SOURCES

FIELD OF INVENTION

Present invention is pertinent in electric generating steam turbine related with energy conversion system.

Present invention (Tezgel CCP - Combined Cooling and Power) is related with an energy conversion system. System designed to convert very poor grade heat in resources like atmosphere or water into electricity to enable heat rejection of cooling process transmittable to distant place. The present invention relates to ORC (Organic Rankine Cycle), Air source Heat pump (reverse Carnot cycle), Steam accumulator, Air jet Nozzle, rotating vortex structure and internal-axis type counter-rotating none-positive-displacement reaction type engine, No iron core Axial magnetic field generator, steam driven feedback pump, control unit for working fluid flow regime. In greater detail, present invention interested in energy conversion from very poor level free environmental heat energy to electricity and store or transmitting it to distant places, leading to reduction of global warming.

PRIOR ART

Current heat pumps performances (COP values) are at least 1:3 (1:8 is possible). We can transfer 3 unit of heat energy from colder region to hotter region with cost of 1 unit energy. Kirchhoff s junction rule dictates that total of through variables entering to a node will be zero (and energy is also a through variable). We should need to draw 4 unit of energy from place where heat pump located and heat energy delivered. If we convert all those 4 unit heat energy to electricity and feedback 1 unit of energy to heat pump to operate and lost another 1 unit due to leakages, still we will have extra 2 unit of electrical energy which will be subject to transmission. There exist many systems in nature which are related with heat. Contraction, Evaporation, Expansion effectuates pressure buildup which is starting point of natural events. Mankind observed and developed several systems using heat to produce force for performing work. In earlier attempts are done on external combustion engines like steam engines. They are reciprocating, positive-displacement type engines with linear movement. Watt (1781) patented first rotary engine. But very first kind of rotary engine was aeolipile (hero engine, Hero of Alexandria 1 ^st CE). Hero engine is first none-positive-displacement reaction type engine (steam turbine). Following studies continued with internal combustion engines.

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SUBSTITUTE SHEETS (RULE 26) Studies on fluids dynamics like Daniel Bernoulli (1738), Giovanni Venturi (1746), Gustaf de Laval (1888) engender very valuable knowledge like relationship between constriction, temperature, density, pressure and speed of fluid flow. The theoretical pressure drop at the

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constriction (throat) is given by Pi-P ₂ =EI/2(V ₂ -Vi ) where 12 is density, P pressure, V speed of fluid. Limiting Venturi effect is when a fluid reaches the state of choked flow where the fluid velocity approaches the local speed of sound, mass flow rate will not increase with further decrease in downstream pressure unless increase upstream pressure which increase density of flow (though the velocity remain constant at throat). The temperature will also increase the local sonic velocity yield increased mass flow rate. Expansion after throat increase flow speed further (De Laval nozzle principle).

Further studies on compressible (elastic) fluids (gases) and thermodynamics determined choked flow as upstream pressure to downstream pressure ratio greater than [(k + 1) / 2] ^{k/ (k " 1)} (where isentropic expansion factor k is specific heat ratios C _p C _v ). The relation between pressure, temperature and density in terms of local sound speed (Mac values) defined as:

ns for i ·d,ea ,l gases - ^{p k} r

^- = /VA . \

Isentropic relatio - , f ^ ^T A = f ^v J

The further studies in Aeronautical Sciences described maximum thrust obtained with throat to exit area ratio calculated by formula

Where A _e exit area, A _t throat area, P _e exit pressure,

stagnation pressure, k specific heat ratio. Also area to throat area relation with Mac values

Ae I— ( i -f- -— -— n

Where Ae exit area, At throat area, m is molecular weight, M Mac value, k specific heat ratio (Remembering stagnation Mac value is zero and throat Mac value is one).

Mass flow rate Q = At Pt !^^where Pt throat pressure, Mw molecular weight, Tt throat temperature, R' universal gas constant A _t throat area. Velocity at exit will be

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SUBSTITUTE SHEETS (RULE 26) ust will be

With this knowledge, we can effectively convert potential energy of pressurized into kinetic energy,

Demand for electricity brings back external combustion engines in fronts. Several issues

(like as thermodynamic cycles) restudied. Oliver Evans (1805) described closed vapor- compression refrigeration cycle. Sadi Carnot (1824) defined relation between work and ratio of Heat difference that shows lower Tcoid also increase efficiency instead of rising T _HOJ . The Rankine cycle is an idealized thermodynamic cycle of a heat engine that converts heat into mechanical work can be defined as; pumping working fluid to boiler, heat added to working fluid to produce pressurized steam which is drives turbine and cooled, condensed back via heat rejection and re-enters back to pump to form a closed loop of fluid circuit. Organic Rankine Cycle (ORC) using organic compounds in place water and steam allows use of lower-temperature heat sources. Also organic compounds are beneficial for momentum transfer because of heavier molecular weight than water.

Nicola Tesia (1913) developed a turbine referred to as bladeless turbine which is also known as the boundary layer or cohesion type turbine. The operation of this turbine exploits momentum transfer due to skin friction drag effect shear stress force beside elongated pathway for flow that increase flow and surface interaction time for momentum transfer Savery ( 1698), Nfewcomen (1712) developed steam engine for pumping water based on positive steam pressure and negative pressure by cooled steam contraction.

OBJECT OF INVENTION

Aim of invention is to produce electricity from very poor grade heat sources like atmosphere with an appropriate turbine structure related to an energy convergent system to enable heat rejection of cooling process transmittable to distant place.

Today's most intimidating problem is global warming. Unfortunately Greenhouse effect was accepted as only suspect for problem and solution seek out in this aspect. We can reduce heat by means of cooling, which is also described as removing energy from the system that containing it. We can't contact subjected environment with another colder environment for cooling. But we can convert heat to electricity and consume it somewhere else. With this

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SUBSTITUTE SHEETS (RULE 26) approach we will not need fossil energy resources anymore since using produced electric energy for work will convert it back to heat energy again.

BRIEF SUMMARY OF INVENTION

Current invention provides a device for electric generation comprising a first rotor which is rotatable about a rotation axis by the action of a pressurized fluid and one or more magnets arranged on the first rotor to rotate together therewith further comprising a second rotor arranged to rotate coaxially with the first rotor by the effect of the pressurized fluid and electric coil windings arranged on the second rotor to rotate together therewith to produce electricity when the first rotor and the second rotor are rotated by the pressurized fluid in opposite directions .

Current invention provides a device for electric generation comprising a first rotor having a plurality of magnets or electric coil windings provided thereon arranged to rotate by the action of a pressurized fluid about a rotation axis; first rotor comprising a nozzle disc having a central inlet through which the pressurized fluid can enter first rotor and one or more openings through which the pressurized fluid can be sprayed in a circumferential direction there from and one or more passages for delivering the pressurized fluid from the central inlet to the one or more openings; a second rotor coaxially arranged with respect to the first rotor comprising a plurality of coaxially arranged conical structures having corresponding electric coil windings or magnets thereon arranged in such a way as to rotate by the effect of the pressurized fluid exiting said nozzle disc and entering between the conical structures, wherein the electric coil windings generate electricity when the pressurized fluid rotates the first rotor and the second rotor in opposite directions such that the plurality of magnets and electric coil windings rotate along each other. The device may further comprise a hollow shaft rotating about the rotation axis, wherein the first rotor is arranged on the hollow shaft such that the pressurized fluid is supplied through the shaft to the nozzle disc.

Present invention briefly converts heat energy of environment to electricity with an appropriate turbine structure. Specialty of present invention is the turbine which possesses one rotating vortex structure and another, internal-axis type counter-rotating none-positive- displacement reaction type rotor, where, both are rotating with effect of same pressurized fluid. Plural amount of magnets arranged on reaction type rotor and (preferably) equal amount of electric coil be placed on counter rotating vortex rotor to produce electricity. With this structure, pressurized fluid rotates both rotors in counter direction that yields magnets are

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SUBSTITUTE SHEETS (RULE 26) rotating against to coils with sum of both rotors speed. Magnets and coils are arranged so that the magnetic flux variation rate is doubled. Therefore, it is possible to generate higher voltage with lower rotation speed limited by lower fluid pressure. Also the energy remained in pressurized fluid leaving reaction rotor (after some amount of momentum transfer to reaction rotor) will be utilized and consumed in vortex rotor structure with secondary momentum transfer to vortex rotor.

Both rotors have at least one channel to allow pressurized fluid to enter and exit. The channel(s) of reaction rotor begins at center and ends at surrounding edge forming jet nozzle(s). The channel of vortex rotor starts from center (where reaction rotor states) and ends at distant edge of vortex structure in axial direction. Vortex rotor provide at least two curved surface structures which are co-axially interlaced parallel to one another preferably nested coaxial cylindrical or conic surface structure and vortex rotor channel(s) established between surfaces of those nested surfaces.

Pressurized fluid supplied to turbine by a steam accumulator where the heat provided to accumulator through a heat pump.

Current invention is further defined by the appended claims, the content of which is included here by reference.

Present invention Tezgel CCP (Combined Cooling and Power) designed as a system, based on thermally coupled two fluid circuits operated with appropriate thermodynamic cycles where heat rejections done to each other, wherein: a) Cooling Fluid Circuit (CFC) is responsible from gathering heat energy from environment and injecting into second circuit. Operating in reverse Carnot thermodynamic cycle.

b) Power Fluid Circuit (PFC) is responsible from converting injected heat into pressurized vapor. Operating in thermodynamic cycle very similar with Rankine cycle.

c) Turbine is responsible from efficiently converting potential energy in pressurized vapor into kinetic energy and transfer momentum to rotors.

d) Electric generator is responsible to generate electricity with produced work from turbine

e) Control logic unit is responsible from controlling flow regime for healthy operation. Details of the invention:

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SU BSTITUTE SH EETS (RU LE 26) Present invention is an energy conversion systems adapted to convert very poor grade heat in resources like atmosphere or water (be called as ambient) into electricity to enable heat rejection of cooling process to distant place.

Said system in item 1 comprises thermally coupled cooling and power elastic fluid circuits regulated by a control unit (Then after are called as CFC and PFC). The heat rejection of each circuit done to other circuit and operate in their own specific thermodynamic cycles.

Said CFC in item 2 (operating in reverse Carnot thermodynamic cycle) comprises; electric battery (29), compressor (1), Working fluid (refrigerant), storage tank (2) (thermally isolated from environment to prevent heat leak in), evaporator (7), heat exchangers (3), (4), (10) and (35) (which is mounted in said tank (2)) are thermally coupled with PFC, heat exchanger (6) thermally coupled with environment. It is the main energy input from environment to said conversion system.

Said PFC in item 2 (operating in similar to Rankie thermodynamic cycle) comprises; organic working fluid (refrigerant), circulation pump (8), heat exchangers (3), (4), (10) & (35) said in item 3 (thermally coupled with CFC), heat exchanger (34) (thermally coupled with environment act as secondary energy input from environment to said conversion system), steam accumulator (5), turbine, electric generator (combined with said turbine), condenser tank (25) (thermally coupled with CFC via heat exchanger (10), and feedback pump tank (28).

Said steam accumulator in item 4 comprises a horizontally placed cylindrical pressure vessel (5), half loaded with said working fluid in item 4, and surface extenders (9) hanged in vessel and safety pressure valve (33) to prevent explosion due to uncontrolled pressure buildup in said vessel (5). Said vessel (5) thermally isolated from environment to prevent heat leak out.

Said surface extenders in item 5 comprises; vertical stack of overflow trays (9). Where shallow trays haying overflow holes to allow excess fluid spillover to down tray. (Surface extension may also be archived alternatively by spraying). Surface extension improves evaporation rate.

Said working fluid in item 4 is an organic compound (refrigerant) which is stable, none hazardous, low boiling point (near to 0°C at 1 bar) and relatively high pressure at operation temperature (typically 80°C)

Said condenser tank in item 4 comprises a vertical placed pressure vessel (25), cooling bars (10) placed in said vessel (25) in the circumferential direction. Said cooling bars

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SUBSTITUTE SHEETS (RULE 26) (10) acting as heat exchanger having longitudinal conduit (26) in center and urchin like pins (27) on one face to extend contact area, Bottom of said pressure vessel (25) is providing space to host for condensed liquid. Said pressure vessel (25) is thermally isolated from environment to prevent heat leak in. The turbine/generator said in item 4 is hanged vertically in this said pressure vessel (25).

9. Said turbine in item 4 comprises a vortex structure as secondary rotor and an internal- axis type a coaxial counter-rotating primary rotor (none-positive-displacement reaction type engine).

10. Said primary rotor in item 9 comprise a nozzle disk (11) between cover disks (36) sandwiched between two flanges (12) made from ferromagnetic material, O-ring sealants (32). One of the flanges (12) bind to a shaft (22) on center and the other said flange bind at center to a vapor carrying pipe (acting as a shaft) coming from a rotary join (16) (which enables free spinning). Said shaft (22) enables hanging the turbine in said condenser vessel (25) via axial thrust bearing (23).

11. Said nozzle disk in item 10 is a disk (11) sandwiched between two other cover disks (36), having one or more slits beginning from center and ends at surrounding edge to form jet nozzle(s) (37) with convergent and divergent sections precisely calculated for maximized thrust. Said nozzle geometry calculation for maximum thrust depends on operation vapor temperature, pressure and specific heat ratios of said working fluid in item 5 and pressure within the condenser vessel (25) and throat area of said nozzle.

The oblique surfaces formed after transonic speed provides additional angular momentum by lifting effect at supersonic flow while guiding to flow for tangential to disk at exit.

12. Said vortex structure in item 9 comprises plurality of co-axially interlaced nested in other one cones (21) having space between them as double of boundary layer for said working fluid vapor, support disk (17) and coil-disk (14) said in item 13 with ball bearings (23) at center for free spin and axial alignment support for said cones (21), vortex ring (24) which start vortex and binds cones stacks (21). Skin friction drag effect at boundary layer, creates a shear stress force which provides second partial momentum (energy) transfer from said vapor to said turbine. Said vortex structure work as counter rotating secondary rotor for turbine.

13. Said electric generator in item 5 comprises magnetic flux circuit structure (12, 13, and 15), coil-disks (14) and a commutator structure (18, 19, 20, and 31). Magnetic flux circuit fastened to primary rotor said in item 9 and coil-disk (14) fastened to vortex

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SUBSTITUTE SHEETS (RULE 26) structure as secondary rotor. Since both rotor spins in counter direction, relative speed of coil-disk (14) versus magnetic field became as sum of both rotors' spin speed. Commutator structure alters generator output from A.C. type to D.C. type. Generator can be used as D.C. type motor (with no iron core, no hysteresis loss) in other application than Tezgel CCP. Without commutator structure generated current is A.C. type in relatively high frequency which may be good for transmission or heating with induction. The D.C. type current is needed for charging battery (29) and be supplied by semiconductor diode bridge. A semiconductor inverter structure may be combined with generator to obtain compatible current with domestic power grid.

Said magnetic flux circuit structure in item 13 comprise plurality of even numbered electro/permanent magnets (13) fastened in circumferential direction on surface of said flanges (12) in item 10 and another flanges (15) made from ferromagnetic material. Said magnets' (13) field direction is perpendicular to said flanges (12 & 15) surfaces and in main axial direction. Polarities of each said magnets (13) are reversed with neighbor one. The distance between flanges (12 & 15) is close to coil-disk (14) thickness and allow the coil-disk (14) rotate freely. Said flanges (15) synchronously rotate with said primary rotor flange (12) due to magnetic coupling. Number of magnets (13) defines number of poles of said generator in item 5. A pair of neighbor magnet (with reverse polarities) on one of the flange and another pair of magnet on the other said flange creates a magnetic field circuit with air gap of coil disk thickness. Said coil-disk in item 13 comprises plurality of trapezoidal shaped coils (30) adjoined each other in the circumferential direction to form a disk (14). Number of coils is equal to number of magnets defined in item 14 and must be even. Coil (30) windings must be counter direction of adjacent one. Coil (30) inner width must be large enough to surround said magnets (13) sizes in item 14. Coil terminals connected to other coils terminals in serial or parallel method to achieve desired output voltage. This connections yield only two terminals for generator. The thickness of coil-disk (14) determines air gap in magnetic flux circuit said in item 13. Said thickness depends on thickness of ball bearing (23) said in item 12 apparatus which placed at center of disk that contributes free spinning and axial alignment support for cone structure (21) said in item 12.

Said commutator structure in item 13 comprises collector disk (17) and two set of carbon brush structure (18).

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SU BSTITUTE SH EETS (RU LE 26) . Said collector disk (17) in item 16 comprise copper conductors (31) fastened on surface of axial alignment disk (17) said in item 12, in the circumferential direction. Number of conductors is equal to generator pole count defined in item 14. Each conductor short circuit (electrically) to next conductor of adjacent one to form two set of conductors. Each set will connect electrically to terminals of generator in item 15.

Descriptions of figures:

Figure 1: A schema of preferred arrangement of energy conversion system according to invention;

Figure 2: Sectional view of a preferred embodiment of the turbine and generator arrangement according to the invention;

Figure 3: Sectional view of a preferred embodiment of the reaction rotor arrangement according to the invention;

Figure 4: A side view of a preferred embodiment of flanges, magnets and coil disk arrangement on common rotation axis as one planar side of reaction rotor according to the invention;

Figure 5: A side and top view of a preferred embodiment of the nozzle disk and nozzle opening according to the invention;

Figure 6: Top view of the coil disk according to the invention

Figure 7: Top view of the magnet and coil size relation according to the invention Figure 8: The slide rings and carbon brushes of the commutator and support disk with commutator contactors according to the invention;

Figure 9: The coil and magnetic field of the arrangement for flux change doubling according to the invention;

Figure 10: Simplified but less efficient alternate arrangement of energy conversion system according to invention

Detailed description of invention:

In following, a preferred embodiment of invention is described. Invention is not bounded with this preferred embodiment; it may be implemented as alternative forms to realize energy conversion from low grade heat sources to electricity through other means to cool atmosphere for preventing global warming. A very

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SUBSTITUTE SHEETS (RULE 26) simplified alternative embodiment is provided in Figure 10 as an example replacing a condensation pump with condenser, liquefy and feedback. Regarding power consumption of condensation pump, this system will be less efficient but still serve the idea. A device for electric generation (= turbine) is shown in Figure 2 comprising: a reaction rotor having a plurality of magnets (13) arranged thereon arranged by the action of a pressurized fluid to rotate about a rotation axis; the reaction rotor comprising a nozzle disc (11) having a central inlet through which said pressurized fluid can enter the reaction rotor and one or more openings through which the pressurized fluid can be sprayed in a circumferential direction there from and one or more passages for delivering the pressurized fluid from the central inlet to the one or more spray openings; a coaxial vortex rotor comprising a plurality of coaxially arranged conical structures (21) having corresponding electric coil windings (30) thereon arranged in such a way as to rotate by the effect of the pressurized fluid exiting the nozzle disc (11) and entering between the conical structures (21), wherein the electric coil windings (30) generate electricity when the pressurized fluid rotates the reaction rotor and vortex rotor in opposite directions.

The device further comprises a hollow shaft (22) rotating about the rotation axis, wherein the reaction rotor is arranged on the shaft (22) and the pressurized fluid is supplied through the shaft (22) to the reaction rotor.

Cooling fluid circuit (CFC):

Compressor (1) powered with electric battery (29), compresses (isentropic) the refrigerant into tank (2) through heat exchangers (3 & 4). Isentropic compression raises refrigerant temperature. Hot fluid passes through heat exchanger (3) for primary heat rejection (thermally coupled with PFC). Temperature of fluid will drop near to operation temperature of PFC. Refrigerant fluid passes through another heat exchanger (4) for secondary heat rejection which is thermally coupled with CFC where temperature almost equal with environment. Temperature of fluid will approach down to ambient temperature since CFC fluid may only warm up to environment temperature. Cooled down CFC fluid be accumulated in tank (2). The heat exchanger (35) within the storage tank (2) (thermally coupled with PFC where

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SUBSTITUTE SHEETS (RULE 26) the power fluid in liquid phases and below the boiling temperature at 1 bar). CFC fluid be cooled down to boiling temperature of PFC fluid in feedback pump operation in PFC. Fluid then enters evaporator (7) and expands as isentropic. Working fluid changes its' state from liquid to gas and further cooled down very below the ambient temperature (even below the boiling temperature of PFC fluid). Cold gas passes through heat exchanger (10) (in condenser (25)) thermally coupled with PFC fluid leaving the turbine gas warm up (but temperature still lower than ambient temperature) and pass through another heat exchanger (6) (thermally coupled with ambient). Gas temperature will approach to ambient temperature. While passing through heat exchanger (4) (thermally coupled with CFC for secondary heat rejection just after primary heat rejection to PFC) its' temperature approaches to operation temperature and enter back to compressor (1), so process cycle will restart.

Power fluid circuit (PFC): Circulation pump (8) in 4 sucks in the working fluid from heat exchanger (3) and pump to steam accumulator (5). Since the heat exchanger (3) & steam accumulator (5) is isobaric this suction yield heat exchanger sucks in working fluid from steam accumulator (5) and circulation goes on. Working fluid is heated in heat exchanger (3) since it is thermally coupled with CFC of 2 where cooling fluid temperature highest there (just after compression) as explained in process of CFC. Sucked hot fluid pour out in steam accumulator (5) fills first tray of surface extenders (9). Excess amount of fluid will spill down to next tray through overflow holes and so on. Total surface area of liquid contacting with vapor determines vaporization rate. Surface extenders contributes vaporization rate. Whenever the pressure in steam accumulator (5) drops down from vaporization pressure than of operation temperature, a flush will occur and working fluid evaporates to gain back the pressure.

As shown in Figure 1 and 2, the pressurized vapor enters into the turbine via solenoid valve (VI) and rotary joint (16) (which enables turbine rotor to rotate freely). Vapor (with pressure quite enough to create choked flow) penetrates to nozzle disk (11) and will be accelerated to transonic speed with convergent section (also lead laminar flow construction due to section length) and supersonic speed at divergent section (De Laval effect) of nozzle. Figures 3, 4 and 5 show a nozzle

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SU BSTITUTE SH EETS (RU LE 26) designed for maximum thrust. The nozzle geometry construction mainly depends on throat area and Mac values (flow speed) distribution. Since the nozzle is constructed from plate and thickness is uniform, only slit (= channel) width is considered. Every point on nozzle slit width must conform formula in prior art. Vapor exit creates a reaction force as quantified in prior arts force formula in opposite direction of rotation. Bending the slit for tangential exit for flow creates oblique surfaces against to supersonic flow. This creates a lifting force on oblique surface which is nearly tangential and in the direction of rotation (In case of annular type nozzle, which is also difficult to manufacture, we can't benefit from this situation). The lifting and reaction forces lead a momentum transfer from vapor to rotor body (free to rotate) which will rotate in counter direction of flow (This momentum transfer still retains some more momentum energy in flow at exit). Created torque on center, at exit equals to radius of disk times total of reaction and lifting forces. After leaving first rotor (= reaction rotor), flow meets with vortex-ring (24). The direction of flow is almost tangential to inner surface of vortex-ring (24) that causes a swirl for flow. This vortex creates skin friction drag effect (shear stress) on vortex-ring (24) that transfers more momentum to vortex-ring (24). Partial pressure at inner space of vortex-ring (24) creates an axial direction force on flow and constructs a helical pathway for flow in axial direction. Helical path elongates flow and cones stacks (21) interaction. After colliding to vortex-ring, Flow splits in opposite axial directions and enters between cone stacks (21) Again skin friction drag effect continues on inner and outer surfaces of cones (21). (Space between cones (21) provides enough for boundary layer formation. Cones axis aligned to turbine shaft (22) by support of generator coil disk (14) and second alignment disk (17)). Drag effect creates force on vortex structure (free to rotate) and cause momentum transfer from flow to vortex structure. Vortex structure becomes a second rotor (= vortex rotor) for turbine and rotates in counter direction of first rotor. Flow leaving cone stacks (21) still preserve angular momentum and vortex continues in condenser vessel (25). Flow meets with cooling bars (10) (thermally coupled with CFC where its' temperature in the lowest value just after expansion) with urchin like pins (27) which creates high Reynolds' numbers. The radial

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SUBSTITUTE SHEETS (RULE 26) laminar flow is now changed to radial again but micro turbulent flow which enhances vapor and cooling surface contact and contribute to condensation.

The vapor be cooled down, condensed and liquefied (Heat rejected into CFC). The liquid form of working fluid is accumulated in bottom of condenser vessel (25). Whenever the collected liquid reaches the predefined value, Control unit opens valve (V3). Liquid flows into feedback pump tank (28) (since the pressure in feedback pump tank (28) is less than condenser vessel (25)).

Whenever enough amounts of liquid collected in feedback pump tank (28), control unit closes valve (V3) and opens valve (V4). Pressurized vapor in steam accumulator (5) rush into feedback pump tank (28) through valve (V4) and feedback pump tank (28) be isobaric with steam accumulator (5). Control unit opens valve (V7) and closes valve (V2). A liquid flow path is constructed (where upstream and downstream equalized for circulation pump (8)).

Flow pass through heat exchanger (35) placed in tank (2) which is thermally coupled with CFC within the tank to cool CFC fluid. Then flow pass through heat exchanger (34) (thermally coupled with environment) and acquire some more energy from environment. Preheated fluid now enters heat exchanger (3) which is thermally coupled with CFC where it has highest temperature (just after compression having temperature above the operation temperature). Fluid heated up and forced into steam accumulator (5) with circulation pump (8).

Whenever feedback pump tank (28) emptied, control unit closes valves (V7 and V4) and opens valve (V2). The fluid circulation from steam accumulator (5) trough heat exchanger (3) will restart. Control unit now opens valve (V5). Hence pressure in feedback pump tank (28) is above than pressure in condenser vessel (25), trapped vapor in feedback pump tank (28) rushed into condenser vessel (25).

Control unit closes back valve (V5). Now small amount of vapor with operation temperature and isobaric with condenser vessel (25) is confined in feedback pump tank (28). The feedback pump tank (28) will start to cool. Cooling yield pressure drops in tank (28) to lower values than of condenser vessel (25). The feedback- pump (28) now ready for next cycle.

Generator:

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SUBSTITUTE SHEETS (RULE 26) Faraday's law on electromotive force on a coil by movement, defined as EMF = N—^— ¹ · Where N is number of turn on coil, B is magnetic field strength and A is coil inner area. If magnetic field B is constant, the area changed by time determines the produced voltage on coil. If we arrange the magnetic field construction on coil area as sum of two opposed fields (as shown in figure 2), resulting effective magnetic field value will be the difference of them since their polarities are reversed. If both field moving synchronically in same direction,

— value change is doubled. The magnetic field strength of leaving magnet from coil area reduced due to leaving and entering opposed magnetic field also neutralize the leaving magnetic field strength. The change in area depends on coil edge length and speed of movement. If the counter wrapped coils adjoined each other, and consecutive reverse polarities magnet train travels synchronously over them (as shown in figure 3), we can create voltage on coils terminals. The magnetic field will be enhanced and more voltage created if we can synchronize another magnet train with reverse polarities to first one, located behind other side of coils.

Radial implementations of this structure requires paramagnetic core to create closed circuit magnetic field. This approach yields considerable amount of energy loss due to hysteresis. We can overcome this with applying magnetic field in axial direction. There will be no need for paramagnetic core and no alteration in magnetic field directions that resulting no hysteresis loss.

To adapt this into a rotational structure in axial manner, we made trapezoidal shaped coils (30) and adjoin them to build a coil disk (14) with ball bearing (23) at center. Number of coils must be even and defines generator pole counts. The thickness of disk must not be too much since it will determines magnetic field circuit air gap (twice of ball bearing thickness; approximately 2 x 8.0mm, 16.0mm. The coil disk will contribute to aforementioned vortex structure cones axial alignment and it must be absolutely perpendicular to axis.). Coil terminals must be connected to other coils terminal in serial or parallel manner to achieve desired voltage. The desired voltage must not be below the voltage needed to charge electric battery (28) used in CFC (15 Volt recommended). Only two terminals for coil-disk will be enough.

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SUBSTITUTE SHEETS (RULE 26) Aforesaid first magnet train will be implement as electro/permanent magnets fastened on turbine primary rotor's ferromagnetic flanges (12) in the circumferential direction and polarities be in opposite with adjacent one. Number of magnets must be equal to number of aforesaid coils. Another set of electro/permanent magnets fastened on a ferromagnetic flange (15) in same manner to build aforesaid second magnet train. Flange (15) fastened to turbine shaft (22) such that magnet polarities are reverse with rotor flange magnets to form axial magnetic field circuits. This structure also creates a magnetic coupling between rotor flange (12) and said flange (15) yields a synchronous spinning for both of them. The magnets width must not be larger than coil inner width as shown in figure 4. Aforesaid coil disk be placed between flanges as shown in figure 5. Since Coil disk fastened to turbine secondary rotor (vortex structure) and magnets fastened to turbine first rotor (which spins counter direction with secondary rotor), Coil disk spins relative to magnetic field in a speed as sum of rotational speeds of turbine primary and secondary rotors. The produced voltage on terminals of coils is A.C. type with frequency generator pole counts times relative spin speed.

A commutator structure developed to convert produced A.C. current into D.C. type. As noticed; the magnetic field change rate will be zero whenever magnet completely enclosed within coil inner area eventually the produced voltage be zero. Generated voltage polarities changed every 360°/pole-count relative angular displacement. Number of pole count conductors (31) fastened on aforesaid vortex cones axis alignment support disk (17) in the circumferential direction. The space between conductors must be equal to width of carbon-brush width to disallow contact of brush and said conductors at zero voltage generation time. The conductors short circuited to conductors next to adjacent one to form two conductors set. Coil disk terminals electrically connected to this conductor sets.

A brush assembly (18) holds a pair of carbon-brush in axial direction with angle as multiple of 360°/pole-count between them fastened on turbine shaft that allows each brush contact to other aforesaid conductors group. This assembly synchronously rotates with turbine first rotor. In each 360°/pole-count relative angular displacement brush alters conductor set. Brushes connected to two slip- rings (32) to allow communication of two other carbon-brushes fixed on none spinning frame. The produced voltage is commutated and become D.C. type

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SUBSTITUTE SHEETS (RULE 26) voltage on carbon-brushes. If we preferred electromagnet in magnet assembly this conversion provides D.C. voltage source for said electromagnets within the rotational structure.

With said commutator structure generator became a D.C. type engine with no hysteresis loss (since there is no polarity altered ferromagnetic core in magnetic field circuit). This design may be utilized in other application other than Tezgel CCP. The commutator structure maybe omitted and produced A.C. type voltage used directly (a semiconductor diode bridge may be used for D.C. type voltage demands to charge electric battery (28) used in CFC). Created A.C. type voltage will have higher frequency may be good to consume in induction type heater at electric consumption point. A semiconductor inverter may be used to convert produced voltage in compatible domestic voltage and frequency values to consume produced electricity in household units or connect to interconnected electric grid.

Control unit: Control unit (called as CU) utilize information gathered from temperature, pressure and level sensors (which are not shown in diagram) mounted in condenser vessel (25), steam accumulator (5), feedback pump tank (28) and voltage sensor connected to generator terminals. CU compares gathered values against preset range table values and generates open/close signals to solenoid valves VI through V8 to regulate flow for the best remedy to situation. CU also keeps system states and states of said valves. (The initial states of valves VI, V2, V6 are Open and V3, V4, V5, V7, V8 are Closed). Monitored events and remedy procedures done by CU explained as:

1. The pressure in steam accumulator (5) below the operation value.

Too much vapor consumed in turbine yields temperature drop, than pressure drop in steam accumulator or CFC hasn't inserted enough heat to PFC yet (at startup). Be sure energy insertion from ambient enabled.

Procedures: HeatUp, Passive_Turbine.

2. The pressure in steam accumulator (5) above the operation value.

CFC inserting too much heat to PFC. Prevent energy insertion from ambient and try to cool down condenser.

Procedures: CoolDown, Active_Turbine, Feedback.

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SUBSTITUTE SHEETS (RULE 26) 3. The temperature in condenser vessel (25) is above the boiling point of PFC fluid.

Too much vapor consumed in turbine or condenser (25) not cooled yet.

Procedures: CoolDown, Passive_Turbine.

4. Level of liquid accumulated in feedback tank (28) is high (enough).

Procedures: Feedback

Reference List:

1. Compressor 21. Cones

2. Refrigerator storage Tank 30 22. Turbine shaft

3. 4. Heat exchangers couples CFC 23. ball bearings

& PFC 24. Vortex ring

5. Steam accumulator 25. Condensation tank

6. Radiator Main energy inlet to 26. Cooling conduits in Cooling system from ambient to CFC 35 bars (10)

7. Evaporator 27. Cooling pins on Cooling bars

8. Circulation pump (10)

9. Surface extenders 28. Feedback storage tank

10. Cooling bars cools & condense 29. Electric accumulator

PFC vapor after turbine exit 40 30. Electric coil

11. Nozzle disk 31. Conductor

12, 15 Ferromagnetic flanges 32. O-Rings

13. Magnets 33. Safety valve

14. Coil disks 34. Radiator secondary energy inlet

16. Rotary Join 45 to system from ambient to PFC

17. Axial alignment support disks 35. Heat exchanger

18. Brush holder 36. Nozzle disk cover

19. Slip rings 37. Nozzle

20. Carbon brushes V1-V8 solenoid valves

17

SUBSTITUTE SHEETS (RULE 26)