EP2587005A1 - Système de stockage d'énergie thermoélectrique avec échange thermique régénératif et procédé de stockage d'énergie thermoélectrique - Google Patents

Système de stockage d'énergie thermoélectrique avec échange thermique régénératif et procédé de stockage d'énergie thermoélectrique Download PDF

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Publication number
EP2587005A1
EP2587005A1 EP11187317.0A EP11187317A EP2587005A1 EP 2587005 A1 EP2587005 A1 EP 2587005A1 EP 11187317 A EP11187317 A EP 11187317A EP 2587005 A1 EP2587005 A1 EP 2587005A1
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EP
European Patent Office
Prior art keywords
thermal storage
working fluid
hot
storage arrangement
heat exchanger
Prior art date
Legal status (The legal status 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 status listed.)
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Application number
EP11187317.0A
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German (de)
English (en)
Inventor
Florian Buchter
Jaroslav Hemrle
Mehmet Mercangoez
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ABB Research Ltd Switzerland
ABB Research Ltd Sweden
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ABB Research Ltd Switzerland
ABB Research Ltd Sweden
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Application filed by ABB Research Ltd Switzerland, ABB Research Ltd Sweden filed Critical ABB Research Ltd Switzerland
Priority to EP11187317.0A priority Critical patent/EP2587005A1/fr
Priority to PCT/EP2012/069157 priority patent/WO2013064317A1/fr
Priority to PCT/EP2012/071534 priority patent/WO2013064524A1/fr
Publication of EP2587005A1 publication Critical patent/EP2587005A1/fr
Withdrawn legal-status Critical Current

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    • 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

Definitions

  • the present invention relates generally to the storage of electric energy. It relates in particular to a system and method for storing electrical energy in the form of thermal energy.
  • Base load generators such as nuclear power plants and generators with stochastic, intermittent energy sources such as wind turbines and solar panels, generate excess electrical power during times of low power demand.
  • Large-scale electrical energy storage systems are a means of diverting this excess energy to times of peak demand and balance the overall electricity generation and consumption.
  • thermoelectric energy storage converts excess electricity to heat in a charging cycle, stores the heat, and converts the heat back to electricity in a discharging cycle, when necessary.
  • TEES thermoelectric energy storage
  • Such an energy storage system is robust, compact, site independent and is suited to the storage of electrical energy in large amounts.
  • Thermal energy can be stored 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 combination of both.
  • the storage medium for the sensible heat can be a solid, liquid, or a gas.
  • the storage medium for the latent heat occurs via a change of phase and can involve any of these phases or a combination of them in series or in parallel.
  • the round-trip efficiency of an electrical energy storage system can be defined as the percentage of electrical energy that can be discharged from the storage in comparison to the electrical energy used to charge the storage, provided that the state of the energy storage system after discharging returns to its initial condition before charging of the storage.
  • the efficiencies of both modes need to be maximized inasmuch as their mutual dependence allows.
  • the charging cycle of a TEES system is also referred to as a heat pump cycle and the discharging cycle of a TEES system is also referred to as a heat engine cycle.
  • heat needs to be transferred from a hot working fluid to a thermal storage medium during the charging cycle and back from the thermal storage medium to the working fluid during the discharging cycle.
  • a heat pump requires work to move thermal energy from a cold source to a warmer heat sink. Since the amount of energy deposited at the hot side is greater than the compression work by an amount equal to the energy taken from the cold side (that is the heat absorbed by the working fluid at the low pressure), a heat pump deposits more heat per work input to the hot storage than resistive heating.
  • 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 TEES system.
  • the charging cycle of a known TEES system comprises a work recovering expander, an evaporator, a compressor and a heat exchanger, all connected in series by a working fluid circuit. Further, a cold storage tank and a hot storage tank containing a fluid thermal storage medium are coupled together via the heat exchanger. Whilst the working fluid passes through the evaporator, it absorbs heat from the ambient or from a thermal bath and evaporates.
  • the discharging cycle of a known TEES system comprises a pump, a condenser, a turbine and a heat exchanger, all connected in series by a working fluid circuit. Again, a cold storage tank and a hot storage tank containing a fluid thermal storage medium are coupled together via the heat exchanger.
  • the working fluid passes through the condenser, it exchanges heat energy with the ambient or the thermal bath and condenses.
  • the same thermal bath such as a river, a lake or a water-ice mixture pool, is used in both the charging and discharging cycles.
  • Figure 1 shows a temperature-entropy diagram of the heat transfer from the charging and discharging cycles in a known TEES system.
  • the charging cycle can be considered to start at reference A and follows an anti-clockwise direction.
  • the dashed curve A to B represents heating a working fluid in a heat exchanger as it flows from a cool heat exchanger to a compressor.
  • B to C in Figure 1 represents a compression process in which the temperature of the working fluid reaches a maximum and a relatively high pressure P2.
  • Solid line C to D indicates the working fluid flowing through the hot storage heat exchanger where heat is transferred to a thermal storage medium and thus the temperature of the working fluid drops.
  • the dashed curve between point D and E illustrates the working fluid passing through a heat exchanger where it delivers its remaining thermal energy to the working fluid flowing countercurrent on the low pressure side of the cycle.
  • Solid line E to F represents the expansion of the working fluid from state P2 to P1 and this recovered energy is transferred either mechanically or electrically to the compressor.
  • the working fluid is now at the lowest energy state in the cycle as it enters the cool storage heat exchanger and harvests thermal energy from the thermal storage medium illustrated by solid line F to A on Figure 1 .
  • the discharging cycle of the present invention may be considered to be the reverse of the above described charging cycle.
  • the vertical arrow to the left hand side of the diagram shows the large temperature span of the hot storage in a prior art system. In this example, between 130 °C and 570 °C.
  • the vertical arrow to the right hand side of the diagram shows the large temperature span of the cold storage in a prior art system. In this example, between 45 °C and 425 °C.
  • a disadvantage of the known art is that relatively large temperature spans are required for both hot side and cold side heat storage materials to reach high efficiencies in a TEES operation.
  • One possibility to retain high efficiency with lower temperature spans is to reduce the temperature differences and the corresponding thermodynamic irreversibility in the heat exchangers and in order to reduce these temperature differences fluid to fluid countercurrent-flow heat exchangers may be utilized.
  • this arrangement is only possible when the heat storage material can flow in a heat exchanger. It can be considered that fine granulated solids such as sand can be made to flow in a heat exchanger but the resulting wear out on heat exchanger walls will tremendously reduce the lifetime of the heat exchangers. Additionally the energy required to transport the solids are quite high and will cause excessive auxiliary losses, which will in turn reduce the TEES efficiency. Thus solids or phase change materials are unsuitable as thermal storage materials for TEES design.
  • water is a preferred thermal storage medium due to its high heat capacity and other amiable physical properties water.
  • the limited operating temperature range of water would increase the footprint of TEES systems.
  • the skilled person may consider increasing the temperature range of this thermal storage medium upwards by increasing the storage vessel pressure but such modification may also reduce overall safety and increase system costs.
  • molten salt is a known thermal storage medium, but at temperatures below 200°C use in a conventional TEES becomes impossible due to freezing.
  • thermoelectric energy storage having a high round-trip efficiency, whilst minimising the storage footprint in m 3 per kWh stored energy.
  • thermoelectric energy storage system for converting electrical energy into thermal energy to be stored and converted back to electrical energy with an improved round-trip efficiency.
  • This objective is achieved by a thermoelectric energy storage system according to claim 1 and a method according to claim 8. Preferred embodiments are evident from the dependent claims.
  • thermoelectric energy storage system having a charging cycle for providing thermal energy to a hot thermal storage arrangement, and a discharging cycle for generating electricity by retrieving the thermal energy from the hot thermal storage arrangement.
  • the thermoelectric energy storage system comprises a working fluid circuit adapted to circulate a gaseous working fluid through the hot thermal storage arrangement and a cold thermal storage arrangement.
  • the hot thermal storage arrangement comprises a heat exchanger and at least two hot storage tanks coupled via a hot storage heat exchanger.
  • the cold thermal storage arrangement comprises a heat exchanger and at least two cold storage tanks coupled via a cold storage heat exchanger.
  • a further heat exchanger is adapted to further cool the working fluid at the output of the hot thermal storage arrangement during the charging cycle, and the further heat exchanger is adapted to pre-heat the working fluid at the input into the hot thermal storage arrangement during a discharging cycle.
  • the working fluid is constantly in gas phase during the charging cycle and the discharging cycle.
  • the further heat exchanger comprises a first input from the first heat exchanger connected to a first output leading to a turbine, and a second input from the cool thermal storage arrangement connected to a second output leading to a compressor.
  • the further heat exchanger comprises a first input from a compressor connected to a first output leading to the hot thermal storage arrangement, and a second input from a turbine connected to a second output leading to the cold thermal storage arrangement.
  • At least one section of a charging cycle or a discharging cycle runs supercritically.
  • the thermal storage medium in the hot storage heat arrangement is liquid and is preferably molten salt.
  • the thermal storage medium in the cold storage heat arrangement is a liquid and is preferably water.
  • the working fluid of the present invention is preferably carbon dioxide.
  • an external cooler is positioned in the discharging cycle system directly after the cool thermal storage arrangement, and preferably the external cooler is connected to an ambient heat sink.
  • the arrangement of the present invention provides flexibility to choose and limit the temperature range at which the heat is stored on the hot and cold sides of the system.
  • a method for storing and retrieving energy in a thermoelectric energy storage system.
  • the method comprising circulating a gaseous working fluid through a hot thermal storage arrangement and a cold thermal storage arrangement.
  • the system is charged by compressing the working fluid and heating a thermal storage medium circulating in the hot storage arrangement and by cooling a thermal storage medium circulating in the cold storage arrangement.
  • the system is discharged by heating the working fluid circulating through the hot thermal storage arrangement and expanding the working fluid through a turbine and by cooling the working fluid circulating through the cold thermal storage arrangement.
  • the working fluid output after heat exchange with the hot thermal storage arrangement during charging is further cooled.
  • the working fluid input into the hot thermal storage arrangement during discharging is pre-heated. Importantly, the working fluid is maintained constantly in a gas phase during both charging and discharging.
  • the step of cooling further the working fluid output after heat exchange with the hot storage during charging comprises transferring heat from the working fluid after heat exchange with the hot storage to the working fluid output after heat exchange with the cold storage.
  • the step of pre-heating the working fluid input into the first heat exchanger during discharging comprises transferring heat from the working fluid exiting the turbine to the working fluid input into the first heat exchanger.
  • At least one section of a charging cycle or a discharging cycle is performed supercritically.
  • the present invention enables the decoupling of the temperatures of the hot side and cold side of the TEES during both charging and discharging cycles by a "regenerative heat exchange" within the cycles. Whilst the charging and discharging modes of operation need to match, the temperature span of the hot and cool storages can be independently selected.
  • FIGS 2 and 3 schematically depict a charging cycle system and a discharging cycle system, respectively, of a TEES system in accordance with an embodiment of the present invention.
  • the charging cycle system 10 shown in Figure 2 comprises a work recovering expander 12, a cool storage heat exchanger 14, a compressor 16, a hot storage heat exchanger 18, and a regenerative heat exchanger 20.
  • a working fluid circulates through the components as indicated by the solid line with arrows in Figure 2 .
  • both the output from the cool storage heat exchanger 14 and the output from the hot storage heat exchanger 18 are passed countercurrent through the regenerative heat exchanger 20.
  • a first thermal storage tank 22 and a second thermal storage tank 24 containing a liquid thermal storage medium are coupled together via the hot storage heat exchanger 18.
  • the thermal storage liquid flows between the first thermal storage tank 22 and the second thermal storage tank 24 as indicated by the dashed line with arrows.
  • a third thermal storage tank 26 and a fourth thermal storage tank 28 containing a liquid thermal storage medium are coupled together via the cool storage heat exchanger 14.
  • the thermal storage liquid flows between the third thermal storage tank 26 and the fourth thermal storage tank 28 as indicated by the dotted line with arrows.
  • the charging cycle system 10 performs a thermodynamic cycle and the working fluid flows around the TEES system in the following manner.
  • the vapor working fluid exiting the cool storage heat exchanger 14 at a relatively low pressure P1 is circulated to the compressor 16 via the regenerative heat exchanger 20.
  • the surplus electrical energy which is to be stored is utilized to compress and heat the working fluid in the compressor 16.
  • the working fluid is at the highest temperature and relatively high pressure P2 in the cycle.
  • the working fluid is fed through the hot storage heat exchanger 18 where the working fluid discards heat into the thermal storage medium.
  • the fluid thermal storage medium is pumped from the first thermal storage tank 22 at T1 through the hot storage heat exchanger to the second thermal storage tank 24 at T2, countercurrent to the working fluid passing through the hot storage heat exchanger 18.
  • the heat energy discarded from the working fluid into the thermal storage medium is stored in the form of sensible heat, where T2 is greater than T1.
  • the compressed working fluid exits the hot storage heat exchanger 18 and enters the regenerative heat exchanger 20, where the remaining heat is transferred out of the compressed working fluid and into the working fluid which is flowing countercurrent and into the compressor 16. After exiting the regenerative heat exchanger the working fluid still has measurable energy due to its state of high pressure at P2. The cooled working fluid then enters the expander 12 where it is expanded back to lower pressure P1. Following this expansion the energy state of the working fluid is too low to be heated solely by regenerative heat exchange. Therefore, working fluid flows from the expander 12 into a cool storage heat exchanger 14 which is utilized to heat the working fluid.
  • the fluid thermal storage medium is pumped from the third thermal storage tank 26 at T3 through the cool storage heat exchanger to the fourth thermal storage tank 28 at T4. It is noted that T3 is greater than T4.
  • the heat energy harvested from the thermal storage medium heats the working fluid passing through the cool storage heat exchanger 14.
  • the discharging cycle system 30 shown in Figure 3 comprises a compressor 32, a regenerative heat exchanger 20, a hot storage heat exchanger 18, a turbine 34, a cool storage heat exchanger 14, and an external cooler 36.
  • a working fluid circulates through these components as indicated by the solid line with arrows in Figure 3 . It is noted that the discharging cycle system 30 utilizes similar components to the charging cycle system 10 with the additional feature of an external cooler 36 which is connected to an ambient heat sink.
  • the apparatus of the discharging cycle system 30 further comprises a first thermal storage tank 22 and a second thermal storage tank 24 containing a fluid thermal storage medium coupled together via the hot storage heat exchanger 18.
  • the thermal storage medium represented by the dashed line in Figure 3
  • a third thermal storage tank 26 and a fourth thermal storage tank 28 containing a fluid thermal storage medium are coupled together via the cool storage heat exchanger 14.
  • the thermal storage medium represented by the dotted line in Figure 3 , is pumped from the fourth thermal storage tank 28 through the cool storage heat exchanger 14 to the third storage tank 26.
  • the discharging cycle system 30 performs a thermodynamic cycle reversing the charging cycle and the working fluid flows around the TEES system in the following manner.
  • the working fluid in liquid form is compressed to a high pressure P2 by a compressor 32.
  • the working fluid then enters the regenerative heat exchanger 20, where it is further heated by the countercurrent working fluid leaving the turbine 34.
  • the working fluid then continues to the hot storage heat exchanger 18 in which heat energy is transferred from the thermal storage medium to the working fluid and the working fluid reaches its highest temperature level in the discharging cycle.
  • the working fluid then exits the hot storage heat exchanger 18 and enters the turbine 34 where the working fluid is expanded back to pressure P1 thereby causing the turbine 34 coupled to a generator (not illustrated) to generate electrical energy.
  • the working fluid then passes through the regenerative heat exchanger 20 and further thermal energy in the working fluid is recovered.
  • the working fluid enters the cool storage heat exchanger 14 in which still further remaining thermal energy is transferred from the working fluid to the thermal storage medium.
  • the previously cooled thermal storage medium contained in the fourth thermal storage tank 28 at a temperature T4 flows countercurrent to the working fluid into the third thermal storage tank 26 at temperature T3, where T3 is greater than T4.
  • the vapor working fluid then discards heat to the ambient via an external cooler 36, where the working fluid reaches the lowest temperature in the cycle, before entering the compressor 32.
  • This placement of external cooling before the compressor 32 of the power generation cycle is thermodynamically more efficient compared to the cooling carried out after the compressor 32 as described in the state of the art in TEES design. This can be explained in two ways:
  • the regenerative heat exchanger 20, the hot storage heat exchanger 18 with first and second thermal storage tanks 22, 24, and the cool storage heat exchanger 14 with third and fourth thermal storage tanks 26, 28, are common to both.
  • the compressor 16 of the charging cycle may be utilized as the turbine 32 of the discharging cycle when operated in reverse (and may be referred to as a turbomachine herein).
  • the charging and discharging cycles may be performed consecutively, not simultaneously. It should also be noted that the working fluid is always in the vapor form in this TEES arrangement. The heat transfer limitations of gases are minimized by the relatively high pressures in the system in operation.
  • each of the three heat exchangers 14, 18, 20 are counterflow or near counterflow heat exchangers.
  • the cool thermal storage medium is a liquid, and is preferably water.
  • the hot storage medium is also a liquid and preferably a molten salt, which is preferably a mixture of sodium nitrate and potassium nitrate.
  • the compressor 16 of the heat pump cycle 10 of the present embodiment is an electrically powered compressor.
  • FIG 4 shows a temperature-entropy diagram of the heat transfer from the cycles in a preferred embodiment of a TEES system of the present invention having a regenerative heat exchanger 20.
  • the thermal storage medium in the hot storage heat exchanger 18 is molten salt and the thermal storage medium in the cold storage heat exchanger 14 is hot water, both under atmospheric pressure.
  • the diagram shows both the charging and discharging cycles.
  • the charging cycle can be considered to start at reference A and follows an anti-clockwise direction.
  • the dashed curve A to B represents the heating the working fluid in the regenerative heat exchanger 20 as it flows from the cool heat exchanger 14 to the compressor 16.
  • B to C in Figure 4 represents the compression process in which the temperature of the working fluid reaches a maximum and a relatively high pressure P2.
  • Solid line C to D indicates the working fluid flowing through the hot storage heat exchanger 18 where heat is transferred to the thermal storage medium and thus the temperature of the working fluid drops.
  • the dashed curve between point D and E illustrates the working fluid passing through the regenerative heat exchanger 20 where it delivers its remaining thermal energy to the working fluid flowing countercurrent on the low pressure side of the cycle.
  • Solid line E to F represents the expansion of the working fluid from state P2 to P1 and this recovered energy is transferred either mechanically or electrically to the compressor 16.
  • the working fluid is now at the lowest energy state in the cycle as it enters the cool storage heat exchanger 14 and harvests thermal energy from the thermal storage medium illustrated by solid line F to A on Figure 4 .
  • the discharging cycle of the present invention may be considered to be the reverse of the above described charging cycle with the exception of the additional cooling from an ambient heat sink 36.
  • This discharging step dissipates the losses due to the irreversibility in the TEES and is represented by the line F to F* in Figure 4 .
  • the working fluid attains the low pressure P1 upon cooling by the external cooler connected to an ambient heat sink prior to entering the compressor where the pressure is increased to P2; indicated by dotted line F* to E.
  • the vertical arrow to the left hand side of the diagram shows the relatively small temperature span of the hot storage in the present system. In this example, between 425°C and 570°C.
  • the vertical arrow to the right hand side of the diagram shows the relatively small temperature span of the cold storage in the present system. In this example, between 45 °C and 105 °C.
  • the arrangement of the present invention provides flexibility to choose and limit the temperature range at which the heat is stored on the hot and cold sides of the system.
  • the relatively high density and relatively high heat transfer coefficient of the carbon dioxide under the TEES cycle conditions also influences the choice of pressures within the cycles. Specifically, the surfaces of the heat exchangers 14, 18, 20 and the size of the turbomachine may be minimized through manipulation of the pressures within the cycles.
  • careful choice of the system parameters may reduce the total required volume of the thermal storage materials and may also reduce the sensitivity of the roundtrip efficiency to the approach temperatures in the thermal storage heat exchangers 14, 18 (primarily due to the large temperature differences within the system).
  • heat balancing with another refrigeration cycle is not necessary and the required amount of cooling water or air is minimal; only that which corresponds to the energy losses in the two cycles.
  • both water and molten salt are used as thermal storage materials, which combination functions to reduce the footprint of the TEES system whilst maintaining high system efficiency.
  • the present invention enables the decoupling of the temperatures of the hot side and cold side of the TEES during both charging and discharging cycles by a "regenerative heat exchange" within the cycles.
  • the temperature span of the hot and cool storages can be independently selected.
  • the cool storage should be colder then the hot storage but otherwise liquid nitrogen may be used as cool thermal storage medium and hot water at 90°C may be used as hot thermal storage medium.
  • molten salt may be used as the hot thermal storage medium and liquid nitrogen as the cool thermal storage medium thereby creating a very large temperature difference in the cycle.
  • the pressure ratio (the ratio of P1 and P2 in the above embodiment) is only weakly affected by the temperature difference between hot and cold sides of the TEES and therefore it is possible to connect a cold side at a very low temperature with a hot side at ambient temperature. Equally, it is possible to connect a cold side at ambient temperature with a hot side at relatively high temperatures. And due to the fact that the working fluid is always in the gas phase, the heat transfer with both the hot and cold sides of the cycle takes place via a change in temperature (and also possibly as an exchange of sensible heat on both sides of the TEES). As indicated above, theoretically, the temperature range within which both cycles can interact with the hot and cold sides may be freely chosen.
  • ammonia and water mixture can be utilized as a thermal storage medium in the cool storage heat exchanger (having a temperature range of -100°C to 50°C).
  • thermal storage mediums include water without additives at atmospheric pressure (having a temperature range of 0°C to 100°C), or thermal oil such as Dowtherm J (having a temperature range of -80°C to 315°C) or molten salt mixture (having a temperature range up to 566°C). Therefore, it can be seen that the choice of thermal storage medium is broad and the charging and discharging cycle parameters can be adapted, dependent upon the thermal storage mediums chosen, for best efficiency and cost tradeoff. Clearly, where very high temperatures are utilized in the heat exchange parts of a TEES cycle, then other components in the system may need to be adapted to operate effectively under high temperature and pressure conditions.
  • carbon dioxide is the preferred working fluid for the present invention
  • other fluids may be used alternatively.
  • other gases have properties which enable them to match similar operating conditions exemplified in Figure 4 , but at lower pressures.

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  • 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)
EP11187317.0A 2011-10-31 2011-10-31 Système de stockage d'énergie thermoélectrique avec échange thermique régénératif et procédé de stockage d'énergie thermoélectrique Withdrawn EP2587005A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP11187317.0A EP2587005A1 (fr) 2011-10-31 2011-10-31 Système de stockage d'énergie thermoélectrique avec échange thermique régénératif et procédé de stockage d'énergie thermoélectrique
PCT/EP2012/069157 WO2013064317A1 (fr) 2011-10-31 2012-09-28 Système de stockage d'énergie électrique comportant un échange de chaleur à récupération, et procédé pour stocker de l'énergie thermoélectrique
PCT/EP2012/071534 WO2013064524A1 (fr) 2011-10-31 2012-10-31 Système de stockage d'énergie thermoélectrique comportant un échangeur de chaleur à récupération et procédé pour stocker de l'énergie thermoélectrique

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EP11187317.0A EP2587005A1 (fr) 2011-10-31 2011-10-31 Système de stockage d'énergie thermoélectrique avec échange thermique régénératif et procédé de stockage d'énergie thermoélectrique

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WO2014193724A1 (fr) * 2013-05-31 2014-12-04 Davidson Chal S Systèmes et procédés pour une montée de la puissance avec un stockage d'énergie
EP2927435A1 (fr) * 2014-04-01 2015-10-07 Alstom Technology Ltd Système de stockage réversible de l'énergie électrique en énergie thermique
WO2017210713A1 (fr) * 2016-06-10 2017-12-14 Technische Universität Wien Centrale thermique
CN114857973A (zh) * 2022-04-24 2022-08-05 西安热工研究院有限公司 一种电热储能系统及换热方法

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US9695715B2 (en) 2014-11-26 2017-07-04 General Electric Company Electrothermal energy storage system and an associated method thereof
DK3379040T3 (da) * 2017-03-20 2021-04-12 Lumenion Gmbh Kraftværk til generering af elektrisk energi og fremgangsmåde til drift af et kraftværk
CN106885232A (zh) * 2017-04-12 2017-06-23 东方电气集团东方锅炉股份有限公司 一种适用于火电机组深度调峰的液态储能系统
CN110206598B (zh) * 2019-06-04 2022-04-01 中国科学院工程热物理研究所 一种基于间接储冷储热的热泵储能发电系统
CN110159380B (zh) * 2019-06-14 2024-06-07 国家电投集团科学技术研究院有限公司 单罐闭式循环储能发电系统
DK181096B1 (en) 2021-04-14 2022-12-12 Stiesdal Storage As Thermal energy storage system with a spray of phase change material and method of its operation

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WO2014193724A1 (fr) * 2013-05-31 2014-12-04 Davidson Chal S Systèmes et procédés pour une montée de la puissance avec un stockage d'énergie
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