WO2013164562A1 - Appareil permettant de stocker de l'énergie et procédé permettant de faire fonctionner un système de stockage d'énergie comprenant un tel appareil - Google Patents

Appareil permettant de stocker de l'énergie et procédé permettant de faire fonctionner un système de stockage d'énergie comprenant un tel appareil Download PDF

Info

Publication number
WO2013164562A1
WO2013164562A1 PCT/GB2013/050423 GB2013050423W WO2013164562A1 WO 2013164562 A1 WO2013164562 A1 WO 2013164562A1 GB 2013050423 W GB2013050423 W GB 2013050423W WO 2013164562 A1 WO2013164562 A1 WO 2013164562A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat
gas
during
store
cycle
Prior art date
Application number
PCT/GB2013/050423
Other languages
English (en)
Inventor
Jonathan Sebastian Howes
James Macnaghten
Original Assignee
Isentropic 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 Isentropic Ltd filed Critical Isentropic Ltd
Publication of WO2013164562A1 publication Critical patent/WO2013164562A1/fr

Links

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
    • F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
    • F01K17/02—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic
    • 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
    • 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
    • F01K3/06—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein the engine being of extraction or non-condensing type
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/14—Gas-turbine plants having means for storing energy, e.g. for meeting peak loads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/0056—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using solid heat storage material
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/14—Combined heat and power generation [CHP]

Definitions

  • the present invention relates to apparatus for storing energy, and particularly but not exclusively to apparatus for receiving and returning energy in the form of electricity (hereinafter referred to as "electricity storage” apparatus).
  • thermodynamic electricity storage system using thermal stores.
  • a hot store and a cold store are connected to each other by a compressor and expander (the latter is often referred to as a turbine in axial flow machinery).
  • a charging mode heat is pumped from one store to the other (i.e. heating the hot store and cooling the cold store) and in a discharge mode the system the process is reversed (i.e. with the cold store being used to cool gas prior to compression and heating in the hot store).
  • the systems can use a variety of different types of compressors and expanders, some examples are reciprocating, rotary screw, sliding vane, axial or centrifugal.
  • the systems can use a thermal storage media, such as a refractory like alumina, or a natural mineral like quartz.
  • the cycles used in the system of WO 2009/044139 may be run as closed cycle processes or as open cycle systems (e.g. where there is one stage that is at near ambient temperature, atmospheric pressure and the working fluid is air).
  • the working gas may advantageously be a monatomic gas such as argon which has a high isentropic index (i.e. for a given pressure change a higher temperature rise is achieved than for a diatomic gas such as nitrogen). This results in a lower peak system pressure which in turn lowers the amount of material required to contain the pressure and hence the cost of the thermal storage vessels.
  • the present applicant has identified the need for an improved heat storage system which allows potential for improved operation over the identified prior art.
  • apparatus for storing energy comprising: a first engine stage configured to act as a compressor during a charging phase of a cycle and as an expander during a discharging phase of the cycle; a first heat store for receiving and storing thermal energy from gas compressed by the first engine stage during the charging phase; a second engine stage configured to act as an expander during the charging phase to expand gas received from the first heat store and as a compressor during the discharging phase; a second heat store for transferring thermal energy to gas expanded by the expander during the charging phase; a heat rejection device for dissipating unwanted heat from a gas flow; and control means (e.g.
  • a controller for varying the degree of thermal coupling between the gas flow and the heat rejection device or varying the level of heat rejection performance provided by the heat rejection device between a lower level during a first part of the cycle and a higher level during a second part of the cycle, with the change from the lower level to the higher level being configured to provide an increase in heat rejection during the second part of the cycle for boosting energy density over the cycle.
  • energy storage apparatus in which the system datum temperature can be artificially lowered below a natural level achievable through continually connected heat exchangers to improve energy capacity and power output during periods when additional storage or output are required. Whilst this increase in storage or output will reduce efficiency of operation, for situations where the second phase of the cycle is arranged to coincide substantially with a period when electricity is very low cost (e.g. free) or in situations in which the apparatus is used in warm climates where storage and output may be limited by high ambient temperatures during periods of the day, this energy penalty may be worth paying for the added value of extra capacity and power output at peak times. Furthermore, where there is use for the heat generated by the decreased efficiency some or all of the increased heat output from the apparatus may be used in a further process.
  • the apparatus comprises a circuit (e.g. gas circuit) configured to allow gas to pass cyclically between the first and second heat stores via the first and second engine stages during at least one of the charging and discharging phase.
  • a circuit e.g. gas circuit
  • first and second engine stages each comprise separate compressor and expander devices. In another embodiment, the first and second engine stages each comprise a device configured to switch between operation as a compressor and operation as an expander.
  • the heat rejection device is configured to receive heat from at least a portion of the gas flow that is directed to the heat rejection device and the control means is configured to vary the degree of thermal coupling by varying the proportion of the gas flow that is directed to the heat rejection device relative the gas flow that bypasses the heat rejection device.
  • the level of heat rejection performance provided by the heat rejection device is varied by increasing or decreasing a flow of coolant through the heat rejection device or varying a lower temperature of the coolant or a combination of both of these techniques.
  • At the lower level heat rejection from the gas flow via the heat rejection device is substantially zero (e.g. substantially all of the gas flow bypasses the heat rejection device (e.g. thermal coupling is substantially zero) or the heat rejection performance provided by the heat rejection device is reduced to a lower limit by stopping a heat rejection process performed by the heat rejection device).
  • the second part of the cycle occurs substantially during the charging phase of the cycle.
  • the second part of the cycle substantially corresponds to the charging phase of the cycle.
  • the heat rejection device comprises heat pump means (e.g. heat pump) operable to remove heat from the gas.
  • the heat pump means comprises means for compressing the at least a portion of gas flow (e.g. a further compressor) and a heat exchanger for transferring heat from the at least a portion of gas flow prior to expansion of the at least a portion of gas flow (e.g. by the expander or by a further expander).
  • the heat pump means is a Brayton cycle heat pump.
  • the heat pump means is thermally coupled to the apparatus by a heat exchanger.
  • the heat pump means is operable to remove heat from the apparatus at a point between the first heat store and the second engine stage.
  • the heat pump means is operable to remove heat from the apparatus at a point between the second heat store and the first engine stage.
  • the first engine stage is configured to act as a multi-stage compressor comprising first and second (e.g. final) compressor stages and the heat rejection device comprises a heat exchanger connectable between the first and second compressor stages to remove heat from gas compressed by the first compressor stage prior to compression of the gas by the second compressor stage.
  • the apparatus further comprises at least one fixed heat exchanger with a constant degree of thermal coupling to the gas flow for dissipating unwanted heat from the gas flow (e.g. to ambient).
  • a method of operating an energy storage system comprising: during a charging phase of a cycle: compressing a gas using a first engine stage; transferring heat from the compressed gas to first heat store for receiving and storing thermal energy from the compressed gas; expanding the gas using a second engine stage after heat from the gas has been transferred to the first heat store; and transferring heat from a second heat store to the expanded gas during the charging phase; and during a discharging phase of the cycle: cooling a gas by transferring heat from the gas to the second heat store; compressing the gas cooled by the second heat store; heating the compressed gas by transferring heat from the first heat store to the gas; and expanding the gas heated by the first heat store to generate a power output; characterised by the step of varying the degree of thermal coupling between a gas flow and a heat rejection device configured to dissipate unwanted heat from the system or varying the level of heat rejection performance provided by the heat rejection device between a lower level during a first part of the cycle
  • the heat rejection device is configured to receive heat from at least a portion of the gas flow that is directed to the heat rejection device and the step of varying the degree of thermal coupling comprises varying the proportion of the gas flow that is directed to the heat rejection device relative to the gas flow that bypasses the heat rejection device.
  • the level of heat rejection performance provided by the heat rejection device is varied by increasing or decreasing a flow of coolant through the heat rejection device or varying a lower temperature of the coolant or a combination of both of these techniques.
  • At the lower level heat rejection from the gas flow via the heat rejection device is substantially zero (e.g. substantially all of the gas flow is made to bypass the heat rejection device or the heat rejection performance provided by the heat rejection device is reduced to a lower limit by stopping a heat rejection process performed by the heat rejection device).
  • the second part of the cycle occurs substantially during the charging phase of the cycle.
  • the second part of the cycle substantially corresponds to the charging phase of the cycle.
  • the heat rejection device comprises heat pump means (e.g. heat pump) operable to remove heat from the gas.
  • heat pump means e.g. heat pump
  • the heat pump means comprises means for heating the at least a portion of gas flow (e.g. a further compressor) and a heat exchanger for transferring heat from the at least a portion of gas flow prior to expansion of the at least a portion of gas flow (e.g. by the expander or by a further expander).
  • the heat pump means is thermally coupled to the apparatus by a heat exchanger.
  • the heat pump means is operable to remove heat from the apparatus at a point between the first heat store and the second engine stage. In one embodiment, the heat pump means is operable to remove heat from the apparatus at a point between the second heat store and the first engine stage.
  • the step of compressing the gas during the charging phase comprises compressing the gas using first and second compressor stages of a multi-stage compressor and the heat rejection device comprises a heat exchanger connectable between the first and second (e.g. final) compressor stages to remove heat from gas compressed by the first compressor stage prior to compression of the gas by the second compressor stage.
  • apparatus for storing energy comprising: a first engine stage configured to act as a compressor during a charging phase of a cycle and as an expander during a discharging phase of the cycle; a first heat store for receiving and storing thermal energy from gas compressed by the first engine stage during the charging phase; a second engine stage configured to act as an expander during the charging phase to expand gas received from the first heat store and as a compressor during the discharging phase; a second heat store for transferring thermal energy to gas expanded by the expander during the charging phase; and a heat rejection device for dissipating unwanted heat from a gas flow at a point between the first heat store and the second engine stage; wherein the second engine stage is operable during the discharging phase to compress gas cooled by the second heat store to an elevated pressure exceeding mean peak gas pressure in the first heat store during the charging phase.
  • energy storage apparatus in provided in which additional heat is dissipated during the discharging phase (by effectively pumping heat from the second heat store to the heat rejection device) providing the potential for an increase in energy density during a subsequent charging phase since at least a part of the second heat store will be at a lower temperature than if the additional heat had not been dissipated whilst the increase in temperature of at least a part of the first heat store is less then the reduction in temperature of the at least a part of the second heat store as a result of the operation of the heat rejection device.
  • this technique for increasing energy density is achieved by using the second engine stage without the need for any further compressor/expander stage.
  • the elevated pressure is at least 10% higher than the mean peak gas pressure in the first heat store during the charging phase.
  • the elevated pressure may be at least 20% higher than the mean peak gas pressure in the first heat store during the charging phase.
  • a method of operating an energy storage system comprising: during a charging phase of a cycle: compressing a gas using a first engine stage; transferring heat from the compressed gas to first heat store for receiving and storing thermal energy from the compressed gas; expanding the gas using a second engine stage after heat from the gas has been transferred to the first heat store; and transferring heat from a second heat store to the expanded gas; and during a discharging phase of the cycle: cooling a gas by transferring heat from the gas to the second heat store; compressing the gas cooled by the second heat store and subsequently dissipating unwanted heat from the gas flow; heating the compressed gas by transferring heat from the first heat store to the gas; and expanding the gas heated by the first heat store to generate a power output
  • the elevated pressure is at least 10% higher than the mean peak gas pressure in the first heat store during the charging phase.
  • the elevated pressure may be at least 20% higher than the mean peak gas pressure in the first heat store during the charging phase.
  • apparatus for storing energy comprising: a first engine stage configured to act as a compressor during a charging phase of a cycle and as an expander during a discharging phase of the cycle; a first heat store for receiving and storing thermal energy from gas compressed by the first engine stage during the charging phase; a second engine stage configured to act as an expander during the charging phase to expand gas received from the first heat store and as a compressor during the discharging phase; a second heat store for transferring thermal energy to gas expanded by the expander during the charging phase; heat pump means (e.g. heat pump) operable to remove unwanted heat from a gas flow.
  • heat pump means e.g. heat pump
  • the heat pump means comprises means for heating the at least a portion of gas flow (e.g. a further compressor) and a heat exchanger for transferring heat from the at least a portion of gas flow prior to expansion of the at least a portion of gas flow (e.g. by the expander or by a further expander).
  • the heat pump means is thermally coupled to the apparatus by a heat exchanger. In one embodiment, the heat pump means is operable to remove heat from the apparatus at a point between the first heat store and the second engine stage.
  • the heat pump means is operable to remove heat from the apparatus at a point between the second heat store and the first engine stage.
  • Figures 1A and IB show a schematic illustration of an electricity storage system of the type disclosed in WO 2009/044139 during a charging phase and discharging phase respectively;
  • Figures 2A and 2B show an electricity storage system according to a first embodiment of the present invention during a charging phase and a discharging phase respectively;
  • Figure 3 shows an electricity storage system according to a second embodiment of the present invention during a charging phase
  • Figures 4 A and 4B show an electricity storage system according to a third embodiment of the present invention during a charging phase and a discharging phase respectively;
  • Figures 5A and 5B show an electricity storage system according to a fourth embodiment of the present invention during a charging phase and a discharging phase respectively.
  • Figures 1A and IB show an electricity storage system 100 of the type disclosed in WO 2009/044139 comprising an insulated hot storage vessel 120 housing a first gas- permeable particulate heat storage structure 121, cold storage vessel 110 housing a second gas-permeable particulate heat storage structure 111, first and second multi-stage compressor/expanders 130, 140, first and second heat exchangers 150, 160 and interconnecting pipes 101, 102, 103 and 104 forming a gas circuit 105 for conveying working gas around the system.
  • the gas then enters hot storage vessel 120 and passes down through particulate heat storage structure 121, where the gas is cooled.
  • the now cooler gas leaves particulate heat storage structure 121 and enters interconnecting pipe 103 where it is exposed to second heat exchanger 160 to bring the temperature of the gas down to a temperature closer to ambient temperature.
  • the charging process can continue until the hot and cold stores are 'fully charged' or stop earlier if required.
  • This overall charging process absorbs energy that is normally supplied from other generating devices via the electric grid.
  • the multi-stage compressor/expanders 130 and 140 are driven by a mechanical device, such as an electric motor (not shown).
  • high temperature gas at a higher pressure enters interconnecting pipe 102 and is expanded by multi-stage compressor/expander 130 to a lower pressure.
  • the gas is cooled during this expansion and passes via interconnecting pipe 101 where it is exposed to first heat exchanger 150 to bring the temperature of the gas down to a temperature closer to ambient temperature.
  • the gas then enters cold storage vessel 110 and passes down through particulate heat storage structure 111 where the gas is further cooled.
  • the now colder gas leaves particulate heat storage structure 111 and enters interconnecting pipe 104.
  • the gas exits interconnecting pipe 104 and enters compressor/expander 140 where the gas is compressed to the higher pressure.
  • the gas then enters hot storage vessel 120 and passes up through particulate heat storage structure 121 where the gas is heated.
  • the now high temperature gas leaves particulate heat storage structure 121 and passes into interconnecting pipe 102 and is expanded by multi-stage compressor/expander 130 with the energy of expansion being used to generate electricity for the electric grid.
  • the discharging process can continue until the hot and cold stores are 'fully discharged' or stop earlier if required.
  • the overall discharging process generates energy that is normally supplied in an electrical form (e.g. back to the electric grid).
  • the multi-stage compressor/expanders 130 and 140 drive a mechanical device, such as an electric generator (not shown).
  • material properties limit the system to a maximum temperature T max of 500 °C.
  • First and second heat exchangers 150, 160 are designed to bring Tdatum down to as close to ambient air temperature as possible.
  • the larger the pumped temperature difference between Tdatum and T max the greater the energy stored during charging/electrical output during discharging.
  • Tdatum is generally 10-20°C hotter than external ambient depending upon the size of the heat exchangers 150,160.
  • the higher Tdatum the lower the compression ratio that will result in a peak temperature of 500 °C. Accordingly, the energy density stored and output power generated by system 100 may be significantly lower in a warmer climate country than in a cooler climate country.
  • peak electricity demand is driven by air conditioning, i.e. discharge of the system is required during periods when the ambient temperature is at its highest. countries with large differences in temperature could see large swings in storage capacity.
  • Figures 2A and 2B show an electricity storage system 200 based on system 100 and comprising an insulated hot storage vessel 220 housing a first gas-permeable particulate heat storage structure 221, cold storage vessel 210 housing a second gas-permeable particulate heat storage structure 211, first and second multi-stage compressor/expanders 230, 240, first and second heat exchangers 250, 260 and interconnecting pipes 201, 202, 203 and 204 forming a gas circuit 205 for conveying working gas around the system.
  • a controller 270 acts to direct working gas cooled by second heat exchanger 260 along a bypass pipe 206 connecting a Brayton cycle heat pump 280 between the second heat exchanger 260 and second compressor/expanders 240 for working directly on the working gas of the main system.
  • Heat pump 280 comprises a compressor 282 for compressing working gas received form the second heat exchanger, a further heat exchanger 284 for receiving heat from working gas after compression by compressor 282 and dissipating heat from the system (e.g. to atmosphere), and an expander 286 for receiving working gas from further heat exchanger 284 and expanding the working gas to a temperature that is lower than the temperature of the gas exiting the second heat exchanger 260.
  • system 200 allows the energy storage capacity to be increased during periods in which increased capacity is required or the efficiency penalty justified (e.g. to meet demand during a high electricity price period or to
  • heat pump 280 By placing heat pump 280 on the high pressure side of the system between hot storage vessel 220 and second multi-stage compressor/expander 240, heat pump 280 (which processes the same amount of gas as each compressor/expander 230, 240) may be smaller and work more efficiently than if positioned on a lower pressure side of the system.
  • Figure 3 shows an electricity storage system 300 based on system 200 and comprising an insulated hot storage vessel 320 housing a first gas-permeable particulate heat storage structure 321, cold storage vessel 310 housing a second gas-permeable particulate heat storage structure 311, first and second multi-stage compressor/expanders
  • system 300 comprises an external heat pump 380 thermally coupled to gas circuit 305 at a point between first heat exchanger 350 and first multi-stage compressor/expanders 330
  • a controller 370 operates to switch external heat pump 380 on during the charging phase to generate a flow of low temperature coolant through further heat exchanger 385 for receiving heat from the working gas of the system. In this way, the working gas is cooled below a temperature that can be achieved by just cooling gas via first heat exchanger 350.
  • controller 370 operates to switch external heat pump 380 off so that flow of coolant is stopped and coolant is allowed to rise to substantially ambient temperature with heat transfer from the working gas to the coolant being minimal in this mode of operation.
  • heat pump 380 when heat pump 380 is switched on during the charging phase there is an increase in heat rejection relative to the level of heat rejection if heat pump 380 was not switched on.
  • This increase in heat rejection during the charging phase allows an increased pressure ratio between hot storage vessel 320 and cold storage vessel 310 and acts to lower the temperature of gas entering cold storage vessel 310 from compressor/expander 340 during charging, for boosting energy density over the complete charge/discharge cycle.
  • Figures 4 A and 4B show an electricity storage system 400 based on system 100 and comprising an insulated hot storage vessel 420 housing a first gas-permeable particulate heat storage structure 421, cold storage vessel 410 housing a second gas-permeable particulate heat storage structure 411, first and second multi-stage compressor/expanders 430, 440, first and second heat exchangers 450, 460 and interconnecting pipes 401, 402, 403 and 404 forming a gas circuit 405 for conveying working gas around the system.
  • a controller 470 acts to direct working gas along a bypass pipe 406 connecting a further heat exchanger 480 between first and last stages of first multi-stage compressor/expander 430.
  • Figures 5 A and 5B show an electricity storage system 500 based on system 100 and comprising an insulated hot storage vessel 520 housing a first gas-permeable particulate heat storage structure 521, cold storage vessel 510 housing a second gas-permeable particulate heat storage structure 511, first and second multi-stage compressor/expanders 530, 540, heat exchanger 560 and interconnecting pipes 501, 502, 503 and 504 forming a gas circuit 505 for conveying working gas around the system.
  • second multi-stage compressor/expander 540 is configured to compress gas cooled by cold storage vessel 510 to an elevated pressure exceeding mean peak gas pressure in the hot storage vessel 520 during the charging phase.
  • This change in the high pressure ratio between charging and discharging effectively acts to pump heat from an upper part of cold storage vessel 510 out though heat exchanger 560 to reduce the temperature of the upper part of cold storage vessel 510 by more than the temperature in a lower part of hot storage vessel 520 is increased.
  • second multi-stage compressor/expander 540 compresses gas to a pressure of approximately 15.1 bar (i.e. 3 bar higher than the approximately 12.1 bar mean peak gas pressure in the hot storage vessel 520 during the charging phase representing an approximately 25% increase in gas pressure.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Separation By Low-Temperature Treatments (AREA)

Abstract

La présente invention se rapporte à un appareil (300) permettant de stocker de l'énergie, ledit appareil comprenant : un premier étage de moteur (330) faisant office de compresseur pendant une phase de charge d'un cycle et faisant office de détendeur pendant une phase de décharge ; un premier accumulateur de chaleur (320) destiné à recevoir et à stocker l'énergie thermique provenant des gaz comprimés par le premier étage de moteur (330) pendant la phase de charge ; un second étage de moteur (340) faisant office de détendeur pendant la phase de charge pour dilater les gaz reçus du premier accumulateur de chaleur (320) et faisant office de compresseur pendant la phase de décharge ; un second accumulateur de chaleur (340) destiné à transférer l'énergie thermique aux gaz dilatés par le détendeur (340) pendant la phase de charge ; un dispositif de dissipation de chaleur (385/380) destiné à dissiper la chaleur non souhaitée provenant d'un flux gazeux ; et un moyen de commande (370) destiné à faire varier le degré de couplage thermique entre le flux gazeux et le dispositif de dissipation de chaleur ou son niveau de performance de dissipation de chaleur entre un niveau inférieur pendant une première partie du cycle (par exemple, une phase de décharge) et un niveau supérieur pendant une seconde partie du cycle (par exemple, une phase de charge) de sorte à augmenter la dissipation de chaleur pendant la seconde partie (de telle sorte que, pendant la charge, le gaz entre dans le second accumulateur de chaleur à une température réduite) pour augmenter la densité d'énergie pendant tout le cycle (par exemple, un cycle de charge/décharge complet).
PCT/GB2013/050423 2012-04-30 2013-02-21 Appareil permettant de stocker de l'énergie et procédé permettant de faire fonctionner un système de stockage d'énergie comprenant un tel appareil WO2013164562A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB201207486A GB2501685A (en) 2012-04-30 2012-04-30 Apparatus for storing energy
GB1207486.0 2012-04-30

Publications (1)

Publication Number Publication Date
WO2013164562A1 true WO2013164562A1 (fr) 2013-11-07

Family

ID=46330523

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB2013/050423 WO2013164562A1 (fr) 2012-04-30 2013-02-21 Appareil permettant de stocker de l'énergie et procédé permettant de faire fonctionner un système de stockage d'énergie comprenant un tel appareil

Country Status (2)

Country Link
GB (1) GB2501685A (fr)
WO (1) WO2013164562A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017025466A1 (fr) 2015-08-09 2017-02-16 Peter Ortmann Dispositif et procédé de conversion d'énergie électrique en chaleur et de stockage de ladite chaleur
WO2017081186A1 (fr) 2015-11-10 2017-05-18 Peter Ortmann Dispositif d'accumulation courant-chaleur-courant et procédé de régulation de charge de ce dernier
WO2017093768A1 (fr) * 2015-12-03 2017-06-08 Cheesecake Energy Ltd. Système de stockage d'énergie
US10280803B2 (en) 2015-04-24 2019-05-07 Peter Ortmann Energy storage device and method for storing energy
CN112610292A (zh) * 2020-12-11 2021-04-06 北京前沿动力科技股份有限公司 一种深度调峰发电系统

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10094219B2 (en) 2010-03-04 2018-10-09 X Development Llc Adiabatic salt energy storage
WO2014052927A1 (fr) 2012-09-27 2014-04-03 Gigawatt Day Storage Systems, Inc. Systèmes et procédés de récupération et de stockage d'énergie
US10233787B2 (en) 2016-12-28 2019-03-19 Malta Inc. Storage of excess heat in cold side of heat engine
US11053847B2 (en) 2016-12-28 2021-07-06 Malta Inc. Baffled thermoclines in thermodynamic cycle systems
US10233833B2 (en) 2016-12-28 2019-03-19 Malta Inc. Pump control of closed cycle power generation system
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
US10221775B2 (en) 2016-12-29 2019-03-05 Malta Inc. Use of external air for closed cycle inventory control
US10801404B2 (en) 2016-12-30 2020-10-13 Malta Inc. Variable pressure turbine
US10436109B2 (en) 2016-12-31 2019-10-08 Malta Inc. Modular thermal storage
WO2019013898A1 (fr) * 2017-07-10 2019-01-17 Dresser-Rand Company Système de stockage d'énergie thermique pompée
CN115485459A (zh) 2019-11-16 2022-12-16 马耳他股份有限公司 泵送热电储存系统
EP4193041A1 (fr) 2020-08-12 2023-06-14 Malta Inc. Système d'accumulation d'énergie thermique par pompage avec intégration en chauffage à distance
US11454167B1 (en) 2020-08-12 2022-09-27 Malta Inc. Pumped heat energy storage system with hot-side thermal integration
US11396826B2 (en) 2020-08-12 2022-07-26 Malta Inc. Pumped heat energy storage system with electric heating integration
US11286804B2 (en) 2020-08-12 2022-03-29 Malta Inc. Pumped heat energy storage system with charge cycle thermal integration
US11480067B2 (en) 2020-08-12 2022-10-25 Malta Inc. Pumped heat energy storage system with generation cycle thermal integration
DK181030B1 (en) * 2021-03-31 2022-10-07 Stiesdal Storage As Thermal energy storage system with phase change material and method of its operation

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009044139A2 (fr) 2007-10-03 2009-04-09 Isentropic Limited Stockage d'énergie
US20100218500A1 (en) * 2007-10-19 2010-09-02 Saipem S.A. Installation and Methods for Storing and Methods for Storing and Restoring Electrical Energy Using a Piston-Type Gas Compression and Expansion Unit
US20100301614A1 (en) * 2007-05-11 2010-12-02 Saipem S.A Installation and Method for Storing and Returning Electrical Energy
EP2275649A1 (fr) * 2009-06-18 2011-01-19 ABB Research Ltd. Système de stockage d'énergie thermoélectrique avec un réservoir de stockage intermédiaire et procédé de stockage d'énergie thermoélectrique
EP2532843A1 (fr) * 2011-06-09 2012-12-12 ABB Research Ltd. Système de stockage d'énergie thermoélectrique doté d'un agencement évaporatif de stockage de glace et procédé de stockage d'énergie thermoélectrique

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2390473A1 (fr) * 2010-05-28 2011-11-30 ABB Research Ltd. Système de stockage d'énergie thermoélectrique et procédé de stockage d'énergie thermoélectrique

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100301614A1 (en) * 2007-05-11 2010-12-02 Saipem S.A Installation and Method for Storing and Returning Electrical Energy
WO2009044139A2 (fr) 2007-10-03 2009-04-09 Isentropic Limited Stockage d'énergie
US20100218500A1 (en) * 2007-10-19 2010-09-02 Saipem S.A. Installation and Methods for Storing and Methods for Storing and Restoring Electrical Energy Using a Piston-Type Gas Compression and Expansion Unit
EP2275649A1 (fr) * 2009-06-18 2011-01-19 ABB Research Ltd. Système de stockage d'énergie thermoélectrique avec un réservoir de stockage intermédiaire et procédé de stockage d'énergie thermoélectrique
EP2532843A1 (fr) * 2011-06-09 2012-12-12 ABB Research Ltd. Système de stockage d'énergie thermoélectrique doté d'un agencement évaporatif de stockage de glace et procédé de stockage d'énergie thermoélectrique

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10280803B2 (en) 2015-04-24 2019-05-07 Peter Ortmann Energy storage device and method for storing energy
WO2017025466A1 (fr) 2015-08-09 2017-02-16 Peter Ortmann Dispositif et procédé de conversion d'énergie électrique en chaleur et de stockage de ladite chaleur
WO2017081186A1 (fr) 2015-11-10 2017-05-18 Peter Ortmann Dispositif d'accumulation courant-chaleur-courant et procédé de régulation de charge de ce dernier
WO2017093768A1 (fr) * 2015-12-03 2017-06-08 Cheesecake Energy Ltd. Système de stockage d'énergie
US10920668B2 (en) 2015-12-03 2021-02-16 Cheesecake Energy Ltd. Energy storage system
CN112610292A (zh) * 2020-12-11 2021-04-06 北京前沿动力科技股份有限公司 一种深度调峰发电系统

Also Published As

Publication number Publication date
GB2501685A (en) 2013-11-06
GB201207486D0 (en) 2012-06-13

Similar Documents

Publication Publication Date Title
WO2013164562A1 (fr) Appareil permettant de stocker de l'énergie et procédé permettant de faire fonctionner un système de stockage d'énergie comprenant un tel appareil
CA2969575C (fr) Systeme de stockage d'energie thermique pompee employant un support de stockage thermique solide transportable
CA2653780C (fr) Dispositif compresseur ameliore
JP6571491B2 (ja) ヒートポンプ
US10358975B2 (en) Compressed air energy storage and power generation device
US8656712B2 (en) Energy storage
EP3186491B1 (fr) Procédé de refroidissement du gaz comprimé d'une installation de compresseur et installation de compresseur dans laquelle ce procédé est appliqué
EP2971620B1 (fr) Systèmes et procédés de gestion de chaleur perdue de basse qualité
JPH07224679A (ja) 圧縮空気エネルギー貯蔵方法及びシステム
US10892642B2 (en) Compressed air energy storage power generation apparatus and compressed air energy storage power generation method
US20120102987A1 (en) Inlet Air Cooling and Moisture Removal Methods and Devices in Advance Adiabatic Compressed Air Energy Storage Systems
US10794278B2 (en) Compressed air storage power generation device
WO2016203980A1 (fr) Dispositif de génération et de stockage d'énergie à air comprimé, et procédé de génération et de stockage d'énergie à air comprimé
JP2016211436A (ja) 圧縮空気貯蔵発電装置
EP2765281B1 (fr) Appareil de cycle de Rankine
JP6906013B2 (ja) ヒートポンプ
WO2024075336A1 (fr) Dispositif de stockage d'énergie à air comprimé et dispositif de pompe à chaleur

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 13713475

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 13713475

Country of ref document: EP

Kind code of ref document: A1