WO2014027093A1 - Système de stockage d'énergie électrothermique et procédé de stockage d'énergie électrothermique - Google Patents

Système de stockage d'énergie électrothermique et procédé de stockage d'énergie électrothermique Download PDF

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Publication number
WO2014027093A1
WO2014027093A1 PCT/EP2013/067162 EP2013067162W WO2014027093A1 WO 2014027093 A1 WO2014027093 A1 WO 2014027093A1 EP 2013067162 W EP2013067162 W EP 2013067162W WO 2014027093 A1 WO2014027093 A1 WO 2014027093A1
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WO
WIPO (PCT)
Prior art keywords
working fluid
thermal energy
turbine
thermal
heat exchanger
Prior art date
Application number
PCT/EP2013/067162
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English (en)
Inventor
Jaroslav Hemrle
Lilian Kaufmann
Mehmet Mercangoez
Andreas Z'graggen
Original Assignee
Abb Research Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Abb Research Ltd filed Critical Abb Research Ltd
Priority to EP13750080.7A priority Critical patent/EP2909451B1/fr
Priority to PL13750080T priority patent/PL2909451T3/pl
Priority to DK13750080.7T priority patent/DK2909451T3/da
Publication of WO2014027093A1 publication Critical patent/WO2014027093A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/006—Accumulators and steam compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
    • F01K25/103—Carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/12—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having two or more accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K9/00—Plants characterised by condensers arranged or modified to co-operate with the engines
    • F01K9/003—Plants characterised by condensers arranged or modified to co-operate with the engines condenser cooling circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/028—Steam generation using heat accumulators

Definitions

  • the present invention relates generally to
  • electrothermal energy storage It relates in particular to a system and method for storing thermal energy according to the preamble of the independent patent claims.
  • Electro-thermal energy storage (ETES) systems are Electro-thermal energy storage (ETES) systems.
  • thermoelectric energy storage sometimes also referred to as thermoelectric energy storage
  • thermoelectric energy storage plays an ever increasing role for production and distribution of energy, in particular electric energy.
  • the basic principles of electro-thermal energy storage are described e.g. in EP 1 577 548 Al and EP 2 157 317 A2, which are hereby included by reference in their entirety.
  • the ETES system described in EP 2157317 A2 converts excess electricity to heat in a charging mode, stores the heat, and converts the heat back to electricity in a discharging mode when required.
  • Such an energy storage system is robust, compact, and suited to the storage of electrical energy in large amounts.
  • Thermal energy can be stored by one or more thermal storage media in the form of sensible heat via a change in temperature or in the form of latent heat via a change of phase or a
  • the storage medium for the sensible heat may be a solid, liquid, or a gas.
  • the storage medium for the latent heat may involve any of these phases or a combination of them in series or in parallel.
  • an electro-thermal energy storage system comprises at least one hot thermal storage arrangement
  • the charging mode of the ETES system is generally realized by operating a heat pump between the cold thermal storage arrangement and the hot thermal storage arrangement, whereas the discharging mode is realized by operating a heat engine between the hot thermal storage arrangement and the cold thermal storage arrangement.
  • Heat pump and heat engine may be individual thermodynamic machines with separate working fluid circuits, possibly containing different working fluids, and without common parts. Preferably, however, a single
  • thermodynamic machine with a single working fluid circuit may be configured to alternatively act as a heat pump or a heat engine by reverting a flow direction of the single working fluid, i.e. by switching between a heat pump cycle and a heat engine cycle.
  • heat needs to be transferred from hot working fluid to the first thermal storage medium during the heat pump cycle and back from the first thermal storage medium to working fluid during the heat engine cycle.
  • a heat pump requires work to move thermal energy from a thermal energy source on a cold side, e.g. the second thermal storage medium of the cold thermal storage arrangement, to a (warmer) thermal energy sink on a hot side, e.g. to the first thermal storage medium of the hot thermal storage arrangement. Since the amount of energy deposited at the hot side is greater than the work required by an amount equal to the energy taken from the cold side, a heat pump will "multiply" the heat as compared to resistive heat generation.
  • the ratio of heat output to work input is called coefficient of performance, and it is a value larger than one. In this way, the use of a heat pump will increase the round-trip efficiency of a ETES system.
  • ETES systems are preferably installed in a so called site independent arrangement, where the ETES would ideally be a closed system without any thermal interaction with its environment.
  • ice storage is preferably foreseen as part of the cold thermal storage arrangement to form the cold end of the charging and discharging cycles of the system; i.e. ice would be produced during in charging mode, while ice would be consumed when the ETES is in discharging mode.
  • CO2 may preferably be used as working fluid; and is preferably evaporated to produce ice when the ETES system is in charging mode, and condensed to melt ice in discharge mode.
  • the ETES system has to interact with an environment in some way in order to compensate for the losses of the involved processes, i.e. release the losses to the
  • auxiliary heat pump which would generate additional cold by interaction with the environment.
  • the cold would be used to cool the second thermal storage medium of the cold thermal storage arrangement, in order to compensate for the losses of the whole system.
  • an additional ammonia chiller could be used to produce additional ice, in particular in the charging mode.
  • the auxiliary heat pump would supply cold to compensate for the losses in order to enable the periodic charging and discharging operation to work repeatedly.
  • WO 2011103306 Al describes a method of keeping energy balance in an electro-thermal energy storage system based on a Rankine cycle.
  • the document discloses a "storage refrigerant circuit that receives input electric power and converts the electric power to stored thermal energy" with "a second
  • the method uses cooling on the hot side after the compressor to balance the electro-thermal energy storage.
  • a temperature difference between the thermal storage medium and the working fluid may be reduced using intermediate thermal storage tanks as described in the applicant's earlier patent application EP 2275649. Such factors would also enable the ETES system to have a higher round-trip efficiency.
  • An electro-thermal energy storage system comprises: a hot thermal storage arrangement comprising a hot storage heat exchanger; a cold thermal storage arrangement comprising a cold storage heat exchanger; a
  • thermodynamic cycle unit configured to transfer thermal energy from the cold storage arrangement to the hot storage arrangement in a charging mode, and to convert thermal energy from the hot storage arrangement into work and, preferably, subsequently into electric energy in a discharging mode
  • thermodynamic cycle unit comprises a fluid circuit for circulating a working fluid through the hot storage heat exchanger as well as through the cold storage heat exchanger, wherein the fluid circuit further comprises a pump for maintaining a circulation of working fluid in the discharging mode and a first turbine for expanding working fluid in the discharging mode; and wherein the thermodynamic cycle unit comprises a second turbine for
  • said second turbine being connected in series with the first turbine so that working fluid may flow from the first to the second turbine in the discharging mode, and an intercooling heat exchanger located in the fluid circuit between the first and the second turbine, said intercooling heat exchanger preferably configured to cool working fluid by exchanging heat with an environment of the electro-thermal energy storage system.
  • intercooling heat exchanger is configured to exchange heat with, in particular to transfer heat to, ambient air.
  • intercooling heat exchanger is configured to exchange heat with, in particular to transfer heat to, ambient water, in particular river water, lake or sea water, or ground water; preferably from a neighborhood of a location of the ETES system.
  • intercooling heat exchanger preferably has one or more of the following properties:
  • intercooling heat exchanger is a counter flow and/or cross flow heat exchanger
  • intercooling heat exchanger is adapted for heat exchange between two fluids, each of which either in liquid or gaseous form;
  • intercooling heat exchanger is adapted for heat exchange between two fluids without occurrence of any mixture and/or direct contact of the two fluids, in particular,
  • intercooling heat exchanger is not a direct contact heat exchanger
  • intercooling heat exchanger is adapted for heat exchange between two fluids without occurrence of any phase
  • intercooling heat exchanger is not a phase change heat exchanger.
  • a method in accordance with the invention for storing and retrieving energy in an electro-thermal energy storage system comprises the steps of: in a charging mode, transferring thermal energy from a cold thermal storage arrangement to a hot thermal storage arrangement by means of a first thermodynamic cycle configured to convert work into thermal energy; in a discharging mode, transferring thermal energy from the hot thermal storage arrangement to the cold thermal storage
  • thermodynamic cycle configured to convert thermal energy into work
  • thermodynamic cycle process comprises the steps of generating work by expanding a working fluid of the second thermodynamic cycle (process) in a first turbine, and (2) generating work by further expanding the working fluid in a second turbine, and cooling the working fluid between steps (1) and (2) by
  • working fluid is cooled between steps (1) and (2) through transfer of heat to ambient air and/or to ambient water, in particular river water, lake or sea water, or ground water; preferably from a neighborhood of a location of the ETES system.
  • an intercooling heat exchanger is preferably provided in a flow path for the working fluid between the first turbine and the second turbine, said intercooling heat exchanger preferably having one or more of the following properties:
  • intercooling heat exchanger is a counter flow and/or cross flow heat exchanger
  • intercooling heat exchanger is adapted for heat exchange between two fluids, each of which either in liquid or gaseous form;
  • intercooling heat exchanger is adapted for heat exchange between two fluids without occurrence of any mixture and/or direct contact of the two fluids, in particular,
  • intercooling heat exchanger is not a direct contact heat exchanger
  • intercooling heat exchanger is adapted for heat exchange between two fluids without occurrence of any phase
  • intercooling heat exchanger is not a phase change heat exchanger.
  • Carbon dioxide (CO2) is preferably used as working fluid.
  • the working fluid may also comprise ammonia (NH3) and/or an organic fluid (such as methane, propane or butane) and/or a refrigerant fluid (such as R 134a (1, 1, 1, 2-Tetrafluoroethane) , R245 fa (1, 1, 1, 3, 3-Pentafluoropropane) ) .
  • NH3 ammonia
  • an organic fluid such as methane, propane or butane
  • a refrigerant fluid such as R 134a (1, 1, 1, 2-Tetrafluoroethane) , R245 fa (1, 1, 1, 3, 3-Pentafluoropropane)
  • Figure 1 shows a simplified schematic diagram of an electro ⁇ thermal energy storage system in accordance with the present invention
  • Figure 2 shows the electro-thermal energy storage from Fig. 1 in a charging mode
  • Figure 3 shows the electro-thermal energy storage from Fig. 1 in a discharging mode
  • FIG. 4 shows a simplified schematic diagram of another preferred embodiment of an electro-thermal energy storage system in accordance with the present invention.
  • Figure 5 shows T-s-diagrams of exemplary thermodynamic cycles
  • FIG. 6 shows a simplified schematic diagram of another preferred embodiment of an electro-thermal energy storage system in accordance with the present invention.
  • Figure 1 shows a simplified schematic diagram of a preferred embodiment of an electro-thermal energy storage system in accordance with the present invention.
  • the system comprises a hot thermal storage arrangement 1, which in turn comprises a hot storage heat exchanger 11, a first storage tank 121 for a first thermal storage medium, in particular for storing first thermal storage medium at a low temperature ⁇ , ⁇ and a second storage tank 122 for the first thermal storage medium, in particular for storing first thermal storage medium at a high temperature T iih > ⁇ , ⁇ .
  • a hot thermal storage arrangement which in turn comprises a hot storage heat exchanger 11, a first storage tank 121 for a first thermal storage medium, in particular for storing first thermal storage medium at a low temperature ⁇ , ⁇ and a second storage tank 122 for the first thermal storage medium, in particular for storing first thermal storage medium at a high temperature T iih > ⁇ , ⁇ .
  • water may be used as first thermal storage medium.
  • the system further comprises a cold thermal storage arrangement 2, which in turn comprises a cold storage heat exchanger 21, and a third storage tank 223 for a second thermal storage medium, preferably also water.
  • the electro-thermal energy storage system shown in Fig. 1 further comprises a thermodynamic cycle unit which, when in operation, executes one of a plurality of thermodynamic cycles.
  • the thermodynamic cycle unit comprises a plurality of fluid conduits for circulating a working fluid through the hot storage heat exchanger 11 and the cold storage heat exchanger 21.
  • a plurality of valves 30a, 30b, 30c, 30d, 30e and 30f allow to switch between different working fluid paths, in particular for switching between a charging and a discharging mode of the electro-thermal energy storage system.
  • Figure 2 shows the electro-thermal energy storage system from Fig. 1 in a charging mode.
  • thermo energy is transferred from the working fluid to a first thermal storage medium, in particular water, which flows from the first storage tank 121 of the hot thermal storage arrangement 1 to the second storage tank 122 of the hot thermal storage arrangement 1, e.g. under influence of a pump.
  • the working fluid After exiting the hot storage heat exchanger 11, the working fluid enters a work recovering expander 31' where its pressure is reduced under recovery of work Wout,0' which may preferably be used to drive a generator for generating electric energy, or may be used to provide at least part of the work Wj_ n , in particular W ⁇ n, 2r by means of mechanical coupling, e.g. to the low pressure compressor block 322 ' .
  • the working fluid enters the cold storage heat exchanger 21, where thermal energy is transferred from the second thermal storage medium to the working fluid, preferably causing the second thermal storage medium to
  • cold may be stored in latent form in cold thermal storage arrangement 2.
  • an evaporative ice storage arrangement as described in European patent application EP11169311, is used as cold thermal storage arrangement 2.
  • ice may be stored on coils as e.g. in commercially available ice storage systems which are as such known to a person skilled in the art.
  • cold may be stored in sensible form, in particular by providing a fourth storage tank for storing second thermal storage medium at a high temperature T 2 , h > ⁇ 2, ⁇ , where ⁇ 2, ⁇ is a low temperature of second thermal storage medium in the third storage tank 223, and T iih > ⁇ 2 , ⁇ , so that second thermal storage medium may flow through cold storage heat exchanger 21 from the fourth storage tank to the third storage tank 223 in charging mode, and vice versa in discharging mode, which will be described below.
  • FIG. 3 shows the electro-thermal energy storage system from Fig. 1 in discharging mode.
  • a working fluid pump 31 pumps condensed working fluid into hot storage heat exchanger 11.
  • thermal energy is transferred from the first thermal storage medium - which in discharging mode flows from the second storage tank 122 of the hot thermal storage arrangement to the first storage tank 121 of the hot thermal storage arrangement 1 -to the working fluid, so that the working fluid is vaporized.
  • the vaporized working fluid then enters a turbine unit.
  • the turbine unit comprises a high pressure turbine block 321 as a first turbine and a low pressure turbine block 322 as a second turbine and is configured to expand the working fluid under recovery of work Kout, 1 an d Due to the expansion, which is preferably at least approximately isentropic, a pressure and temperature of the working fluid is decreased. Subsequently, the working fluid enters cold storage heat exchanger 21, where thermal energy is transferred from the working fluid to the second thermal storage medium, thus causing the working fluid to condense and preferably the second thermal storage medium to melt .
  • Each of the turbine blocks 321, 322 and compressor blocks 321', 322' may have a single or multiple stages, and may be of either radial or axial type.
  • the turbine blocks 321, 322 may be separate, individual turbines, but may also be parts of an integrated two-block turbine with integrated air cooler. The same applies to compressor blocks 321', 322'.
  • An air cooler 33 is provided in a working fluid path between low pressure turbine block 322 and high pressure turbine block 321.
  • Working fluid passing through the air cooler 33 may transfer thermal energy to an environment of the ETES system, in particular to ambient air surrounding the ETES system. Removing heat from the working fluid in this manner allows to balance the overall losses of the ETES system.
  • a control of the air cooler 33, and/or the turbine blocks 321 and 322, and/or the compressor blocks, needs to allow for variations in an ambient temperature, e.g. by adjusting the cooling performance of the air cooler 33, e.g. through a
  • Valves 30e and 30f from Fig. 1 are not shown in Figs. 2 and 3 to improve readability.
  • the invention could also be realized with fixed working fluid paths as shown in Figs. 2 and 3.
  • a single compressor could be used in this case rather than the two compressor blocks 321', 322'.
  • FIG 4 shows a simplified schematic diagram of another preferred embodiment of an electro-thermal energy storage system in accordance with the present invention.
  • the system comprises a revertible
  • thermodynamic machine unit comprising a first thermodynamic machine block 321'' and a second thermodynamic machine block 322 ' ' , which function as second and first compressor in charging mode, and as first and second turbine in discharging mode.
  • Air cooler 33' is again provided in a working fluid path between first thermodynamic machine block 321'' and second thermodynamic machine block 322 ' ' .
  • cooling performance of air cooler 33' can be individually adjusted for charging mode and discharging mode, and air cooler 33' may be completely switched off for each mode.
  • an auxiliary revertible thermodynamic machine may be foreseen in any of the embodiments described above or below, which is capable of providing a functionality of both working fluid pump 31 and work recovering expander 31' by reverting a direction of rotation of the auxiliary revertible thermodynamic machine.
  • Figure 5 shows T-s-diagrams of exemplary thermodynamic cycles that working fluid in the above described embodiments may be subjected to.
  • Fig. 5a shows a T-s-diagram of a first thermodynamic cycle which the working fluid undergoes in charging mode.
  • the working fluid enters the cold storage heat exchanger 21 of the cold storage arrangement 2, where it absorbs solidification energy from the second thermal storage medium, leading to an increase in the working fluid's entropy s.
  • working fluid enters the low pressure compressor block 322 ' , at point cl2 the high pressure compressor block 321', where it is compressed to a maximum pressure of 14 MPa.
  • working fluid enters the hot storage heat exchanger 11 of the hot storage arrangement 1, where it transfers heat to the first thermal storage medium and is in return cooled down to approximately 10°C.
  • working fluid enters the work recovering expander 31', where it is at least approximately isentropically expanded and returned to point c40.
  • Fig. 5b shows a T-s-diagram of a second thermodynamic cycle which the working fluid undergoes in discharging mode.
  • the working fluid enters the cold storage heat exchanger 21 of the cold storage arrangement 2, where it melts solidified second thermal storage medium, leading to an decrease in the working fluid's entropy s.
  • working fluid enters the working fluid pump 31, by which it is pumped into the hot storage heat exchanger 11 of the hot storage arrangement 1, which it enters at point d30.
  • working fluid is heated to approximately 120°C by heat exchange with the second thermal storage medium, raising its pressure to the maximum value of 14 Mpa.
  • working fluid enters the high pressure turbine 321, where it is expanded under recovery of work Kout, 1 as described above, and thus is cooled to around 45°C.
  • working fluid enters the air cooler 33, where it is cooled to around 35°C at an at least approximately constant pressure of around 6 Mpa.
  • working fluid enters the low pressure turbine 322, where it is further expanded under recovery of work Kout,2 as also described above, and returned to point d20.
  • FIG. 6 shows a simplified schematic diagram of another preferred embodiment of an electro-thermal energy storage system in accordance with the present invention.
  • the embodiment shown in Fig. 6 is similar to the one from Fig. 1, but comprises an additional hot thermal storage arrangement 1 ' .
  • An additional air cooler 33' ' is located between the hot thermal storage arrangement 1 and the additional hot thermal storage arrangement 1'.
  • Valves 30g allow to selectively direct a part or all of the working fluid flowing between the hot thermal storage arrangement 1 and the additional hot thermal storage arrangement 1' through the additional air cooler 33' ', or to bypass the latter completely.
  • the additional air cooler 33'' may be
  • a fluid connection - including a control valve and possibly a pump - for thermal storage medium is provided between second storage tank 122 of hot thermal storage arrangement 1 and a first storage tank 121' of the additional hot thermal storage arrangement 1 ' to allow for balancing respective levels of thermal storage medium (not shown in Fig. 6) .
  • additional hot thermal storage arrangement 1 ' may advantageously be provided adjacent to the additional hot thermal storage arrangement 1 ' , preferably in series with further additional air coolers, in particular to allow for split streams and/or varying flow rates of working fluids between parts of a split stream heat exchanger and/or individual heat exchangers, as e.g. described in EP 2 275 649 Al or EP 2 182 179 Al .
  • first thermal storage medium may be cooled by releasing some thermal energy to the ambient, in particular in a supplementary heat exchanger.
  • An electro-thermal energy storage system comprising
  • a hot thermal storage arrangement (1) comprising a hot
  • a cold thermal storage arrangement (2) comprising a cold storage heat exchanger (21),
  • thermodynamic cycle unit configured to i) transfer thermal energy from the cold storage arrangement (2) to the hot storage arrangement (1) in a charging mode
  • thermodynamic cycle unit comprising
  • a fluid circuit for circulating a working fluid through the hot storage heat exchanger as well as through the cold storage heat exchanger comprising
  • thermodynamic cycle unit comprises
  • said second turbine being connected in series with the first turbine so that working fluid may flow from the first to the second turbine in the discharging mode, iii) an intercooling heat exchanger (33) located in the
  • the electro-thermal energy storage system of item 1 wherein the intercooling heat exchanger (33) is configured to cool working fluid flowing from the first turbine (321) to the second turbine (322) in the discharging mode.
  • the electro-thermal energy storage system of item 1 wherein the intercooling heat exchanger (33) is configured to cool working fluid flowing from the first compressor to the second compressor in the charging mode.
  • the electro-thermal energy storage system of item 1, wherein the intercooling heat exchanger (33) is an air cooler.
  • the electro-thermal energy storage system according to any preceding item, wherein the working fluid is CO2 ⁇
  • the electro-thermal energy storage system according to any preceding item, wherein the cold thermal storage medium is water .
  • the electro-thermal energy storage system according to any preceding item, wherein the cold thermal storage medium is a mixture of water and at least one further component.
  • the electro-thermal energy storage system according to any preceding item, comprising one or more valves (30a, 30b, 30c, 30d, 30e, 30f) allowing for selective opening, closing and/or throttling one or more fluid connections.
  • a method for storing and retrieving energy in an electrothermal energy storage system comprising the steps of
  • thermodynamic cycle i) transferring thermal energy from a cold thermal storage arrangement (2) to a hot thermal storage arrangement (1) ii) by means of a first thermodynamic cycle
  • thermodynamic cycle process comprises the steps of

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Abstract

L'invention concerne un système et un procédé de stockage d'énergie électrothermique, le système comprenant : un ensemble (1) de stockage thermique chaud comprenant un échangeur de chaleur de stockage chaud (11); un ensemble de stockage thermique froid (2) comprenant un échangeur de chaleur de stockage froid (21); une unité de cycle thermodynamique conçue pour transférer de l'énergie thermique de l'ensemble de stockage froid à l'ensemble de stockage chaud dans un mode de charge, et pour convertir de l'énergie thermique provenant de l'ensemble de stockage chaud en travail et, de préférence, ensuite en énergie électrique dans un mode de décharge. L'unité de cycle thermodynamique comprend un circuit de fluide pour faire circuler un fluide de travail à travers l'échangeur de chaleur de stockage chaud ainsi qu'à travers l'échangeur de chaleur de stockage froid. Le circuit de fluide comprend en outre une pompe (31) pour maintenir en circulation un fluide de travail dans le mode de décharge et une première turbine (321) pour détendre le fluide de travail dans le mode de décharge. L'unité de cycle thermodynamique comprend une deuxième turbine (322) pour détendre le fluide de travail dans le mode de décharge, ladite deuxième turbine étant connectée en série à la première turbine de telle sorte que le fluide de travail puisse s'écouler de la première à la deuxième turbine dans le mode de décharge, et un échangeur de chaleur de refroidissement intermédiaire (33) situé entre la première et la deuxième turbine dans le circuit de fluide.
PCT/EP2013/067162 2012-08-17 2013-08-16 Système de stockage d'énergie électrothermique et procédé de stockage d'énergie électrothermique WO2014027093A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP13750080.7A EP2909451B1 (fr) 2012-08-17 2013-08-16 Système de stockage d'énergie électrothermique et procédé pour stocker de l'énergie électrothermique
PL13750080T PL2909451T3 (pl) 2012-08-17 2013-08-16 System magazynowania energii elektrotermicznej i sposób magazynowania energii elektrotermicznej
DK13750080.7T DK2909451T3 (da) 2012-08-17 2013-08-16 Elektrotermisk energilagringssystem og fremgangsmåde til lagring af elektrotermisk energi

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP12180815.8A EP2698506A1 (fr) 2012-08-17 2012-08-17 Système de stockage d'énergie électrothermique et procédé pour stocker de l'énergie électrothermique
EP12180815.8 2012-08-17

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WO2014027093A1 true WO2014027093A1 (fr) 2014-02-20

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DK (1) DK2909451T3 (fr)
PL (1) PL2909451T3 (fr)
WO (1) WO2014027093A1 (fr)

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US20170159498A1 (en) * 2012-09-27 2017-06-08 X Development Llc Pumped Thermal Systems with Dedicated Compressor/Turbine Pairs
US10436109B2 (en) 2016-12-31 2019-10-08 Malta Inc. Modular thermal storage
CN110366632A (zh) * 2016-12-29 2019-10-22 马耳他股份有限公司 使用外部空气进行闭合循环库存控制
US10458284B2 (en) 2016-12-28 2019-10-29 Malta Inc. Variable pressure inventory control of closed cycle system with a high pressure tank and an intermediate pressure tank
US10801404B2 (en) 2016-12-30 2020-10-13 Malta Inc. Variable pressure turbine
US10907513B2 (en) 2010-03-04 2021-02-02 Malta Inc. Adiabatic salt energy storage
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PL2909451T3 (pl) 2021-12-20

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