown in largely the same state as similarly described in relation to Figure 6d sub.3 with the exception of the change in the notable quadrants of designation.

[00267] With reference now to Figure 6e sub.12, the system is shown in the same nodal state as similarly shown and described in relation to Figure 6d sub.l thereby completing the annotation of system operation 'full-circle' through four liquid fluid sourcing operations as effected largely by timing disk 1900's rotation and VCM 2000' s pressure management, compression and concurrent evacuation functions, and with continued operation thereof said system functions system operation may be continued until load disconnection or service requirement may need to place the unit off-line, at which time system enable valve 1940 as well as gaseous pressurization control fluid preload valve 1965 would be closed to shut off the application of gaseous pressurization control fluid (to wind down the work generation process over a time period. Also, depending upon the nature and or urgency of service required, high pressure liquid fluid isolation valve 1949 may be commanded closed to stop turbine 200 in shorter fashion.

[00268] As indicated in the lower section of Figure 6a, the presently discussed invention contemplates the maintenance of a positive pressure of gaseous pressurization control fluid in the cavity between the upper thick end-disc of turbine 200 and said turbine disc's adjacent housing containment surface, and also between said turbine's lower thick end disc and work generation means so as to reduce the effect of negatively imposing fluidic drag upon said work generating turbine 200. Said positive gaseous pressure provided through leak/purge pressure regulator 1942 and accompanying leak/purge isolation shut-off valves 1943 (actuated independently) and conduit 1975 permitting said fluid's filling of said cavity. As previously indicated, said gaseous pressurization control fluid loading may further permit the integration of the dynamic disc spacing function of the invention to tailor the inter-disc spacing effectively at runtime to accommodate given combinations of system variables including: working fluid temperature and viscosity as well as disc turbine angular velocity. As shown, said gaseous positive pressurization also permits the integration of a closed loop liquid fluid purge sub-system in which upper leak/purge discharge valve(s) 1973 normally open during system operation permit the passage of leaked liquid fluid bypassing sealing means (otherwise pooling in the base of work generation turbine 200' s housing and eventually parasitically loading same) to fall into provided leak/purge reservoirs 1941, said leaked liquid fluid being held within reservoir(s) 1941 by normally closed lower leak/purge discharge valves 1973. On a scheduled interval synchronised with timing disk 1900' s rotation, a PLC or other controller mean's reception and processing of pulse counts provided by position-indicating reed relay sensor 1904' s state information (or another discrete cyclically availed system signal) may cause a decision making algorithm to close upper leak/purge discharge valves 1973 and thereafter open lower leak/purge isolation valves 1973, and thereafter cycle leak/purge isolation valve 1943 in the leak/purge fluid return conduit 1974 as required to largely void liquid fluid from leak/purge reservoirs so as to keep work generation means housing area devoid of freestanding liquid fluid, said liquid fluid being caused by said purge system to return to an inactive pressurization reservoir 330 undergoing the pre-loading stage of pressure management/conservation so as to assist said pre-loading of pressurization control fluid and at length nullify the load implicated upon the system's high pressure gaseous reservoir 1990 as well as VCM 2000 to supply said leak/purge gaseous fluid. Following said liquid fluid's displacement by said leak/purge system into said reservoir 330, the closure of the leak/purge isolation valve 1943 in leak/purge liquid fluid return conduit 1974 and subsequent cycling of upper and lower leak/purge discharge valves 1973 to the respective states shown in the figure may thereby return the system to its normal state to prevent liquid fluid from imposing drag on turbine 200' s work generation as discussed.

[00269] Work generation means indicated comprises similar permanent magnetic generation means indicated in Figures 1 and 2 as illustrated by permanent magnets 268 and 269, cores 270 and windings 267 there-for. Due to the potential for inundation in the work generation housing area at bottom, it is foreseeable that power conditioning and storage means would require separate external housing and storage means there-for, or alternately the provision of a PTO coupling and auxiliary shaft connection (whether through magnetic coupling and containment/isolation there-for, or as may alternately be provided via direct coupling and a suitably rated packing means capable of preventing loss of the closed loop gaseous pressurization control fluid required for sustained operation of the VIVE presented.

[00270] While gaseous pressurization control fluid of VIVE embodiments is anticipated to remain therein for extended durations following successful system commissioning including testing exceeding the normal high and low pressure ranges of operation for extended periods with extensive cycling testing as well there-under said anticipated pressures, valve(s) 1964 utilized for initial system pressurization and liquid fluid fill may nevertheless be periodically utilized to restore the system's mass of pressurization control fluid as required, said replenishment being advantageously effected while the system is off-line, however which operation may also be provided while the system is on-line when a given pressurization reservoir 330 is in inactive and in process of being drawn down to low pressure during which time the slight extension of said draw-down period at atmospheric pressure may be provided without significant impact upon the vacuum/low pressure required by the work generation process, with VCM providing required pressure amplification to the high pressure of high pressure reservoir 1990 in due course.

[00271] Also, with further integration of timing disk 1900 may also provide positive shut-off functionality in place of or alongside liquid fluid check valve(s) 290/291 to permit or prevent the admission of liquid working fluid into pressurization reservoir(s) at run-time via the provision of a central circular cut-out in reservoir cover 1911 and the associated incorporation of a shaft or cylinder affixed thereto timing disk 1900' s underside with effective seals provided there-for or may alternately be provided (with no cut-out in 1911) via the provision of a magnetic coupling means mounted upon or embedded within timing disk 1900' s underside (ie: directly above the center region of reservoir fill conduit 1912) whereat the provision of a magnetically driven shaft and or cylindrical sleeve open at its bottom and flush mounted there-with the inner wall of conduit 1912 and having o-ring isolation means there-between said sleeve (not shown) and conduit 1912 and riding upon smooth bearing means isolated by said o-ring means (and preferably unaffected by contact with the liquid fluid or its vapour) so as to permit largely free rotation with minimum opposition, with said cylindrical sleeve having an appropriate arc length cut-out therein of the check valve's cut-out through-hole height through which liquid fluid may flow into said reservoir(s) under provided differential pressure application, said cylindrical sleeve being synchronized either to timing disk 1900' s rotation in real-time or otherwise discretely keyed as by magnetic circuits made or broken with timing disk 1900' s rotation (ie: in conjunction with other mechanical or magnetic actuations availed thereby) so as to be oriented largely in sync with the timing disk 1900' s vacuum/low pressure extraction hole 1921 so that only the presently liquid fluid receiving reservoir may actually receive liquid fluid when required, whereas without such accommodation, leakage there-into inactive reservoir(s) at vacuum/low pressure may otherwise occur (in cases where only check valves are provided in the liquid fluid discharge path of given VIVE embodiments).

[00272]

[00273] Referring now to Figure 7a, Tesla-type disc turbines and compressors, heat exchangers, conduits, reservoirs and valves are illustrated to be applied to the recovery of heat energy from combustion 'flue gases' while concurrently capturing said carbon emissions in prelude to a methodology which may extend from small through large scale combustion gas emissions from residential through commercial and industrial sources including diesel, coal and natural gas fired power plants, boilers and incinerators, home water heaters and wood burning stoves and other appliance(s)' flue gases, however, which flue gas emissions herein are contemplated to be provided by a residential natural gas furnace 640 for purposes of discussion.

[00274] As per typical furnace operation the combustion process provides heat to the domicile in which it is installed by way of a heat exchanger located within said furnace 640, however, since flue gas discharge pipe(s) 658 while in service are extremely hot to the touch even the layman without a thermometer may readily conclude that discharged combustion emissions sent 'out the flue' contain a great deal of wasted heat energy represented in the figure by Q _JN c _ombust i _on • By contrast to the prior art practice discharging quantifiably immense measures of wasted heat energy (globally considered) which needlessly heat-loads the atmosphere and increases the concentration of carbon- dioxide (greenhouse gas), particulates and other pollutants therein, the present invention not only contemplates the extraction and usage of a significant portion of the heat energy possessed by flue gases prior to their expulsion from domiciles or processes under consideration (said heat energy for recovery comprising the flue gas mixture's considerable remnant heat, motor heat losses from the expelling means - typically a fan motor, and also the heat of compression to be discussed), but the invention further contemplates the provision of a methodology by which said harmful atmospheric loading need not occur at all except in the event of primary system failures during which time a failsafe prior art system triggered to operate may expel said gases to the atmosphere until such time as the primary system(s) to be provided by the presently discussed invention may be returned to service.

[00275] At lower right in the figure, a single domicile's connectivity to: mid-pressure carbon capture / transfer conduit 583 (by way of the central core of tube heat exchanger(s) 612 and 613), and; condensate collection / drain conduit 526 (permitting moisture removal from carbon emissions produced by the domicile or other emitters' combustion system) are illustrated, and while the central and or distributed compression plants contemplated to further receive, filter, dehumidify, compress and cool unto liquefaction of said flue gas emissions (largely comprising CO ₂ gas) are not shown, the means hereinafter described is nevertheless contemplated to offer important service in new 'carbon economies' in which return on investment (ROI) from carbon sequestration measures may cooperate in the realization of a more sustainable way to realize our net zero carbon emissions goals in the short period of time foreseen as being requisite, said ROI therefore being a key element and an important selling feature of such systems. However, in order for the presently disclosed invention to offer said extended benefits and play a valuable part in superseding the current lack of containment for said carbon emissions, the elements discussed in the figure require implementation on very large scales.

[00276] Fortunately for the invention its implementation offers significant ROI to those integrating the method for sustainability and owing its great contribution toward energy efficiency as well as toward carbon reduction it is anticipated that a high percentage of the proposed energy related retrofits' cost outlay may be recovered under government related energy efficiency grants, rebates, or incentive plans so as to be both a very attractive cost savings measure as well as greatly more affordable to users looking to significantly reduce their fossil fuel consumption. Meanwhile the significant savings anticipated may ensure that (even without government energy related incentives) the upgrade specified may pay for itself in cost savings within a reasonable number of years and that the portion of the system directly delivering said energy, cost, and carbon savings to the customer / emitter (even in the absence of external carbon capture and condensate conduit(s) and other infrastructure required by the grander design, should they not be available right away) shall be delivered upon said systems' start-ups and that the heat recovery achieved over the long term shall provide great energy and carbon conservation translating into continued energy savings thereafter thereby providing a system of increasing value with time, which savings may be of further extended importance in carbon-taxed countries.

[00277] While the presently described system may be considered as 'just another pipe or two in the ground' to a construction worker laying pipe and may largely make use of the existing line and grade of trenches already required for customary sewer, storm drainage and or electrical and other services' pipelines lain throughout urban and suburban regions and therefore the present system's installation may be 'cost piggy-backed' to a degree with other services' installations, the far-reaching implication of carbon emitters' connection to 'those extra pipes in the ground' (ie: "the design"), beyond energy savings and carbon reduction and carbon sequestration provided and or facilitated thereby, is that with point-of-use or distributed turbines equipped with regulation and electric and or other work generation means, that with coaxially rotating Tesla-type compressors it may be both plausible and possible to pressurize, cool and liquefy said flue gases into a largely LCO2 product thereafter isolated and provided thermal energy input to vaporize said flue gases (largely CO ₂ ) into high vapour pressure working fluid by which a new methodology of power generation may be provided based on cold engine technology, heat extraction from ambient environment or industrial or combustion sources along with evaporative cooling and the remunerative employment of carbon emissions as a working fluid with which to provide sustainable power.

[00278] With the successful capture of carbon emissions via their pressurization and containment within systems arranged to further communicate and cooperate with carbon sequestration (CS) systems, Figure 9c illustrates that the LCO2 product produced by sequestration system compression means may release fantastic pressure energy potential for work generation purposes providing pressure-compatible heat-exchanger and conduit means there-for. Since Tesla-type turbines may be driven with gaseous CO ₂ and may remain un-fouled for extended periods of time owing the utilization of boundary layer energy transfer wherein the drive fluid substantially does not touch the disc surfaces under normal operation, with it is evident that for as much LCO2 could be produced, that there would be equitable market for its immediate consumption in the form of electrical power production from point of use residential and larger turbine-generators and or other work generation capacity such as turbine-driven compression plants or co- rotating electrical generation means through the conversion of excess heat energy supplied there-into a wide area heat sinking network comprising ambient, residential, commercial and industrial heat collection conduits and heat sinking means. An aspect of such a proposed system methodology is that with said distributed generation capable of utilizing flue gases as a working fluid generator, the present bottleneck of providing electrical transmission capacity to conduct the energy from the generation source to the load may be relieved to a degree, since the carbon capture conduits proposed in the method would already include the provision of LCO2 liquefied product delivery required for distributed cooling (heat extraction) purposes, and said distributed (evaporative) cooling processes providing sources of high pressure working fluid and generation capacity wherever heat-islands, solar thermal, environmental cooling (ie: air conditioning) and other heat sources are found, said distributed high pressure (CO ₂ ) gaseous working fluid would be made available as working fluid to drive loads concurrently, whereby said working fluid made available system-wide to point-of-use (POU) or distributed generators (DG) with which to drive electrical generation means either: exhausting to atmosphere - in which case emitting POU or DG may be billed by the system according to carbon emissions released to the atmosphere in addition to a transmission (conduit conduction) service charge, or preferably; emitters may provide a more elaborate system such as the one indicated in the figure capable of controlled injection and or re-injection into said carbon capture conduit(s) 583 at the required pressure in which case said emitters may instead be billed only for LC02 use according to transmission cost alone based on utilized throughput which may be measured in a number of ways, and; and it would be preferable for smaller DG and may be deemed requisite for larger DG to incorporate sufficient heat energy collection means as would add sufficiently surplus superheat to the vapour produced by power generation facilities as well as provide sufficient secondary and tertiary heat extraction means in combination with compression means there-for as would enable said DG to achieve further energy extraction from the vapour en-route to as well as through said re-compression stages as to avail substantial re-liquefaction and re-insertion of said emissions into said high pressure LCO2 conduit 584 network, in which cases no user fees may be charged to such responsible DG for which the up-front system cost and the timely upgrades and maintenance and personnel costs there-for should be the only overhead costs to said DG operation enabled to earn proceeds from such power generation facilities greatly more attractive than present-day power generation wherein the cost of the fuel required to be combusted represents both a high cost as well as ongoing drain on the financial success and sustainability of such systems owing the carbon footprint to be dealt with (in time). Such a user fee based system may provide ongoing monies for expansion of said carbon capture conduits, and it may be stated that with sufficient heat sink and isolated LCO2 exposed to even ambient (or desirously hotter) natural and or anthropogenic heat sources availed, that sufficient high pressure working fluid may be availed by which to assist in the provision of the surplus energy generation required not only for electrical production, but also to provide re-liquefaction of said emissions (CO ₂ ) for their remunerative use, especially in light of the compression (to be discussed further) at combustion point sources which may advantageously be mandated into law to force polluting emitters (combustion based energy consumers) to add significant compression to their emissions prior to their release, whether in the absence of the required infrastructure said emissions may be locally stored and later released across a disc turbine to recuperate a component of the electrical energy utilized to operate the motor driving the Tesla-type compressor compressing said emissions, or alternately (and greatly more preferably) that the discussed infrastructure be provided and utilized to capture largely all stationary carbon emissions thereby.

[00279] While the instant invention applicable to point of use combustion gas emissions may provide ready access to very significant per capita energy, cost and carbon savings owing the minimized fuel consumption accordant the heat energy conserved in the method at the source, the overall system design providing synergistic energy transfers between respective heat sources (ie: the heat in said captured carbon emissions) and heat exchangers there-for wherein liquid heat extraction working fluids vaporizing and thereby maintaining high gaseous fluid pressure(s) in turbine working fluid feed reservoir(s) respective to preferably cascading heat extraction loop(s), with respective turbine(s) driven by respective vapour species' high pressure evaporate(s) concurrently driving co-rotating compression means comprising further (multi-stage, if required) disc compression runners developing radial pressure gradients in response to the optionally variable angular velocity of the rotor to which they are attached, said pressure gradients being further made optionally configurable by the dynamic disc spacing apparatus(es) of the invention which may thereby provide dynamically controllable pressure regulation means (either with or in the absence of further pressure regulation means) by which to maintain largely the correct pressure(s) accordant to optimized rates of evaporative cooling of primary, secondary, etc. heat extraction loop(s) at length providing serviceable temperature reduction through the absorption of heat transferred through large surface areas of heat exchanger conduit walls, with said respective-loop compression means in conjunction with said evaporative cooling means (causing condensation in the working fluid in which it is extracting heat from and the substantial liquefaction thereof stationary carbon emitters' emissions), which condensation process releasing the latent heat of vaporization may be captured by an enveloping evaporative cooling working fluid and conduits there-for maintained at the correct pressure required for preferably steady film evaporation of respective working fluids where utilized by the system by the combination of disc turbine(s) and further isolated disc compression runner(s), similarly inter-cooled and after-cooled with yet another (if required) heat extraction loop etc. with largely steady-state temperature differentials developing across each respective thermal transfer stage accordant to the operating pressure and temperature differentials availed by the system so that post liquid fluid condensation of - said LCO2 and other contemplated heat extraction working fluids selected for their high vapour pressure and volatility, work production in proportion to the heat energy absorbed by said liquid heat extraction fluid(s) may be remuneratively provided through said thermal energy transfer, said condensate being provided to CS networks including those of the present system utilized for cooling purposes wherein said liquid fluid(s) returned to said cooling (heat extraction) conduits (whether: en-mas se as generally indicated in the inset at upper left wherein central carbon capture conduit 583 is immersed in the LCO2 of conduit 584 preferably to a depth which may be maintained by a control system there-for such that the weight of said conduit 583 may be largely supported by the buoyancy offered through said partial immersion ie: as provided by the resultant upward force thereupon said conduit as described by Archimedes - while considering that intermediary supports should also be provided for empty-pipe and other low level conditions, or; whether said liquid fluids are more sparingly provided to said cooling (heat extraction) conduits so as to maximize the surface area at work in providing active evaporative cooling as illustrated in the inset at upper right wherein said LCO2 may occupy a serviceably limited height of each of a plurality of smaller diameter tubing permitting adequate flow area for the evolving vapours produced by heat extraction, or alternately as indicated in the main figure at lower left, wherein a rotating film applicator mechanism continuously applying three respective films of liquid methane or liquid ethane to the external surface of said conduit 583 while a Tesla- type compressor communicating with the same inter-conduit (583 and 584) region maintains the pressure therein slightly lower than the vapour pressure accordant the design temperature desired to be applied for cooling (heat extraction) purposes, and which in any case) said condensate being returned to said cooling conduits is caused to be inserted there-into with energy level(s) permitting ready, yet largely steady evaporation owing its provision there-into by run-time-configurable compression means and heat extraction where required so that the internal energy level of said condensate approaches that required by the liquid fluid to exceed the latent heat of vaporization respective to the given fluid species and thereby may readily evaporate to cause continuous cooling of the fluid contained within conduit(s) 583.

[00280] With said continuous evaporation of LCO2 in work- sequestered in heat collection arrays (utilizing part of the climate change problem in support of the solution), the internal temperature of the fluid contained within said conduit 583 (ie: said compressed carbon emissions) may be desirously lowered en-route to subsequent compression whereat, where-through, and where-by said various stages of further compression carbon emissions may be cooled by additional means which may include liquid methane (natural gas) and or liquid ethane (the vapour pressure(s) of which are given in Figure 9a) in closed loop tube 625, flat plate (not shown) and or film evaporation heat exchanger(s) illustrated in the figure, with said cooling of CO ₂ vapour causing an accordant evaporation and high pressure to be generated in the vapour of said closed loop volatile organic compound (VOC, natural gas) cooling fluid. With said high pressure methane or ethane vapour being developed through thermal communication through very large surface areas of heat exchange, a large volumetric through-put of said vapour may be collected as by a reservoir, with said high pressure vapour being further regulated to provide a serviceable feed pressure by system design applied to the tangential inlet of a further disc turbine 597 driving the shaft of a secondary compression means (contemplated to be advantageously provided by a multi-stage Tesla-type compressor, and although shown in the figure to comprise a separate shaft, may equally be located upon the same shaft as the CO ₂ work generation turbine 590, provided optimization of insulation and isolation of process temperature differentials is maintained). While illustrated to provide electrical work, the provision of superheat may be required for such operation and where unavailable, compression and liquefaction alone may be the mandate of work generation means for at least certain periods of the day or season(s) when for example, the requisite pressure energy of evaporate from heat extraction(s) from: waste heat; solar heat; heat islands; desert heat; geothermal heat; ocean thermal heat; ambient atmospheric heat and or largely any ambient or greater temperature heat source (indicated centrally in the figure under the hearing "New Generation") may not be available and therefore to provide the additional superheating of LCO2 and said VOC vapours required en-masse to avail sufficient multiplexed working fluid (respective to species-specific heat extraction loops) to produce electrical power, as may be provided through increased pressure set-point(s) of regulation means 615 and or 238 whereby and said greater pressure feed-source availed to drive said turbine may produce electrical energy output while concomitantly providing cooling at the heat source.

[00281] With means by which to effect the capture and liquefaction of CO ₂ a new branch of environmentally-responsible power generation may begin to oppose the course of global warming and climate change by truncating fossil fuel emissions through conservation availed, and further capturing, compressing, cooling, filtering and de- watering said emissions at their source without significant energy expenditure beyond the current art practice of blowing hot combustion gases out into the atmosphere, which method may also readily provide an acceptable first stage carbon capture and storage feed- stock input. By extension to its logical conclusion, centralized compression plants discussed but not shown may receive significantly cooled and pre-compressed flue gases permitting said compression plants to thereby compress and cool said emissions more readily to the point of liquefaction with a significant reduction in energy consumption requirement to do so. Thereafter providing said liquefied medium to primary supply conduits 584 (or branches thereof) where-from networks of heat collection apparatus embodied by heat exchangers of high pressure capacity (which may include pre-cooling of the emissions themselves on approach to said compression plants forming a network- wide cascade cooling sequence which may largely begin at the source of emissions) and reservoirs and valves may receive and isolate said liquefied product for purposes of adding heat energy to same, said heat causing the substantial vaporization thereof combinedly great quantities of LCO2 to produce a high volume of high pressure CO ₂ vapour made available to said point of use or distributed (turbines) generators who instead of receiving and being billed for natural gas, may instead be billed for the usage of compressed CO ₂ which is capable of driving turbines such as Tesla-type turbines to produce electricity. The fact that presently described system may utilize turbine inlet working fluid temperatures which are much lower than prior art combustion flue gases provided to typical prior art heat engines is significant since the colder temperatures may favourably influence the ability of the system to re-compress and liquefy said (already cold) CO ₂ working fluid, and it may be stated that such systems configured so as to trap, receive, and convert the heat of compression substantially expended by the system while liquefying said CO ₂ vapour and also trap receive and convert the heat of vaporization (upon condensation) as by the evaporation and passage of a heat extraction fluid through a turbine for work generation purposes, and meanwhile be so tuned such that the influx of heat from the contemplated sources discussed in combination with the remnant heat of vaporization (released upon condensation) which may to a degree be left in the liquid condensing there-from compression means as by the realization of a biphasic compression process producing approximately the correct proportion of liquid vs. vapour (post compression) so that the heat added via compression and retained in the vapour included with the liquid discharge may provide a significant component of the latent heat of vaporization required to cause said heat extraction condensate to re- vaporize when provided to cooling conduit(s) 584 whereby the significantly minimized heat required to be extracted (compared to combustion exhausts) may translate into more ready (and less a less energy-consuming) evaporate re-liquefaction. Heat energy provided to the system by a system heat input may therefore be readily made available with which to vaporize said LC02 translating into a ready supply of vaporized working fluid at high pressure which may provide greater energy than that required for its ongoing re-compression in light of the cooling processes to be discussed, which excess energy may then be deliverable to work generation means such as an electrical generator.

[00282] Although the retro-fit of existing domiciles and buildings is foreseen, it must be understood that implementation of the total system design shall require that infrastructure be provided in the form of external-to-domicile (or commercial or industrial site) high pressure heat-extraction (cooling) conduits/tubes 584 thermally communicating with the remnant-heat-bearing flue gas contained therein mid-pressure carbon capture flue gas conduits 583 forming an effective heat-transfer couple illustrated in three variations in the figure as tube-in-tube and film evaporation type heat exchangers well insulated about their exterior with a high R-value insulation 620 and further provided both vapour barrier and preferably dry containment which may be provided by a further largely sealed drainage type conduit means offering water inundation, weather protection as well as failsafe pressure loss containment, in which said thermally coupled conduits may be buried thereby protecting insulation and appurtenances from largely any installation hazard meanwhile permitting said flue gas conduit 583 and its flue gas contents to be conducted to said central compression plant(s) alongside condensate discharge/drain conduits 526 further protected from freezing. While for ultimate benefit to be realized by the design in terms of global warming potential reduction it is desirous that full implementation of the complete system methodology be effected, the discussed per capita energy and carbon savings may in any case be availed to domicile and other buildings and processes as retrofit measures even in the absence of the requisite external connectivity infrastructure. Since said conduits are necessary to realize said full benefit from the system, however, and said conduit(s)' installation (laying) may necessarily entail soil disturbance (trenching), it may be anticipated that initial system integrations may be carried out during the construction phase of new housing and other infrastructures during which said conduit networks and interconnection appliances may be installed to prepare for their eventual loading with carbon-dioxide flue gases, LCO2, and if required liquids such as methane or ethane (in oxygen-free closed loop containment) or alternately other cryogenic liquids such as LN2 in controlled measures where required by the system.

[00283] Illustrated in the inset at upper left in the figure carbon capture conduits 583 forming the inner element of a tube-in-tube heat exchanger 611 is shown to offer service in providing heat recovery vis-a-vis the cooling capacity offered by low boiling point heat extraction working fluid contained (sequestered) by design within heat extraction conduit(s) 584 either enveloping said heat-laden flue gas conduit(s) 583, or alternately being included there-within said first mentioned flue gas conduit(s) 583 wherein smaller and preferably equidistantly supported high pressure conduit(s) 584 illustrated in the inset at upper right may provide greater heat transfer capacity via greater surface area(s) of thermal communication.

[00284] Considering that the illustrated system may provide heat energy extraction from compressed flue gases (ie: those in carbon capture conduits 583) which have already undergone temperature reduction through thermal energy transferred to water loops indicated by tube-in-tube heat exchanger 613, it may therefore be contemplated that LCO2 provided in the basic configuration illustrated may also be applied to thermal energy extraction from many different sources (some of which being indicated centrally in the figure under the caption "New Generation"), whereby such sources as urban heat islands in proximity to said carbon capture and flue gas conduit networks may with accordant temperature reduction in the hosting medium produce evaporate for application to a work generation means by way of pressure regulation means while producing cooling as an advantageous by-product of service wherever utilized. Further heat island examples include tarmac and asphalt surfaces of parking lots, commercial rooftops, and highway road surfaces all of which may be populated with high pressure compatible capillary conduits or tubing 584 a short distance below their surfaces which when heated by the sun may permit great thermal energy transfer there-into contained low boiling point liquid fluid to develop high vapour pressure at length supplied to reservoirs there-for which may thereby be maintained at high pressure, and with sufficient heat input may thereby supply an ample or surplus volume of high pressure working fluid to said generation means owing the great expanse of heat collection surfaces available for thermal energy harvest (said reservoirs being embodied by capacity 330 in the figure). Urban heat islands abound and take many forms including: dark roof-tops and building surfaces of all kinds (especially south-facing surfaces in the northern hemisphere and northern surfaces in the southern hemisphere) which may similarly be provided an array of high pressure rated tubing intermittently loaded with LCO2 by which to provide multiplexed high pressure carbon dioxide working fluid. Highway and road systems, as well as other environments which may also be considered heat traps / heat sinks including the arctic ocean which in the greater absence of pack ice is becoming too hot, as are; other oceans wherein coral reefs, for example are being thermally overloaded, as may rivers and streams. It may also be considered that the presently discussed concept of energy generation may be put into power production service where prior art fuel resources are not available (ie: gasoline) simply through the provision of insulated and protected LCO2 conduit(s) to locations requiring cooling and whereupon providing said cooling by absorbing said waste heat, solar heat, or other excess heat loads of nuisance through destructive heat intensity, power generation as a by-product of carbon capture may thus be provided, with the exhaust from contemplated Tesla-type turbines in such applications preferably being returned to the carbon capture networks through conduit means and appurtenances there-for similar to those indicated in the figure.

[00285] That energy generation may be provided by the presently described system from the heat contained in the ambient atmospheric medium may be extremely significant in poor, dry desert lands, whereat the cooling provided through the evaporation process may produce collectable water on the evaporators of such systems exposed to the air which en-masse may assist in developing arable lands upon which to grow food crops for the hungry. Energy generation may also be provided at depth wherein the evaporation of LCO2 in heat exchange tubing or flat plate heat exchangers serving as tubular screen elements or fluid collection device surfaces (developing high vapour pressures further supplied to reservoirs and regulation means as generally indicated in the figure under the "New Generation" caption as the Geo thermal heat input 617, may as previously discussed concurrently provide cooling of water or sea- water fluid currents having the effect of increasing the water viscosity and density of the fluid currents applied to Tesla and or Thrupp type disc turbines which may thus be torque-enhanced through the cooling capacity provided to the liquid working fluid through the present design's co-application as indicated by application of Equation 3, whereby said viscosity increase for any given fluid velocity shall result in greater shear stress, torque, and by extension also the energy return from said devices. Yet further applications abound whereby, for example, whereby the heat from air-conditioner exhaust-heated air as well as other thermal energy sources may be removed prior to the expulsion of said heated air to atmosphere, and it is foreseeable that through the extended implementation of the invention, liquid water of ambient temperatures, normally discharged lukewarm bath water, and or hot cooking water normally wasted in significant measures may be robbed thus of a portion of its energy through the design which may have the effect of turning said hot and warm waters into chilled water or ice as required to provide refrigeration and air-conditioning capacity which cooling capacity may, through the further employment of an insulated reservoir with which to store said chilled water and or ice product in combination with another hydronic heat exchanger therein said reservoir comprising a mass of tubing extending also to the air-handling unit of domiciles or other establishments (by way of a circulating means such as a pump, which pump may also be simply provided by a disc runner comprising a few discs spaced about W apart keyed to a shaft and turned by a motor or another means, such as by a turbine). It may be stated that use of the invention as generally indicated in the figure under the New Generation caption as Waste Heat may thereby permit the utilization of the present invention may to distribute said cooling to greatly decrease the reliance on CFCs, HCFCs and air-conditioning appliances in general with accordant carbon footprint, energy conservation and cost savings further availed by preventing excess load in summer-time upon electrical generating facilities which regularly become over-taxed by air-conditioning requirements in the globally warming world.

[00286] At upper centre in the figure a tube-in-pipe heat exchanger 611 is illustrated comprising inner flue gas transfer conduit 583 and exterior high pressure LCO2 conduit 584 there- surrounding which provides an arrangement to trap heat escaping inner conduit 583 within the primary heat extraction conduit 584 which may either represent a flowing LCO2 575 stream preferably running counter-current to the emissions bound for central or distributed compression plants, or may be static LCO2 575 collecting heat and vaporizing said low boiling point working fluid while cooling the inner contained pipe, with said heat transfer couple insulated 620 against heat loss to the ambient medium or ground there- surrounding said conduit/heat exchange couple, whereby the heat transferred to said LCO2 conduit 584 may be substantially passed into the outer LCO2 bearing conduit developing high vapour pressure therein. It may also be considered that anywhere along the path to work generation means where exposure to hot industrial waste water (or other sources of waste heat in excess of conduit 584' s internal temperature, that additional heat-sinking may be effected should requisite thermal interfacing means be provided there-for, with which to better sustain the work generation working fluid supply at pressure and required volume, and which may by extension also pre-cool industrial effluents otherwise heat-loading rivers or other natural water ecosystems with waste heat.

[00287] The inset at upper right in the figure illustrates an alternate heat transfer couple physical configuration wherein (by contrast to the former configuration providing heat- laden conduit 583's immersion in the LCO2 575 or other heat extraction fluid) said heat- bearing conduit 583's are rather provided single or two-component mating inserts 578 providing a plurality of recesses in which high pressure conduit(s) 584 may be seated (one of which mating halves are illustrated) and which may be substantially sandwiched between flange connections, said inserts while providing said plurality of connection points for an equivalent plurality of heat extraction conduits 584 also provide sufficient inter conduit circulation space sufficient to weld, bond, or tighten compression fittings there-about said conduits if desired or required after they are aligned and slotted into position between said insert(s) 578 and also to support inner conduit convection currents aiding the thermal transport. Whereas a linear conduit 584 arrangement is depicted in the figure, the alternate provision of a spiral arrangement of said high pressure conduit(s) 584 may tend to rotate the flow and minimize the pipe frictional losses therein to assist the compression agents receiving said conduit 583 throughput to also experience minimized losses accordingly, meanwhile said CO ₂ (or other contemplated low boiling point liquid fluid) vapour evolving there-from being substantially contained within said conduits 584 and or reservoir(s) there-communicating-with said conduit(s) 584 and inserts 578 (further providing annular channels there-between said couple or alternately providing a circumferential channel offering sealing capability with the inside diameter of conduit(s) 583 where-between said 'sandwiched' conduit(s) 584 flow- channels passing through said insert(s) 578 to permit egress for evolving vapour and or alternately permitting the filling of liquid fluid such as LCO2 there-into each conduit 584 while protecting against high pressure fluid escape by a further plurality of high durometer o-rings sitting in precision grooves or in another embodiment via the provision of circumferential welds thereabout the outside perimeter of said insert(s) thereby joined to conduit(s) 583 about their inside diameter, in the case of single- component inserts) permitting evolved vapour to merge into a common annular region which may thereby provide a confined region maintained at said high gaseous (vapour) pressure by the evolution of vapour occurring in said LCO2 conduits 584 due to thermal energy transport there-into. The plurality of conduit-584-receiving through-holes 579 (into which said conduit(s) are confined at the time of installation) milled in said annular channel are contemplated to provide o-ring fitted annular pockets at the entry points there-to said through holes 579 so as to seal there-about said LCO2 high pressure conduit(s) 584 preventing egress of said LCO2 and its vapour. A connection to said insert made above the liquid fluid level thereby provides egress for said evolved vapour to pass unto work generation means through high pressure conduit 1994 and valves to be further discussed, substantially providing one input to a multiplexed working fluid supply reservoir 330.

[00288] The further integration of bearing-set(s) in the insert couple(s) 578 with inlet(s) (for LCO2 entry) fed for example to one or more of a few isolated inlet port(s) singularly or equidistantly arranged about the perimeter of said couple 578 at particular location(s), and with an annular outlet (for high pressure evaporate) communicating with all conduit(s) 584 (except those into which LCO2 575 is sourced), with an external drive arrangement the provided arrangement may permit the steady rotation of the circumferential array of small diameter LCO2-bearing conduits 584 whereby said constant rotation of said conduits 584 provided may thereby cause a film of LCO2 to be maintained on the inside surface(s) of the whole length of each conduit 584 (thereby providing a great surface area of active evaporative cooling, and kept at the appropriate pressure for optimized evaporative cooling to a desirously cold temperature (to pre- condense to a degree said captures carbon emissions) as by a pressure regulator 615 setting the rate of discharge from said conduit array (unto work-producing turbine working fluid reservoir 330) optimized heat energy transfer into said conduits 584 from the captured pressurized carbon emissions may thereby be provided through steady evaporation of said LCO2 film, and with liquid fluid being replenished (loaded) at a particular location during the rotation cycle while isolated from evaporation.

[00289] Yet another foreseeable configuration of the film evaporation means illustrated in the inset at upper right may be provided by the plurality of conduit means 584 being fixedly located in space with respect to each other and in general also to conduit 583, however, instead of rotating around the inside of conduit 583 on a large bearing means as in the aforementioned example (wherein all of said conduit(s) 584 remain fixed with respect to the centreline of said conduit 583 and to each other and substantially keep the same face orientated toward conduit 583 LD. at all times), said alternate proposed method of film evaporation provides for the array of conduit(s) 584 to rather be provided individual mechanical seals as well as smooth bearing means there-for, which in combination with a common means for turning each of said conduit(s) 584 of the circular array (such as by a magnetically turned tension belt or toothed fitting alternately turned by means of a chain drive or magnetic coupling means with said magnetic drive force passing easily through the wall of conduit 583 contemplated to be provided by a dense plastic material, or alternately a permanent magnet means may actuate the rotation of said conduit(s) 584) whereby provided rotation by a motor or alternately via electromagnetic pulses of alternating polarity issued by one or more coil(s) which pulses guided by ferromagnetic means may cause the rotation of said conduit(s) on their respective longitudinal centreline axes separate to substantially rotate said conduit(s) 584 to wet the inside circumference thereof with LCO2 in preparation for continued evaporation, which rotations may be synchronous or alternately sequentially applied.

[00290] The configuration illustrated in the main figure may also provide a LCO2 film application, however as previously indicated, said embodiment applies said LCO2 film to the exterior of said carbon capture conduit 583 directly, which may thereby require a high pressure rating of service for both said (mid-) pressure carbon capture conduit 583 as well as said outer evaporate conduit since said pressure shall therein be applied to both conduits - the inner conduit's external surface and the outer conduit's internal surface - (as similarly required by the physical conduit arrangement in the inset at upper centre providing immersion). The previously mentioned outer sheathing conduit 641 providing secondary containment in the event of system leaks as well as protection is illustrated, and the operation of rotational means permitting the application of a film by said roller means 605 and wipers 606 providing a largely continuous film application as said roller means 605 driven by rotating drive means 608 driven by an external means (not shown, such as a motor), said roller means 605 aligned in guide means 609 (such as tracks or axial circumferential hard-stops) which when said external mechanism is in rotation, may thereby drive said innermost mechanism's driven elements 608 (which may comprise permanent magnets arranged in inverted polarity sequence from one shell level to the next adjacent element in subsequent rotating mechanisms respective to each shell (conduit) and thereby revolve said film applicator mechanism about carbon capture conduit 583, said film applicator mechanism including LCO2 capillary tube(s) 607 permitting LCO2 (or another liquid heat extraction fluid) maintained at an advantageous pressure near, yet below the vapour pressure of the selected liquid heat extraction fluid, to be provided through a plurality of longitudinally aligned holes oriented toward conduit 583 however within the gap between said conduit 583 and film applicator wiper 606 so that as the mechanism is rotated a film may accordantly be deposited on the outside of the pipe from which heat is to be extracted.

[00291] Due to the great cost of wide diameter pipe capable of withstanding the high pressure required of the conduits 584 of the application, for this reason, rotating versions of the film evaporator system depicted in the inset at upper right may be preferred for economic as well as in terms of surface area of cooling provided, since only a single large diameter conduit 583 is required therein which may have a pressure rating requirement of that of the intended operating pressure of the captured carbon emissions which may safely be handled by thick, rigid, plastic sewage or drainage type conduits already manufactured in large sizes (and which need not have a surface with a finely specified surface tolerance as may be requested for roller and wiper arrangements' even application of said film).

[00292] Whatever the chosen configuration, connections preferred to be located at the top of mid-pressure conduit(s) 583 may communicate high pressure vapour through a top-mounted high pressure conduit 1994 connection to and through further pressure regulator 615 and isolation valve 1996 means as flow(s) 616 issuing into capacity 330, which fluid may join evaporate issuing from condensate discharge reservoir 585 and or lower elevation supply reservoir 585 high pressure valves 1996 to provide a multiplexed working fluid by which to supply turbine 590. The figure illustrates an LCO2 transfer in progress from LCO2 condensate discharge reservoir 585 into said lower elevation LCO2 supply reservoir 585, with both reservoirs having check valve means permitting them to supply working fluid to turbine 590 through conduit 638 along with working fluid from reservoir 330 for a period of time, which may be required at times to make up added volumes of working fluid which may not be available, for example, before dawn or when combustion flue gas heat local to the DG becomes limited for whatever reason (the goal of the design) and or during maintenance periods on other loops discussed.

[00293] Forwardly looking to said eventuality, it may be stated that from the time of system inception it should be a concurrent operational plan to increase the amount of high pressure compatible heat sink in the ambient environment (in as creative and aesthetically pleasingly a manner as possible) so as to wherever possible tap known heat islands for their heat while providing said heat sink (heat conductive tubing or pipe) with glazing means (transparent enclosure) so as to trap said heat within said glazing and thereby provide it to the presently disclosed system through said heat sink thermally communicating with LCO2 inlet (source) and a high pressure outlet reservoir so that largely all sources of waste heat and undesired excessive heat may be removed and provided to the system. This being done in advance of the declining years of fossil fuel consumption may therein provide networks of said heat-communicating conduit means which would drive metals industries along the way while concurrently ensuring that as time goes on the renewable sources of heat may be multiplexed together to provide sufficient thermal transfer for domicile to receive power or LCO2 by which to produce their own power through distributed grids and off-grid power generation capacity whereby fossil fuels as well as carbon dioxide (the perceived anthropogenic causes of climate change) may be beneficially kept cold except where heat extraction is desired wherein their closed loop utilization as power generation elements may be relied upon into the future wherein their cooling capacities, heat extraction and pressurization potentials may be employed (instead of the wasteful practice of combusting the former for the measure of heat energy obtained there-from which causes disproportionate amounts of the latter and incumbent particulate pollution as well as heat loading of the atmosphere by comparison).

[00294] With vapour pressure from reservoirs 585 permitted to be relieved via check valve(s) over-pressurization of said reservoirs during their filling as with compressor 632' s condensate may be averted and as discussed, high vapour pressures may be relieved across turbine 590 for work generation purposes. With the provision of LCO2 through transfer conduits 635 to cooling loads such as those represented by carbon capture conduit 583' s remnant heat or other cooling loads indicated under the caption "New Generation" as through extended conduit means 635 as flow 636, said reservoirs' LCO2 isolation valves 576 may be closed largely concurrently with the opening of high pressure gaseous isolation valves 1996 to permit the vapour pressure(s) of said heat sources to join the other turbine supply reservoir 330 vapour sources passing through high pressure conduit 638 as required to provide high pressure CO ₂ to further regulation means 238 and preferably adjustable convergent-divergent tangential nozzle inlet 262 producing a high velocity working fluid inlet 263 driving work generation means 590 contemplated to be a single or multi- staged Tesla-type disc turbine 200 coaxially mounted to work conversion means 632 and extraction means 280 (which electrical energy extraction may be provided by MultiTAP generation means discussed herein for low profile electrical generation service alongside said Tesla-type turbine) with said vapour working fluid exiting the turbine at axial outlet 259 where-from said lower pressure CO ₂ may be strongly drawn through low pressure conduit 580 (immersed in or otherwise thermally communicating with a preferably cold low boiling point liquid heat extraction fluid contemplated in the figure to be liquid methane or liquid ethane which may preferably be applied as a continuously evaporating film to achieve low CO ₂ temperatures facilitating compression and liquefaction) to intake 295 of 1 ^st CO ₂ compressor 629 driven by an isolated however, co-rotating methane or ethane (hereinafter referred to as ethane for purposes of discussion) vapour turbine 597 supplied high pressure ethane evaporate generated through thermal energy extraction from heat exchange with turbine 590' s CO ₂ vapour exhaust developing high pressure in reservoir 599 in response to heat extraction owing thermal energy conduction there-into said ethane working fluid from: conduit 580; liquid ethane tube heat exchangers 625 of both 1 ^st 629 and 2 ^nd 632 CO ₂ compressors where- within (not illustrated) and where-about said compressors, tubing forming largely contiguous coils, or alternately cold heads or flat plate type neat exchangers wherein said liquid heat extraction fluid may largely surround said heat-possessing fluid and thereby be permitted to absorb or extract said heat energy from full surface area(s) thereof said compressors may surround same, while; the heat of compression added by of 1st multi-stage compressor 629 to compression discharge 631 issuing through conduit 630 as well as the heat of 2 ^nd multistage compressor 632 compression discharge 288 issuing through conduit 594 may all extract heat from said CO ₂ evaporate through said vaporization of liquid ethane whereby said heat energy extraction there-from may advantageously minimize the energy required for said CO ₂ compression and liquefaction.

[00295] Post 1st multi-stage compressor 629 compression, said compression discharge 631 is provided by way of conduit 630 (also exposed to the cooling action of thermal communication with liquid ethane to facilitate compression) as a working fluid source to 2 ^nd multi-stage CO ₂ compressor 632 compression intake 295 where-through significant compression may be added to said CO ₂ working fluid while it is concurrently cooled by the evaporation of liquid ethane (or another suitable low boiling point liquid fluid) so that a greatly condensed biphasic discharge may be provided at outlet 293. It should be realized that with the condensation of liquid developing within the rotor, that relief for said condensate from the housing of the Tesla compression device need be provided in order to prevent parasitic loading of the rotor and diminishing or destroying its compression capacity as well as limiting the capability of turbine 590 to provide the angular velocity required for said advantageous compression, and holes may need to be provided from latter stages of compression for this purpose leading to isolated reservoir(s) or conduits therefore providing said LCO2 condensate(s) to appropriate cooling loops may be provided or alternately said compressor 632 may be vertically mounted or alternately side-insertion mounted so as to immerse the housing of said compressor in very cold liquid ethane or otherwise provide a film evaporation application there- suiting same in order to significantly enhance compression and the removal of the latent heat of vaporization so as to permit said CO ₂ to return to the liquid state upon reaching discharge from compressor 632 as flow 288. Since it may be anticipated that a portion of the CO ₂ may remain in the gaseous state at this point, further cooling is likewise anticipated to be required to substantially condense the remainder said of gaseous CO ₂ fluid, and accordingly said biphasic CO ₂ discharge outlet flow 288 is configured to pass through further cooling means to be discussed.

[00296] With the discharge of disc compression device 632 issuing from outlet 293 at greater pressure than the sum of check valve 1962's cracking (opening) pressure rating plus the downstream-of-check-valve pressure, said compressed discharge cooled prior to 1 ^st multi-stage compression, during 1 ^st multi-stage compression, post 1 ^st multi-stage compression, during 2 ^nd multi-stage compression, may also undergo significant post 2 ^nd multi-stage compression through which said biphasic discharge may be permitted to flow downward through auxiliary high pressure conduit means 594 to be further cooled through said conduit's immersion in said liquid ethane (or other functionally effective thermal communication such as via film evaporation techniques discussed), said largely cooled and compressed high pressure discharge substantially condensing there-through said conduit 594 with distance, said high pressure discharge flow(s) passing there-into first reservoir 585 (whether falling there-into through a connection there-to, or whether, as illustrated, said conduit 594 may be welded or flanged there-to said reservoir 585 with a high pressure compatible seal permitting said conduit 594 to pass through the liquid fluid, and being immersed therein may permit further condensation of said remnant high pressure vapour at length discharging and thereby contacting said preferably very cold LCO2 fluid upon its egress from said conduit 594 whereupon entering into the cold liquid, the heat (energy) of vaporization may be substantially absorbed by the cold liquid mass while excess volumes of higher energy pressurized vapour may escape through said check valve to re-source turbine 590 which work extraction may ensure that during a second pass through the presented CO ₂ compression cycle, that said molecules of higher energy evaporate may more readily condense, and meanwhile the liquid level may continue to rise therein said reservoir 585 until such time as a further LCO2 transfer is effected to distribute said LC02 to said cooling (heat extraction potential) loads discussed.

[00297] As indicated said middle reservoir liquid discharge and gaseous fluid valves may provide intermittent communication with lower reservoir 585 through LCO2 isolation valve 576 which as shown may also provides egress for excess high pressure vapour to re-source the turbine prime mover through high pressure isolation valve 1996 (so as to maintain a minimum back-pressure in said lower reservoir 585). Intermittently said reservoir shall be emptied of its liquid fluid content via the scheduled or liquid fluid level (controls not indicated there-for) driven opening of LCO2 valve(s) 576 in insulated conduit(s) 635 extending there-from whereby said low boiling point liquid fluid may be returned to high pressure LCO2 sequestration line 584 followed by closure of valve 576 to enable said LCO2 to remuneratively receive heat, vaporize, drive the prime mover to generate work, be re-cooled and re-compressed, and repeat said work cycle ad-infinitum or until said conduit means and or system requires maintenance or replacement, for which reason said mid-pressure carbon capture line 583 (for example, in a preferred embodiment thereof illustrated in the inset at upper right) may be provided with regularly spaced access hatches preferably adjacent or between gate valves in conduit 583 so that service on given legs of the carbon capture conduit may be effected in a reduced-risk confined space environment while maintaining the charge in the rest of conduit 583, during which times a temporary bypass event may be permissible, or for extended maintenance, said regularly spaced access hatches may also provide connectivity for high-pressure rigid or flexible duct to channel said emissions in external containment for the duration required.

[00298] LCO2 may also be further supplied to load the system's primary heat extraction high pressure LCO2 sequestration conduit(s) 584 (within or otherwise in thermal communication with carbon capture conduit 583) while lowermost LCO2 isolation valve 576 in conduit 635 is open, which valve may be later opened as required by the rate of evaporation effected to replenish LCO2 fill accordantly therein. As illustrated in the figure, the system provides compression and cooling elements which are higher in elevation than the conduits and or other cooling loads (heat extraction heat sources) so that with a minimum of energy consumption gravity feed may if desired be utilized to transfer heat extraction fluids issuing from reservoir(s) 585 to their destination provided suitably insulated and wide enough diameter liquid fluid conduit(s) 635 there-for. Thereafter in operation evolving LCO2 575 may be subsequently re-admitted to the primary heat extraction working fluid mass of the lowest reservoir 585 through a respective LCO2 isolation valve 576 and be further admitted unto conduit 584 as required to further remuneratively absorb heat energy from heat-laden flue gases at a time constant respecting the volume of capacities 585 as well as other factors including the heat absorption rate by LCO2 in said reservoir(s), the temperature differential between cooling liquids and the vapour which they are designed to cool, and other considerations obvious to one skilled in the art, while understanding that further cooling means (to be later discussed in terms of evaporative cooling provisions) may be provided to facilitate the removal of heat from compressed working fluid and thereby permit the formation of LCO2.

[00299] As illustrated, said compression means may be provided with a tube type heat exchanger 625 of high pressure rating placed in thermal communication with said compression means' housing (which tube heat exchanger may preferably be arranged in a circular/spiral formation about the inside of said compression means' housing in effective thermal contact therewith so that as expelled working fluid issues from the various stages of compression and is driven at velocity toward the walls of said housing, the boundary layer of vapour attached to said heat exchange coils may be greatly disturbed so that both the velocity of expulsion as well as friction there- accordant to the impingement of said vapour upon said heat exchange coils and also the heat of compression may be substantially applied in undiminished intensity to permit said heat exchanger's heat conductive tubing containing said primary heat extraction working fluid - liquid ethane or another colder working fluid in different embodiments - to be effectively thermally loaded with heat energy so as to remove said heat energy effectively from the compressor discharges at the various pressures, substantially utilizing cooling means to effect dynamic to static pressure recovery within the compressor segments), and or alternately said compression means' housing may be immersed in a reservoir of said liquefied heat extraction medium (which may be facilitated with a vertically oriented shaft as previously discussed) so that the heat of compression may be substantially removed there-from the compressed gaseous vapour medium and thereby facilitate the previously mentioned process whereby a portion of said compressor discharge may readily reach temperatures and pressures of condensation and return to the liquid phase. Concurrent with the cooling provided to the turbine / compressor discharge, said cold low boiling point liquid fluid (liquid ethane for example, in which conduit 594 is immersed) shall acquire heat through thermal communication there-into said fluid, and accordingly shall evaporate and thereby maintain an accordant vapour pressure which in combination with the other heat absorbed by said liquid ethane heat extraction fluid applied for cooling purposes across the system, said high evaporate pressure provided as flow 595 through conduit(s) 596 may then multiplex heat extracted from appropriate regions of the system together with said conduits and reservoir 599 providing an excess to the requisite capacity required to supply energy to drive auxiliary-compression vapour-ethane-turbine 629 by way of pressure regulator 569 setting an appropriate working fluid pressure to drive said turbine 597 in combination with a further preferably adjustable convergent-divergent nozzle such as a de Laval nozzle, or alternately a Tesla type variable nozzle which may have a rectangular cross section nozzle integrated therein would also provide a responsive choice for mass production purposes.

[00300] While first liquid ethane supply valve 568 in liquid ethane branch supply conduit 586 and either or both of second liquid ethane valve(s) 568 in subsequent conduit(s) 567 are also open, liquid ethane may be supplied to upper reservoir(s) 599, and the system' s larger liquid ethane collection (preferably vacuum- insulated) reservoir 599 may also be substantially filled with liquid ethane 598 during system commissioning phase in this manner with valve(s) 565 open. It should be understood that the illustrated figure does not necessarily represent vertical spatial relationships adequately in all circumstances, and for example, gaseous isolation valve(s) 565 communicating with reservoir(s) 599 may best be closed (as illustrated) so as to prevent liquid ethane 598 fluid from entering 'lower' conduit 596 which may for a period limit the gaseous working fluid throughput required to drive turbine 597 depending upon the volume of liquid ethane in question, and for this reason said vapour-ethane turbine 597 and compressor 629 as well as conduit(s) communicating there-with same may accordantly best be located above the elevation of said liquid ethane fluid fill conduit(s) 586 and 567.

[00301] While as discussed another preferably colder low temperature boiling point liquid heat extraction fluid such as methane may alternately be utilized for cooling purposes herein, Figure 9a illustrates that this shall require the provision of very robust pressure-rated heat sink conduits, reservoirs, and valves which may accordantly require pressure ratings in excess of 5000PSI to 'safely' implement such a system (providing for the possibility of dysfunctional reservoir(s) cooling means permitting the warming thereof to ambient temperatures. While disc turbines on the other hand may be substantially indifferent to operation at such pressures and it may be stated that disc turbines and disc compressors offering the advantage over other turbines and compressors of being capable of biphasic operation with condensation in the runners being a non-issue whereas it may be a serious and even destructive issue to other turbines - that with appropriately configured disc spacing there-for (which due to deviances from the design operation of many of the other components and frictional factors of a substantial system which may only be discovered at the time of commissioning), that the variable disc spacing apparatus of the fluid energy conversion invention may be an advantageously applied asset to such systems which may permit fine tuning of turbine and compression configurations at run-time so as to adjust for other system deficiencies to a degree.

[00302] A controlled feed of liquid ethane issuing there-from reservoir(s) 599 thereafter may subsequently provide intervening compression heat extraction (cooling) heat exchanger(s) 625 of various possible configurations with steadily fed liquid ethane heat extraction fluid by and with which to cool CO ₂ compression features and fluids issuing there-from said compression means 629 and 632 through controlled pressure evaporation thereof said liquid ethane. With the discussed legs of heat extraction producing high pressure ethane vapour in an isolated closed loop, with said pressurized ethane vapour being provided as ethane vapour flow 595 to and through regulation means 569 and thereafter turbine 597 to develop the work required to provide first stage compression of CO ₂ vapour via compression means 629 co-rotating there-with said turbine 597, the compression and liquefaction of said vapour into preferably low temperature condensate returned to liquid ethane reservoir(s) 599 post expansion across turbine 597 remains a course of further discussion.

[00303] Where DG facilities are located near present-day continuous-burn combustion facilities or industrial processes where-at large measures of waste heat discharge on a continuous basis, or preferably (and looking to the future) where renewable energy facilities may produce large measures of clean renewable energy, the energy required to re-compress said secondary heat extraction (cooling) fluid as well as liquefy same may readily be availed in conjunction with multi-staged Tesla-type compressors coaxially driven upon the same shaft as disc turbine means, driven, by for example by steam (for which application the Tesla turbine was originally developed) whereby the torque required to develop power from said high pressure water vapour subsequently either discharged to atmosphere post development of shaft work or alternately said steam being substantially returned to condensate via the preferable employment of closed loop heat recovery whereby further energies may be recovered and utilized for many possible uses whereupon said water condensation a warm feed-stock for subsequent steam production may be provided to continuously provide said high pressure steam for remunerative energy production, said steam being preferably returned to the system via gravity feed into a reservoir located at an higher elevation than said tertiary heat extraction (cooling) water loops to negate the requirement for energy consumption to pump said condensate whenever and wherever possible for energy conservation reasons. Thereby with either steam generation in conjunction with heat sources already discussed (preferably clean sources), or alternately with renewable energy systems, the presently discussed design may thereby provide the required shaft work to compress and liquefy said secondary ethane heat extraction fluid, and with excess electrical energy may provide further commercial scale cooling (if required) to deliver said ethane condensate at a desirously cold temperature.

[00304] Forwardly looking to substantial replacement of the prior art pollution- condoning methods of heating and power generation globally imposing direct atmospheric loading, the presently disclosed figure and methodology rather provide a system which: may be adaptable to existing combustion systems provided the required carbon sequestration (CS) conduit array(s) are run through housing developments or commercial and or industrial complexes under consideration; may utilize existing system(s) as failsafe back-ups in the event of primary system failure; instead of operating a blower to expel greenhouse gases and particulates into the air, the present invention provides a multi-stage Tesla-type compression runner to remove hot combustion gases from the combustion source vis-a-vis said compression means' evacuation capacity and charge same into heat exchangers via its compression capacity (offering quantifiable heat reclamation which may provide heat for potable hot water pre-heating, hot water radiative heating capacity as well as ambient air heating) while maintaining a combustion permissive pressure in the combustion chamber through the integration of the dynamic disc spacing functionality of the invention and or variable speed motor, controller, and pressure and flow sensing device(s); provides pre- compression of carbon emissions as a first step in the carbon sequestration process; provides pre-cooling thereof said compressed emissions through the various heat extraction(s) discussed; may provide substantial de-watering thereof said pre-cooled compressed emissions and delivery of same into a condensate drain line 526; and at length deposit said compressed, cooled, de-watered carbon emissions into a CS network branch conduit 583 wherein and where-through said captured carbon emissions are provided no egress except there-through central compression plant(s) by way of said CS conduit 583 network.

[00305] The captured, compressed, cooled, carbon emissions of the system having had significant measures of heat energy removed: firstly by energy recovery water and air recirculation loops which may increase the net energy efficiency of combustion processes thereat; secondly by heat energy removed there-from through the withdrawal of warm condensate; thirdly from continuous thermal communication with CS LCO2 contained in conduit 584 during said flue gas' transit residence time within or otherwise adjacent said CS conduit 583 network, and; fourthly via the contemplated integration of film evaporation techniques (which may utilize the benefit of co-rotation there-with the already-in-motion Tesla compressor by providing another isolated stage of compression as well as connectivity there-for the maintenance of a controlled pressure in the heat- transfer region respective to the film application of preferably a hydrocarbon of very low boiling point (such as Ethane, Propane or Butane, for which the vapour pressures thereof are illustrated in Figure 9a) which through the employment of magnetic coupling technique may permit said isolated compression stage(s) to communicate the pressure required for the steady, non-flashing evaporation thereof said liquid gaseous fluid applied to the outside of conduit(s) or capacities requiring system-critical cooling so as to maintain cold temperature (remove heat from) there-about and or there- within carbon capture conduit(s) 583 and CS LCO2 conduit(s) 584 over significant distances on approach to, there- surrounding, as well as within critical areas of the system such as about the perimeter of disc compression devices to achieve lower temperatures of operation and facilitate the transition to the liquid phase while also capturing the heat of condensation within the system where it may be off-loaded into alternate heat transfer loop(s) such as water pre-heat or boiler feed-stream pre-heats amongst others. On approach to said central compression 'plants' compression intakes the evacuative effect of the compressor intake's suction may also be augmented while providing increased density to the flue gas emissions there-approaching said intake(s) by passing the respective branches of said lower pressure conduit(s) (with appropriately fitted high pressure-rating conduit(s) there-for) through large scale conduits or reservoirs of LCO2 treated with said film evaporation technique to provide very low temperature on approach to as well as throughout compression.

[00306] As illustrated in the figure, combustion flue gases issuing from fuel-burning device(s) such as furnace 650 may be provided passage through normally open safety shut-off valve 659 (preventing back-flow of pressurized flue gases into the domicile) into combustion exhaust low pressure duct 652 and thereby supply VCM VCM 2000 with working fluid which it may effect multi-stage compression upon through primary 283, secondary 284, tertiary 285 and or further stages of compression. While in other embodiments motor 265 driving said VCM may be arranged to be the same motor as that driving fail-safe (prior art) blower device 660, the presently illustrated embodiment which may in part represent a retro-fit of an existing combustion system, offers independent means by which to discharge said combustion flue gases (exhaust) including: a previously existing fail-safe combustion vent duct 658; an auxiliary fail-safe combustion vent duct for pressurized flue gases, as well as; the primary carbon capture influent conduit 571 conducting the point-source or combination-source emissions unto mid-pressure carbon capture conduit 583.

[00307] An important safety consideration represented at some point in the certification process of such a system would be the preference of all pressurized system components to be sealed within a containment 618 preventing back-flow to the interior of the domicile or other utilized location, while permitting pressurization to escape to the out- of-doors through exterior environmental protection box 273, however, by way of insulated communication paths which may substantially prevent back-flow into the containment(s) through the employment of check-flap means or valvular conduit means (4) requiring no moving parts, or a combination thereof.

[00308] As indicated, a primary heat extraction loop is provided largely comprising tube heat exchanger 612 and its heat exchange fluid, a pump and a reservoir (latter elements not shown in the figure) which may be locally or remotely located to said heat exchanger absorbing and communicating remnant combustion heat from the flue gas carrier into said heat exchange working fluid (herein contemplated to be water but which may be another fluid) thereby absorbing significant heat from said combustion flue gas exhaust which from a mid-high efficiency furnace, for example, may discharge at temperatures in excess of 100 ⁰ C for durations of 8 or more minutes per burn, with said burns being spaced apart in time fixing a duty cycle of operation (for purposes of illustration of two or more times per hour in mid-Canadian winter) depending upon factors including: temperature set-point; volume of air to be heated; indoor air temperature prior to said combustion burn which may be surmised to be further dependent upon many factors including: season; seasonal temperature variation; time of day; home insulation characteristics, etc.) which in any estimation, over the course of a 24-hour period may represent over 6.5 hours of hot water-heating potential which is typically discarded in unfortunately practiced prior art combustion strategies.

[00309] Although illustrated motor 265 may be omitted from the illustrated heat collection loop or may be alternately be provided a separate cooling loop of lower temperature which may more effectively utilize motor heat losses while permitting adequate ventilation, it is nevertheless significant that the present waste-heat energy recovery methods may acquire motor heat loss as well as the greater heat of compression which may also be absorbed into said heat exchange working fluid(s) controlled to intermittently flow during combustion periods by, for example, pump(s) there-for cued to start a few seconds after the combustion burn commences, and be shut down thereafter a timed duration after the finish of said combustion burn so as to permit significant heat acquisition, with said heat being further conducted through preferably insulated inbound 624 and outbound 622 conduits in the hosting water or other heat transfer fluid(s) at length communicated to and largely retained in, for example, a hot- water preheat tank wherein the potable water supply piping to a hot water heater brought into the same pre-heat tank (not shown) may substantially collect and heat said potable water prior to water-heater-entry and thereby greatly minimize the burn-time of combustion or electrical energy utilized to maintain the temperature of said water-heater reservoir between prescribed temperature set-point(s) through the recuperation of energy previously discarded in prior art systems, and thereby it may be stated that the present system may minimize energy use in the domicile while significantly extending the net efficiency of combustion processes (through the further heat energies collected and used) therein while concomitantly minimizing carbon footprints imposed. [00310] In preparation for the combustion burn, VCM 2000 in similar fashion to prior art blowers shall be started in advance of combustion initiation to ensure that an acceptable draft is created with which to sustain combustion (ensuring that subsequently generated emissions may be carried out of the fresh air zone of the domicile safely thereby eliminating hazard from the noxious flue gas emissions of combustion). During said VCM 2000' s start-up period, safety shut-off valve 659 shall remain open (and shall only be commanded closed in should reverse flow be detected by flow transmitter 648, should significant CO ₂ be detected by CO ₂ analyzer / transmitter 573 while furnace 640 is not in a burn cycle - which may indicate emissions back-flow through a leak or leaky check-valve, in which case safety shut-off valve 572 shall also be closed and an alarm system contact energized to warn occupants of the back-flow possibility as well as preferably call a service company having emergency pager service and remote view and or control access for remote service and troubleshooting capability, with said CO ₂ transmitter 573 or an alternate transmitter preferably having the capability to additionally monitor the ambient atmosphere within heat collection containment enclosure 618 for CO as well as CO ₂ ) with compressed combustion exhaust failsafe valve 645 also remaining open to ensure that the carbon sequestration conduit 583 is not unnecessarily loaded with clean air, which may also be ensured via closure of carbon capture isolation valve 572 during said initial VCM 2000 start-up, which valve closure may be based upon a substantially zero CO and 0.03% CO ₂ transmitter process variable value (information) being fed to CO ₂ controller 574.

[00311] The combustion burn commencement may be recognized in a number of ways including: the change of state of a furnace relay output, or; the spike of differential temperature developed upon hot combustion gases issuing into furnace outlet duct 652 subsequently sensed by differential temperature transmitter 646 referencing said temperature to the outlet temperature of heat exchanger 613, or; the rise of CO ₂ concentration sensed by CO ₂ analyzer / transmitter 573, any of which signals may then be further utilized by a fast-response PLC or other controller to intelligently operate the illustrated carbon capture / heat extraction system illustrated to drive the opening of carbon capture isolation valve 572 largely concurrently with the closure of compressed combustion exhaust failsafe valve 645 to direct the CO2 bearing emissions load unto a designated carbon capture inlet whether individualized as shown, or alternately an input to a header which header may provide a plurality of inlets there-for neighbouring emitters' emissions to be commonly conducted unto sequestration as through a commonly shared carbon capture influent conduit 571. A dual (or optional) placement of valve 645 is indicated to permit the system to either largely clear warm emissions with the pre-combustion air-flow (along with the CO ₂ / CO concentrations therein represented), which would concurrently affect the net energy recuperation by blowing cool air through the desirously warm heat exchanger 613 (ie: with the actuation of lower compressed combustion exhaust / air bypass valve 645, or alternately advantageously retain remnant heat contained in heat exchanger 613 (even if contained within CO ₂ / CO laden flue gases) with the actuation of upper compressed combustion exhaust / air bypass valve 645 which by comparison would permit said air throughput to be discharged through vent 644.

[00312] The system illustrated indicates that noxious flue 650 gases are provided a path through VCM 2000 compression stages which result in a significantly elevated discharge pressure from its final stage, and with air-bypass valve 645 closed and with VCM 2000 discharge pressure in excess of check valve 1962' s cracking pressure (anticipated to be slight, since it is positioned more as a means of backflow prevention than for pressure regulation) said check valve 1962 shall be opened permitting said compressed combustion flue gas exhaust 654 to pass through the central conduit 656 of tube-in-tube heat exchanger 613, wherein a very hot discharge may be anticipated, and the provision of a desirously lengthy heat exchanger 613 either in series there- with the aforementioned heat exchanger 612, or alternately which may be provided in addition thereto former heat exchanger 612 (and thereby require the provision of alternate inlet 624 as well as outlet 622 conduits there-for conducting the heat accumulated thereby said secondary thermal communication indicated to a further load such as a hydronic heating loop for basement floor or radiative heat exchangers or for other contemplated home use(s) about the domicile or elsewhere) may be provided to utilize said further collected thermal energy. With alternate compressed combustion exhaust failsafe / air bypass valve 645 closed, heat-exchanger-cooled emissions may pass through carbon capture / safety shut-off valve 572, through coalescing filter 587 or another scrubber type of filter (removing particulates such as carbon black as well as condensate from the emissions discharge), past or through flow-meter 648's measuring element (the flow signal of which may be: utilized for interlock purposes; may be monitored in real-time both by the user' s local control system as well as by a security company contracted for emergency response; tallied by the central compression plant requiring to match its compression capacity to the carbon capture load imposed in order to maintain said conduit array(s) 583 between largely steady pressure limits conducive to system operation, and; which signal may also be utilized for billing purposes in new carbon offsetting economies whereby countries imposing carbon taxes to in part pay for the carbon capture and sequestration means contemplated may be herein provided access to true emissions data), with said compressed, cooled, filtered and de-watered combustion emissions 657 being further conducted through check valve 1962, manual shut-off valve 570, carbon capture influent conduit 571 and thereafter subsequently deposited into carbon capture conduit 583 when the pressure (as may be confirmed by pressure transmitter 1989) rises to a magnitude greater than the sum of check valve cracking 1962 pressure plus the pressure in carbon capture mid-pressure conduit 583 (as may be confirmed via carbon capture pressure transmitter 589, which signal or value may be a networked value provided on a data buss for best economy since said pressure indication may be valid over a fairly extensive length of carbon capture conduit 583 thereby not requiring the expense of redundant transmitter means there-for.

[00313] In order for users of the system to estimate net energy savings, differential temperature transmitter 646 may be utilized to provide a measure of the thermal energy prevented from escaping to atmosphere (and therefore largely equivalent to the thermal energy saved and thereby made useful to domicile owners and or other property owners and processes in the form of useful heat energy as well as cost savings). Concerned with the prevention of atmospheric heat loading as well as containment of said emissions there-from combustion processes, the presently illustrated figure illustrates the derivation of a temperature differential between the raw combustion exhaust (which as discussed may issue into conduit duct 652 at temperatures in excess of 90 ⁰ C) and the temperature down-stream of heat exchanger 613. While a flow-meter in the heat exchanger's water or other heat exchange fluid circulation loop (not shown) may provide a direct flow value for multiplication with the temperature differential to obtain a resultant energy product representing the conservation achieved by the system, a measure may alternately be derived indirectly via the totalized flow-rate of carbon emissions captured which value may be obtained from flow-meter 648.

[00314] As indicated, compressed, cooled dewatered flue gas emissions 657 in the method are to be provided significant thermal residence time with heat sinking means to lower the temperature thereof said emissions while en-route to central compression plant(s). Upon entry into said carbon capture conduit 583 of great volume (in consideration of the need for such containment means, and therefore also the intended extent of the very large CS conduit network(s) contemplated) and although the cooling capacity respecting said residence time in the CS conduit 583 network shall be large so as to offer continuous volumetric reduction of carbon emissions there-adjacent said LCO2 sequestration/heat extraction fluid conduit(s) 584, it is equally contemplated that the continuous ingress of compressed, captured carbon emissions (compressed gas) into said carbon capture and storage conduit array(s) 583 from the myriad inlets contemplated respecting individual or header capture-point sources of small through large volume(s) at pressure may maintain a largely consistent (owing an average frequency of furnace burns, power turbine duty, boiler operations and other combustion exhausts which may over short term periods of hours or days be regular) however seasonally variant feed volume proportionate to fossil fuel consumption from said stationary sources which may in any case be reconciled via change of angular velocity and or dynamically adjusted disc spacing of said Tesla-type multi-stage compression means accordant to demand (for compression), in any case representing a very large energy product within said conduit 583 array.

[00315] Said coalescing filter 587 or other scrubber means employed deriving condensate from the compressed, cooled captured emissions as indicated may be isolated for filter cleaning or cartridge replacement by valve(s) 572, 1972, and 570. In operation coalescing filter 587 may generate condensate permitted to fall through open condensate isolation valve 1972 into condensate pot 1970 while condensate discharge valve 1976 remains closed to prevent condensate drain / collection conduit 526 from being un-duly loaded with flue gas emissions which may adversely affect myriad other system users contemplated to be intermittently also discharging condensate into the same branch conduit 526 concurrently, and in consideration of the myriad partial pressures which may be thus forced into said conduit 526 and the potential that pressurization thereof said conduit may adversely affect filter 587 and or potentially soil check valve 1962 in extreme pressurization scenarios, it may be foreseen that control strategies governing the valve sequence of operations for the discharge (insertion) of condensate into condensate conduit 526 need be universally adopted to prevent said significant pressurizations thereof said condensate conduit 526 which may include closure of valve 1972 and or cycling thereof until condensate pot 1970 is largely empty. During intended discharges of accumulated condensate, which may be treated as a carbonic acid solution for purposes of the provision of conduit means' 526 physical construction through which its carriage to suitable downstream filtration and scrubbing means may be effected (which means may be located at said central compression plants as they may be located elsewhere), said acidified condensate (acidified owing the high concentration of gaseous CO ₂ through the portion of the system wherein condensation accumulates) requiring neutralization may there-at become a source of carbonic acid for industrial requirements via further standardization processing of said solution there-for.

[00316] While dependent upon the cracking pressure rating of check valve(s) 1962 utilized (first adjacent VCM 2000 discharge, and second between flow-meter 648 and shut-off valve 570) different flow characters may be obtained permitting said check valve(s) to be utilized for both back-flow prevention (shut-off) as well as for regulation purposes which may discretely trap flue gas emissions within heat exchanger(s) illustrated at different pressures accordant said different cracking pressure(s) and thereby achieve different relative heat sinking residence times (time constants of thermal conductivity) which may permit greater or lesser quantities of heat to be captured from given combustion burns' heat-bearing flue gases, the contemplated control strategy prefers to employ low cracking pressure check valves (and or isolation valves in place of said check valves) in combination with extended lengths of heat exchanger 613 so that the residual pressure in said heat exchanger and other internal-to-domicile conduits may be kept as low as possible for safety consideration.

[00317] With carbon emissions being pressurized into carbon capture conduit(s) 583 comprising an extensive array from myriad sources / emitters, it may rightly be suggested that turbines discharging to atmosphere might be operated to convert the energy product represented by the compressed, cooled, filtered and de-watered gaseous mixture (ie: that contained in the expansive carbon capture conduit array(s) 583) into usable form in combination with work generation means rotating there-with said turbine(s) such as may be afforded by the Multi-phase Toroidal Annular Power (Multi- TAP) generation means discussed, or said energy might be utilized to add further compression energy as by the coaxial driving of a further multi-stage compression runner(s). In either case the capture of said compressed gaseous fluid represents stored energy producing capacity at length capable of extending the service of the fossil fuels burned in the first instance, and with the cooling of said emissions before pressurized- insertion there-into said carbon capture conduit 583 network being provided, and with further cooling also being provided while in thermal communication there-with evaporative film cooling means and or LCO2 conduit(s) 584 while therein said conduit(s) 583, it would make sense, therefore, if the conversion of energy potential at this stage were desired, to isolate said cooled emissions and provide high temperature heat exchange through which to pass said emissions en-route to their being applied as working fluid to turbine(s) for work generation purposes so as to increase the pressure of said 'captured carbon emission working fluid' before its use to develop work there-with.

[00318] With the primary goal of the present system being to substantially never release said carbon emissions to the atmosphere, while providing a method which may become a future power generation practice which through development of infrastructure in a timely manner may thereby already be in place to support the CS networks and be at the ready to replace fossil fuel usage with lower temperature heat extraction and energy production as by the presently disclosed system 'geared' to cooperate with said CS systems and their capacities by offering sustainable paths there-into said sequestration network(s) (ie: by utilizing normally discarded energy spent by prior art high speed blower(s) to blow heat and CO ₂ laden emissions into the atmosphere - instead, to compress, cool, clean and prepare said emissions for liquefaction as discussed), and also offering energy generation there-from the pressure energy provided to said carbon emissions. In order to develop energy from 'the problem' (ie: CO ₂ emissions) the system applies wherever possible cool LCO2 with which to abstract heat from waste and surroundings so as to put said greenhouse gas' low boiling point and substantial vapour pressure to work at humankind's behest in remunerative work generation.

[00319] While significant energy recuperation from combustion flue gases through their pressurization and cooling are provided herein and their subsequent cleaning, de- watering, and capture are also critically important functions of the present fluid energy conversion embodiment, equally important is the provision of sequestered LCO2 for use as a liquid working fluid possessing significant potential energy, said condensed low temperature boiling point working fluid being provided through LCO2 isolation valve(s) 576 to preferably a plurality of heat-exchange evaporators 617 where-from evolving high pressure carbon-dioxide evaporate regulated to a common working fluid pressure (preferably exceeding that of turbine feed pressure regulator 238 setting) by respective pressure regulator(s) 615 and passing through open high pressure gaseous isolation valves 1996 may thereby provide high pressure gaseous working fluid as inputs 616 developed through heat transfer into said various heat sources 617 of ambient and greater temperature(s), mentioned previously and subsequently herein, which inputs 616 multiplexed together may provide a combined working fluid source comprised of a plurality of different heat sources. The versatility of CO ₂ use as a working fluid is well understood and is applied to many industrial applications not requiring mention herein yet for illustrative purposes it is interesting to note that the familiar example of the CO ₂ rifle and cartridge bearing liquid CO ₂ are a powerful example of the energy product capable through the absorption of ambient heat into its LC02 which achieves a very high pressure of service equal to the vapour pressure of CO ₂ at the given temperature (referenced in Figure 9c). Since myriad heat sources 617 (beyond those indicated in the figure) may be provided and which may concurrently absorb heat (represented by Q _IN designation) and subsequently evaporate LC02 into its gaseous form, it may be stated that geothermal, solar thermal, waste heat, heat islands, tarmacs, ambient air, ambient water, heated industrial effluents and many more applications heat loading both local as well as the global environment may be tapped for their excess heat energy and be subsequently cooled thereby the application of LC02 without departing from the spirit of the invention.

[00320] Multiplexed gaseous CO ₂ evaporate providing a combined high pressurize working fluid input may then be supplied to reservoir 330 at run-time by which either independent or cooperative sourcing of turbine 590 may be achieved in controlled fashion through further turbine feed pressure regulator 238, and provided sufficient pressure and volume of said working fluid are available, generation means 280 may also be optionally operated concurrently with said multi-stage compression to produce electrical energy output from excess thermal energy. With tremendous heat being available 24/7 from geothermal energies right below our feet, it is contemplated that ground-water and soil immune high pressure compatible conduits comprising thick- walled stainless steel, copper or brass tubing in network- like arrays which may be installed beneath the frost line in many environments may provide steady thermal energy influx there-into said conduit arrays 584 through largely ongoing evaporation of LCO2 admitted on an intermittent schedule into said heat exchange tubing array. Rigidly affixed roof-top solar thermal conduit arrays 584 for example pinned beneath or between preferably dark metal clad roofing and or siding elements and similarly loaded with LCO2 or otherwise provided by heat conductive panels insulated from heat-loss preferably including glazing means with said solar thermal conduit arrays also isolated from said LCO2 supply as by LCO2 valve(s) 576, with valve 1996 and or check valve egress being provided there-from said heat collection array(s) into a high pressure reservoir 330, may also generate significant quantities of CO ₂ vapour for application to work generation means. Many sources of waste heat, ambient water and or atmospheric air heat extraction arrays in conjunction with LCO2 conduit 584 arrays for example simply laid out across the desert to absorb heat from the sun and sand, or said heat accumulation conduits alternately being embedded in 'solar attenuators' (or solar blockers for complete shade requirement applications) such as may be positioned overhead above patios or which may be included into privacy fences via one or more layer(s) of coiled small diameter high pressure rating copper tubing substantially sandwiched between glass elements such as discarded sliding glass doors with vinyl trim where-between said elements a feed-water stream ensuring coil coverage throughout sunny periods may develop and retain significant measures of heat energy between said glass panes - especially if said solar attenuators or blockers are also provided a dark media within said circulated liquid, which media may comprise largely any natural media such as mica, magnetite, carbon or even carbon black, waste India ink or in brown-fields power projects, even toxic wastes such as used paint thinners, turpentines, toluenes or other used or waste chemicals might be mixed in to provide a diluted mixture offering varied optical densities providing different levels of heat capture - may be utilized to capture heat energy both within the liquid as well as in the heat extraction media, so that if desired, said inter-window heat-capture fluid may be circulated to provide heat exchange. Alternately which heat extraction coils 584 may be fixedly attached to a metal backing well insulated for excellent thermal capture and transfer) which during periods of solar input may substantially thermally load said contained LCO2 with heat energy and cause its evaporation to extendedly provide another example of a ready-made high pressure CO ₂ working fluid input 616 admitted through valve(s) 1996 or header means there-for multiplexing working fluid input sources to said reservoir 330 thereafter providing work generation via turbine 590.

[00321] The temperature differential provided by given heat source(s) associated with a system input (with respect to the temperature of sequestered LCO2 in conduit(s) 584) may vary widely and still generate a serviceable CO ₂ vapour pressure and volume of evaporate with which to drive turbine(s) 590 tasked with driving coaxially mounted compression means 632 largely returning the CO ₂ vapour to the liquid phase upon reaching the required pressure, with the understanding that extended cooling means may also be provided to relieve said compressed CO ₂ vapours of the latent heat of vaporization to subsequently enhance the rate of transition to the liquid phase (ie: as described in respect to said liquid ethane secondary heat extraction loops discussed previously). While solar energy collectors (including any of the different embodiments thereof already discussed) may be provided as "New Generation" heat source(s) 617 to the system and may for a portion of the day provide rapid thermal energy transfer into the LC02 medium and thereby provide high CO ₂ vapour pressures and volumes as a substantial input to reservoir 330 with sufficient excess energy to not only drive turbine 590 and coaxially rotating compression means 632, but said high energy inputs may also drive electrical output to loads from a coaxially co-rotating generation means 280, and with sufficient superheat the work output realized may be increased, or said excess energy may be applied to turn a second energy generation means (not shown) so as to accommodate peak load periods of electrical energy requirements. It may also be stated that the provision of multiple stage turbines may permit a significantly more complete expansion process through turbine(s) 590 so as to more completely utilize the energy provided from superheat when it is available, which may significantly reduce the temperature of the turbine exhaust proportionately there-with owing the greater expansion ratio availed, which expansion-derived cooling in conjunction with the subsequently provided (preferably evaporative) cooling to better permit said vapour's compression and liquefaction.

[00322] By comparison (to solar thermal heat and other superheat sources), however, while the cooler anticipated temperature of the pre-cooled pre-compressed, dewatered flue gas emissions migrating through conduit array(s) 583 may generate CO ₂ vapour in conduit(s) 584 thermally communicating there-with said captured emissions, they may do so at a significantly slower rate in proportion to the slower time constant of thermal energy transfer into conduit array(s) 584 owing the lower temperature differential provided. While understanding that said latter heat-source may be available 24/7 by comparison to some of the other possible heat sources indicated and therefore said evolved vapour may be provided at a lower pressure accordant the vapour pressure(s) attained through residence time at a given temperature input, in any case CO ₂ vapour upon passing through conduit 1994 extending from carbon capture conduit(s) 584 through regulation means 615 and isolation valve 1996 into reservoir 330 may occur at even ambient temperatures to supply working fluid to turbine 590 as previously discussed, however, may or may not (by contrast to said hotter heat sources) provide sufficient energy to drive electrical generation means 280 in addition to said compression means 632 (which compression is required of the method to provide sustainable carbon capture and storage) owing the lesser rate of thermal energy influx transferred into said conduit(s) 584 or other heat source(s) 617 provided to the system as energy input(s).

[00323] Although said CS conduit 584 arrays located within or otherwise thermally communicating with the captured, cooled, and compressed carbon emissions of conduit arrays 583 represent a lower temperature (and therefore an accordantly lower pressure potential input 616 source of vapour to said heat collection array), as previously discussed, the successful evaporation of desirously great quantities of LCO2 via heat transfer there-from said captured 'emissions' nevertheless represents a critical source of LCO2 evaporate, and whereas means for providing enhanced evaporative cooling thereof said captured carbon emissions have been discussed in relation to Figure 7a in general terms, it should be understood that while said methods may be advantageously practiced utilizing liquid ethane or another very low boiling point, the use of CO ₂ is specified herein to provide serviceable use for as much of said greenhouse gas as possible to enhance its value in sequestration. Meanwhile, the figure does not indicate the intention that the inter-turbine-and-compressor conduits are also to be provided confined evaporative cooling where- within the correct pressure accordant the desired temperature of cooling with said methods is provided whereby utilizing liquid ethane or another very low temperature boiling point liquid which may provide effective cooling of CO ₂ vapour, compressed CO ₂ vapour, and also CO ₂ condensate, for with the greater cooling of said captured carbon emissions an accordant comparative conservation of energy required to liquefy said carbon emissions for CS storage and or uses specified herein.

[00324] While with said lower temperature heat sources it is evident that the net work generated by the system may result in no significant net positive energy generation other than the compression and cooling capacity sought, it may be conjectured that with a greater mass of heat sink means well distributed as capillaries and conduits of expansive heat collection arrays with segmental branches thereof combinedly extracting even low grade heat sources represented by said compressed, cooled, and captured carbon emissions of conduit arrays 583, through the resultant vaporization of greater masses of LCO2 even if at lower temperature (ie: availed with greater masses of distributed heat sink means), very large volumes of vaporization may concurrently also be provided by which to generate the work required of the system, it must be realized that even said lower grade heat extraction, vaporization and resultantly had work generation at distributed points of generation may actually enhance the ability of the system to liquefy said emissions at central compression plant(s) 'down-stream' owing the additional cooling capacity thus concurrently availed), and therefore it should be considered that the evaporative cooling means described may not only be advantageous over the kilometres of said conduit means approaching said central compression plants, but said evaporative cooling means are contemplated by the invention to be most effectively practiced across the whole of the networked infrastructures comprising the substantially comprising the carbon capture conduits 583 and their integrated cooling means associated with conduits 584 of varied configurations provided for here-in.

[00325] While it is recognized that combustion as an accepted practice may continue largely unabated for many years to come despite climate change concern and the invention accordingly describes a path to the conservation of significant per capita measures of energy and therein indicates quantifiable cost savings while also providing for the local compression, cooling and capture of stationary emitters' combustion flue gases - provided adequate system conduit infrastructure means there-for, the eventuality provided for by 'the design' of said preferably evaporative cooling carbon capture networks discussed may also provide the framework for the changeover to sustainable distributed grid communities in which there is no need for combustion (nor, therefore, additional influx of carbon emissions into system conduit(s) discussed).

[00326] Whether the intended system design shall accommodate combustion flue gas input or not (ie: whether it is a retro-fit system designed to accommodate cross over to non-combustion based energy generation) or rather if said design shall be from inception a standalone multiplexed heat input energy conversion system, differences in the extent of infrastructure and services provided there-for municipal scale energy generation needs may vary according to the presently described design, however in general, the following elements need be provided in such a closed loop carbon capture and sequestration network spanning the breadth of a municipal energy generation system (under the assumption that said design is to provide standalone non-combusting energy generation): an excess volume of flow-through turbine 'exhaust' containment comprising expansive well insulated low pressure / high volume conduit means wherein gaseous CO ₂ discharged from work extracting disc turbine(s) may en-route to compression, be provided sufficient residence time in thermal communication with cold surfaces as to be significantly pre-cooled, by; evaporative film or other efficient heat exchanger (cooling) means wherein a cold isolated secondary heat extraction fluid maintained at an advantageous pressure by turbines and compressors may permit heat extraction therefrom the primary low pressure turbine exhaust (ie: via heat transfer there-into said cold liquid secondary heat extraction fluid resulting in the vaporization thereof said secondary heat extraction fluid and further provision of secondary working fluid), and with; similar preferably evaporative film continuous cooling means extracting further heat from said primary loop CO ₂ working fluid vapour during compression, between compression stages as well as post-compression (making said primary working fluid more easily liquefiable); suitably sized and configured multi-stage Tesla-type disc compression means receiving said pre-cooled primary working fluid vapour may through multiple stages of compression and secondary loop cooling largely liquefy said primary working fluid, with said compression means being driven by; appropriately configured Tesla-type disc turbine(s) providing the work required to drive said cold fluid compression via said coaxially co-rotating disc compressor(s) as well as electrical load placed upon the system through; electrical energy generation produced during 'the fall' of the primary working fluid from higher (pressure) energy level to lower (pressure) energy level where-through said electrical energy generation means co-rotating therewith said turbine means may be driven via the application of; expanding volumes of high pressure higher temperature gaseous primary working fluid applied to said Tesla turbine(s) at length provided from; a sufficiently large network of high pressure compatible LCO2 heat sinking conduits widely distributed throughout the environs of the community in question (especially tapping available hot heat sources) wherein a preferably surplus mass of LCO2 maintained at all times in actively heat sinking redundant branches of heat accumulation network(s) alternately receiving LCO2, absorbing heat energy to the point of vaporization, and or thereafter with sufficient residence time, heat sink volume(s), and amongst a plurality of such heat sources and heat exchanger means there-for, a largely continuous high pressure multiplexed source of working fluid which may be in excess of that required to match the load demands placed on the system may be provided through the continuous vaporization (and or boiling) until near exhaustion of said sequestered LCO2 which may thereafter be refilled in advance of (said derived evaporate there-from) being required, by which means; said surplus gaseous primary working fluid may be continuously supplied to insulated (where required) high pressure conduits collecting said pressure energy from the multiplexed ambient and warmer heat sources, said conduit means provided at a volume accordant to pass the required volumetric throughput of the power requirement demand into sufficiently large volume high pressure compatible (insulated containment(s) where external environs are cold, and or alternately un-insulated containment(s) where higher temperature storage environs may be available by which the development of superheat prior to said fluid being provided as a working fluid input to system work extraction means may thereby increase the work generation capacity of the system, wherein) conduits, reservoirs, regulators and valve means by which masses of CO ₂ working fluid may be stored and provided on demand to said disc turbine(s), so as to; supply the daily energy requirement and peak loads of domiciles within range of given DG power generating facilities, and meanwhile; re-compressing unto the required pressure for liquefaction said utilized gaseous primary working fluid in conjunction with shaft work and energy recovery by and from secondary and tertiary (if required) cooling means as well as turbines and compression means there-for, whereby further heat extraction of the heat of compression and other heat from said primary, secondary and tertiary working fluids may be provided by the system, which in combination with; the further utilization of suitable scale embodiments of renewable energy generation methods and systems previously discussed (18), further power requirement beyond that provided by the present design may be provided from said alternate energy generation methods and be engaged for example in the form of electrical energy applied to the shaft of further compression means, and or be applied so as to produce further cooling as by commercial cooling systems, or should said other renewable energy generation systems be located in proximity to the presently described system, either direct coupling of said renewable energy sources or alternately of work converted there-from to drive auxiliary compression means may convert the kinetic energy of creeks, rivers, solar energy, ocean and or tidal currents, vortices, waterfalls, waves, whirlpools and or wind near to communities so as to harness these substantial energy inputs to provide the compression energy required to make such communities sustainable, with a fixed mass of carbon dioxide and natural gas (in non-combustion mode) remuneratively working to provide energy generation in cooperation with nature instead of burning what is naturally provided.

[00327] It is anticipatable that the evaporative cooling means described and preferred may be most effective with said LCO2 substantially flowing counter-current to the emissions-flow bound for points of central and or distributed compression so as to avail best heat transfer, with multi-layer thermal insulation being provided to advantage where fluid transfer is to be provided, and where heat extraction is to be provided, it may be considered that significant thermal energy input may be provided simply by laying a plurality of un-insulated conduit(s) in the ground (ie: as in geothermal style), connecting them in a star network or alternately a grid, charging said network with LCO2 and providing inter-communicating high pressure compatible conduit means there-between said buried LCO2 bearing heat extraction conduit(s), and a further connection of said network of heat accumulation conduits(s) to the inlet(s) of one or more disc turbine(s) (ie: as indicated by elements 590 in the figure). Depending upon regional latitude and other factors well known in the art of geothermal energy conversion, said buried LCO2 conduit array may 'warm up' to 15°C (for example) which may develop a ready supply of substantially 700PSI vapour pressure working fluid (CO ₂ evaporate) by which work may be provided at a steady rate according to the capability of said system to re-liquefy said CO ₂ vapour (ie: to remove the back-pressure on the work generation turbine and process), which re-liquefaction may be provided in largely the same manner as already discussed with the employment of secondary and if required a tertiary heat extraction fluids and the provision of conduits, valves and reservoirs of appropriate pressure rating, as well as means for isolated compression and work generation and conversion as embodied by Tesla-type turbine(s) 590 fitted with high pressure rated housings and pressure regulation means there-for by which said turbine working fluid may be controlled to at length provide a regulated turbine angular velocity and work output thereby.

[00328] It may be stated that with foreknowledge of urban and suburban development plans, that pipe-laying contracting companies (in light of the proposed method of energy generation) may play an important part of future energy generation systems' through the anticipatory laying of the requisite system conduit(s) there-for heat accumulation, carbon capture as well as condensate, and that once successful embodiments of such systems are proven, that natural gas services need not even be brought into futuristic subdivisions, since electrical energy generation may be created based upon the vaporization of LCO2 alone as described herein in conjunction with Tesla disc turbines and compressors. However, proposed herein for service as secondary heat extraction fluid for use in evaporative cooling (heat extraction) system conduit(s) and other heat exchanger(s), it is rather anticipatable that a small storage facility may be provided which may be maintained over long periods of time without substantial depletion with the provision of said natural gas to system conduits in place of combustion units where- into fossil fuels may enter, however, never return. In such systems as are presently described, the sizable cost of prior-art-requisite natural gas conduits may instead be invested in the cost of the present systems' conduits means which may further reduce the 'real cost factor' of providing wholly independent renewable based communities from inception. It may also be stated that the added cost respective to (water) condensate/drain return conduits may also be saved since CO ₂ and LCO2 are substantially dry, and with the maintenance of system conduits' pressures in excess of the atmospheric pressure, no significant moisture build-up in the system may be anticipated. Thus distributed energy generation facilities may be provided in advance of new development(s)' realizations so that full power for said developments construction and longevity may be provided by naturally availed heat energy which may then, later, when the cost of said anticipatory power provision has begun to pay for itself, may have completely done so, or at any other convenient time thereafter, whence the power provided by nature-harnessed may then be utilized to power the equipment substantially utilized to build the community previously planned.

[00329] LCO2 and natural gas employed as system-wide heat extraction agent(s) may as discussed provide substantial environmental cooling, pre-compression cooling, intra- compression cooling as well as post-compression cooling as discussed, and may thereby avail a decrease in the net energy requirement to sustain carbon sequestration liquefaction operations into the future, and may also provide other cooling benefits while concomitantly producing high pressure evaporate(s) via thermal energy absorption, with said evaporate(s) thereof serving as working fluid(s) applied to drive Tesla-type turbine(s) working via disc turbine principles already discussed to either develop the electricity required to operate large diameter and or high angular velocity Tesla-type multi-stage compression devices at said central and or distributed compression facilities, or alternately drive said compression means directly. It must be understood, however, that owing irreversible losses in the work generation processes plus the fact that a goal of combustion-input-accepting systems according to the full design is to retain largely all CO ₂ turbine drive evaporate (that working fluid generated via heat extraction), plus, the total of 'new' emissions (arriving at said central or distributed compression plants via conduit array(s) 583) in captivity via the liquefaction of both said fluids, that the volume of liquefied LCO2 represented thereby may obviously be immediately excessive (although with time, said combustion flue gas emissions inputs may decline as combustion input sources represented in the present figure - to be discussed in detail - decline over time in favour of renewable energy generation means), and therefore that the energy required to produce the (excess) volume of LCO2 to be compressed and liquefied by the presently described system and sent elsewhere to CS vaults may greatly exceed the energy extractable by the system in the environs unless extensive heat sink be provided and that without a great excess of LCO2 in excess heat sink and high pressure reservoirs of the system accordant the load foreseen by said 'new emissions' that the quantity of evaporate produced via heat absorption designed for local energy production alone may alone not be sufficient to compress unto the point of condensation (and thereby liquefy) more than a fraction of said additional compressed and cooled captured carbon emissions received at the axial intake of said multi-stage compressors without the application of further emissions compression and further cooling means by which to assist said compression and liquefaction sequence through the lowering of the temperature of said inbound emissions as in a cascade cooling sequence. However, the design already takes such cooling into account through the contemplation of evaporative film cooling means disclosed, and whereby the employment of CO ₂ evaporative cooling has been specified in part to create as much demand for said greenhouse gas in captivity as possible over the full length- extent of desirously long carbon capture conduits and in part since CO ₂ is, chemically- speaking, non-flammable and non-explosive, it may be stated that better cooling capacity may be offered through the employment of natural gas (ie: methane or ethane) in said evaporative cooling conduit(s) without significant change to the appearance of the design except that with a greater tendency for cryo-condensation on said high pressure liquid heat extraction conduit(s) 584, the need for greater pre-capture de- humidification may be more apparent, although in successfully functioning systems with no leaks in said evaporative cooling conduit(s) 584 (which leaks may be readily detected with on-pipe analog sensing means such as a combustible(s) gas detection transmitter) with said systems utilizing thick rigid plastic sewer type conduits typically rated to about 240 PSI, the implication of condensation may be minimal provided said pipes are unaffected by carbonic acid. So while carbon-dioxide may be utilized for evaporative cooling purposes, it may be anticipated that systems designed to accept and sequester significantly more CO ₂ (as LCO2 furthered to CS vaults) than they have the capacity to liquefy based on their inherent energy production compression and cooling capacities may be assisted through the employment of said natural gas in evaporative film cooling systems throughout, with the obvious qualification that the requirement for intensified safety is implicated with the use of said gas owing its very low short term exposure level concentration.

[00330] While the illustration at left in Figure 7a may apply to distributed energy generation systems utilizing evolving CO ₂ evaporate (remote to central compression plants) to drive turbine 590 and coaxially driven multi-stage compressor 632 and work generation means 280 on demand to develop re-compression of CO ₂ vapour into LCO2 subsequently returned unto sequestration in isolated sub-array conduit(s) 584, and said coaxially co-rotating elements may generally represent the working configuration of central compression plants, said central compression plants, by comparison, may be of significantly larger scale. For example, while the illustrated system conduit(s) and complement of co-axially rotating work production elements (with the assurance of sufficient drainage to ensure their freedom from parasitic loading through pooled water contact with the disc runner) may be located underground, and the reservoirs, regulators and distribution conduits etc. respective to external-to-domicile apparatus may be housed in an insulated above-ground shed (or rather in-ground for enhanced personal safety), the central compression facility by comparison may be much larger in scale, may have multiples of said compression means (for purposes of illustration) having central axial inlets specifically oriented and sized so as to directly receive said cooled, compressed, filtered and de-watered combustion flue gas (carbon emission) product through conduit(s) of like diameter to said axial inlet hole patterns' diameter(s), with said large diameter respective conduit(s) 583 being directly aligned there-with compressor-respective compression intakes so as to offer a system also designed to minimize of piping head losses due to friction, wherefore said conduit(s) 583 may optionally provide appurtenances specified by Schauberger (23, 24, 25) to decrease said frictional losses by separating the core flow from the boundary wall flow as well as rotating said inner flow. As already discussed, the evaporative cooling high pressure conduit(s) 584 means previously discussed (in reference to the configuration at upper right in the figure) may advantageously (in this regard) take on the form of spiral, which through such a configuration may not only help to rotate the flow for minimized frictional losses as suggested (23, 24, 25), but with said conduit(s) configured thus, a further strategy for wetting the conduits may be proposed whereby applying the vapour pressure availed by through evaporation it may be stated that a high differential pressure pulse of methane evaporate applied in first insert(s) 578 but not in second insert(s) 578 may produce there-through said spiralled conduits suitably arranged such that while remaining largely parallel to the wall surfaces of conduit(s) 583, with said conduits being circumferentially rotated from one insert 578 to the next, that said pulse may thereby create force moments which may then provide rotation of said rotational means if required, or in other embodiments rotation of said conduits may not even be required (to obtain adequate wetting for acceptable film evaporation performance to be sustained) where said conduit form in combination with a suitable differential pressure pulse may largely create desirous wetting without ongoing energy consumption as by a drive means in other embodiments.

[00331] Further contemplated components of such a central compression plant are the provision of desirously large residence time(s) in communication with substantially cold (cooling) surfaces of large cross-sectional area and length in the conduit sections both upstream and downstream of said compression plant as well as there-between intra- compression plant conduits between compressors, and stages thereof, as well as conduits leading from turbine discharge(s) to compressor(s) intakes, (however, an exception being turbines, where-between respective stages thereof a desirous amount of heat may be retained, and superheat applied where available). Desirously large conduit zones or conduits in parallel for extended length may be provided to permit a large zone of cooling without great frictional losses, with said zones in single element devices rather taking form resembling the inverse form to that of a venturi tube wherein isolated, thermally communicating, large capacity film evaporation means such as those previously described where-into liquid heat exchange fluid may enter on a scheduled basis in closed loop for purposes of filling or intermittent wetting thereof cavities respective to said isolated array segments with respective discharge paths from each array branch in communication with one or more Tesla-type compression stages (preferably configured to co-rotate there- with a main work generation means' shaft for best energy conservation while providing completely isolated working fluid paths from said main CO ₂ compression elements as by the employment of a magnetic coupling and separate conduit means there-for) which isolated compression stages' purpose(s), whether further served via the dynamic disc spacing functionality of the invention or alternately by the employment of pressure regulation means there-for, being the may dynamic adjustment and maintenance of the pressure in said film evaporation means at the correct pressure appropriate to the desirously cold temperature set-point required for cooling of each respective pressure stage such that the energy required for said evaporation at the given temperature and pressure combination is provided by the influx of heat energy from the compressed emissions, and not through the over-zealous application of vacuum by said compression means which would comparatively waste the film application and rapidly boil the liquid away with little or no cooling provided.

[00332] In reference to Figure 9a, it may be noted via extrapolation that the hydrocarbons Methane, Ethane, Propane, and Butane possess vapour pressures relating to serviceable temperatures of operation which may be successfully integrated into the presently described methodology should the observance (or rather avoidance) of: explosive ranges of operation; oxygen; sparking; arcing; and other forms of electrostatic discharge, lightning and or other hazards be addressed by contemplated designs. Owing the requirement for non-sparking, non-arcing etc. operation, it may be stated that said evaporative cooling compression runners may most safely be driven by turbines themselves driven by CO ₂ evaporate as opposed to an electric motor which at some point in its operational lifetime may issue a discharge of sorts, however the provision of a totally enclosed envelope electric motor may prevent such occurrence from igniting the hydrocarbon compression loop, as may the provision of said magnetic coupling there-for the isolation of said CO ₂ and hydrocarbon loops. While Figure 9a indicates that different gas species may adequately serve in the system contemplated, and that very low temperatures of operation may be availed by which to provide emissions cooling to further assist in the liquefaction of CO ₂ on larger scales (should an appropriate Tesla- type compressor configuration be provided there-for operating in the correct pressure range for a given selected hydrocarbon), the economics of constructing a system suiting a particular hydrocarbon governed by safety factors, pressure ratings, configuration and design of conduit and evaporative cooling means' required there-for may determine which hydrocarbon may be cost-effectively designed into the system. By contrast to the majority of prior art the present system seeks to sequester hydrocarbons for purposes of evaporative cooling instead of combustion, combustion being rather avoided by the presently described method by all means.

[00333] Pre-compressed, pre-cooled, filtered and de- watered emissions entering said wide section of conduit 583 (up-stream of CO ₂ compressor(s) intake) and thereat passing between hydrocarbon-based film evaporators embodied by eccentric tube-in- larger-tube configurations or alternately in flat-plate heat exchanger or other arrangement(s) specifically designed for such evaporative cooling service offering large surface area cold communication may significantly enhance the pre-cooling of captured emissions prior to entry into said further Tesla-type compression means there-for. Also, evaporative cooling means of large volumetric imposition either alone or working in conjunction with LCO2 cooling means may also offer great surface area cooling in advantageously larger diameter housings than the disc compression runners respective to each stage of compression and thereby provide extended residence time for compressed emissions in respective stages of co-axial compression whereby inter-stage cooling may also be significantly enhanced to facilitate the change to the liquid phase. Discharge conduits extending from the final stage of compression may be reduced in volume in consideration of the anticipated ratio of compression as well as liquefaction effected across said multi-stage compression means, it may be considered an advantage that the supplied LCO2 medium may be provided as a biphasic liquid and gaseous mixture preferably comprising a high percentage of liquid phase CO ₂ - said discharge either entering directly into highly insulated master supply conduit(s) 584 serving LCO2 to large area networks of LCO2 users at point-of use locations (including New Generation and Distributed Generation means indicated in the figure, whereat various heat sources utilized may vaporize LCO2 as well as expand the evaporate there-from for either application to point-of-use disc turbine(s) not shown in the figure, or said evaporate being as shown in the figure expanded across DG disc turbines 590 for electrical or other work generation purposes), or alternately into a transitory conduit wherein further cooling and electrical energy expenditure for further compression may at length provide the final cooling and compression required to induce at least the largest portion of the working fluid to transition to the liquid phase with the product there-from being substantially prepared to join other carbon sequestration efforts' flows to CS vaults and or be conducted (preferably with the aid of gravity to minimize pumping energy requirement there-for) to cooling loads discussed already whereby energy generation in cold engine fashion may be provided to assist in the net replacement of combustion based energy generation to speed to reduction of the impact of fossil fuel derived atmospheric heat and CO ₂ loading.

[00334] Cold LCO2 first admitted into said conduit array(s) 584 wherein exposed to thermal energy influx from conduit(s) 583 (or other heat sources discussed) shall in due course acquire the required quantity of heat necessary to exceed the latent heat of vaporization at the given pressure and shall in due course thereafter begin to evaporate at a rate proportionate to the rate of thermal energy transport there-into said LCO2 through the wall thickness of heat extraction conduit(s) 584. With the provision of independent heat accumulation arrays comprising LCO2 valve(s) 576, evaporators, reservoirs (if utilized), and conduits there-for (as embodied in the figure under "New Generation", with LCO2 being supplied from master array supply conduit(s) 584 or 635, said heat accumulation array(s) may be isolated in respective separate-space envelopes permitting continuous heat extraction from the provided heat source(s) 617. While as indicated in the figure, all heat sources may concurrently source working fluid to a given distributed generator, it must be understood that appropriate instrumentation and control means shall be required to effect the timely isolation of said respective heat sources from the LCO2 master or branch supply conduit(s) as by valve(s) 576 while said separate- space array envelopes are concurrently permitted to exhaust said evolving vapour through pressure regulator(s) 615 and high pressure valve(s) 1996, and equally important that said heat accumulation array(s) be capable of isolation from said high pressure reservoirs 330 as by the closure of high pressure valve(s) 1996 to permit said heat accumulation array's filling with LCO2.

[00335] Since the goal of the system is to provide continuous heat extraction it is obvious that replenishment of LCO2 need be provided in advance of said fluid's exhaustion owing the depletion of said evolving gaseous CO ₂ permitted via its sourcing drive working fluid to Tesla-type work generation turbine(s). Therefore to provide said continuous heat extraction resulting in continuous cooling it is imperative that the system be designed to ideally provide redundancy in the heat sink means, and or (at least be) controlled so as to permit the loading of LCO2 into said respective heat accumulation arrays at largely indexed and preferably overlapping time intervals so that one or more heat accumulation sub-array(s) may be receiving cold LCO2 while others are substantially contributing to the turbine working fluid reservoir 330, said scheduling of operation resulting in the variously provided heat accumulation arrays to individually be in various stages, namely: just-filled with cold LCO2 as through open LCO2 isolation valve(s) 576 subsequently closed when the respective array is replete with LCO2, at which time thermal energy absorption may begin to bring the liquid to higher temperature and concurrently develop a high vapour pressure, during which time isolation valve 1996 respective to the heat source in question may be closed, or; full of LCO2 fluid and already brought to evaporation temperature and working fluid pressure and thereby vaporizing and thereby issuing high pressure gaseous working fluid through pressure regulator 615 and high pressure isolation valve(s) 1996 into reservoir 330, or; with LCO2 liquid level depleting while sourcing high pressure gaseous working fluid to reservoir 330 through pressure regulator 615 and high pressure isolation valve(s) 1996 as discussed, or; somewhere in between the aforementioned conditions,

[00336] While the contemplated control system for the overall distributed generation and central compression plant system strategy presented are on the scale of mega- engineering and therefore go beyond the scope of the basic combustion efficiency enhancement and carbon capture provided for herein, the versatility of disc turbines may again be important to consider since they may operate with biphasic working fluids without issue and while it may be stated that a timed schedule of operation in combination with discrete pressure switches, level switches and valves may effect the timely operation of appropriate control valve(s) to at length operate the independent LCO2 filling operations required, it may be anticipated that a large scale distributed network control system providing analog as well as discrete sensing and control means in combination with networked PLCs and large I/O capacity SCADA systems may best fulfill operation and control requirements of the overall system contemplated herein with a host of dedicated system operators staffed full-time to over-see safe system operation and maintenance of the mid through high pressure systems foreseeable.

[00337] While an average annual natural gas (methane, CH ₄ ) consumption of 2500 m ³ /year relates to a 6.8 m ³ daily CO ₂ emissions volume at STP, 0 ⁰ C, 101.3 kPa, (whereat CO ₂ has a specific volume of 0.5058 m /kg) or about 13.4 kg CO ₂ release per day average per home, the present methodology of the invention prefers rather to utilize said natural gas as an efficient heat extraction agent in evaporative cooling mode (and by extension preserve its usefulness to mankind substantially indefinitely instead of combusting said substance, whether efficiently or inefficiently, which by comparison destroys its extended usefulness), said evaporative cooling rather utilizing said fluid at low temperature at conducive pressures in containment in either first thermal communication with CO ₂ to be brought up to storage pressure and down to storage temperature via compression and heat extraction unto liquefaction, or alternately via second thermal communication whereby said fluid may be caused to extract thermal energy from LCO2 for its preservation in liquefied state to cooperate with CS efforts and power generation availed through down-stream heat abstraction.

[00338] Furnaces typically operate their integral blower in advance of the combustion burn to ensure their safe operation prior to initiating the burn (to validate the system's capability to safely clear all flue gases from the domicile or other emissions source' host building under consideration), and with said blower operating beyond the actual natural gas 'burn-time' a control system requirement is brought to light whereby the carbon capture conduit means 583 may be unduly loaded with atmospheric air (in the absence of a solution there-to) said representative concentration of air ingress being a source of concern to the present system methodology concerned with the sequestration of CO ₂ (not air), since said air may cause unwanted moisture accumulation in the carbon capture conduit(s) 583 further increasing the potential for formation of carbonic acid solution in said conduit(s) 583 which may limit the choices for acceptable conduit material. Accordingly the present system provides carbon capture isolation valve 572 which may be cued to close a configurable amount of time post termination of the furnace's burn, and also especially be caused to await a command based upon CO ₂ concentration or another signal (prior to opening) to ensure that only CO ₂ laden emissions are loaded into carbon capture conduit.

[00339] For the system to operate at optimal domicile-respective efficiency in terms of heat recuperation from the captured gaseous carbon emission, it would be advantageous if the volume of heat sink provided would match the pressurized volume of said carbon emissions so that with each burn, the volume of injected flue gas into the heat exchanger component of the system would equal the compressed volume of the flue gas by-product of combustion to enable the heat-laden carbon emission to substantially lose most of its heat to the provided heat exchanger(s) prior to being displaced unto injection into carbon capture conduit(s) 583. Accordingly, contemplation of heat exchanger sizing need be considered to design an effective system there-for, and with said 6.8 m of CO ₂ flue gas at STP over the course of a 24 hour period (assuming 2 combustion burns per hour for purposes of illustration, and 48 burns per day by extension) representing a per-burn volume of about 142 litres at STP, in consideration of a contemplated carbon capture injection pressure requirement for said flue gas of 4 bar gauge pressure (for purposes of illustration) for said captured emissions to be effectively injected into carbon capture conduit 583, a calculated compressed volume of emissions may rather be about 28 litres, which relates to providing a heat exchanger, for example, of 1" copper tube there-for of 57m (or 187 feet) in length to feasibly receive the total volume of emissions from each combustion burn which may thereby be substantially held in-situ to capture a maximum of heat energy there-from throughout the inter-burn period. This in turn relates to a requirement of about 16 twelve foot lengths of 'M' copper pipe or tubing which represents an entirely acceptable cost component to a system which may recuperate an anticipated-to-be-great quantity of heat on a per-day basis, through the capture of (normally wasted and polluting) carbon emissions, not mentioning for the moment the extensive beneficial effect which the very capture of said emissions would have on a global scale if this method would become the status-quo for construction of all new housing, especially with the anticipated demand for retro-fit of domiciles and other emitters combustion sources once the conservation and cost savings become realized and widely known.

[00340] A big picture view of the presently contemplated system provides colossal volumes of heat bearing flue gases from myriad carbon emission sources which first compressed and forced to give up a large portion of their contained heat energy to heat extraction loops largely at the source(s) of combustion, and subsequently joined by cooled, compressed, filtered and de-watered emissions from other myriads of combustion flue gas inputs to the contemplated networked system conduits there-for representing the requisite provision of infrastructure means and connectivity there-to said carbon capture conduit(s) to be provided by industry and governments to be located within an economically feasible (conduit construction cost) distance there-from combustion emission source(s) so that while ideally mandatory connectivity there-to may be required under law for all carbon emissions, that said infrastructure provision may make it economically feasible for home-owners, as well as commercial and industrial emitters alike to substantially 'help themselves' to the step change in efficiency provided by the energy recuperations discussed by coming forward with their share of the cost to utilize the connectivity provided, whereupon ready payback on the investment of heat exchange and controls therefore may commence upon system installation which may substantially lower the required number of furnace 'burns' through discussed heat recuperations, and with said conduit(s) infrastructure provided being sized first in accordance with economic feasibility (in terms of readily recuperated costs, a portion of net savings by each user may be deemed a tariff on system usage to offset the construction costs of said required infrastructure) wherein a more modest demonstration scale system may first be constructed, and with time and experience later designed for the anticipated total regional user emissions injection into said carbon capture conduit(s) 583 on scales permitting the inclusion of whole towns' and cities' pre-cooled, pre-de-watered and pre-compressed carbon emissions being communicated there-into large diameter actively cooled conduits bound and destined for further compression and cooling unto liquefaction at central compression plants by large diameter and advantageously high angular velocity of rotation disc compression means. While central compression plants driving large compressors may operate locally to high populations, alternate auxiliary compression means preferably driven by renewable and or clean sources of power (for example, in the form of the mountain-top Tesla-type turbine wind power generation station indicated in Figures Ic, Id and 2a for high winds energy harvest, and or also by the exhaustive list of other renewable energy applications capable of driving an auxiliary compression load) by nature of being supplied significantly pre-compressed and pre-cooled working fluid from first stage compression (ie: distributed multi-stage Tesla-type VCM 2000s compressing combustion flue gas) and being provided further cooling means discussed, the significantly decreased power requirement imposed by compression of "pre-compressed and pre-cooled" emissions compared with "uncompressed and hot" emissions shall concurrently make it much more economically feasible for carbon capture and sequestration efforts to liquefy the carbon emissions on the grand scale required to nullify or reverse human-kind's contribution to climate change, which reversal may in part be well represented and more feasibly realized through the rapid integration of the method herein discussed owing said pre-cooling and pre-compression of emissions provided which at length offers: a great deal of energy conservation in terms of fossil fuel consumption; a proportionate cost savings respective to said conservation; a great quantity of ongoing heat reclamation at reasonable initial cost outlay; comparative 'free' compression and cooling of carbon emissions; capture of carbon emissions; further energy recovery from the cooling of captured carbon emissions while en-route to compression, liquefaction and sequestration vaults; the increase of density (reduction in specific volume owing the in-transit cooling provided) of said carbon emissions accordingly with said further energy recovery from said captured carbon emissions while in captivity and en-route to said sequestration vault(s); new uses for carbon emissions through power generation offered via heat recovery and evaporation of LCO2 product produced by the system in conjunction with disc turbine(s) and disc compression technology; new applications for gaining expertise in the field of disc turbine usage; a fundamental change from the usage of fossil fuels as combustion sources to their employment as cooling agents and preferably only permitting their burning for occasional aesthetic purposes instead of for home heating, with heating instead (in time) being rather produced from work conversion energy recovery from a new "anthropogenic carbon-cycle" in which LCO2 may be considered the fuel and hydrocarbons their chilling agents; substantially providing energy recovery from cold-engine technology applied on very large scale, said cold engines providing energy recovery by way of the thermal communication of heat energy from the ambient and hotter mediums into cold LCO2 and volatile organic liquid mediums including said hydrocarbons controlled between advantageous pressures so as to provide evaporative cooling through heat exchangers of great length and or capacity with said hydrocarbon being contained in internally or externally located high pressure compatible conduit(s) 584, with said evaporate communicating with disc compression means returning said hydrocarbon to the liquid state through isolated compression in the absence of oxygen while conserving the heat energy of vaporization (upon said condensation thereof said pre-pressurized hydrocarbon) by surrounding said heat exchange couple(s) with further heat collection apparatus and fluid in containment which may include a further thermally conductive heat sink conduit means of lower pressure rating which may contain water or another liquid fluid of lower however serving boiling point substantially permitting hydrocarbons to cool carbon emissions (instead of carbon emissions being generated from hydrocarbons) on requisite scales of economy, with work generation as well as cooling thereof said flue gases effected on a grand scale over the length of desirously very large arrays of said conduit means concurrently providing transport of said cooled flue gases there-through to central compression facilities at the end of the line whereat further filtering, dehumidification, compression and cooling unto liquefaction of said flue gases (carbon emissions) into a product which may be returned to said outer conduit/tubing array 583 or which may be provided for furtherance to said carbon sequestration vaults as well as other points of use according to the invention whereat said largely LCO2 product may be utilized for power generation as well as cooling capacity in far-ranging heat transfer applications (some of which have been discussed or alluded to herein) which when considered in terms of their combined capacities for utilization of LCO2 as an evaporative cooling 'fuel', the discussed and foreseeable applications intended may provide point a path forward to sustainable closed-loop power generation which in large usage may positively influence the course of climate change through the requirement for desirously large volumes of LCO2 to be ever contained in heat-sinking apparatuses where further energy extraction capacity growing with the extent of the conduit(s) infrastructure provided, with said conduit(s) providing important ongoing cooling capacity further availing power generation there-from evaporate generated through said cooling, said cooling availing better economy of compression by the method, which method cooperating favourably to provide ROI from CS efforts in the form of both power generation and also temperature reduction through said cooling capacity provided, said cooling capacity and method being capable of application anywhere on he globe may therefore be directed to producing power as a by-product of heat extraction in first critical regions of our globe including the polar ice-shelf boundaries of Greenland and Antarctica under attack from warming air and warmer seas wherein excess thermal energy for recovery may concurrently be availed for extraction, which heat extraction may result in the cooling of the seawater to the advantage of the formation of new ice in the polar regions (with appropriate staging and fluids selection), and which method may likewise provide cooling in the tropics where very large arrays of wave energy harvesting energy to run compression means may concurrently generate temperature reduction to control and remove hurricane input potential from the warm oceanic water thereat while providing said wave energy conversion and also whereby either solar thermal energy conversion may be built there-into the method to provide the power necessary to add extra compression and or cooling, or said wave energy conversion floating apparatus simply providing reflection of a majority portion of the thermal energy load received from the sun to concomitantly cooperate with the cooling to be provided through the prevention of thermal overload of the surface waters thereat with an appropriate wave energy harvesting array-element density, oceanic cooling may be provided with advantage and ROI.

[00341] While ongoing demonstration of long-term CS vault service continues (said vaults largely comprising saline aquifers and oil and gas-field cavities and/or permeable rock and other strata formations at suitable depths), the present invention offers new power generation capacity as ROI from said ongoing LCO2 liquefaction processes while concurrently affording cooling potential wherever said LCO2 is permitted to thermally communicate through high-pressure compatible heat exchangers substantially offering controlled egress for a portion of said LCO2 product en-route to said CS vaults. Wholly separate satellite capacities may alternately receive the CS-bound liquefied CO ₂ product for purposes of power generation utilizing said LCO2 as a source working fluid in combination with solar thermal, heat-island energy extraction and conversion, OTEC, ambient heat as well as in residential, industrial, and commercial waste heat recovery (and elsewhere) to add CS capacity beyond that capable of being sent to vault(s) via immediately available conduits there-for, meanwhile providing return on investment which may in part pay for the furtherance of CS efforts and infrastructure into the future.

[00342] It is evident upon examination of the vapour pressure curve for carbon-dioxide (in reference to Figure 9c) that a substantial vapour pressure shall be availed upon evaporation of said LCO2 contained in high-pressure rating conduits utilized as working fluid for work generation means (turbine 590 indicated in Figure 7a) whereby a method and system following there-from may simultaneously convert heat from a plurality of sources into renewable zero emission energy. The figure indicates not only combustion exhaust cooling to provide energy input to vaporize LCO2 into high pressure gaseous CO ₂ working fluid, but also indicates separate heat extraction loops entirely (as generally indicated by New Generation in the figure) which may all simultaneously contribute to a multiplexed working fluid source respective to an array of heat sources, with said working fluid being at length supplied to one or more disc turbines at a regulated pressure where-through said work generation process further heat may be extracted there-from said gaseous fluid evaporate through the throttling process to further cool the CO ₂ vapour in preparation for its subsequent re-compression, whereby a system of energy generation from the vaporization of LCO2 may be generally defined in which: pressurized working fluid accumulating in a high pressure reservoir prior to its expansion across a work generating prime mover and its subsequent re-compression unto liquefaction via co-rotating compressor and cooling means with produced LCO2's subsequent deposition into sequentially opened segments of a heat accumulation array comprising heat sinks, heat sources, reservoirs and valves may provide energy generation in substantially closed loop. Thermal coupling of heat accumulation array segments to ambient and warmer heat sources including those extracting work from the system itself may effect post-compression of isolated working fluid which thereby attains sufficient pressure to be (re-)liquefied, where-after its re-deposition into heat accumulation array(s), its heat energy gain and vaporization and remunerative resourcing of the prime mover may continuously develop work. Gaseous egress from array segments via discharge paths commonly communicating with the prime mover supply reservoir provide a multiplexed source of prime mover working fluid capable of sustaining continuous work output.

[00343] With biphasic gaseous and liquid CO ₂ already in use in trans-critical refrigeration systems contemplating work extraction (46) to increase efficiencies thereof, demonstrable work is already in progress which prefers CO ₂ to be employed as the primary working fluid in similar-temperature-range heat extraction application. Tesla turbines and compressors known to operate with largely any fluid possessing a serviceable viscosity character may work well in conjunction with CO ₂ as discussed herein, and thereby industrial, commercial, and residential emissions being forced into regulated pipelines bound for carbon sequestration compression & liquefaction plants may in a twist actually drive the development of new energy generation. Known to have a high cooling capacity, carbon dioxide may therefore provide great heat load recovery from said emissions via heat exchangers designed specifically for large volume heat exchange as suggested herein. Therefore, while fossil fuels are still being burned for their heat and work capacities, the added measures of the remnant heat which (beyond that which the present invention suggests may be readily extracted prior to ejection from domiciles and other point-of-use emitters' buildings) thereafter captured in carbon capture conduits 583 may through the use of LCO2 as disclosed provide at least part of the heat energy required to effect thermal energy gain in other working fluids which in response to evaporation on large scales may likewise develop large vapour pressures which may also sustain the operation of Tesla type turbines (whereby it may be stated that Methane also possess a serviceable viscosity forwardly looking to integration with the present invention in a non-combustion mode of service in evaporative cooling mode).

[00344] While the presently disclosed method may permit economically feasible capture of great quantities of emissions in said conduits 583 bound for compression, cooling, liquefaction and sequestration means, this shall require the replacement or bypassing (preferably in parallel) of the various existing arrangements of blowers operating at the various points of combustion including residential furnace blower emissions exiting through chimney-pipes, industrial emissions blown out through diffusers, and enormous power plant emission through the tall stacks in order to prevent the emission of pollution and CO2 forced out into the atmosphere where it causes environmental and ecologic damage via pollution of the air we breathe. Therefore, by utilizing combinations of coaxially rotating vacuum-compression disc turbine and compressor devices of the Tesla type which should not provide any more electrical load on given emitters power budgets (as compared with utilizing prior art pitched bladed fans or blowers known to require power increasing with the cube of their operating speed) currently employed to pollute the atmosphere in operational 'service' today, whereas by contrast, the utilization of the Tesla technology globally for CS purposes evidently may serve very well in the disclosed path to a sustainable future through heat abstraction (ie: within said CS pipelines) which may be utilized as discussed for heat-engine heat sourcing, or which may alternately be utilized for other heat-exchange to reduce the energy requirements, for example, to pre-heat boiler steam water or for other water-heating applications, working with CS system conduits to facilitate the extraction of the heat load we 'normally' impose upon our environments through our actions (fossil fuel usage), and at length enable us to derive energy from our fossil fuel waste by-products while containing them, re-using them in said point of use heat engines employing CO ₂ as a working fluid, subsequently re-compressed, re-liquefied ad-infinitum (in conjunction with other CS vaults receiving the bulk of liquefied CO ₂ throughput until such time as the world no longer has or has need of fossil fuels as a combustion energy source, by which time other renewables, including geothermal, waste-heat, solar, heat-island heat extraction, very efficient reciprocating hydro power generation methods and vacuum viscosity engines and other efficient technologies described herein, along with other viable and established renewable technologies shall provide for our energy needs in conjunction with the extended and remunerative service of sequestered carbon emissions and hydrocarbons in non-combustion evaporative cooling modes there-ever-after.

[00345] Whereas the system has been depicted with tube 612 as well as tube-in-tube heat exchangers 612/613 functioning to recover the heats of combustion and compression, in other embodiments of such heat recovery systems, larger capacity heat sink reservoirs filled with a suitable liquid heat extraction fluid may instead be designed to receive said heats as by routing conduit 655 there-into said reservoir at or near its top and thereafter being passed as heat sink conduit 612 there-through said reservoir such that throughout its series length it is (and where utilized, other isolated heat recovery branches are) arranged to maintain a steady downward inclination so as to permit evolving condensate to pass freely through said heat exchange reservoir without pooling, and in the alternate case of run(s) of conduit 612 comprising a plurality of parallel interconnected conduits (providing a less restricted flow path through said heat exchanger) that said condensate may likewise not be permitted to pool as by the similar maintenance of suitable slope there-through to discharge from said reservoir, with each run of conduit 655 being provided isolation means at inlet and outlet ends preferably located external to said reservoir to permit controlled isolation of individual heat-sink conduit 655 paths which may further permit decision making contingency in case of leak development requiring patching or replacement of particular conduit(s) 655 or when maintenance cleaning of said conduits may be required over time to remove accumulated soot.

[00346] In similar fashion to the figure, transfer of said heat to another location for use may be provided by conduits 613 also being routed there-through the liquid heat sink fluid within said larger capacity reservoir, whereby circulation of a heat transfer fluid 622/624 may permit heat utilization elsewhere.

[00347] With the utilization of a reservoir instead of the tube in tube arrangement, the system may be easier to prepare and install, and the requirement for larger diameter high temperature combustion-exhaust-compatible external tubing/piping which must satisfy the safety prerequisite of being capable of withstanding the full heat of combustion products (in the event that leak(s) developing in the outer liquid heat recovery fluid loop conduit partially or completely drain said liquid heat extraction fluid). The larger diameter outer conduit material representing a significant cost of such systems being swapped for the specification of said larger capacity heat sink reservoir(s) may thereby permit a plurality of segregated pressurized combustion exhaust conduits 612 to maximize the system's capability to extract an optimum amount of heat from each charge of high temperature pressurized combustion exhaust by providing each charge an acceptably long residence time within said segregated conduits 612 under full immersion in the bulk liquid heat extraction fluid so that a more substantial heat recovery may be enabled.

[00348] It may also be stated that with the provision of a mounting fixture built into said higher capacity reservoir as well as an (above or below liquid level) inlet connection between combustion exhaust conduit 652 and the inlet of low pressure compression stage 283 (note that the motor there-for would be mounted external to said reservoir and provided suitable electrical isolation there-from) as well as an outlet connection from the final stage of provided compression (285 in the figure), that the heat of compression provided by elements 283 through 285 of the system by nature of being submerged and able to communicate heat through VCM 2000' s housing directly into the reservoir's heat recovery fluid, that a more complete heat of compression recovery there-from may result in comparison to a tube heat exchanger 612 wrapped around said compression means. Where multiple heat extraction conduits 612 are utilized, a programmed sequence of inlet (and possibly outlet) selector valves operating in cooperation with check valve(s) in each path may control the duty cycle and therefore residence time of heat-bearing compressed fluid in each submerged heat transfer conduit (612). Also, to further reduce the temperature of discharged combustion exhaust and concurrently extract more heat from said exhausts for useful purpose, it may be stated that secondary and possibly tertiary heat sinking liquid fluid reservoir(s) may be installed in series with the first and each branch of heat sink conduit 612 may be run in series there-from one to the next with heat transfer conduits 613 passing heat transfer fluid 622/624 may be likewise caused to circulate there-through each in reverse order to increase the temperature of the heat transfer fluid in stages.

[00349] The added costs implicated to outfit given fluid energy conversion disc device systems with a dynamic disc positioning sub-system may be deemed unnecessary where largely constant flow velocity and fluid viscosity conditions are availed by particular applications (for example, in cases of the liquid fluidic lift system disclosed in respect to Figure 2, where subterranean and or well insulated conduits may largely control the temperature of the fluid and therefore also its viscosity and the flow velocity of the fluid may remain substantially constant in the downhill direction under normal operating conditions). In these cases, a manually adjustable disc positioning system may be provided at comparatively reduced cost by providing one or more end disc(s) equipped with, for example, one or more cam adjustable or threaded screw mechanism(s) capable of applying adjustable tension or compression in opposition to a similarly positioned pressure-plate component in turn applying pressure to spacers and springs or permanent magnet disc spacing elements as previously discussed. In systems where manually adjustable disc positioning is provided, the required disc spacing may be calculated and then set, or alternately the system disc spacing may be approximated, set, and then through a trial and error procedure of quantifying observable power derivation under the given fluid conditions and hence re-adjusting disc spacing, the most advantageous disc spacing may thereby be arrived at.

[00350] It is evident that once system parameters have been honed and disc spacing optimized for given application(s), that identical flow, (pipe or other conduit) friction, fluid velocity and viscosity conditions as well as disc device rotor configuration(s) provided by an identical (or alike in said terms) application(s) may benefit from the precedent of learned disc spacing previously found to be of service, whereby an identical disc spacing may be configured for like disc device element(s) of said like system(s). While fixed disc spacing may therefore in many cases be preferable for reducing system cost, in other systems changing fluid conditions, load application, as well as maintenance requirements may all provide valid reason for incurring said added cost of components required to provide configurable manual and or dynamic disc spacing to avail benefit under said conditions.

[00351] Referring now to Figure 7b, an alternate application of the simultaneous application of pressure differentials is illustrated in the context of moving heat collection fluid to a solar thermal energy collector with an associated pressure differential application system provided there-for.

With reference now to Figure 8, a portion of a disc runner with magnetic disc spacing elements is shown wherein end-discs 234 having bellows 464 concealed behind an axially positioned 'pressure-plate' disc 250b, said bellows 464 being filled with a pressurized medium 236 at run-time and said controllably regulated 238 pressurized medium 236 admitted to the disc runner by way of conduit 240 and conduit connector 241 is shown entering into bellows 464 through port 242 at run-time to effectively set disc spacing according to the pressure of said control fluid medium 236, the pressure of which being set by an automatic controller sending a control signal to regulator 238 to adjust said pressure within said bellows further based upon the working fluid kinetic viscosity and rotor angular velocity via ingress and egress of a required mass of fluid volume under said automated control pressure so as to effect axial shift of discs 216 having magnetic elements bonded, set, or fixed to discs 216, said magnetic elements preferably being flush-mounted within the disc surface so that upon changing control pressure set-points, said discs 216 may find a position of rest intermediate said end-discs 234 which (provided equivalent magnetic strength magnets are provided) said position of rest between said end disc magnets 465 may be largely equidistant each other owing the instantaneous positioning effect of permanent magnets. With said magnetic positioning magnets about each through-bolt 224 of each disc 216 or at another place on the disc provided that the utilized configuration provides symmetric location of said elements about the disc surfaces, with all discs 216 having said positioned magnets 252 installed at the same respective locations on each discs, the full complement of discs 216 between said end discs may be magnetically positioned proportionately according to the control fluid pressure (and at length, process conditions observed), with said end disc magnets located in protective isolation within or adjacent said bellows 464 behind a further protective pressure plate 250b.

With reference now to Figure 9, charts provided were referenced with respect to earlier figures.

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