The present disclosure relates to the use of compressed fluid, such as atmospheric air, oil or various other liquids or gases, in the generation of electrical energy. More particularly, the present disclosure relates to a system or apparatus, in which the compressed fluid is circulated through a turbine to generate electrical energy with high efficiency.

Systems or apparatus of the present disclosure may be suitable for application in any system consuming electricity, but more particularly applications including automotive vehicles, commercial vehicles (such as trucks and busses), vehicles commonly used for public transport (such as trains, metro rail and trams).

Background

A problem associated with comparable systems which exhaust compressed fluid after circulating it through a turbine may be that the momentum of the exhausted fluid is lost and not utilised in the generation of electrical energy.

With rising costs of fuel and increasing social pressure to move away from fossil fuels and towards a greater dependence on renewable sources of energy, there is a desire to develop ever more efficient engines or renewable energy alternatives.

A problem associated with known renewable sources of electricity generation is the mismatch between the rate of generation and the rate of demand. Solar energy, for example, can only be produced during the day and peaks in the middle of the day whilst peak demand on the UK national grid is usually in the evening. Therefore, there exists a need for storage of electrical energy produced from solar, wind and other renewable sources that cannot be easily tempered with fluctuating demand.

When it comes to addressing these above-mentioned problems in the development of automotive vehicles there are several problems with existing solutions. Existing reciprocating engines used in hydrocarbon-fuel -powdered automotive vehicles suffer from low ⁷ efficiency and are therefore costly in fuel and are often dependent on fossil fuels entirely. Equally, lithium - ion-battery-powered vehicles and hydrogen-fuel-cell-powered vehicles have a low fuel density and therefore need to cany' around more fuel for a given range which reduces energy efficiency in transporting the extra weight. Further, lithium-ion batteries suffer from a long refuel /recharge time.

Summary

According to a first aspect of the invention there is provided an apparatus for generating electrical energy comprising fluid circulating apparatus, suitable for circulating pressurised fluid, comprising a closed-loop pipeline arranged to connect the components of fluid circulating apparatus in series; the components of the fluid circulating apparatus comprising a fluid propulsion means comprising a fluid intake and a fluid output; a plurality of turbines connected in series by the closed-loop pipeline, the plurality of turbines comprising at least a first turbine and a last turbine, wherein the first turbine comprises a turbine intake and the last turbine comprises a turbine output; a cooling means, for cooling the pressurised fluid, comprising a cooling intake and a cooling output, wherein the turbine output is connected to the cooling intake by the closed-loop pipeline; wherein the fluid output of the fluid propulsion means is connected to the turbine intake by the closed-loop pipeline; wherein the cooling output is connected to the fluid intake of the fluid propulsion means by the closed-loop pipeline; the apparatus for generating electrical energy further comprising a reserve tank arranged to supply reserve fluid to the fluid circulating apparatus; a pressure tank for providing an initial fluid flow to overcome a start-up inertia of the plurality of turbines, the pressure tank comprising a compressor to maintain a predetermined pressure in the pressure tank; at least one alternator mechanically connected to each of the plurality of turbines such that rotation of the turbine provides rotation to the alternator which in turn generates electrical energy.

Preferably, the pressure tank is further suitable for maintaining an energy efficiency of the fluid propulsion means by eliminating inrush currents.

Optionally, the fluid may be air, the closed-loop pipeline may be 10mm in diameter, and the fluid may be pressurised to 30 bar.

Optionally, the fluid propulsion means and the plurality of turbines may be arranged in line with the closed-loop pipeline. The plurality of turbines may optionally comprise at least three turbines and the at least one alternator mechanically connected to the last turbine may optionally have a lower power rating than the at least one alternator mechanically connected to the first turbine. An advantage of these features may be that the momentum of the exhaust fluid from all but the last turbine may be captured by a subsequent turbine in the plurality of turbines connected in series. This may be particularly advantageous when the at least one alternator mechanically connected to the last turbine may optionally have a lower power rating than the at least one alternator mechanically connected to the first turbine because the momentum of the fluid may decrease after passing through each turbine due to calculated mechanical loss within the minimum and maximum rotation per minute (rpm) values of the alternators.

Optionally, the at least one alternator may comprise two identical alternators. An advantage of this feature may be the provision of more efficient direct current (DC) generation, for example when charging a battery or other DC powered component or appliance.

Optionally, the fluid propulsion means may comprise a turbofan and/or an inline compressor.

Optionally, the cooling means may comprise any of: a fluid discharge valve, a cooling radiator, a surface cooler.

Optionally, the closed-loop pipeline may be enclosed with a second security pipeline. The apparatus for generating electrical energy may, optionally, further comprise at least one security component. The at least one security component may comprise any of: a motorised pressure relief valve and/or a mechanical pressure relief valve.

Optionally, the apparatus for generating electrical energy may further comprise an automation system. The automation system may comprise any of: control valves, check valves, sensors, temperature sensors, pressure sensors, flow sensors, control means and/or means for logging measurements. Optionally, the reserve tank may have a lower pressure than the fluid circulating apparatus and the pressure tank, the reserve tank and the fluid circulating apparatus may all be connected to one another. The apparatus for generating electrical energy may further comprise one, two or three additional pressurised tanks and the tanks may be connected to one another and to the fluid circulating apparatus such that they maintain a continuous flow through the tanks and the fluid circulating apparatus.

Optionally, the reserve tank may comprise at least one section of pipe which together substantially form an oval shape.

According to a second aspect of the present invention there is provided an electrical power generator comprising a closed-loop turbine comprising a turbofan, a pressurised tank, a reserve tank and a series of turbines.

According to a third aspect of the present invention there is provided an apparatus for generating electrical energy comprising fluid circulating apparatus, suitable for circulating pressurised fluid, comprising a closed-loop pipeline arranged to connect the components of fluid circulating apparatus in series; the components of the fluid circulating apparatus comprising a fluid propulsion means comprising a fluid intake and a fluid output; a plurality of turbines connected in series by the closed-loop pipeline, the plurality of turbines comprising at least a first turbine and a last turbine, wherein the first turbine comprises a turbine intake and the last turbine comprises a turbine output; a cooling means, for cooling the pressurised fluid, comprising a cooling intake and a cooling output, wherein the turbine output is connected to the fluid intake of the fluid propulsion means by the closed-loop pipeline; the apparatus for generating electrical energy further comprising a reserve tank arranged to supply reserve fluid to the fluid circulating apparatus; a pressure tank for providing an initial fluid flow to overcome a start-up inertia of the plurality of turbines and maintaining an energy efficiency of the fluid propulsion means by eliminating inrush currents, the pressure tank comprising a compressor to maintain a predetermined pressure in the pressure tank; at least one alternator mechanically connected to each of the plurality of turbines such that rotation of the turbine provides rotation to the alternator which in turn generates electrical energy. Optionally, the fluid may be air and the closed-loop pipeline may, preferably, be ½ inch (12.7mm) in diameter (but not limited thereto), and the fluid may be pressurised to 40 bar (4000 kPa) or more.

Optionally, the fluid propulsion means and the plurality of turbines may be arranged in line with the closed-loop pipeline. The plurality of turbines may optionally comprise at least three turbines and the at least two alternators mechanically connected to the last turbine may optionally have a lower power rating than the at least two alternators mechanically connected to the first turbine. An advantage of these features may be that the momentum of the exhaust fluid from all but the last turbine may be captured by a subsequent turbine in the plurality of turbines connected in series. This may be particularly advantageous when the at least two alternators mechanically connected to the last turbine may optionally have a lower power rating than the at least two alternators mechanically connected to the first turbine because the momentum of the fluid may decrease after passing through each turbine due to calculated mechanical loss within the minimum and maximum rotation per minute (rpm) values of the alternators.

Optionally, the at least two alternators may comprise two identical alternators. An advantage of this feature may be the provision of more efficient direct current (DC) generation, for example when charging a battery or other DC powered component or appliance.

The fluid propulsion means may comprise a hydraulics supplied “TurboPiston” (Variable Voluminous High Pressure Tube Pump) and/or an inline compressor.

Optionally, the cooling means may comprise any of: a fluid discharge valve, a cooling radiator, a surface cooler.

Optionally, the closed-loop pipeline may be enclosed with a second security pipeline. The apparatus for generating electrical energy may, optionally, further comprise at least one security component. The at least one security component may comprise any of: a motorised pressure relief valve and/or a mechanical pressure relief valve. Optionally, the apparatus for generating electrical energy may further comprise an automation system. The automation system may comprise any of: control valves, check valves, sensors, temperature sensors, pressure sensors, flow sensors, control means and/or means for logging measurements.

Optionally, the reserve tank may have a lower pressure than the fluid circulating apparatus and the pressure tank, the reserve tank and the fluid circulating apparatus may all be connected to one another. The apparatus for generating electrical energy may further comprise one, two or three additional pressurised tanks and the tanks may be connected to one another and to the fluid circulating apparatus such that they maintain a continuous flow through the tanks and the fluid circulating apparatus.

Optionally, the reserve tank may comprise at least one section of pipe which together substantially form an oval shape.

According to a fourth aspect of the present invention there is provided an electrical power generator comprising a closed-loop turbine comprising a hydraulics supplied “TurboPiston” (Variable Voluminous High Pressure Tube Pump), a pressurised tank, a reserve tank and a series of turbines.

In the context of the present disclosure, the concept of electricity generation includes the process of generating electrical energy from other forms of energy and the concept of alternator power rating includes the power range at which the alternator performs at its peak safety and efficiency.

Brief Description of the Drawings

Embodiments of the disclosure will now be described, by way of example only, and with reference to the drawings in which:

Figures 1 schematically illustrates a plan view of an apparatus according to a first embodiment of the present disclosure; Figure 2 schematically illustrates a plan view of an apparatus according to a second embodiment of the present disclosure;

Figure 3 schematically illustrates a cross-section of a turbine and turbine housing of the first and second embodiments of the present disclosure;

Figures 4a and 4b schematically illustrate cross-sections depicting first and second positions, respectively, of the turbine of the first and second embodiments of the present disclosure; Figure 5 schematically illustrates an enlarged plan view of the apparatus according to the first embodiment of the present disclosure;

Figure 6 illustrates a perspective view of the apparatus according to the first embodiment of the present disclosure;

Figure 7 illustrates a perspective view of the turbine housing of the first and second embodiments of the present disclosure;

Figure 8 illustrates an enlarged plan view of the apparatus according to the first embodiment of the present disclosure;

Figures 9a and 9b schematically illustrate a side view and a plan view, respectively, of the turbine housing of the first and second embodiments of the present disclosure.

Figure 10 schematically illustrates a plan view of an apparatus according to an embodiment of the present disclosure;

Figure 11 schematically illustrates a cross-section of a turbine and turbine housing of the embodiments of the present disclosure;

Figures 12a and 12b schematically illustrate cross-sections depicting first and second positions, respectively, of the turbine of the embodiments of the present disclosure;

Figure 13 illustrates a perspective view of the apparatus according to an embodiment of the present disclosure;

Figure 14 illustrates a perspective view of the turbine housing of the embodiments of the present disclosure;

Figure 15 illustrates an enlarged plan view of the apparatus according to an embodiment of the present disclosure;

Figures 16a and 16b schematically illustrate a side view and a cross-section view, respectively, of the turbine housing of an embodiment of the present disclosure;

Figures 17a and 17b illustrate a cross-section view and a side view, respectively, of the TurboPiston of an embodiment of the present disclosure; Figures 18a and 18b illustrate perspective views of the TurboPiston of an embodiment of the present disclosure;

Figure 19 schematically illustrates a piston of an embodiment of the present disclosure in which the shaft of the piston is vertical;

Figure 20 illustrates a telescopic piston of an embodiment of the present disclosure in a retracted position;

Figure 21 illustrates the telescopic piston of an embodiment of the present disclosure in an extended position;

Figure 22 illustrates the hydraulics supplied to piston of an embodiment of the present disclosure;

Figure 23 schematically illustrates a plan view of an apparatus during a first half cycle according to an embodiment of the present disclosure;

Figure 24 schematically illustrates a plan view of an apparatus during a second half cycle according to an embodiment of the present disclosure;

Figure 25 schematically illustrates an enlarged plan view of a pneumatic/hydraulic cylinder arrangement according to an embodiment of the present disclosure;

Figure 26 schematically illustrates a plan view of an apparatus according to an embodiment of the present disclosure;

Figure 27 schematically illustrates a cross-section view of an air accelerator according to an embodiment of the present disclosure.

Detailed Description

Figures 1, 5 and 6 show a first embodiment of the present disclosure in which an apparatus 101 for generating electrical energy comprises a fluid circulating apparatus which is suitable for circulating pressurised fluid. The fluid circulating apparatus comprises a closed-loop pipeline 102 which connects together the other components of the fluid circulating apparatus in series such that the fluid can flow 170 to, from and through each of the components.

The further components of the fluid circulating apparatus comprise a turbofan (or compressor) 110, a first turbine 103, a second turbine 104, a third turbine 105 and a cooling radiator 114 all arranged in series and looping back round to the turbofan 110 and all connected in order by the close-loop pipeline 102. Such a closed-loop pipeline 102 may have a diameter of 10mm.

The fluid circulating apparatus may also include a number of security components and/or components of a system for providing automation. In the first embodiment these may include a valved pipeline release 125 which may also include a nozzle with a silencer 126 for discharging fluid in the event, for example, that operation pressure limits are exceeded. Such a valved pipeline release 125 may be located immediately after the third turbine 105 on the closed-loop pipeline 102.

Further security components may include a closed-loop pipeline check valve 121 for preventing back flow of the circulating fluid. Such a closed-loop pipeline check valve 121 may be located between the turbofan 110 and the first turbine 103 on the closed-loop pipeline 102. The fluid circulating apparatus may also include a mechanical pressure relief valve 123 to discharge fluid in case the operation pressure limited are exceeded.

With particular reference to Figure 5, a further security component may include a valved bypass 119 of the turbofan 110 which may comprise a bypass valve 160. The valved bypass 119 may be opened if the pressure of the fluid leaving the turbofan is above operational or otherwise predefined limits. This may be done in addition to or instead of decreasing the driving frequency of the turbofan 110. Such a valve bypass 119 may include a pipeline with a diameter of 10mm.

Flow of the fluid through the closed-loop pipeline 102 and therefore through the fluid circulating apparatus may be controlled by a pipeline flow valve 124. Such a pipeline flow valve 124 may be located between the mechanical pressure relief valve 123 and the first turbine 103.

Fluid may be circulated around the fluid circulating apparatus by the turbofan 110 and power may be supplied to the turbines 103, 104, 105 by passage of the fluid through them. The turbines 103, 104, 105 may be airtight (for example when the circulating fluid is air) and may comprise airtight bearings. The turbines 103, 104, 105 and the turbofan 110 may be connected in line with the 10mm closed-loop pipeline 102. Each of the first, second and third turbines 103, 104, 105 may include a first, second and third pair of alternators 107, 108, 109, respectively, mechanically connected to the respective turbines 103, 104, 105 such that rotation of the turbines 103, 104, 105 provides rotation to the alternators 107, 108, 109 which in turn generates electrical energy. The turbines 103, 104, 105 are rotated by the circulation of fluid through them. Each pair of alternators 107, 108, 109 may be identical to one another and may be connected to the same shaft 307.

The apparatus for generating electrical energy 101 further comprises a reserve tank 106 arranged to supply reserve fluid to the fluid circulating apparatus and connected to the closed- loop pipeline 102 by a first reserve tank/loop pipeline valved connection 118 and a second reserve tank/loop pipeline valved connection 122. The first reserve tank/loop pipeline valved connection 118 also comprises a reserve tank/loop pipeline check valve 117 which only permits the flow of fluid from the reserve tank 106 to the close-loop pipeline 102.

The reserve tank 106 may have a lower pressure than the closed-loop pipeline 102 and the first reserve tank/loop pipeline valved connection 118 is provided to supply reserve fluid from the reserve tank 106 to the closed-loop pipeline 102.

The second reserve tank/loop pipeline valved connection 122 is provided to allow excess fluid within the closed-loop pipeline 102 to escape the closed-loop pipeline in the event that a maximum fluid volume, temperature and/or pressure is reached without expelling the fluid from the apparatus 101 entirely.

The apparatus for generating electrical energy 101 further comprises a pressure tank 111 for providing an initial fluid flow to overcome a start-up inertia of the turbines 103, 104, 105 and for maintaining an energy efficiency of the turbofan and/or inline compressor by eliminating inrush currents. The pressure tank 111 comprises a compressor 112 to maintain a predetermined pressure in the pressure tank 111.

The pressure tank 111 may be connected to the closed-loop pipeline 102 by a pressure tank/loop pipeline valved connection 115 and connected to the reserve tank 106 by a pressure tank/reserve tank valved connection 116. By means of these valved connections 115, 116 fluid may be provided to the closed-loop pipeline 102 and the reserve tank 106 in the event that they become depleted.

In addition to the cooling radiator 114, there may also be provided a surface cooler 113 located on the surface of the closed-loop pipeline 102. The surface cooler 113 may be located on the section of closed-loop pipeline 102 between the cooling radiator and the turbofan. The fluid may also be cooled by being discharged from the apparatus 101 by opening the valved pipeline release 125 or to the reserve tank 106 by opening the second reserve tank/loop pipeline valved connection 122. In embodiments in which the fluid is air (or other gas) any condensation in the closed-loop pipe 102 line may also be discharged with, for example, an air water separator filter pneumatic regulator.

As a further security measure, the close-loop pipeline 102 may be enclosed with a second security pipeline (not shown).

The apparatus for generating electrical energy 101 may further comprises an automation system. Such a system may comprise any of control valves, check valves, sensors, temperature sensors, pressure sensors, flow sensors, control means and/or means for logging measurements. Such a system may be configured to carry out a variety of operation programmes or scenarios automatically with minimal human intervention. For example, a control means may electronically operate any of the above-mentioned valved connections by means of motorised valves.

During operation of the first embodiment, the pressure tank/loop pipeline valved connection 115 and the valved pipeline release 125 may be opened and the pressurised fluid from the pressure tank 111 generates high fluid speed through the turbines 103, 104, 105. Once the turbines 103, 104, 105 reaches a predetermine speed, the turbofan (or compressor) 110 is started and the pressure tank/loop pipeline valved connection 115 and the valved pipeline release 125 are closed. An aim of supplying pressurised air from the pressure tank 111 or the reserve tank 106 to the turbofan (or compressor) 110 may be to maintain an energy efficiency when compared with working with 1 standard atmosphere (atm). If the reserve tank 106 pressure is below a predetermined value, the pressure tank/reserve tank valved connection 116 can be opened to increase the pressure in the reserve tank 106. If the pressure in the closed-loop pipeline 102 rises above a predetermined valve, the mechanical pressure relief valve 123 opens for safety and security purposes. If the pressure in the closed- loop pipeline 102 falls below a predetermined value, the pressure tank/loop pipeline valved connection 115 may be opened and may be closed if the pressure in the closed-loop pipeline 102 rises above a predetermined value. The turbofan (or compressor) 110 may be supplied with additional fluid from the reserve tank 106 via the first reserve tank/loop pipeline valved connection 118.

In relation to exemplary pressures of the first embodiment, the preferable pressure for the pressure tank 111 may be 200 bar. A preferable pressure for the reserve tank may be 20 bar and a preferable pressure for the close-loop pipeline may be 30 bar. Further, a preferable diameter for the reserve tank may be 250 mm and the reserve tank may be a section or sections of pipeline.

Referring now to the second embodiment of the present disclosure shown in Figure 2. As will be apparent form the Figures, the apparatus 201 of the second embodiment shares some features in common with the apparatus 101 of the first embodiment. As with the apparatus 101 of the first embodiment, the apparatus 201 of the second embodiment is an apparatus for generating electrical energy and comprises a fluid circulating apparatus which is suitable for circulating pressurised fluid. The fluid circulating apparatus comprises a closed-loop pipeline 202 which connects together the other components of the fluid circulating apparatus in series such that the fluid can flow 270 to, from and through each of the components.

The further components of the fluid circulating apparatus comprise a first turbine 203, a second turbine 204, a third turbine 205 all arranged in series. As in the first embodiment each turbine 203, 204, 205 is mechanically connected to a pair of alternators 207, 208, 209.

The apparatus 202 may also include a valved pipeline release 225 which may also include a nozzle with a silencer 226 for discharging fluid as in the first embodiment. Flow of the fluid through the closed-loop pipeline 202 and therefore through the fluid circulating apparatus may be controlled by a pipeline flow valve 224.

However, the apparatus 202 of the second embodiment differs in that the fluid propulsion means comprises a series of pressurised tanks which are arranged and configured to circulate pressurised fluid through the turbines 203, 204, 205.

The apparatus 202 shown in Figure 2 comprises a first fluid tank 211, a second fluid tank 230, a third fluid tank 231, a fourth fluid tank 232 and a fifth fluid tank 233.

These series of fluid tanks 211, 230, 231, 232, 233 have a variety of different pressures and are connected to each other via motorised-valve connections with a variety of different combinations to maintain a continuous flow between them and the closed-loop pipeline 202.

Each of the fluid tanks 211, 230, 231, 232, 233 comprises a respective pressure sensor 260, 261, 262, 263, 264 which in combination with time programmes and/or other automatic control may be used to supply pressurised fluid flow through the turbines 203, 204, 205 and thereby generate electrical energy.

Such automatic control may ensure than no two fluid tanks 211, 230, 231, 232, 233 are balanced in pressure.

The first fluid tank may comprise a compressor 212 to keep the pressure tank 211 pressurised. The fluid tanks 211, 230, 231, 232, 233 may have a maximum pressure of 500 bar.

An example of the motorised-valve connections between the fluid tanks 211, 230, 231, 232, 233 is shown in Figure 2 and includes a first first tank/fourth tank valved connection 234, a first first tank/third tank valved connection 235, a second first tank/fourth tank valved connection 236, a first tank/second air tank valved connection 237, a second first tank/third tank valved connection 238, a second tank/fourth tank valved connection 239, a second tank/third tank valved connection 240, a second tank/fifth tank valved connection 241, a first third tank/fifth tank valved connection 242, a third tank/fourth tank valved connection 243, a second third tank/fifth tank valved connection 244 and a fourth tank/fifth tank valved connection 245. Each valved connection may comprise a respective valve 271, 272, 275, 276, 277, 278, 279, 280 which may be located adjacent one of the fluid tanks 211, 230, 231, 232, 233. At least one of the fluid tanks 211, 230, 231, 232, 233 may further comprise pressure release valves 273, 274.

To enable measurement of pressure, flow and temperature in the closed-loop pipeline 202, a flow sensor 252 and a temperature sensor 251 are located on the closed-loop pipeline 202 and may be located between the fifth fluid tank 233 and the first turbine 203. Pressure sensors 250 are also provided on the closed-loop pipeline 202 and may be located either side of the turbines 203, 204, 205.

Referring now to Figures 3, 4a, 4b, 7, 8, 9a and 9b, Figure 3 shows a cross-section of a turbine 301 as implemented in the above-mentioned embodiments. As can be seen from Figure 3, the turbine 301 comprises a turbine housing 302 which comprises a turbine inlet 303 and a turbine outlet 304. Within the turbine housing 302, turbine fluid chambers 306 are separated by turbine winglets 305.

As can be seen from Figures 4a and 4b, the turbine inlet 303 and the turbine outlet 304 are inline such that as fluid passes through the turbine it first impacts a turbine winglet 305 and the momentum of the fluid drives the winglet 305 from a first position shown in Figure 4a to a second position shown in Figure 4b. In the first position the turbine winglet 305 is located towards the turbine inlet 303 but the flow of the fluid drives the turbine winglet 305 towards the turbine outlet 304.

In the first position, the turbine fluid chamber 306 is filled with fluid entering the turbine 301 through the turbine inlet 303. In the second position, the fluid in the turbine fluid chamber 306 is released out of the turbine 301 through the turbine outlet 304.

This sequence is repeated continuously through the operation of the apparatus 101, 201 and thereby rotates the turbine 301.

The turbine 301 may be further powered by a pressure difference between the fluid at the turbine inlet 303 and the fluid at the turbine outlet 304, namely a higher pressure at the turbine inlet 303 than at the turbine outlet 304. Figure 7 shows a perspective view of an illustration of the turbine 301 and shows a shaft 307 protruding from the turbine housing 302 for mechanical attachment to a pair of alternators 308. The turbine housing 302 may comprise metal.

The arrangement of the turbine 301 with the alternator pair 308 can be seen in the side view of Figure 9a and the plan view of Figure 9b.

An enlarged view of the first embodiment is shown in Figure 8 and shows a plan view of the arrangement of the three turbines 103, 104, 105 of the first embodiment.

Alternative Embodiments

Figures 1 to 7b show a first embodiment of the present disclosure in which an apparatus 101 for generating electrical energy comprises a fluid circulating apparatus which is suitable for circulating pressurised fluid. The fluid circulating apparatus comprises a closed-loop pipeline

102, which connects together the other components of the fluid circulating apparatus in series such that the fluid can flow to, from and through each of the components.

Further components of the fluid circulating apparatus comprise a first turbine 103, a second turbine 104 and a third turbine 105 all arranged in series and all connected in order by the closeloop pipeline 102 which further loops around to connect the third turbine 105 to the first turbine

103. A hydraulically actuated "TurboPiston" (Variable Volume High Pressure Tubing Pump) 110 is connected to the closed-loop pipeline 102 to pressurize air in the closed-loop pipeline 102. Such a closed-loop pipeline 102 may have a diameter of ½ inch (preferably but not limited thereto).

The fluid circulating apparatus may also include a number of security components and/or components of a system for providing automation. These may include a valved pipeline release 125 which may also include a nozzle with a silencer 126 for discharging fluid in the event, for example, that operation pressure limits are exceeded. Such a valved pipeline release 125 may be located immediately after the third turbine 105 on the closed-loop pipeline 102. Further security components may include a closed-loop pipeline check valve (not shown) for preventing back flow of the circulating fluid. Such a closed-loop pipeline check valve (not shown) may be located between the hydraulics supplied “TurboPiston” (Variable Voluminous High Pressure Tube Pump) 110 and the first turbine 103 on the closed-loop pipeline 102. The fluid circulating apparatus may also include a mechanical pressure relief valve (not shown) to discharge fluid in case the operation pressure limited are exceeded.

A further security component may include a valved bypass (not shown) of the hydraulics supplied “TurboPiston” (Variable Voluminous High Pressure Tube Pump) 110. The valved bypass (not shown) may be opened if the pressure of the fluid leaving the TurboPiston 110 is above operational or otherwise predefined limits. This may be done in addition to or instead of decreasing the driving frequency of the hydraulics supplied “TurboPiston” (Variable Voluminous High Pressure Tube Pump) 110. Such a valve bypass (not shown) may include a pipeline with a diameter of E> inch.

Flow of the fluid through the closed-loop pipeline 102 and therefore through the fluid circulating apparatus may be controlled by a pipeline flow valve (not shown). Such a pipeline flow valve (not shown) may be located between the mechanical pressure relief valve (not shown) and the first turbine 103.

Fluid may be circulated around the fluid circulating apparatus by the turbofan 110 and power may be supplied to the turbines 103, 104, 105 by passage of the fluid through them. The turbines 103, 104, 105 may be airtight (for example when the circulating fluid is air) and may comprise airtight bearings. The turbines 103, 104, 105 and the hydraulics supplied “TurboPiston” (Variable Voluminous High Pressure Tube Pump) 110 may be connected in line with the ½ inch closed-loop pipeline 102.

Each of the first, second and third turbines 103, 104, 105 may include a first, second and third pair of alternators 107, 108, 109, respectively, mechanically connected to the respective turbines 103, 104, 105 such that rotation of the turbines 103, 104, 105 provides rotation to the alternators 107, 108, 109 which in turn generates electrical energy. The turbines 103, 104, 105 are rotated by the circulation of fluid through them. Each pair of alternators 107, 108, 109 may be identical to one another and may be connected to the same inside shaft (not shown).

The apparatus for generating electrical energy 101 further comprises a reserve tank 111 arranged to supply reserve fluid to the fluid circulating apparatus and connected to the closed- loop pipeline 102 by a first reserve tank/loop pipeline valved connection (not shown) and a second reserve tank/loop pipeline valved connection (not shown). The first reserve tank/loop pipeline valved connection (not shown) also comprises a reserve tank/loop pipeline check valve (not shown) which only permits the flow of fluid from the reserve tank 111 to the close-loop pipeline 102.

The reserve tank 111 may have a lower pressure than the closed-loop pipeline 102 and the first reserve tank/loop pipeline valved connection (not shown) is provided to supply reserve fluid from the reserve tank 111 to the closed-loop pipeline 102.

The second reserve tank/loop pipeline valved connection (not shown) is provided to allow excess fluid within the closed-loop pipeline 102 to escape the closed-loop pipeline in the event that a maximum fluid volume, temperature and/or pressure is reached without expelling the fluid from the apparatus 101 entirely.

The apparatus for generating electrical energy 101 further comprises a pressure tank 111 for providing an initial fluid flow to overcome a start-up inertia of the turbines 103, 104, 105 and for maintaining an energy efficiency of the hydraulics supplied “TurboPiston” (Variable Voluminous High Pressure Tube Pump), and/or inline compressor by eliminating inrush currents. The pressure tank 111 comprises a compressor (not shown) to maintain a predetermined pressure in the pressure tank 111.

The pressure tank 111 may be connected to the closed-loop pipeline 102 by a pressure tank/loop pipeline valved connection (not shown) and connected to the reserve tank 111 by a pressure tank/reserve tank valved connection (not shown). By means of these valved connections, fluid may be provided to the closed-loop pipeline 102 and the reserve tank 111 in the event that they become depleted. In addition to a cooling radiator (not shown), there may also be provided a surface cooler (not shown) located on the surface of the closed-loop pipeline 102. In embodiments in which the fluid is air (or other gas) any condensation in the closed-loop pipe 102 line may also be discharged with, for example, an air water separator filter pneumatic regulator.

As a further security measure, the close-loop pipeline 102 may be enclosed with a second security pipeline (not shown).

The apparatus for generating electrical energy 101 may further comprises an automation system. Such a system may comprise any of: control valves, check valves, sensors, temperature sensors, pressure sensors, flow sensors, control means and/or means for logging measurements.

Such a system may be configured to carry out a variety of operation programmes or scenarios automatically with minimal human intervention. For example, a control means may electronically operate any of the above-mentioned valved connections by means of motorised valves.

During operation of the present embodiment, the pressure tank/loop pipeline valved connection (not shown) and the valved pipeline release (not shown) may be opened and the pressurised fluid from the pressure tank 111 generates high fluid speed through the turbines 103, 104, 105. Once the turbines 103, 104, 105 reach a predetermine speed, the hydraulics supplied “TurboPiston” (Variable Voluminous High Pressure Tube Pump) (or compressor) 110 is started and the pressure tank/loop pipeline valved connection (not shown) and the valved pipeline release (not shown) are closed. An aim of supplying pressurised air from the pressure tank (not shown) or the reserve tank 111 to the hydraulics supplied “TurboPiston” (Variable Voluminous High Pressure Tube Pump) 110 may be to maintain an energy efficiency when compared with working with 1 standard atmosphere (atm).

If the reserve tank 111 pressure is below a predetermined value, the pressure tank/reserve tank valved connection (not shown) can be opened to increase the pressure in the reserve tank 111. If the pressure in the closed-loop pipeline 102 rises above a predetermined valve, the mechanical pressure relief valve (not shown) opens for safety and security purposes. If the pressure in the closed-loop pipeline 102 falls below a predetermined value, the pressure tank/loop pipeline valved connection (not shown) may be opened and may be closed if the pressure in the closed-loop pipeline 102 rises above a predetermined value. The hydraulics supplied “TurboPiston” (Variable Voluminous High Pressure Tube Pump) 110 may be supplied with additional fluid from the reserve tank 111 via the first reserve tank/loop pipeline valved connection (not shown).

In relation to exemplary pressures of the present embodiment, the preferable pressure for the pressure tank 111 may be 200 bar. A preferable pressure for the reserve tank may be 20 bar and a preferable pressure for the close-loop pipeline may be 40 bar or more. Further, a preferable diameter for the reserve tank may be 250 mm and the reserve tank may be a section or sections of pipeline.

Referring now to Figures 2, 3a, 3b, 5, 6, 7a and 7b, Figure 2 shows a cross-section of a turbine 201 as implemented in the above-mentioned embodiments. As can be seen from Figure 2, the turbine 201 comprises a turbine housing which comprises a turbine inlet 203 and a turbine outlet 204. Within the turbine housing, turbine fluid chambers 206 are separated by turbine winglets 205. The turbine 201 further comprises a redundant line 210.

As can be seen from Figures 3a and 3b, the turbine inlet 203 and the turbine outlet 204 are inline such that as fluid passes through the turbine it first impacts a turbine winglet 205 and the momentum of the fluid drives the winglet 205 from a first position shown in Figure 3a to a second position shown in Figure 3b. In the first position the turbine winglet 205 is located towards the turbine inlet 203 but the flow of the fluid drives the turbine winglet 205 towards the turbine outlet 204.

In the first position, the turbine fluid chamber 206 is filled with fluid entering the turbine 201 through the turbine inlet 203. In the second position, the fluid in the turbine fluid chamber 206 is released out of the turbine 201 through the turbine outlet 204.

This sequence is repeated continuously through the operation of the apparatus 101, 201 and thereby rotates the turbine 201. The turbine 201 may be further powered by a pressure difference between the fluid at the turbine inlet 203 and the fluid at the turbine outlet 204, namely a higher pressure at the turbine inlet 203 than at the turbine outlet 204.

Figure 5 shows a perspective view of an illustration of a turbine 501, according to the embodiments described herein, which comprises an inside shaft (not shown) for mechanical attachment to a pair of alternators 308. The turbine housing 502 may comprise metal.

The arrangement of the turbine 301 with the alternator pair 308 can be seen in the cross-section view of Figure 7b.

An enlarged view of the first embodiment is shown in Figure 6 and shows a plan view of the arrangement of the three turbines 103, 104, 105 of the present embodiment.

Hydraulic supplied “TurboPiston” (Variable Voluminous High Pressure Tube Pump)

With reference to Figures 8a to 13, the hydraulic supplied “TurboPiston” (Variable Voluminous High Pressure Tube Pump) 110 may provide, simultaneously, high efficiency and high pressure and may be used at 100 bar pressure and above. According to an embodiment of the present disclosure, the TurboPiston 110 may be provided with one single cylinder.

The Variable Voluminous High Pressure Tube Pump of the present disclosure may be controlled with four smart valves (not shown) operated by automation.

Referring specifically to Figures 8a to 9b, the hydraulic supplied “TurboPiston” (Variable Voluminous High Pressure Tube Pump) 110 may comprise a slidable piston shaft 830 which may pass through a first chamber 832 and a second chamber 833 of the TurboPiston 110 and may be sealed at each end of the TurboPiston 110 by a first chamber piston cover 831 and a second chamber piston cover 834. The slidable piston shaft 830 may also pass through the chamber dividing wall 839 which may separate the first chamber 832 from the second chamber 833 such that there may be created a pressure difference between the two chambers 832, 833. Both the first chamber 832 and the second chamber 833 may be enclosed by a main body 837 of the TurboPiston 110.

The first chamber 832 may comprise a first chamber output valve 835 and a first chamber input valve 838 and the second chamber 833 may comprise a second chamber output valve 842 and a second chamber input valve 841.

The TurboPiston 110 may be connected to the closed-loop pipeline 102 such that fluid (such as compressed air) may be driven from the first chamber 832 to the second chamber 833 through the components of the fluid circulating apparatus.

The piston shaft 830 may be driven from one side of the TurboPiston 110 by hydraulic fluid via the opening of a valve (not shown).

The TurboPiston 110 may be arranged such that the shaft and the piston heads are sealed.

With a first hydraulic action in the first chamber 832, fluid (such as compressed air) may be driven through the closed-loop pipeline 102 and through the components of the fluid circulating apparatus (including through the turbines 103, 104, 105) to the second chamber 833.

Equally, fluid (such as compressed air) in the second chamber may be passed through the closed-loop pipeline, and through the turbines 103, 104, 105, with movement of the piston shaft 830 and return to the first chamber 832.

There may be two smart valves (not shown), one inlet and one outlet on each piston head (not shown). Intelligent valves may be controlled by an automation system which may provide an instant response to ensure the system operates continuously.

By taking compressed air, for example, from the closed-loop pipeline 102, using appropriate methods, the compressed air can be stored, pressurized and transferred back to either of the chambers 832, 833 of the piston.

The abundance of air in the atmosphere ensures the cost of obtaining atmospheric air to be low.

If necessary, excessive compressed air may be pushed back into the reserve tank 111.

Referring to Figure 13, there may be provided a pump motor 1302 which may be supplied with 0.4kw and 0.9kw power to provide hydraulic drive to the TurboPiston 110.

Electrical energy may be supplied to the pump motor 1302 by the six alternators 107, 108, 109 each generating 5.5kw of power.

The TurboPiston 110 circulates air through the closed-loop pipeline 102 with high flow rates.

Pneumatic valves and automation systems (not shown) will be used to obtain all linear movements.

Air, which is a source of pneumatic energy, may be obtained unlimitedly from the atmosphere. Speed and force values of the system may be adjusted to and from different levels. Compressed air may be transported without loss or leakage through the closed-loop pipeline 102. By adjusting the piston speed, the flow rate may be changed at desired values when necessary. System operating pressure may be controlled by regulators and pressure sensors such that it is maintained at 40 bar or above.

With the use of a pressure regulator (not shown) the pressures of the system may be limited thereby a safe system that controls the pressure power may be provided.

In the event that excessive pressure and values that exceed the regulator are reached, the pressure can be kept at the desired level again with a by-pass outlet (not shown).

In the event that linear motion is needed, the direction of motion can be diverted to the opposite direction. The system does not have to stop to move the piston shaft 830 in the opposite direction. Equally, speed can be adjusted whilst the piston shaft 830 is in motion and may be increased or decreased. It is possible to obtain various speed values without any steps.

As shown in Figure 13, oil 1303 may be used as the fluid in the hydraulic system, the components that need lubrication are provided with the oil 1303 directly. While the system is operation, the oil valves (not shown) may be lubricated along with other elements that the oil 1303 may pass through.

In the present embodiment it may be possible to adjust and control the movements of the piston shaft 830 very precisely. The present embodiment may also be suitable for continuous work.

If the hydraulic system encounters an unexpected load or resistance while operating, it may stop. Once this overload is removed, it may continue to act as usual. Meanwhile, the automated safety valve operation, as described above, may eliminate the damage caused by the increased pressure. There may be a circuit designed with logic valves, such that the cylinder may be controlled by four logic valves (not shown) In hydraulic cylinders, when the cylinder reaches the end of the stroke, the piston and the cylinder base or throat may hit each other. This impact may damage the bearings and sealing elements of the cylinder and may cause fragmentation in the fasteners. In embodiments of the present disclosure this problem may be overcome by stopping the rapidly moving cylinder by slowing it down and thereby eliminate the effect of the impact. This may be achieved by proportionally controlling a directional valve of the cylinder (not shown) and thereby slow down and stop the piston shaft 830 at the end of a stroke via the signals sent to the valve.

Alternatively or additionally, two buffer bushings may be installed in front of and behind the piston of the cylinder. As the cylinder approaches the end of its stroke, these bushings restrict the flow of oil into the tank and force it to pass through a small channel in the cylinder neck or base.

Further, a regulated valve may be added and thereby cushioning is blocked and the cushioning rate may be changed.

The bump effect (cushioning) that the piston faces at the end of a stroke, may be mitigated by using an appropriate valve which may assist in optimizing the system.

Referring now to Figure 10, in an embodiment of the present disclosure in which the piston shaft 1030 is substantially vertical, the piston head 1031 may be driven in a downwards direction by its own weight. Additionally or alternatively, an external pressure 1032 may be applied to the piston head 1031 to drive it downwards. Such a downwards direction may be opposite to the direction in which the piston is hydraulically urged. Thereby, the weight or external pressure 1032 may serve to return the piston to a retracted position.

Referring to Figures 11 and 12, according to some embodiments of the present disclosure, the piston may be a telescopic piston 1130. Such a telescopic piston 1130 may be more space effective compared with conventional pistons (not shown). The telescopic piston 1130 may be configured to constantly disorder the balance of pressure in the system.

Advantages of the hydraulics supplied “TurboPiston ”

The above-described embodiments of the present disclosure provide a system with economic, clean, safe and simple compressed air for use in the generation of electricity.

In embodiments in which the fluid is compressed atmospheric air the fluid is readily obtainable which can be easily stored. Atmospheric air may be easily cleaned by filtering and extraction of it may not harm the environment and may be economically sourced.

By virtue of the use of pneumatics, speed may be adjusted easily and continuously. It may, thereby, be possible to obtain linear and continuous motion.

A further advantage of the above-described embodiments may be that the hydraulic elements may be small in volume and cover little space. Although they generate great pressure and force, their structure may be small.

Embodiments of the present disclosure may be controlled remotely and may be suitable for automatic control.

A further advantage may be the production of regular movement with reduced vibration. Hydraulic fluid may be incompressible thereby a rigid and regular movement may be obtained.

Further, the hydraulic aspect of the above-described embodiments may work silently and noiselessly whilst large forces and moments may be created. Further Alternative Embodiments

Figures 23 and 24 illustrate first and second half cycles, respectively, of a further embodiment of the present disclosure in which an apparatus 2301 for generating electrical energy comprises a fluid circulating apparatus which is suitable for circulating pressurised fluid. The fluid circulating apparatus comprises a closed-loop pipeline 2302, which connects together the further the components of the fluid circulating apparatus such that the fluid can flow to, from and through components of the fluid circulating apparatus.

The fluid circulating apparatus further comprises a first turbine 2303, a second turbine 2304 and a third turbine 2305 arranged in series and connected in order by the closed-loop pipeline 2302.

Each of the first, second and third turbines 2303, 2304, 2305 may be mechanically connected to each other by, for example, a common axle 2381 which in turn may be mechanically connected to an alternator (or other electrical generator) 2307 such that rotation of the turbines 2303, 2304, 2305 provides rotation to the alternator 2307 which in turn generates electrical energy. The turbines 2303, 2304, 2305 are rotated by the circulation of fluid through them.

A pneumatic/hydraulic cylinder arrangement 2310 is connected to the closed-loop pipeline 2302 to pressurise air in the closed-loop pipeline 2302.

The pneumatic/hydraulic cylinder arrangement 2310 is a hybrid arrangement comprising a first pneumatic cylinder 2351 and a second pneumatic cylinder 2352 and a hydraulic cylinder 2353, each with a respective piston 2354, 2355, 2356 and each piston mechanically connected to each other piston, for example, located on the same piston shaft 2357.

The pneumatic/hydraulic cylinder arrangement 2310 is electrically driven by a hydraulic power unit (not shown) and/or a reserve tank (not shown although described in more detail in the preceding embodiments). The hydraulic power unit may drive hydraulic fluid from a first hydraulic chamber 2358 to a second hydraulic chamber 2359 and thereby move the hydraulic piston 2356 which in turn moves the piston shaft 2357 such that the first pneumatic piston 2354 is urged to pressurise and expel air out of the first pneumatic chamber 2360. Simultaneously, such a movement also urges the second pneumatic piston 2355 such that the second pneumatic chamber 2361 expands and draws air into the second pneumatic chamber 2361. This sequence of actions may occur in a second half cycle of the apparatus 2301.

Equally, in a first half cycle of the apparatus 2301, the opposite action may occur such that the hydraulic power unit may drive hydraulic fluid from the second hydraulic chamber 2359 to the first hydraulic chamber 2358 and thereby move the hydraulic piston 2356 which in turn moves the piston shaft 2357 such that the first pneumatic piston 2354 is urged to expand and draw-in in to the first pneumatic chamber 2360. Simultaneously, such a movement may also urge the second pneumatic piston 2355 such that the second pneumatic chamber 2361 compresses and expels air out of the second pneumatic chamber 2361.

During operation, air may be received via the closed-loop pipeline 2302 to the pneumatic/hydraulic cylinder arrangement 2310 from the exhaust of the third turbine 2305. The closed-loop pipeline 2302 may split in to a first chamber intake 2362 and a valved second chamber intake 2363. The first chamber intake 2362 may itself be valved and may comprise first and second valves 2364, 2365.

The first chamber intake 2362 may supply the first pneumatic chamber 2360 with low pressure air from the exhaust of the third turbine 2305 and the valve second chamber intake 2363 may supply the second pneumatic chamber 2361 with low pressure air from the exhaust of the third turbine 2305.

Pressurised air may be expelled from the first pneumatic chamber 2360 via a valved first chamber output 2366 and from the second pneumatic chamber 2361 via a second chamber output 2367. The second chamber output 2367 may itself be valved and may comprise third and fourth valves 2368, 2369.

The valved first chamber output 2366 and the second chamber output 2367 may join together to reform the closed-loop pipeline 2302 and may themselves be components of the closed- loop pipeline 2302. The pressurised air exiting the pneumatic/hydraulic cylinder arrangement 2310 may supply the first turbine 2303. The flow of air may follow the arrows 2370 in an anticlockwise direction around the closed-loop pipeline 2302.

Figure 23 illustrates the first half cycle in which the first, second, third and fourth valves 2364, 2365, 2368, 2369 are open and the valve second chamber intake 2363 and valved first chamber output 2366 are closed.

Figure 24 illustrates the second half cycle in which the first, second, third and fourth valves 2364, 2365, 2368, 2369 are closed and the valve second chamber intake 2363 and valved first chamber output 2366 are open.

At least one of the turbines 2303, 2304, 2305 may comprise an air expander. The closed-loop pipeline may have a diameter of 0.5 inches (12.7mm).

The apparatus may further comprise a reserve tank (not shown) for receiving any excess pressure in the closed-loop pipeline 2302. This may be regulated by an additional control valve system (not shown).

The closed-loop pipeline 2302 may further comprise apparatus for cooling and for maintaining pressure within predetermined parameters. The closed-loop pipeline 2302 may further comprise an outer pipeline (not shown) surrounding an inner pipeline (not shown). Such an outer pipeline may provide protection from explosion of the inner pipeline and damage to the inner pipeline.

The closed-loop pipeline 2302 may comprise a bleed valve (not shown) for extracting condensation that may form in the closed-loop pipeline 2302.

Referring to Figure 25, the valves 2364, 2365, 2368, 2369, 2363, 2366 may be connected to a network 2372 which may also be connected to sensors 2371. Such a network 2372 may be connected to an automatic voltage regulator (AVR) 2643 which in turn may be connected to a programmable logic controller (PLC) 2648 which may determine and automate the closure of valves based on pressure and temperature parameters being exceeded.

Referring now to Figure 26, the apparatus of Figures 23 to 25 may constitute part of an alternative embodiment of the present disclosure as illustrated in Figure 26.

The closed-loop pipeline 2302 may further comprise an air accelerator 2681 that may be arranged on the closed-loop pipeline 2302 such that it receives air from the pneumatic/hydraulic cylinder arrangement 2310 and may accelerate the air flow of the air passing through it.

The apparatus 2601 illustrated in Figure 26 may further comprises a starting tank 2683 which may be pressurised to 200 bar (20000 kPa) by, for example, a dedicated compressor 2684. The starting tank 2683 may be arranged in connection with the closed-loop pipeline 2302 such that pressurised air may be provided to the turbines to overcome their rotational inertia. The starting tank may comprise a starting tank pressure sensor 2640 and a starting tank temperature sensor 2641 which may be communicatively connected to the automatic voltage regulator (AVR) 2643 for automated monitoring.

Further temperature and pressure sensors are communicatively connected to the AVR 2643 such as the pre-turbine temperature sensor 2644 and the pre-turbine pressure sensor 2645 and the post-turbine temperature sensor 2646 and the post-turbine pressure sensor 2647. Data received from these sensors may assist the automated system in determining actuation of the components of the apparatus 2601.

The apparatus 2601 comprises a combined turbine and alternator 2685 which may also comprise alternator cooling means 2682. The alternator may be electrically connected to a battery management system 2686 which itself may comprise one or more of a AC to DC rectifier, a battery bank, a battery cooling means and a three phase inverter (for example a hybrid inverter). Electrical power generated by the alternator may be used to power components of the apparatus 2601 and may be distributed to the relevant components by a control board 2688 and may supply at least one of any of the cooling means 2682 of the apparatus 2601, the compressor 2684, the pneumatic/hydraulic cylinder arrangement 2310 with electrical power.

The alternator cooling means 2682 may supplied with power by electrical connection one 2693, the hydraulic cooling means (not shown) may be supplied with power by electrical connection two 2694, the compressor 2684 may be supplied with power by electrical connection three 2695, the hydraulic power unit 2620 may be supplied with power by electrical connection four 2696, the battery cooling means 2621 may be supplied with power by electrical connection five 2697, the inverter cooling means (not shown) may be supplied with power by electrical connection six 2698, the AVR 2643 may be supplied with power by electrical connection seven 2699, the programmable logic controller (PLC) 2648 may be supplied with power by electrical connection eight 2610.

The apparatus may further comprise at least one check valve 2691 and/or pressure release valve 2692 along any of the length of pipeline, for example along the closed-loop pipeline 2302. The apparatus 2601 may further include temperature and pressure sensors in pressurised components for monitoring.

Turbines

The turbine blade profiles may be optimized for a pulsating air flow therethrough and may be suitable for blade rotational speed from 3000rpm to 40,000rpm, directly proportional to air pressure and flow therethrough.

The turbine fluid intake and outlet may be of the same diameter and on the same axis.

Alternators

The alternators may comprise permanent magnet rotors and may be suitable for power generation at 400Hz. The alternators are may be capable of withstanding high rotational, varying speeds (acceleration) and, therefore, mechanical stress. It is anticipated that the alternators will be of permanent magnet rotor design and similar to those used on aircraft

Operation

The pneumatic/hydraulic cylinder arrangement 2310 may be dynamically controlled, by an automated computer system or otherwise, to increase air pressure in response to increased power demand from, for example, increased load on the power generating components of the apparatus.

The apparatus may further comprise a supervisory system (not shown) arranged to operate the valves of the pneumatic and hydraulic intakes and outputs. Such a supervisory system may be configured to operate and optimise the actuation of the valves to achieve a predetermined pressure and/or flow of the circulating fluid.

Starting tanks and batteries of the relevant apparatus may be full charged and pressurised before the apparatus is used.

The pressure and speed lost from the circulating fluid after passage through one or more turbines may be re-established by the pneumatic/hydraulic cylinder arrangement 2310 and/or the air accelerator 2681.

Air Accelerator

Figure 27 illustrates an air accelerator 2681 according to embodiments of the present disclosure, which may comprise a screw compressor 2771 comprising a cone-shaped rotor 2772. The cone-shaped rotor 2772 may be directly driven by a high-speed electric motor or through a gear box. An advantage of this component may be to increase air pressure and/or air flow of the air supplying the turbines.

The air accelerator 2681 may add control and flexibility since pressure and flow of the circulating fluid, such as air, may be readily adjusted via a motor speed control system. The cone-shaped rotor may be configured for use at between 6000rpm and 24,000rpm. Different performance results can readily be obtained by changing the conical angle and number of screw blades incorporated cone-shaped rotor.

Sensors may be used to measure the air pressure and flow and may be utilised by the supervisory system, for example, to determine the actuation of the air accelerator 2681. The air accelerator 2681 may be configured to utilize external (atmospheric) air when necessary.

Alternatives

A reserve tank or line with a pressure lower than that of the closed-loop pipeline may supply or remove air from the closed-loop pipeline for stabilization purposes.

A supervisory system may comprise control valves, check valves, various sensors, and control hardware to facilitate operation and monitoring.

In the event that pressure above a predetermined threshold is detected at a pneumatic cylinder outlet, the actuation of the pneumatic/hydraulic cylinder arrangement may be modulated.

Batteries

The batteries described above may comprise lithium-ion batteries and may be rated at 240VDC with lOOAh capacity and/or may be matched to the DC link voltage of the rectifier/inverter units.

Any of the above-described apparatus may further comprise a battery management system, (BMS) which may be configured for use in an energy storage system and, for example, applicable to high voltage UPS systems with outputs of 100V to 800V DC. The batteries may provide backup power for a time that may exceed 10 minutes. The batteries may be comprise battery racks and CBMS, GBMS. Each battery rack may integrate with an intelligent BMU therein. Electrical Interface

To convert the turbine mechanical output to useable electrical energy, one or more of the following components may be used:

• Electrical generator, (either permanent magnet, induction, or wound rotor synchronous. This embodiment proposes a two pole, high speed permanent magnet design)

• Frequency converter - rectifier unit, (with DC link to Inverter)

• Frequency converter - inverter unit

• Transformer, if necessary, for voltage matching and/or compatibility

• Circuit Breaker and/or protective devices

• Grid connection

• Local Load (if present)

• AC/DC converter for battery voltage matching

• Battery and battery management system

The electrical generator may have a rating of lOkW and/or a driver turbine maximum operating speed of 10,000rpm. A suitable generator may have two rotor magnetic poles therefore its maximum output frequency may be 166Hz. It thus may be necessary to additionally incorporate a power electronic frequency converter, (PEC), to match the high generator frequency and varying voltage to a conventional distribution or local network. Electrical generators may incorporate internal voltage regulators. Since the electrical output of the generator may vary in response to changes in air pressure and velocity supplied to the turbine, the frequency converter frequency and voltage may be optimally controllable such that output may be stable at 110 - 380V and/or 50Hz, for example. A further interposing transformer may be necessary to match any difference in voltage to either local or grid connected supplies.

Individual power electronic converters may be incorporated such that control and synchronization of the generator outputs may be readily undertaken and efficiency maintained. A battery storage system (BESS) may be connected via a DC link of the Power Electronic Converter(s). This may consist of either Lead Acid or Lithium-Ion batteries. The BESS may be intended to provide an electrical energy supply which can adequately compensate for variations in supply originating from the turbine generators.

The power electronic converter may take the form of a self-contained drive package whereby all rectifier and inverter components are included within a single cabinet. Alternatively, separate rectifier and inverter units may be provided. The use of separate units may have an advantage in that convenient access to the DC link for battery connections can be provided.

Since the turbine/alternator configuration may be operating in a cyclic mode according to air pressure/flow variations, rotational speed and frequency may constantly vary between maximum and minimum values. The rectifier/inverter unit may therefore be suitable for operating with such a regime, the Li-Ion battery being used to store electrical energy produced.

In the case where more than one turbine/alternator combination is utilized in a drive train, either in series or in parallel, it may be necessary to ensure that all final electrical outputs are correctly matched and synchronized together. This may be suitably accomplished using phase-locked-loop control circuitry built within the inverter section electronics. A further advantage of having separate and individually adjustable converter systems may be the ability to optimally adjust for discrepancies in load sharing and for speed differences between the generators. There may also be the provision of some redundancy should one generator combination fail. CLAUSES

The present disclosure includes the following clauses:

1. An apparatus for generating electrical energy comprising: fluid circulating apparatus, suitable for circulating pressurised fluid, comprising: a closed-loop pipeline arranged to connect the components of fluid circulating apparatus in series; the components of the fluid circulating apparatus comprising: a fluid propulsion means comprising a fluid intake and a fluid output; a plurality of turbines connected in series by the closed-loop pipeline, the plurality of turbines comprising at least a first turbine and a last turbine, wherein the first turbine comprises a turbine intake and the last turbine comprises a turbine output; a cooling means, for cooling the pressurised fluid, comprising a cooling intake and a cooling output, wherein the turbine output is connected to the cooling intake by the closed-loop pipeline; wherein the fluid output of the fluid propulsion means is connected to the turbine intake by the closed-loop pipeline; wherein the cooling output is connected to the fluid intake of the fluid propulsion means by the closed-loop pipeline; the apparatus for generating electrical energy further comprising: a reserve tank arranged to supply reserve fluid to the fluid circulating apparatus; a pressure tank for providing an initial fluid flow to overcome a start-up inertia of the plurality of turbines and maintaining an energy efficiency of the fluid propulsion means by eliminating inrush currents, the pressure tank comprising a compressor to maintain a predetermined pressure in the pressure tank; at least one alternator mechanically connected to each of the plurality of turbines such that rotation of the turbine provides rotation to the alternator which in turn generates electrical energy.

2. An apparatus according to clause 1 , wherein the fluid is air. An apparatus according to any preceding clause, wherein the closed-loop pipeline is ½ inch in diameter. An apparatus according any preceding clause, wherein the plurality of turbines comprises at least three turbines. An apparatus according to any preceding clause, wherein the fluid propulsion means comprises a hydraulics supplied “TurboPiston” (Variable Voluminous High Pressure Tube Pump). An apparatus according to any preceding clause, wherein the fluid propulsion means comprises an inline compressor. An apparatus according to any preceding clause, wherein the closed-loop pipeline is enclosed with a second security pipeline. An apparatus according to any preceding clause, wherein the fluid propulsion means and the plurality of turbines are arranged in line with the closed-loop pipeline. An apparatus according to any preceding clause, wherein the at least two alternator comprises two identical alternators. An apparatus according to any preceding clause, wherein the reserve tank has a lower pressure than the fluid circulating apparatus. An apparatus according to any preceding clause, wherein the apparatus for generating electrical energy further comprises an automation system. An apparatus according to clause 11 , wherein the automation system comprises any of: control valves, check valves, sensors, temperature sensors, pressure sensors, flow sensors, control means, means for logging measurements. An apparatus according to any preceding clause, wherein the apparatus for generating electrical energy further comprises at least one security component. An apparatus according to clause 13, wherein the at least one security component comprises any of: a motorised pressure relief valve, a mechanical pressure relief valve. An apparatus according to any preceding clause, wherein the pressure tank, the reserve tank and the fluid circulating apparatus are all connected to one another. An apparatus according to any preceding clause, wherein the apparatus for generating electrical energy further comprises a one, two or three additional pressurised tanks. An apparatus according to clause 16, wherein the tanks are connected to one another and to the fluid circulating apparatus such that they maintain a continuous flow through the tanks and the fluid circulating apparatus. An apparatus according to any preceding clause, wherein the reserve tank comprises at least one section of pipe which together substantially form an oval shape. An apparatus according to any preceding clause, wherein the at least one alternator mechanically connected to the last turbine has a lower power rating than the at least one alternator mechanically connected to the first turbine. An apparatus according to any preceding clause, wherein the pressurised fluid is pressurised to 40 bar or more. An electrical power generator comprising a closed-loop turbine comprising a hydraulics supplied “TurboPiston” (Variable Voluminous High Pressure Tube Pump), a pressurised tank, a reserve tank and a series of turbines.