EP2390473A1 - Système de stockage d'énergie thermoélectrique et procédé de stockage d'énergie thermoélectrique - Google Patents

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

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Publication number
EP2390473A1
EP2390473A1 EP10164288A EP10164288A EP2390473A1 EP 2390473 A1 EP2390473 A1 EP 2390473A1 EP 10164288 A EP10164288 A EP 10164288A EP 10164288 A EP10164288 A EP 10164288A EP 2390473 A1 EP2390473 A1 EP 2390473A1
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EP
European Patent Office
Prior art keywords
working fluid
heat
pressure
intermediate pressure
cycle
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.)
Withdrawn
Application number
EP10164288A
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German (de)
English (en)
Inventor
Jaroslav Hemrle
Lilian Kaufmann
Mehmet Mercangoez
Christian Ohler
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ABB Research Ltd Switzerland
ABB Research Ltd Sweden
Original Assignee
ABB Research Ltd Switzerland
ABB Research Ltd Sweden
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 Switzerland, ABB Research Ltd Sweden filed Critical ABB Research Ltd Switzerland
Priority to EP10164288A priority Critical patent/EP2390473A1/fr
Priority to CN2011800368821A priority patent/CN103003531A/zh
Priority to PCT/EP2011/057799 priority patent/WO2011147701A1/fr
Publication of EP2390473A1 publication Critical patent/EP2390473A1/fr
Priority to US13/687,235 priority patent/US20130087301A1/en
Withdrawn legal-status Critical Current

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    • 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
    • F28D17/00—Regenerative heat-exchange apparatus in which a stationary intermediate heat-transfer medium or body is contacted successively by each heat-exchange medium, e.g. using granular particles
    • 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
    • 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

Definitions

  • the present invention relates generally to the storage of electric energy. It relates in particular to a system and a method for storing electric energy in the form of thermal energy in a thermal energy storage.
  • 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 may be robust, compact, site independent and may be suited to the storage of electrical energy in large amounts.
  • Thermal energy may 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 may be a solid, liquid, or a gas.
  • the storage medium for the latent heat occurs via a change of phase and may 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 may 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.
  • thermoelectric energy storage system The roundtrip efficiency of the thermoelectric energy storage system is limited for various reasons rooted in the second law of thermodynamics.
  • the first reason relates to the coefficient of performance of the system.
  • thermoelectric energy storage systems because they are not concerned with heat for the exclusive purpose of storing electricity.
  • thermoelectric energy storage having a high round-trip efficiency, whilst minimising the system costs involved.
  • An aspect of the invention relates to a thermoelectric energy storage system for storing electrical energy by transferring thermal energy to a thermal storage in a charging cycle, and for generating electricity by retrieving the thermal energy from the thermal storage in a discharging cycle.
  • the thermoelectric energy storage system comprises a working fluid circuit circulating a working fluid; a first compressor, in the charging cycle, compressing the working fluid from a low pressure to an intermediate pressure (such that the temperature of the working fluid is rising), an intercooler, in the charging cycle, cooling the working fluid at the intermediate pressure (for lowering the temperature of the working fluid), a second compressor, in the charging cycle, compressing the working fluid from the intermediate pressure to a high pressure, a first heat exchanger, in the charging cycle, transferring heat from the working fluid at the high pressure to the thermal storage and, in the discharging cycle, transferring heat from the thermal storage to the working fluid at the high pressure.
  • the working fluid may be compressed in two stages: from the low pressure to the intermediate pressure in a first stage and from the intermediate pressure to the high pressure in a second stage.
  • the intercooler comprises a flash intercooler and/or a second heat exchanger.
  • the intercooling may be carried out by (a) flashing a portion of the working fluid (taken from the output of a expander) in the flash intercooler and/or by (b) heating a secondary thermal storage with the second heat exchanger.
  • This may have the advantage of (a) reducing the compressor energy of the first stage without compromising the thermal energy delivered to the main thermal storage and/or of (b) carrying out a reheat in the discharging cycle by using the secondary thermal storage to increase the power output.
  • second heat exchanger in the charging cycle, transfers heat from the working fluid at the intermediate pressure to a second thermal storage and, in the discharging cycle, transfers heat from the second thermal storage to the working fluid at intermediate pressure.
  • flash intercooler for one stage one can use the flash intercooler and for another one can use a thermal storage heat exchanger.
  • flash intercoolers exclusively, for example two flash intercoolers. In this case there may not be any reheat stages in the discharging cycle.
  • thermal storage heat exchangers for intercooling exclusively, for example two heat exchangers. In this case there may be more than one reheat stage in the discharging cycle.
  • thermoelectric energy storage system may be referred to as a heat pump cycle and the discharging cycle of a thermoelectric energy storage system may be 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, i.e. the thermal storage medium part of a thermoelectric energy storage, is greater than the compression work by an amount equal to the energy taken from the cold side, i.e.
  • 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 thermoelectric energy storage system.
  • thermoelectric energy storage system may comprise 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, for example, containing a fluid thermal storage medium may be 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 thermoelectric energy storage system may comprise a pump, a condenser, a turbine and a heat exchanger, all connected in series by a working fluid circuit.
  • a cold storage tank and a hot storage tank for example, containing a fluid thermal storage medium may be coupled together via the heat exchanger. Whilst 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, may be used in both the charging and discharging cycles.
  • the present invention overcomes the problem of an excessive temperature rise in the working fluid during compression in the charging cycle.
  • This problem occurs where the ratio of the highest operating pressure of a transcritical thermoelectric energy storage system to the evaporator pressure of the charging cycle is relatively great.
  • this excessive temperature rise is detrimental to the completion of the compression process in a single stage unless the working fluid is heated to an acceptably high temperature.
  • thermoelectric energy storage system where the charging and discharging cycles are designed to have corresponding compressor intercooling and reheat sections, respectively, with matching heat loads and temperature levels, and where an intercooler may be used for cooling each of the additional compression stages of the charging cycle.
  • intercoolers are located at the corresponding compressor discharges and are fed with partially expanded working fluid from the condenser exit, such that the heat of compression is absorbed by the process of vaporizing the liquid part of the working fluid.
  • the present invention provides a multi-stage compression system in which the working fluid is cooled close to its saturation temperature as it is output from each intermediate compression stage.
  • the heat released from the working fluid during said cooling is recovered and utilised to improve roundtrip efficiency of the thermoelectric energy storage system.
  • a further aspect of the invention relates to a method for storing electrical energy in a charging cycle and retrieving electrical energy in a discharging cycle.
  • the charging cycle comprises the steps: compressing the working fluid from a low pressure to an intermediate pressure for storing electrical energy (particularly for converting electrical energy into heat energy); cooling the working fluid at the intermediate pressure; compressing the working fluid from the intermediate pressure to a high pressure for storing electrical energy; transferring heat from the working fluid at the high pressure to the thermal storage.
  • the discharging cycle comprises the steps: transferring heat from the thermal storage to the working fluid at the high pressure; expanding the working fluid from the high pressure for generating electrical energy.
  • FIGS. 1a and 1b show a simplified schematic diagram of a thermoelectric energy storage system 10 according to an embodiment of the invention.
  • the charging cycle system 12 shown in Figure 1 a comprises a first compression stage with a compressor 14, a second compression stage with a compressor 16 and a third compression stage with a compressor 18.
  • the charging cycle system 12 comprises further a first expansion stage with an expander 20 and a second expansion stage with an expansion valve 22.
  • a working fluid circulates through all components of a working fluid circuit 24 as indicated by the solid line with arrows.
  • the charging cycle system 12 comprises a stream splitter 26 between the expander 20 and the expansion valve 22, a flash intercooler 28 between the compressor 14 and the compressor 16 and a heat exchanger 30 between the compressor 16 and the compressor 18.
  • the charging cycle system 12 comprises a heat exchanger 34, and at the low pressure side 36, the charging cycle system 12 comprises a heat exchanger 38.
  • the charging cycle system 12 performs a transcritical cycle and the working fluid flows around the thermoelectric energy storage system 10 in the following manner.
  • the working fluid enters the expander 20 where the working fluid is expanded from a high pressure to a lower (intermediate) pressure.
  • the working fluid stream is split in two streams by the stream splitter 26, with a first portion of the working fluid flowing to the second expansion stage with expansion valve 22 and a second portion passing directly to the flash intercooler 28.
  • the working fluid passes to the heat exchanger 38 where the working fluid absorbs heat from the ambient or from a cold storage 40 and evaporates.
  • the heat exchanger 38 is a counter flow heat exchanger 38 and a cold storage medium circulates from a first cold storage tank 42 to a second cold storage tank 44 for exchanging heat with the working fluid.
  • the vaporised working fluid is circulated to a first compression stage in which surplus electrical energy is utilized to compress and heat the working fluid in a compressor 14 from the low pressure to the intermediate pressure. On exiting the compressor 14, this first portion of working fluid is mixed with the relatively cooler, second portion of working fluid in the flash intercooler 28.
  • the mixed working fluids pass to a second compression stage which comprises the compressor 16.
  • a second compression stage which comprises the compressor 16.
  • further surplus electrical energy is utilized to compress the working fluid from the intermediate pressure to a higher second intermediate pressure.
  • the working fluid mass flow through the second compression stage is greater than the working fluid mass flow through the first compression stage.
  • the working fluid passes through the heat exchanger 30 where it is cooled as heat energy is transferred from the working fluid to a thermal storage medium from a further heat storage 46.
  • the heat exchanger 30 is a counter flow heat exchanger 30 and the storage medium circulates from a first storage tank 48 to a second storage tank 50 for exchanging heat with the working fluid.
  • the working fluid is then directed to a third compression stage where it passes through the compressor 18 before entering the heat exchanger 34.
  • the third compression stage again surplus electrical energy is driving the compressor 18 for compressing the working fluid from the second intermediate pressure to the (higher) high pressure.
  • heat energy is transferred from the working fluid into a thermal storage medium from a hot storage 52.
  • the heat exchanger 34 is a counter flow heat exchanger 34 and the storage medium circulates from a first hot storage tank 54 to a second hot storage tank 56 for exchanging heat with the working fluid.
  • the flash intercooler 28 is a spray intercooler 28. In alternative embodiments, other types of flash intercoolers 28 may be used.
  • intercooler 28, 30 is required in the charging cycle 12 in order to achieve improved efficiency of the system 10.
  • each compression stage may be equipped with a flash intercooler 28, when reheat options are not considered in the discharging cycle. It should be noted that different working fluids may be used for the different cycles, as long as the temperature levels for the heat load of the heat pump, the heat storage and the heat engine are chosen appropriately.
  • the charging cycle may operate in the temperature range of 5°C and 120 °C.
  • the intercooling occurs at a temperature levels well distributed within this range.
  • the system 10 comprises a first expander 20, in the charging cycle, expanding the working fluid after the first heat exchanger 34 to the intermediate pressure; wherein, in the charging cycle, a first portion of the working fluid at the intermediate pressure is input directly into the flash intercooler 28.
  • the system 10 comprises a second expander 22, in the charging cycle, expanding a second portion of the working fluid at the intermediate pressure to the low pressure.
  • the system 10 comprises a third heat exchanger 38, in the charging cycle, transferring heat from a third thermal storage 40 to the working fluid at low pressure and, in the discharging cycle, transferring heat from the working fluid at low pressure to the third thermal storage.
  • the intercooler comprises a flash intercooler 28 and a third heat exchanger 30, wherein, in the charging cycle, the working fluid between the flash intercooler and the third heat exchanger is compressed from a first intermediate pressure to a second intermediate pressure by a further compressor 16.
  • the working fluid in the discharging cycle system 58 coming from the heat exchanger 38 is pumped from the low pressure to the high pressure by pump 60. After that the working fluid is heated in the heat exchanger 34 and enters a first turbine 62 for converting the heat into mechanical and subsequently into electrical energy. The working fluid is reheated again in heat exchanger 30 and enters a second turbine 64 for generating further electrical energy. In the first turbine 62 the working fluid is expanded from the high pressure to the intermediate pressure and in the second turbine 64 to the low pressure. After that the working fluid is cooled in the heat exchanger 38.
  • the system 10 comprises a first turbine 62, in the discharging cycle, expanding the working fluid from the high pressure to the intermediate pressure for generating electrical energy and/or a second turbine 64, in the discharging cycle, expanding the working fluid from the intermediate pressure to the low pressure for generating electrical energy.
  • the system 10 comprises a pump 60, in the discharging cycle, pumping the working fluid from the low pressure to the high pressure during the discharging cycle.
  • FIGs 2a and 3a show a charging cycle 12a, 12b, and Figures 2b and 3b a discharging cycle 58a, 58b of a transcritical thermoelectric energy storage system 10. The cycles are depicted in pressure-enthalpy diagrams.
  • a vapor dome 66 is indicated.
  • the critical point 68 of the working fluid is shown on top of the vapor dome.
  • the working fluid is in liquid phase
  • the working fluid is in gas phase (wet steam phase).
  • the working fluid is in a mixed liquid and gas phase.
  • a phase change of the working fluid only occurs, when a state change passes the limiting line of the vapor dome 66.
  • stated change over the vapor dome 66 and over the critical point 68 do not contain phase changes and may be called transcritical.
  • nearly all state changes of the working fluid in the charging cycle and the discharging cycle are transcritical, and therefore the charging cycle and the discharging cycle are referred to as transcritical.
  • FIG 2a illustrates the charging cycle 12 of a storage system 10 which may comprise two heat exchangers 30 for intercooling the working fluid.
  • the charging cycle 12a follows a counter-clockwise direction as indicated by the arrows.
  • the charging cycle 12a starts at point A where the working fluid is first evaporated at a low pressure 70 by utilizing, for example a low grade heat source such as ambient air or by a heat exchanger 38. This transition is indicated in Figure 2a with the line from point A to point B1.
  • the resultant vapor is compressed utilizing electrical energy in three stages from point B1 to C1 to a first intermediate pressure 72, from B2 to C2 to a second intermediate pressure 74, and from B3 to C3 to a high pressure 76.
  • Such compression occurring in three stages is a consequence of the thermoelectric energy storage 10 having a compressor train comprising three individual units, for example the compressors 14, 16, 18.
  • the working fluid is cooled from point C1 to B2 and point C2 to B3.
  • the working fluid may be cooled by two heat exchangers 30.
  • the hot compressed working fluid exiting the compression train at point C3 is cooled down at constant pressure 76 to point D, for example in a heat exchanger 34. Since the cycle 12a is supercritical between the points C3 and D, no condensation of the working fluid takes place. The heat rejected between point C1 to B2, C2 to B3, and C3 and D is transferred to a thermal storage medium via heat exchangers 30, 34, thereby storing the heat energy. After reaching point D, the cooled working fluid is returned to its initial low pressure state 70 at point A via a thermostatic expansion valve 22 or alternatively with an energy recovering expander.
  • FIG. 2b illustrates the discharging cycle of a thermoelectric energy storage system 10 with one turbine 62 that follows a clockwise direction as indicated by the arrows.
  • the discharging cycle 58a starts with the compression of the working fluid as it is pumped from point E to point F from low pressure 70 to high pressure 76, for example by pump 60. From point F to point G, the working fluid is in contact with the thermal storage medium in a direct or indirect manner, wherein stored heat is transferred from the thermal storage medium to the working fluid. For example, this may be done with a heat exchanger 34.
  • the working fluid is in a supercritical state between point F and point G, hence no evaporation takes place.
  • the subsequent expansion of the working fluid in a turbine 62 from pressure 76 to pressure 70 in order to generate electricity is represented between point G and point H.
  • the working fluid is condensed to its initial state by exchanging heat, for example with a cooling medium such as ambient air or with a cold storage 40 via a heat exchanger 38. This is represented from point H to point E on Figure 2b .
  • thermodynamic cycles 12a, 58a shown in Figures 2a and 2b would use the same working fluid, it is noted that the total heat energy generated in the charging cycle 12a is greater than the heat energy requirement of the discharging cycle 58a.
  • the total heat energy required for functioning of the discharging cycle 58a which is equal to the enthalpy difference from point F to point G in Figure 1b , can be provided solely by the heat energy released during the charging cycle between point C3 and point D in Figure 1a .
  • a storage system 10 with a charging cycle 12a comprises a discharging cycle, wherein the heat stored during intercooling is used for reheating the working fluid between the expansions in turbines 62, 64.
  • a storage system 10 with a discharging cycle 58a comprises a discharging cycle, wherein a flash intercooler 28 is used for cooling the working fluid between two compression stages.
  • Figure 3a and Figure 3b depict a charging cycle 12b and a discharging cycle 58b, respectively, on a pressure-enthalpy diagram, which may be performed by an embodiment of the transcritical thermoelectric energy storage system 10 shown in Figures 1 a and 1 b.
  • the charging cycle 12b follows a counter-clockwise direction as indicated by the arrows.
  • the charging cycle 12b starts with the expansion of the working fluid which occurs in two stages, between point D and point A1 from pressure 76 to pressure 72 (expander 20), and between point A1 and point A2 from pressure 72 to pressure 70 (expansion valve 22).
  • the working fluid stream is divided at point A1 (stream splitter 26), where a first portion is diverted to point B2 and the remaining portion is expanded further to point A2 (expansion valve 22).
  • the third compression stage from pressure 74 to pressure 76 occurs between points B3 and C3 (compressor 18).
  • thermoelectric energy storage 10 having a compressor train comprising three individual units 14, 16, 18. In between each of these compression stages the working fluid is cooled from point C1 to B2 and point C2 to B3 at constant pressure.
  • the hot compressed working fluid exiting the compression train at point C3 is cooled down at constant pressure 76 to point D (heat exchanger 34). Since the cycle 12b is supercritical between the points C3 and D, no condensation of the working fluid takes place.
  • the rejected heat energy between points C3 and D is stored in a thermal storage medium (hot storage 52). After reaching point D, the cooled working fluid is returned to its initial low pressure state 70 at point A1 via a work recovering expander 20 / thermostatic expansion valve 22.
  • the flash intercooler 28 utilized in the charging cycle 12b may be a direct-contact heat exchanger, where the liquid working fluid from point A1 to be evaporated is injected or sprayed into the compressed working fluid vapour flow at C1.
  • a direct-contact heat exchanger comprises a shell filled with a packing of a high specific surface area in order to increase the wetted heat transfer area.
  • FIG 3b illustrates the discharging cycle 58b of the thermoelectric energy storage system 10 that follows a clockwise direction as indicated by the arrows.
  • the discharging cycle starts with the compression (pump 60) of the working fluid from low pressure 70 to high pressure 76 and this transition is indicated in Figure 3b with the line from point E to point F.
  • the working fluid is in contact with the thermal storage medium in a direct or indirect manner, wherein stored heat is transferred from the thermal storage medium to the working fluid at constant pressure (heat exchanger 34).
  • the working fluid is in a supercritical state between point F and point G1, hence no evaporation takes place.
  • the subsequent expansion of the working fluid in a turbine 62 in order to generate electricity is represented between point G1 and point H1.
  • a reheat stage at pressure 74 where the reheat energy is provided from the thermal storage 46.
  • said thermal storage 46 is coupled to the heat exchanger 30 corresponding to the second intercooling stage in the charging cycle 12b.
  • every compressor stage in the charging cycle can be equipped with a separate flash intercooler.
  • different working fluids may be utilized in the charging and discharging cycles.
  • the temperature levels for the charging cycle, the heat storage and the discharging cycle must be adjusted to ensure transfer of heat in the desired direction.
  • water is used as the working fluid in the charging cycle.
  • another fluid with a high boiling point may be utilised instead of water.
  • the intercooling heat load is at a suitably high temperature to be stored and used to drive a secondary discharging cycle having a low boiling point working fluid (such as hydrocarbon).
  • thermal energy stored during intercooling can be efficiently recovered without utilising a flash intercooler.
  • thermoelectric energy storage system may be replaced with a multi-purpose heat exchange device that can assume both roles, since the use of the evaporator in the charging cycle and the use of the condenser in the discharging cycle will be carried out in different periods.
  • turbine and the compressor roles can be carried out by the same machinery, referred to herein as a thermodynamic machine, capable of achieving both tasks.
  • temperatures, the pressures and the amount of working fluid exiting the stream splitter 26 may be measured and these values may be controlled by valves situated in the working fluid circuit.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP10164288A 2010-05-28 2010-05-28 Système de stockage d'énergie thermoélectrique et procédé de stockage d'énergie thermoélectrique Withdrawn EP2390473A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP10164288A EP2390473A1 (fr) 2010-05-28 2010-05-28 Système de stockage d'énergie thermoélectrique et procédé de stockage d'énergie thermoélectrique
CN2011800368821A CN103003531A (zh) 2010-05-28 2011-05-13 用于储存热电能的热电能量储存系统和方法
PCT/EP2011/057799 WO2011147701A1 (fr) 2010-05-28 2011-05-13 Système de stockage d'énergie thermoélectrique et procédé pour stocker de l'énergie thermoélectrique
US13/687,235 US20130087301A1 (en) 2010-05-28 2012-11-28 Thermoelectric energy storage system and method for storing thermoelectric energy

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EP10164288A EP2390473A1 (fr) 2010-05-28 2010-05-28 Système de stockage d'énergie thermoélectrique et procédé de stockage d'énergie thermoélectrique

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EP (1) EP2390473A1 (fr)
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WO (1) WO2011147701A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2501685A (en) * 2012-04-30 2013-11-06 Isentropic Ltd Apparatus for storing energy
WO2013164563A1 (fr) * 2012-04-30 2013-11-07 Isentropic Ltd Appareil de stockage d'énergie et procédé de fonctionnement d'un système de stockage d'énergie
EP2698506A1 (fr) * 2012-08-17 2014-02-19 ABB Research Ltd. Système de stockage d'énergie électrothermique et procédé pour stocker de l'énergie électrothermique
EP2759679A1 (fr) * 2013-01-23 2014-07-30 Siemens Aktiengesellschaft Dispositif de stockage thermique destiné à l'utilisation de chaleur à basse température
WO2013119145A3 (fr) * 2012-02-10 2015-07-16 Александр Петрович САМОЙЛОВ Procédé d'accumulation, de stockage et de récupération d'énergie mécanique et installation pour sa mise en oeuvre (et variantes)
WO2016126300A3 (fr) * 2014-11-26 2016-10-27 General Electric Company Système de stockage d'énergie électrothermique
US9932830B2 (en) 2010-03-04 2018-04-03 X Development Llc Adiabatic salt electric energy storage
US10012448B2 (en) 2012-09-27 2018-07-03 X Development Llc Systems and methods for energy storage and retrieval
US10082104B2 (en) 2016-12-30 2018-09-25 X Development Llc Atmospheric storage and transfer of thermal energy
US10082045B2 (en) 2016-12-28 2018-09-25 X Development Llc Use of regenerator in thermodynamic cycle system
US10221775B2 (en) 2016-12-29 2019-03-05 Malta Inc. Use of external air for closed cycle inventory control
US10233833B2 (en) 2016-12-28 2019-03-19 Malta Inc. Pump control of closed cycle power generation system
US10233787B2 (en) 2016-12-28 2019-03-19 Malta Inc. Storage of excess heat in cold side of heat engine
US10280804B2 (en) 2016-12-29 2019-05-07 Malta Inc. Thermocline arrays
US10436109B2 (en) 2016-12-31 2019-10-08 Malta Inc. Modular thermal storage
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
US10934895B2 (en) 2013-03-04 2021-03-02 Echogen Power Systems, Llc Heat engine systems with high net power supercritical carbon dioxide circuits
WO2021069327A1 (fr) * 2019-10-11 2021-04-15 Enolcon Gmbh Système de stockage d'énergie thermique comprenant une unité de stockage de chaleur à lit tassé et une unité de stockage de froid à lit tassé et procédé permettant de faire fonctionner un système de stockage d'énergie thermique
US11053847B2 (en) 2016-12-28 2021-07-06 Malta Inc. Baffled thermoclines in thermodynamic cycle systems
US11187112B2 (en) 2018-06-27 2021-11-30 Echogen Power Systems Llc Systems and methods for generating electricity via a pumped thermal energy storage system
US11286804B2 (en) 2020-08-12 2022-03-29 Malta Inc. Pumped heat energy storage system with charge cycle thermal integration
US11293309B2 (en) 2014-11-03 2022-04-05 Echogen Power Systems, Llc Active thrust management of a turbopump within a supercritical working fluid circuit in a heat engine system
US11396826B2 (en) 2020-08-12 2022-07-26 Malta Inc. Pumped heat energy storage system with electric heating integration
US11435120B2 (en) 2020-05-05 2022-09-06 Echogen Power Systems (Delaware), Inc. Split expansion heat pump cycle
US11454167B1 (en) 2020-08-12 2022-09-27 Malta Inc. Pumped heat energy storage system with hot-side thermal integration
US11480067B2 (en) 2020-08-12 2022-10-25 Malta Inc. Pumped heat energy storage system with generation cycle thermal integration
US11486305B2 (en) 2020-08-12 2022-11-01 Malta Inc. Pumped heat energy storage system with load following
US11629638B2 (en) 2020-12-09 2023-04-18 Supercritical Storage Company, Inc. Three reservoir electric thermal energy storage system
US11678615B2 (en) 2018-01-11 2023-06-20 Lancium Llc Method and system for dynamic power delivery to a flexible growcenter using unutilized energy sources
US11852043B2 (en) 2019-11-16 2023-12-26 Malta Inc. Pumped heat electric storage system with recirculation
US11982228B2 (en) 2020-08-12 2024-05-14 Malta Inc. Pumped heat energy storage system with steam cycle

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9267414B2 (en) * 2010-08-26 2016-02-23 Modine Manufacturing Company Waste heat recovery system and method of operating the same
EP2602443A1 (fr) * 2011-12-08 2013-06-12 Alstom Technology Ltd Stockage dýélectricité
WO2013102537A2 (fr) * 2012-01-03 2013-07-11 Abb Research Ltd Système de stockage d'énergie électrothermique équipé d'un dispositif de stockage de glace à évaporation amélioré et procédé pour stocker de l'énergie électrothermique
WO2014146007A1 (fr) * 2013-03-15 2014-09-18 Electratherm, Inc. Appareils, systèmes et procédés de gestion de chaleur perdue de basse qualité
CN103195525B (zh) * 2013-03-19 2014-12-31 中国科学院理化技术研究所 一种正逆有机朗肯循环储能的方法及系统
GB201310717D0 (en) * 2013-06-16 2013-07-31 Garvey Seamus D Direct-drive power conversion system for wind turbines compatible with energy storage
US9394807B1 (en) * 2015-03-16 2016-07-19 Sten Kreuger Apparatus, system, and methods for mechanical energy regeneration
GB2538092A (en) * 2015-05-07 2016-11-09 Turner David Heat exchanger assisted - refrigeration, cooling and heating
GB2538784A (en) * 2015-05-28 2016-11-30 Highview Entpr Ltd Improvements in energy storage
US20170314422A1 (en) * 2016-04-27 2017-11-02 Tao Song Engine Exhaust and Cooling System for Power Production
CN109000385B (zh) * 2018-07-04 2020-06-09 江苏科技大学 一种多源高温热泵装置及工作方法
WO2024033752A1 (fr) * 2022-08-10 2024-02-15 Briola Stefano Installation de pompe à chaleur à haute température, utilisable de manière réversible dans un autre mode de fonctionnement comme installation de co/tri-génération
DE102022211960A1 (de) * 2022-11-11 2024-05-16 Siemens Energy Global GmbH & Co. KG Kombianlage und Verfahren zum Betreiben einer Kombianlage

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3165905A (en) 1962-08-15 1965-01-19 Trane Co Refrigerating machine including an economizer
DE10055202A1 (de) * 2000-08-04 2002-02-21 Rerum Cognitio Ges Fuer Markti Dampfkraft-/Arbeitsprozeß mit erhöhtem mechanischen Wirkungsgrad für die Elektroenergiegewinnung im Kreisprozeß sowie Anordnung zu seiner Durchführung
EP1577548A1 (fr) 2004-03-16 2005-09-21 Abb Research Ltd. Dispositif et procédé de stockage d'énergie thermale et de génération d'électricité
DE102006007119A1 (de) * 2006-02-16 2007-08-23 Wolf, Bodo M., Dr. Verfahren zur Speicherung und Rückgewinnung von Energie
US20080137797A1 (en) * 2005-12-21 2008-06-12 Andrew Maxwell Peter Electricity and steam generation from a helium-cooled nuclear reactor
EP2157317A2 (fr) 2008-08-19 2010-02-24 ABB Research LTD Système de stockage d'énergie thermoélectrique et procédé de stockage d'énergie thermoélectrique

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7600390B2 (en) * 2004-10-21 2009-10-13 Tecumseh Products Company Method and apparatus for control of carbon dioxide gas cooler pressure by use of a two-stage compressor
WO2008079129A1 (fr) * 2006-12-26 2008-07-03 Carrier Corporation Système de réfrigération équipé d'un économiseur, d'un refroidisseur intermédiaire et d'un compresseur à plusieurs étages
PL2182179T3 (pl) * 2008-07-16 2011-10-31 Abb Research Ltd Układ do magazynowania energii termoelektrycznej i sposób magazynowania energii termoelektrycznej
US20110100010A1 (en) * 2009-10-30 2011-05-05 Freund Sebastian W Adiabatic compressed air energy storage system with liquid thermal energy storage

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3165905A (en) 1962-08-15 1965-01-19 Trane Co Refrigerating machine including an economizer
DE10055202A1 (de) * 2000-08-04 2002-02-21 Rerum Cognitio Ges Fuer Markti Dampfkraft-/Arbeitsprozeß mit erhöhtem mechanischen Wirkungsgrad für die Elektroenergiegewinnung im Kreisprozeß sowie Anordnung zu seiner Durchführung
EP1577548A1 (fr) 2004-03-16 2005-09-21 Abb Research Ltd. Dispositif et procédé de stockage d'énergie thermale et de génération d'électricité
US20080137797A1 (en) * 2005-12-21 2008-06-12 Andrew Maxwell Peter Electricity and steam generation from a helium-cooled nuclear reactor
DE102006007119A1 (de) * 2006-02-16 2007-08-23 Wolf, Bodo M., Dr. Verfahren zur Speicherung und Rückgewinnung von Energie
EP2157317A2 (fr) 2008-08-19 2010-02-24 ABB Research LTD Système de stockage d'énergie thermoélectrique et procédé de stockage d'énergie thermoélectrique

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
LACHNER B. F.; NELLIS G. F.; REINDL D. T.: "The commercial feasibility of the use of water vapor as a refrigerant", INTERNATIONAL JOURNAL OF REFRIGERATION, vol. 30, 2007, pages 699 - 708

Cited By (64)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9932830B2 (en) 2010-03-04 2018-04-03 X Development Llc Adiabatic salt electric energy storage
US10907513B2 (en) 2010-03-04 2021-02-02 Malta Inc. Adiabatic salt energy storage
US10094219B2 (en) 2010-03-04 2018-10-09 X Development Llc Adiabatic salt energy storage
US11761336B2 (en) 2010-03-04 2023-09-19 Malta Inc. Adiabatic salt energy storage
WO2013119145A3 (fr) * 2012-02-10 2015-07-16 Александр Петрович САМОЙЛОВ Procédé d'accumulation, de stockage et de récupération d'énergie mécanique et installation pour sa mise en oeuvre (et variantes)
WO2013164563A1 (fr) * 2012-04-30 2013-11-07 Isentropic Ltd Appareil de stockage d'énergie et procédé de fonctionnement d'un système de stockage d'énergie
GB2501685A (en) * 2012-04-30 2013-11-06 Isentropic Ltd Apparatus for storing energy
WO2014027093A1 (fr) * 2012-08-17 2014-02-20 Abb Research Ltd Système de stockage d'énergie électrothermique et procédé de stockage d'énergie électrothermique
EP2698506A1 (fr) * 2012-08-17 2014-02-19 ABB Research Ltd. Système de stockage d'énergie électrothermique et procédé pour stocker de l'énergie électrothermique
US10288357B2 (en) 2012-09-27 2019-05-14 Malta Inc. Hybrid pumped thermal systems
US10443452B2 (en) 2012-09-27 2019-10-15 Malta Inc. Methods of hot and cold side charging in thermal energy storage systems
US11754319B2 (en) 2012-09-27 2023-09-12 Malta Inc. Pumped thermal storage cycles with turbomachine speed control
US10012448B2 (en) 2012-09-27 2018-07-03 X Development Llc Systems and methods for energy storage and retrieval
US11156385B2 (en) 2012-09-27 2021-10-26 Malta Inc. Pumped thermal storage cycles with working fluid management
US10458721B2 (en) 2012-09-27 2019-10-29 Malta Inc. Pumped thermal storage cycles with recuperation
US10422250B2 (en) 2012-09-27 2019-09-24 Malta Inc. Pumped thermal systems with variable stator pressure ratio control
US10428693B2 (en) 2012-09-27 2019-10-01 Malta Inc. Pumped thermal systems with dedicated compressor/turbine pairs
US10428694B2 (en) 2012-09-27 2019-10-01 Malta Inc. Pumped thermal and energy storage system units with pumped thermal system and energy storage system subunits
US10458283B2 (en) 2012-09-27 2019-10-29 Malta Inc. Varying compression ratios in energy storage and retrieval systems
EP2759679A1 (fr) * 2013-01-23 2014-07-30 Siemens Aktiengesellschaft Dispositif de stockage thermique destiné à l'utilisation de chaleur à basse température
WO2014114531A1 (fr) 2013-01-23 2014-07-31 Siemens Aktiengesellschaft Dispositif d'accumulation thermique permettant d'utiliser de la chaleur basse température
US10934895B2 (en) 2013-03-04 2021-03-02 Echogen Power Systems, Llc Heat engine systems with high net power supercritical carbon dioxide circuits
US11293309B2 (en) 2014-11-03 2022-04-05 Echogen Power Systems, Llc Active thrust management of a turbopump within a supercritical working fluid circuit in a heat engine system
WO2016126300A3 (fr) * 2014-11-26 2016-10-27 General Electric Company Système de stockage d'énergie électrothermique
US10920674B2 (en) 2016-12-28 2021-02-16 Malta Inc. Variable pressure inventory control of closed cycle system with a high pressure tank and an intermediate pressure tank
US10233833B2 (en) 2016-12-28 2019-03-19 Malta Inc. Pump control of closed cycle power generation system
US11927130B2 (en) 2016-12-28 2024-03-12 Malta Inc. Pump control of closed cycle power generation system
US11053847B2 (en) 2016-12-28 2021-07-06 Malta Inc. Baffled thermoclines in thermodynamic cycle systems
US11591956B2 (en) 2016-12-28 2023-02-28 Malta Inc. Baffled thermoclines in thermodynamic generation cycle systems
US10907510B2 (en) 2016-12-28 2021-02-02 Malta Inc. Storage of excess heat in cold side of heat engine
US11454168B2 (en) 2016-12-28 2022-09-27 Malta Inc. Pump control of closed cycle power generation system
US10082045B2 (en) 2016-12-28 2018-09-25 X Development Llc Use of regenerator in thermodynamic cycle system
US10920667B2 (en) 2016-12-28 2021-02-16 Malta Inc. Pump control of closed cycle power generation system
US11371442B2 (en) 2016-12-28 2022-06-28 Malta Inc. Variable pressure inventory control of closed cycle system with a high pressure tank and an intermediate pressure tank
US11512613B2 (en) 2016-12-28 2022-11-29 Malta Inc. Storage of excess heat in cold side of heat engine
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
US10233787B2 (en) 2016-12-28 2019-03-19 Malta Inc. Storage of excess heat in cold side of heat engine
US11578622B2 (en) 2016-12-29 2023-02-14 Malta Inc. Use of external air for closed cycle inventory control
US10280804B2 (en) 2016-12-29 2019-05-07 Malta Inc. Thermocline arrays
US10221775B2 (en) 2016-12-29 2019-03-05 Malta Inc. Use of external air for closed cycle inventory control
US10907548B2 (en) 2016-12-29 2021-02-02 Malta Inc. Use of external air for closed cycle inventory control
US11352951B2 (en) 2016-12-30 2022-06-07 Malta Inc. Variable pressure turbine
US10082104B2 (en) 2016-12-30 2018-09-25 X Development Llc Atmospheric storage and transfer of thermal energy
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
US11655759B2 (en) 2016-12-31 2023-05-23 Malta, Inc. Modular thermal storage
US10830134B2 (en) 2016-12-31 2020-11-10 Malta Inc. Modular thermal storage
US11678615B2 (en) 2018-01-11 2023-06-20 Lancium Llc Method and system for dynamic power delivery to a flexible growcenter using unutilized energy sources
US11187112B2 (en) 2018-06-27 2021-11-30 Echogen Power Systems Llc Systems and methods for generating electricity via a pumped thermal energy storage system
US11624318B2 (en) 2019-10-11 2023-04-11 Enolcon Gmbh Thermal energy storage system comprising a packed-bed heat storage unit and a packed-bed cold storage unit, and method for operating a thermal energy storage system
WO2021069327A1 (fr) * 2019-10-11 2021-04-15 Enolcon Gmbh Système de stockage d'énergie thermique comprenant une unité de stockage de chaleur à lit tassé et une unité de stockage de froid à lit tassé et procédé permettant de faire fonctionner un système de stockage d'énergie thermique
US11852043B2 (en) 2019-11-16 2023-12-26 Malta Inc. Pumped heat electric storage system with recirculation
US11435120B2 (en) 2020-05-05 2022-09-06 Echogen Power Systems (Delaware), Inc. Split expansion heat pump cycle
US11846197B2 (en) 2020-08-12 2023-12-19 Malta Inc. Pumped heat energy storage system with charge cycle thermal integration
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
US11840932B1 (en) 2020-08-12 2023-12-12 Malta Inc. Pumped heat energy storage system with generation cycle thermal integration
US11578650B2 (en) 2020-08-12 2023-02-14 Malta Inc. Pumped heat energy storage system with hot-side thermal integration
US11480067B2 (en) 2020-08-12 2022-10-25 Malta Inc. Pumped heat energy storage system with generation cycle thermal integration
US11885244B2 (en) 2020-08-12 2024-01-30 Malta Inc. Pumped heat energy storage system with electric heating integration
US11486305B2 (en) 2020-08-12 2022-11-01 Malta Inc. Pumped heat energy storage system with load following
US11982228B2 (en) 2020-08-12 2024-05-14 Malta Inc. Pumped heat energy storage system with steam cycle
US11629638B2 (en) 2020-12-09 2023-04-18 Supercritical Storage Company, Inc. Three reservoir electric thermal energy storage system

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