ENERGY STORAGE PLANT AND PROCESS

Abstract

An energy storage plant includes a casing for the storage of a working fluid different from atmospheric air, in gaseous phase and in pressure equilibrium with the atmosphere; and a tank for the storage of said working fluid in liquid or super-critical phase with a temperature close to the critical temperature. The critical temperature is close to the ambient temperature. The plant is configured to perform a closed cyclic thermodynamic transformation, first in one direction in a charge configuration and then in an opposite direction in a discharge configuration, between said casing and said tank. In the charge configuration the plant stores heat and pressure and in the discharge configuration generates mechanical energy to drive a driven machine.

Claims

1.-15 (canceled)

16. An energy storage plant, comprising: a working fluid different from atmospheric air; a casing configured to store the working fluid, in a gaseous phase, wherein the casing is a pressure-balloon or has the structure of a gasometer so that the working fluid in said casing is in pressure equilibrium with the atmosphere at low or zero over-pressure; a tank configured to store said working fluid in liquid or super-critical phase with a temperature close to the critical temperature; wherein said critical temperature is close to the ambient temperature; and at least a driven machine different from an electric generator, wherein the plant is configured to perform a closed cyclic thermodynamic transformation, first in one direction in a charge configuration and then in an opposite direction in a discharge configuration, between said casing and said tank, wherein in the charge configuration the plant stores heat and pressure, and wherein in the discharge configuration the plant generates mechanical energy and transfers it to the driven machine to drive said driven machine.

17. The plant of claim 16, wherein the working fluid has the following chemical-physical properties: critical temperature between 0° C. and 200° C., density at 25° C. between 0.5 kg/m.sup.3 and 10 kg/m.sup.3.

18. The plant of claim 16, further comprising: a compressor and a motor mechanically connected to each other; a turbine mechanically connected to the driven machine; said casing externally in contact with the atmosphere and delimiting at its interior a volume configured to contain the working fluid at atmospheric pressure or substantially atmospheric pressure, wherein said volume is selectively in fluid communication with an inlet of the compressor or with an outlet of the turbine; a primary heat exchanger selectively in fluid communication with an outlet of the compressor or with an inlet of the turbine; said tank in fluid communication with the primary heat exchanger to accumulate the working fluid; a secondary heat exchanger operationally active between the primary heat exchanger and the tank or in said tank; and said plant being configured to operate in the charge configuration or in the discharge configuration, wherein, in the charge configuration, the casing is in fluid communication with the inlet of the compressor and the primary heat exchanger is in fluid communication with the outlet of the compressor, the turbine is at rest, the motor is operating and drives the compressor to compress the working fluid coming from the casing, the primary heat exchanger works as a cooler to remove heat from the compressed working fluid, cool it and store thermal energy, the secondary heat exchanger works as a cooler to remove additional heat from the compressed working fluid and store further thermal energy, the tank receives and stores the compressed and cooled working fluid, wherein the working fluid stored in the tank has a temperature close to its own critical temperature, and wherein, in the discharge configuration, the casing is in fluid communication with the outlet of the turbine and the primary heat exchanger is in fluid communication with the inlet of the turbine, the compressor is at rest, the secondary heat exchanger works as a heater to transfer heat to the working fluid coming from the tank, the primary heat exchanger works as a heater to transfer further heat to the working fluid and heat it, the turbine is rotated by the heated working fluid and drives the driven machine, the working fluid returns in the casing at atmospheric or substantially atmospheric pressure.

19. The plant of claim 16, wherein the driven machine is a compressor or a pump.

20. The plant of claim 16, wherein the motor is an electric motor or a heat engine.

21. The plant of claim 16, further comprising a further heat exchanger operationally coupled to an additional heat source and operationally placed between the turbine and the primary heat exchanger, wherein said further heat exchanger is configured to further heat the working fluid in the discharge configuration before entering the turbine.

22. The plant of claim 21, wherein the additional heat source is chosen among: a solar source, industrial recovery waste heat, and gas turbine exhaust heat.

23. The plant of claim 18, further comprising a generator mechanically connected or connectable to the turbine, wherein, in the discharge configuration, the turbine drives the generator, also generating electric energy.

24. The plant of claim 23, wherein the motor and the generator are separate elements; or wherein the motor and the generator are defined by a single motor-generator and the plant comprises connection devices interposed between said motor-generator and the compressor and the turbine to connect mechanically and alternately the motor-generator to the compressor or to the turbine.

25. The plant of claim 18, comprising an auxiliary motor connected to the driven machine and configured to drive said driven machine at least when the plant is in the charge configuration; and an auxiliary generator mechanically interposed between the turbine and the driven machine and connection devices interposed between the auxiliary generator and the turbine to selectively connect said auxiliary generator to the turbine, wherein the auxiliary motor and the auxiliary generator are defined by a single auxiliary motor-generator.

26. A process for energy storage implemented with the plant of claim 16, the process comprising: carrying out the closed thermodynamic cyclic transformation, first in one direction in a charge configuration/phase and then in an opposite direction in a discharge configuration/phase, between the casing for the storage of the working fluid different from atmospheric air, in a gaseous phase and in pressure equilibrium with the atmosphere, and the tank for the storage of said working fluid in a liquid or super-critical phase with a temperature close to the critical temperature, wherein said critical temperature is close to the ambient temperature, wherein, in the charge phase, the process accumulates heat and pressure and in the discharge phase generates mechanical energy and transmits it to a driven machine different from an electric generator to drive said driven machine, and wherein, during the closed cyclic thermodynamic transformation, the working fluid in the casing is in equilibrium of pressure with the atmosphere at low or zero over-pressure.

27. The process of claim 26, wherein the charge phase comprises: compressing said working fluid, coming from said casing externally in contact with the atmosphere and delimiting at its interior a volume configured to contain the working fluid at atmospheric pressure or substantially atmospheric, absorbing energy; introducing the compressed working fluid through a primary heat exchanger and a secondary heat exchanger placed in series to bring a temperature of the working fluid close to its own critical temperature, wherein the primary heat exchanger works as a cooler to remove heat from the compressed working fluid, cool it and store thermal energy, wherein the secondary heat exchanger works as a cooler to remove further heat from the compressed working fluid and store further thermal energy; and accumulating the cooled working fluid in said tank; wherein the secondary heat exchanger and the primary heat exchanger carry out a super-critical transformation of the working fluid so that said working fluid is accumulated in the tank in super-critical phase or wherein the secondary heat exchanger and the primary heat exchanger carry out a sub-critical transformation of the working fluid so that said working fluid is accumulated in the tank in liquid phase, wherein a temperature of the working fluid accumulated in the tank is between 0° C. and 100° C. and wherein a pressure of the working fluid accumulated in the tank is between 10 bar and 150 bar.

28. The process of claim 26, wherein said working fluid has the following physical-chemical properties: critical temperature between 0° C. and 200 ° C., density at 25° C. between 0.5 kg/m.sup.3 and 10 kg/m.sup.3.

29. The process of claim 27, wherein the phase of discharge and generation of mechanical energy comprises: passing the working fluid, coming from the tank, through the secondary heat exchanger and the primary heat exchanger, wherein the secondary heat exchanger works as a heater to transfer heat to the working fluid coming from the tank, wherein the primary heat exchanger works as a heater to transfer further heat to the working fluid and heat it; passing the heated working fluid through a turbine mechanically connected to the driven machine, wherein the turbine is rotated by the heated working fluid and drives the driven machine, wherein the working fluid expands and cools down in the turbine; and re-introducing the working fluid coming from the turbine into the casing at atmospheric or substantially atmospheric pressure.

30. The process of claim 29, wherein in the phase of discharge and generation of mechanical energy, between the primary heat exchanger and the turbine, it is provided to further heat the working fluid through an additional heat source.

31. The process of claim 26, wherein said critical temperature is between 0° C. and 100° C.

32. The process of claim 26, wherein said working fluid is selected from the group comprising: CO.sub.2, SF.sub.6, N.sub.2O.

33. The process of claim 29, wherein the additional heat source is selected from among: a solar source, industrial recovery waste heat, and gas turbine exhaust heat.

Description

DESCRIPTION OF THE DRAWINGS

[0167] Such description will be set forth hereinbelow with reference to the enclosed drawings, provided as only as a non-limiting example, in which:

[0168] FIG. 1 schematically illustrates an embodiment of an energy storage plant according to the present invention;

[0169] FIG. 2 is a T-S diagram illustrating a process according to the present invention actuated in the plant of FIG. 1;

[0170] FIG. 3 illustrates an embodiment variant of the plant of FIG. 1;

[0171] FIG. 4 illustrates a further embodiment variant of the plant of FIG. 1;

[0172] FIG. 5 illustrates a portion of the plant according to the present invention;

[0173] FIG. 6 illustrates a further embodiment of an energy storage plant according to the present invention.

DETAILED DESCRIPTION

[0174] With reference to the enclosed figures, reference number 1 overall indicates an energy storage plant according to the present invention.

[0175] The plant 1 for example operates with a working fluid different from atmospheric air. For example, the plant 1 operates with a working fluid selected from the group comprising: carbon dioxide CO.sub.2, sulfur hexafluoride SF.sub.6, dinitrogen oxide N.sub.2O. In the following description, the working fluid used together with the described plant 1 is carbon dioxide CO.sub.2.

[0176] The plant 1 is configured to perform a closed cyclic thermodynamic transformation (CTT), first in one direction in a charge configuration/phase and then in an opposite direction in a discharge configuration/phase, wherein in the charge configuration the plant 1 stores heat and pressure and in the discharge configuration it generates electric energy.

[0177] With reference to FIG. 1, the plant 1 comprises a turbine 2 and a compressor 3 mechanically connected to a shaft of a single motor-generator 4. The motor-generator 4, the compressor 3 and the turbine 2 are arranged on a same axis. A shaft of the turbine 2 is coupled to one end of the shaft of the motor-generator 4 by means of connection devices, e.g. of friction type, which allow connecting and disconnecting, upon command, the turbine 2 to/from the motor-generator 4. Analogously, a shaft of the compressor 3 is coupled to an opposite end of the shaft of the motor-generator 4 by means of connection devices, e.g. of friction type, which allow connecting and disconnecting, upon command, the compressor 3 to/from the motor-generator 4.

[0178] The turbine is also mechanically connected by means of transmission elements 301, represented only in a schematic manner, to a driven machine 300, schematically represented in FIG. 1, different from a generator or from a motor-generator. Such driven machine 300 may, for example, be a compressor of air or of natural gas for pipelines or for liquified natural gas (LNG) or of process gas, a pump for water or for process gas, or in any case a generally driven machine.

[0179] In the embodiment variant illustrated in FIG. 3, the motor 4a and the generator 4b are separate elements. In such case, the motor is stably connected to the compressor 3 and the generator is stably connected to the transmission elements 301 and to the turbine 2. The motor 4a is an electric motor.

[0180] In the further variant of FIG. 4, between the driven machine 300 and the turbine 2, an auxiliary motor-generator 302 is installed and connection devices 303 of friction type are interposed between the auxiliary motor-generator 302 and the turbine 2 to selectively connect the auxiliary motor-generator 302 and the driven machine 300 to the turbine 2.

[0181] In further variants, the turbine 2 is mechanically connected only to one or more driven machines and it is not connected or connectable to any generator or motor-generator. For example, FIG. 5 illustrates the turbine 2 directly connected to the shaft of a compressor used for the compression of a process fluid “F”. The compressor constitutes the driven machine 300. In the illustrated example, the shaft of the turbine 2 and the shaft of the compressor 300 are integral and the two machines rotate the same number of revolutions. In further variants, a reducer or gear transmission box can be provided, interposed between the turbine 2 and the compressor 300.

[0182] In further variants, not illustrated in detail in the enclosed figures, the motor 4a connected to the compressor 3 is not an electric motor but a drive machine that does not exploit electricity in order to be driven. For example, the motor 4a is a turbine, e.g. a gas turbine or vapor turbine or a wind turbine or a hydraulic turbine.

[0183] The plant 1 comprises a casing 5 preferably defined by a pressure-balloon made of flexible material, for example of PVC coated polyester fabric. The pressure-balloon is arranged at the surface and is externally in contact with the atmospheric air. The pressure-balloon delimits, at its interior, a volume configured to contain the working fluid at atmospheric pressure or substantially atmospheric pressure, i.e. in pressure equilibrium with the atmosphere. The casing 5 can also be attained as a gasometer or any other system for storing gas at low or zero over-pressure.

[0184] First pipes 6 are extended between the casing 5 and an inlet 3a of the compressor 3 and between the casing 5 and an outlet 2b of the turbine 2 in order to place the internal volume of the casing 5 in fluid communication with said compressor 3 and turbine 2. A valve or a valves system, not illustrated, can be operationally placed on the first pipes 6 in order to alternately place in fluid communication the casing 5 with the inlet 3a of the compressor 3 or the outlet 2b of the turbine 2 with the casing 5. The plant 1 comprises a primary heat exchanger 7 which can be selectively placed in fluid communication with an outlet 3b of the compressor 3 or with an inlet 2a of the turbine 2. For such purpose, second pipes 8 are extended between the inlet 2a of the turbine 2 and the primary heat exchanger 7 and between the outlet 3b of the compressor 3 and the primary heat exchanger 7. A valve, or a valves system, not illustrated, is operationally placed on the second pipes 8 in order to alternately place in fluid communication the primary heat exchanger 7 with the inlet 2a of the turbine 2 or the outlet 3b of the compressor 3 with the primary heat exchanger 7. In a preferred embodiment, only the valve or valves system placed on the second pipes 8 is present.

[0185] A tank 9 is in fluid communication with the primary heat exchanger 7 and is configured for accumulating the working fluid in liquid or super-critical phase.

[0186] The tank 9 is preferably made of metal with an external wall of spherical shape.

[0187] A secondary heat exchanger 10 is operationally active between the primary heat exchanger 7 and the tank 9, or in said tank 9, and is configured to operate on the working fluid accumulated or in charge phase in the tank 9. According to that illustrated in the embodiment of FIG. 1, the secondary heat exchanger 10 is integrated in the tank 9, in the sense that it has its own heat exchange portion 11 housed within the tank 9 and configured to be hit by the working fluid contained in said tank 9. Third pipes 12 are extended between the primary heat exchanger 7 and the tank 9 in order to place in fluid communication said primary heat exchanger 7 with said tank 9 and with said secondary heat exchanger 10.

[0188] In the schematic representation of FIG. 1, the plant 1 may also comprise an additional heat exchanger 13 operationally placed between the casing 5 and the compressor 2 and between the casing 5 and the turbine 2 and possibly a cooler 13a positioned on a branch of the first pipes 6 connected to the outlet 2b of the turbine 2.

[0189] The plant 1 also comprises a control unit, not illustrated, operationally connected to the different elements of the plant 1 itself and configured/programmed for managing the operation thereof.

[0190] The plant 1 is configured to operate in a charge configuration or in a discharge configuration, i.e. to execute a process comprising an energy charge phase and a phase of discharge and generation of energy.

[0191] In the charge configuration, the plant 1 starts from a first state in which the working fluid (CO.sub.2) in gaseous form is entirely contained in the casing 5 at the atmospheric pressure or substantially atmospheric pressure and at a temperature substantially equal to the ambient temperature (point A of the T-S diagram of FIG. 2). The casing 5, by means of the valves system, is placed in communication with the inlet 3a of the compressor 3 while the communication with the outlet 2b of the turbine 2 is blocked. In addition, by means of the valves system, the primary heat exchanger 7 is placed in fluid communication with the outlet 3b of the compressor 3 and the communication with the inlet 2a of the turbine 2 is blocked. The motor-generator 4 is coupled to the solo compressor 3 and is uncoupled from the turbine 2 (which is at rest) and from the driven machine 300. The motor-generator 4 works as motor to drive the compressor 3 so as to compress the working fluid coming from the casing 5. The driven machine 300 may, for example, independently work, moved by a respective auxiliary motor dedicated thereto and not illustrated in the enclosed figures.

[0192] Before entering within the compressor 3, the working fluid traverses the additional heat exchanger 13 which works as a heater in order to pre-heat the working fluid (point B of the T-S diagram of FIG. 2). The working fluid is then compressed in the compressor 3 and is heated (point C of the T-S diagram of FIG. 2). The working fluid then flows through the primary heat exchanger 7 which works as a cooler to remove heat from the compressed working fluid, cool it (point D of the T-S diagram of FIG. 2) and store the thermal energy removed from said working fluid. In the point D, the working fluid is situated at a temperature lower than the critical temperature of said fluid and in a point on the left part of the Andrews curve or slightly outside the curve in conditions of slight over-heating. The abovementioned compression may be adiabatic, inter-cooled or isothermal.

[0193] The working fluid enters into the tank 9 where the secondary heat exchanger 10, which in this configuration works as a cooler, removes further heat from the working fluid and stores further thermal energy. The working fluid traverses the saturated vapor zone up to reaching the liquid phase (point E of the T-S diagram of FIG. 2). The tank 9 therefore stores the working fluid in liquid phase at a temperature lower than its own critical temperature Tc. In this second state, the working fluid (CO.sub.2, Tc=31° C.) in liquid form, for example at 20° C., is fully contained in the tank 9. The secondary heat exchanger 10 and the primary heat exchanger 9 are therefore configured for operating a sub-critical transformation of the working fluid so that said working fluid is accumulated in the tank 9 in liquid phase.

[0194] In the discharge configuration, the plant 1 starts from the second state (point F of the T-S diagram of FIG. 2). The casing 5, by means of the valves system, is placed in communication with the outlet 2b of the turbine 2 while the communication with the inlet 3a of the compressor 3 is blocked. In addition, by means of the valves system, the primary heat exchanger 7 is placed in fluid communication with the inlet 2a of the turbine 2 and the communication with the outlet 3b of the compressor 3 is blocked. The motor-generator 4 is coupled to the turbine 2 and to the driven machine 300 and is uncoupled from the compressor 3 (which is at rest) and works as generator rotated by the turbine 2 driven by the working fluid in expansion. The turbine 2 also drives the driven machine 300, which receives energy from said turbine and may therefore be driven by means of the previously accumulated energy.

[0195] The secondary heat exchanger 10 works as a heater and transfers part of the heat, previously accumulated in the charge configuration, to the working fluid in the tank 9. The working fluid traverses the saturated vapor zone up to reaching the vapor phase (point G of the T-S diagram of FIG. 2). The working fluid traverses the primary heat exchanger 7 which now works as a heater and transfers further heat, previously accumulated in the charge configuration, to the working fluid and heats it (point H of the T-S diagram of FIG. 2).

[0196] The heated working fluid enters into the turbine 2, it is expanded and it is cooled (point I of the T-S diagram of FIG. 2) and causes the rotation of the turbine 2. The turbine 2, rotated by the heated working fluid, drives the driven machine 300 and the motor-generator 4 which works as generator and generates electric energy. The expansion of the working fluid in the turbine may be adiabatic, inter-heated or isothermal.

[0197] The working fluid exiting from the turbine 2 is cooled in the additional heat exchanger 13 (point J of the T-S diagram of FIG. 2) and returns into the casing 5 at the atmospheric pressure or substantially atmospheric pressure. The additional heat exchanger 13 in this phase accumulates additional thermal energy, in a respective further thermal energy storage device, which will be used in the subsequent charge phase in order to pre-heat said working fluid.

[0198] In the transformation illustrated in FIG. 2, the secondary circuit 20 is configured to remove heat from the working fluid, in the charge configuration, or to transfer heat to the working fluid, in the discharge configuration, to a temperature close to the ambient temperature, for example about 20° C.

[0199] Both in the charge configuration/phase and in the discharge configuration/phase, in order for the secondary heat exchanger 10 to operate in conditions close to the ambient temperature, due to the fact that the fluid has a critical temperature close to the ambient temperature, it is possible that the step of removing heat and/or the step of supplying heat by the secondary heat exchanger is/are assisted by a phase of direct or indirect exchange with the atmosphere.

[0200] For example, a temperature of the working fluid (CO.sub.2) accumulated in the tank 9 is 24° C. and a pressure of the working fluid accumulated in the tank 9 is 65 bar. The density of the CO.sub.2 at 25° C. and at atmospheric pressure is about 1.8 kg/m.sup.3. The density of the CO.sub.2 in the tank 9 is about 730 kg/m.sup.3. The ratio between the density of the working fluid when it is contained in the tank 9 in the indicated conditions and the density of the same working fluid when it is contained in the casing 5 at atmospheric conditions is therefore about 400. It is observed in this regard that, if in place of the CO.sub.2 atmospheric air stored at 65 bar and 24° C. is used in the tank 9, its density would only be 78 kg/m.sup.3 and the volume of the tank 9 theoretically necessary would be about ten times greater.

[0201] By way of example, for a plant 1 according to the invention capable of accumulating energy for 100 MWh, the volume of the pressure-balloon is about 400000 m.sup.3 while the volume of the tank is about 1000 m.sup.3.

[0202] The primary heat exchanger 7 may be a heat regenerator with fixed bed comprising a thermal mass constituted, for example, by metallic balls. In the charge configuration/phase, the thermal mass is hit by the compressed and hot working fluid, which transfers heat to the metallic balls which accumulate thermal energy. In the discharge configuration/phase, the thermal mass is hit by the cold working fluid, which absorbs heat from the metallic balls and is heated. In a variant that is not illustrated, the heat regenerator may also be of the type with movable bed. The primary heat exchanger 7 is therefore a thermal accumulator (Thermal Energy Storage TES).

[0203] In place of the heat regenerator with fixed bed, other types may be provided.

[0204] In embodiment variants, the secondary heat exchanger 10 and the primary heat exchanger 7 are configured for operating a super-critical transformation of the working fluid so that said working fluid is accumulated in the tank in super-critical phase. Unlike that illustrated in FIG. 2, the primary exchanger 7 removes heat from the working fluid up to bring it to a temperature higher than the critical temperature and above the Andrews curve. Subsequently, the secondary exchanger 10 carries the working fluid in super-critical phase by making it follow the right part of the Andrews curve.

[0205] For example, a temperature of the working fluid (CO.sub.2) accumulated in the tank 9 in super-critical phase is 25° C. and a pressure of the working fluid accumulated in the tank 9 is 100 bar. The density of the CO.sub.2 at 25° C. and at the atmospheric pressure is about 1.8 kg/m.sup.3. The density of the CO.sub.2 in the tank 9 is about 815 kg/m.sup.3. The ratio between the density of the working fluid when it is contained in the tank 9 in the indicated conditions and the density of the same working fluid when it is contained in the casing 5 at atmospheric conditions is therefore about 450.

[0206] In addition, the secondary heat exchanger may be provided with systems for adjusting the flow rate and/or the temperature of secondary fluid, typically water or air, capable of adjusting the pressure in the storage tanks within certain limits, when the system operates in sub-critical conditions. The temperature adjustment may for example be carried out by means of supply of heat from the atmosphere or removal of heat into the atmosphere, also by exploiting the normal environmental air and water temperature oscillations at different times of the day.

[0207] In the illustrated embodiments which use CO.sub.2 as working fluid, a CO.sub.2 dehydration system, a dehumidifier, e.g. with zeolites, is also preferably present in order to prevent potential formation of carbonic acid in the circuit.

[0208] FIG. 6 illustrates a further variant of the plant 1. Here, the main elements common to FIG. 1 are visible, i.e. the turbine 2, the compressor 3, the motor-generator 4, the casing 5, the primary heat exchanger 7 (thermal accumulator TES), the tank 9 and the secondary heat exchanger 10. The plant 1 illustrated herein also comprises the additional heat exchanger 13. As in the embodiment of FIG. 4, the secondary heat exchanger 10 is interposed between the primary heat exchanger 7 and the tank 9, i.e. it is not integrated in the tank 9. In a manner similar to the plant of FIG. 2, the secondary heat exchanger 10 comprises a secondary circuit 20 traversed by a secondary fluid, e.g. water. The secondary circuit 20, in addition to the heat exchange portion 11 comprises a secondary storage chamber 200, for the hot secondary fluid accumulated after having removed heat from the working fluid in the charge configuration/phase of the apparatus/process and for the cold secondary fluid accumulated after having transferred heat to the working fluid in the discharge configuration/phase of the apparatus/process. The abovementioned secondary storage chamber 200 is also coupled to a radiator 23 provided with one or more fans 24 placed on a recirculation duct which, for example, cools the secondary fluid during the night and heats it during the day. The abovementioned secondary storage chamber 200 is also connected by means of a respective circuit 210 to the additional heat exchanger 13.

[0209] In this embodiment variant, the plant 1 also comprises at least one further heat exchanger 220 which receives heat from an additional heat source 230. The further heat exchanger 220 is placed on the second pipes 8, between the inlet 2a of the turbine 2 and the primary heat exchanger 7. The additional heat source 230 is, as a non-limiting example, a solar source (e.g. solar field), industrial waste heat recovery, gas turbine exhaust heat, etc. The additional heat source 230 supplies additional heat during the discharge phase. The temperature to which the working fluid is brought in the discharge phase and just before entering the turbine 2, by means of the additional heat source 230 and the further heat exchanger 220, is higher than the temperature of the working fluid which is obtained at the end of compression during the charge phase. For example, the temperature to which the working fluid is brought by means of the additional heat source 230 and the further heat exchanger 220 is about 100° C., though also 200° C. or even 300° C. or even 400° C. higher than the temperature of the working fluid at the end of compression.

[0210] The plant 1 is also provided with an auxiliary thermal accumulator (Thermal Energy Storage TES) 240 connected, by means of suitable circuits, to the compressor 2 and to the turbine 2 so as to attain, in the compressor 3 (during the charge phase), an inter-cooled compression (with one or more inter-coolings) and to attain, in the turbine 2 (during the discharge phase), an inter-heated expansion (with one or more inter-heatings). The heat accumulated in the auxiliary thermal accumulator 240 during the inter-cooled compression is entirely or partly used in order to make the inter-heated expansion.

LIST OF ELEMENTS

[0211] 1 energy storage plant [0212] 2 turbine [0213] 2a inlet turbine [0214] 2b outlet turbine [0215] 3 compressor [0216] 3a inlet compressor [0217] 3b outlet compressor [0218] 4 motor-generator [0219] 4a motor [0220] 4b generator [0221] 5 casing [0222] 6 first pipes [0223] 7 primary heat exchanger [0224] 8 second pipes [0225] 9 tank [0226] 10 secondary heat exchanger [0227] 11 heat exchange portion of the secondary heat exchanger [0228] 12 third pipes [0229] 13 additional heat exchanger [0230] 13a cooler [0231] 20 secondary circuit [0232] 200 secondary storage chamber [0233] 210 circuit of the additional heat exchanger [0234] 220 further heat exchanger [0235] 230 additional heat source [0236] 240 auxiliary thermal accumulator [0237] 300 driven machine [0238] 301 transmission elements [0239] 302 auxiliary motor-generator [0240] 303 connection devices