EP2312129A1 - System zum Speichern von thermoelektrischer Energie mit einem internen Wärmetauscher und Verfahren zur Speicherung von thermoelektrischer Energie - Google Patents

System zum Speichern von thermoelektrischer Energie mit einem internen Wärmetauscher und Verfahren zur Speicherung von thermoelektrischer Energie Download PDF

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Publication number
EP2312129A1
EP2312129A1 EP09172831A EP09172831A EP2312129A1 EP 2312129 A1 EP2312129 A1 EP 2312129A1 EP 09172831 A EP09172831 A EP 09172831A EP 09172831 A EP09172831 A EP 09172831A EP 2312129 A1 EP2312129 A1 EP 2312129A1
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EP
European Patent Office
Prior art keywords
heat exchanger
working fluid
cycle
discharging
storage medium
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Withdrawn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
EP09172831A
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English (en)
French (fr)
Inventor
Mehmet Mercangoez
Jaroslav Hemrle
Lilian Kaufmann
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
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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 EP09172831A priority Critical patent/EP2312129A1/de
Priority to RU2012119524/06A priority patent/RU2012119524A/ru
Priority to JP2012532631A priority patent/JP2013507559A/ja
Priority to PCT/EP2010/065217 priority patent/WO2011045282A2/en
Priority to CN2010800469777A priority patent/CN102575529A/zh
Publication of EP2312129A1 publication Critical patent/EP2312129A1/de
Priority to US13/444,451 priority patent/US20120222423A1/en
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/12—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
    • F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
    • F01K11/04—Plants characterised by the engines being structurally combined with boilers or condensers the boilers or condensers being rotated in use
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/006—Accumulators and steam compressors

Definitions

  • the present invention relates generally to the storage of electric energy. It relates in particular to a system and method for storing electric energy in the form of thermal energy in 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 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 roundtrip efficiency of the TEES 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.
  • 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, i.e. the thermal storage medium part of a TEES, 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 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 an enthalpy-pressure diagram of the heat transfer from the cycles in a known TEES system.
  • the solid line quadrangle shows both the charging and discharging cycles.
  • the charging cycle can be considered to start at the lower left corner (indicated as I) and follows an anti-clockwise direction.
  • Point I corresponds to the working fluid state before receiving heat from the evaporator 14.
  • the temperature of the working fluid in this state is approximately -5°C to 10°C.
  • the working fluid is evaporated at constant pressure and temperature to reach point II of Figure 1 .
  • the working fluid is then compressed isentropically to the state shown as point III.
  • the temperature of the working fluid in this state is approximately 90°C to 120°C.
  • the pressure of the working fluid may be up to the order of 20MPa due to the proximity to the critical point.
  • Heat from the working fluid is transferred in an isobaric process between points III and IV to the thermal storage medium in a counter-current flow heat exchanger.
  • the working fluid is then expanded between points IV and I, in an isentropic expansion device, which enables recovery of the energy contained in the pressurized working fluid.
  • thermoelectric energy storage having a high roundtrip efficiency, whilst minimising the system costs involved.
  • 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 6. Preferred embodiments are evident from the dependent claims.
  • thermoelectric energy storage system which has a charging cycle for providing thermal energy to a thermal storage, and a discharging cycle for generating electricity by retrieving the thermal energy from the thermal storage.
  • the thermoelectric energy storage system comprises a working fluid circuit for circulating a working fluid through a first heat exchanger and a second heat exchanger, a thermal storage medium circuit for circulating a thermal storage medium.
  • the thermal storage medium circuit has at least one hot storage tank coupled to a cold storage tank via the first heat exchanger.
  • the second heat exchanger further cools the working fluid at the output of the first heat exchanger, and the amount of heat energy stored in the thermal storage medium is adjusted to ensure similar thermal storage medium temperatures during the charging cycle and discharging cycle.
  • the second heat exchanger pre-heats the working fluid at the input into the first heat exchanger, and the amount of heat energy extracted from the thermal storage medium is adjusted to ensure similar thermal storage medium temperatures during the charging cycle and discharging cycle.
  • the amount of heat energy stored is tuned such that the thermal storage medium temperature in the hot storage tank is approximately the same during charging and discharging, and that the thermal storage medium temperature in the cold storage tank is approximately the same during charging and discharging.
  • the temperature in the hot storage tank is 120° C and the temperature in the cold storage tank is 10° C.
  • the present invention utilises low cost storage materials and the first and second heat exchangers operate at a high efficiency.
  • the thermal storage medium is a liquid, and is preferably water.
  • the working fluid of the present invention is preferably carbon dioxide.
  • the second heat exchanger comprises; a first input from the first heat exchanger connected to a first output leading to an expander, and a second input from a condenser connected to a second output leading to a compressor.
  • the second heat exchanger comprises; a first input from a pump connected to a first output leading to the first heat exchanger, and a second input from a thermodynamic machine connected to a second output leading to a condenser.
  • At least one section of a charging cycle or a discharging cycle runs transcritically.
  • either the charging cycle or the discharging cycle may run without the second heat exchanger.
  • a method for storing and retrieving energy in a thermoelectric energy storage system.
  • the method comprises charging the system by heating a thermal storage medium, wherein the thermal storage medium circulates between at least one hot storage tank coupled to a cold storage tank, and discharging the system by heating a working fluid in a working fluid circuit with heat from the thermal storage medium and expanding the working fluid through a thermodynamic machine.
  • the method further comprises cooling further the working fluid output from a first heat exchanger during charging to enable the amount of heat energy stored in the thermal storage medium to be adjusted to ensure similar thermal storage medium temperatures during the charging cycle and discharging cycle, and pre-heating the working fluid input into the first heat exchanger during discharging to enable the amount of heat energy extracted from the thermal storage medium to be adjusted to ensure similar thermal storage medium temperatures during the charging cycle and discharging cycle.
  • the minimization of the temperature difference between the charging and discharging of the thermal storage medium in the hot tank and the cold tank results in a higher round-trip efficiency of the system.
  • the step of cooling further the working fluid output from the first heat exchanger during charging further comprises transferring heat from the working fluid exiting the first heat exchanger to the working fluid output from an evaporator.
  • the step of pre-heating the working fluid input into the first heat exchanger during discharging further comprises transferring heat from the working fluid exiting the thermodynamic machine to the working fluid input into the first heat exchanger.
  • the thermodynamic machine may also be referred to as a turbine.
  • At least one section of a charging cycle or a discharging cycle is performed transcritically.
  • the present invention minimises the amount of heat energy required for the adjustment of storage medium temperatures for charging and discharging, thereby minimising the size of the thermal storage required.
  • the present invention maximises the work performed by the cycle during charging and discharging for a given maximum pressure and maximum temperature of the working fluid at point IV, Figure 4 in the cycle.
  • this maximises the round-trip efficiency of the system.
  • 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, an evaporator 14, a compressor 16, a high temperature heat exchanger 18, and an internal 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 evaporator 14 and the output from the high temperature heat exchanger 18 are passed through the internal heat exchanger 20.
  • a cold storage tank 22 and a hot storage tank 24 containing a liquid thermal storage medium are coupled together via the heat exchanger 18.
  • the thermal storage liquid flows between the cold storage tank 22 and the hot storage tank 24 as indicated by the dashed 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 vaporized working fluid exiting the evaporator 14 is circulated to the compressor 16 via the internal 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 pressure of the cycle.
  • the working fluid is fed through the high temperature heat exchanger 18 where the working fluid discards heat into the thermal storage medium.
  • the compressed working fluid exits the heat exchanger 18 and enters the internal heat exchanger 20, where the remaining heat is transferred out of the compressed working fluid and into the working fluid at the outlet of the evaporator 14.
  • the cooled working fluid then enters the expander 12.
  • the working fluid is expanded to a lower pressure which corresponds to the evaporator inlet pressure.
  • the working fluid flows from the expander 12 back into the evaporator 14.
  • the fluid thermal storage medium is pumped from the cold storage tank 22 through the heat exchanger 18 to the hot storage tank 24.
  • the heat energy discarded from the working fluid into the thermal storage medium is stored in the form of sensible heat.
  • the discharging cycle system 26 shown in Figure 3 comprises a pump 28, a condenser 30, a turbine 32, a high temperature heat exchanger 18, and an internal heat exchanger 20.
  • a working fluid circulates through these components as indicated by the dotted line with arrows in Figure 3 .
  • a cold storage tank 22 and a hot storage tank 24 containing a fluid thermal storage medium are coupled together via the high temperature heat exchanger 18.
  • the thermal storage medium represented by the dashed line in Figure 3 , is pumped from the hot storage tank 24 through the heat exchanger to the cold storage tank 22.
  • the discharging cycle system 26 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 pumped to a high pressure by pump 28.
  • the working fluid then enters the internal heat exchanger 20, where it is preheated by the working fluid leaving the turbine 32.
  • the working fluid then continues to the high temperature 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 cycle.
  • the working fluid then exits the high temperature heat exchanger 18 and enters the turbine 32 where the working fluid is expanded thereby causing the turbine 32 coupled to a generator (not illustrated) to generate electrical energy.
  • the working fluid enters the condenser 30, where the working fluid is condensed by exchanging heat energy with a further thermal storage medium (not illustrated).
  • the condensed working fluid exits the condenser 30 via an outlet and is pumped again into the internal heat exchanger 20 via the pump 28.
  • the internal heat exchanger 20, the condenser 14, 30, the high temperature heat exchanger 18, cold storage tank 22, hot storage tank 24 and thermal storage medium are common to both.
  • the condenser 14, 30 may be common to both the charging and discharging cycle systems. The charging and discharging cycles may be performed consecutively, not simultaneously.
  • the high temperature heat exchanger is a counterflow heat exchanger, and the working fluid of the cycle is preferably carbon dioxide.
  • the internal heat exchanger is a counter-flow heat exchanger.
  • the thermal storage medium is a liquid, and is preferably water.
  • the compressor of the present embodiment is an electrically powered compressor.
  • thermodynamic cycle of the present invention includes heat exchange in a subcritical range as well as in a supercritical range; therefore the process follows a transcritical cycle.
  • Figure 4 shows an enthalpy-pressure diagram of the heat transfer from the cycles in a TEES system of the present invention having an internal heat exchanger.
  • the solid line quadrangle shows both the charging and discharging cycles.
  • the charging cycle can be considered to start at the lower left corner (indicated as I) and follows an anti-clockwise direction.
  • Point I corresponds to the working fluid state before receiving heat from the evaporator 14. Generally, the temperature of the working fluid in this state is approximately -5°C to 10°C.
  • the working fluid is evaporated at constant pressure and temperature to reach point II of Figure 4 .
  • the working fluid is then heated in the internal heat exchanger 20 to reach point III.
  • the working fluid is then compressed isentropically to the state shown as point IV.
  • the temperature of the working fluid in this state is approximately 100°C to 180°C.
  • the pressure of the working fluid may be up to the order of 20MPa due to the proximity to the critical point.
  • Heat from the working fluid is transferred in an isobaric process between points IV and V to the thermal storage medium in a counter-current flow heat exchanger.
  • the residual heat in the working fluid is discarded in the internal heat exchanger, shown from points V to VI. This residual heat provides the heat energy used to heat the working fluid between points II and III.
  • the working fluid is then expanded between points VI and I, in an isentropic expansion device, which enables recovery of the stored energy.
  • the TEES system with an internal heat exchanger within the working fluid circuit advantageously facilitates matching of the charging and discharging modes of operation. Such matching is required in order to achieve a high degree of reversibility.
  • the degree of reversibility (heat loss minimization) depends on the inlet and outlet temperatures of the working fluid stream entering and exiting the high temperature heat exchanger (with the thermal storage medium).
  • the operating temperatures of the TEES system in the charging mode of operation are chosen to ensure that the minimum required amount of heat at the minimum required temperature range is stored in the thermal storage medium to enable operation of the discharging mode. Therefore, in the charging cycle, the temperature of the working fluid stream leaving the high temperature heat exchanger and entering the internal heat exchanger should be chosen according to this minimizing condition. Similarly, in the discharging cycle, the superheat remaining in the working fluid stream leaving the turbine should be used to the maximum extent for preheating the working fluid stream entering the high temperature heat exchanger. In this way, the amount of heat energy needed from the thermal storage medium is minimized, which in turn will minimize the volume of thermal storage medium required.
  • the operating temperatures of the internal heat exchanger are then determined based on the combined conditions from charging and discharging modes of operation. The size of the internal heat exchanger may be chosen to accommodate the larger of the heat energy loads from the charging mode and the discharging mode.
  • the use of such an internal heat exchanger may be referred to as a "regenerative TEES scheme".
  • the regenerative charging and discharging cycles may be considered to result in two competing effects, in both the charging and discharging modes of operation.
  • the positive effect is the increased heat input via the evaporator 14 and the negative effect is the increased compression work due to higher compressor inlet temperature.
  • the evaporator 14 takes heat from a low temperature heat source, such as ice or cold water, and therewith evaporates working fluid passing through the evaporator.
  • the positive effect is the increased heat input to the high pressure side of the system and the negative effect is the loss of recovered work due to extraction of a portion of the working fluid vapor from a lower pressure stage of the system.
  • the positive effects outweigh the negative ones and such regenerative operation results in a net gain of efficiency.
  • the internal heat exchanger 20 may be used either during the charging mode or the discharging mode, and bypassed during the other mode. Such an embodiment is dependent upon the operating conditions and relative temperatures of the evaporator 14 and condenser 30.
  • the size and type of internal heat exchanger 20 may be varied dependent upon the specific TEES design. For instance, if an additional low grade waste heat source is available, the charging cycle may be modified, and the properties of the internal heat exchanger would have to be readapted in order to ensure a high degree of reversibility with minimal heat loss.
  • thermal storage medium is generally water (if necessary, in a pressurized container), other materials, such as oil or molten salt, may also be used.
  • the condenser and the evaporator in the TEES 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.
  • the 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.

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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)
EP09172831A 2009-10-13 2009-10-13 System zum Speichern von thermoelektrischer Energie mit einem internen Wärmetauscher und Verfahren zur Speicherung von thermoelektrischer Energie Withdrawn EP2312129A1 (de)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP09172831A EP2312129A1 (de) 2009-10-13 2009-10-13 System zum Speichern von thermoelektrischer Energie mit einem internen Wärmetauscher und Verfahren zur Speicherung von thermoelektrischer Energie
RU2012119524/06A RU2012119524A (ru) 2009-10-13 2010-10-11 Система аккумулирования термоэлектрической энергии с встроенным теплообменником и способ аккумулирования термоэлектрической энергии
JP2012532631A JP2013507559A (ja) 2009-10-13 2010-10-11 内部熱交換器を有する熱電気エネルギー貯蔵システム及び熱電気エネルギーを蓄えるための方法
PCT/EP2010/065217 WO2011045282A2 (en) 2009-10-13 2010-10-11 Thermoelectric energy storage system having an internal heat exchanger and method for storing thermoelectric energy
CN2010800469777A CN102575529A (zh) 2009-10-13 2010-10-11 具有内部热交换器的热电能量存储系统和用于储存热电能量的方法
US13/444,451 US20120222423A1 (en) 2009-10-13 2012-04-11 Thermoelectric energy storage system having an internal heat exchanger and method for storing thermoelectric energy

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP09172831A EP2312129A1 (de) 2009-10-13 2009-10-13 System zum Speichern von thermoelektrischer Energie mit einem internen Wärmetauscher und Verfahren zur Speicherung von thermoelektrischer Energie

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EP2312129A1 true EP2312129A1 (de) 2011-04-20

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EP09172831A Withdrawn EP2312129A1 (de) 2009-10-13 2009-10-13 System zum Speichern von thermoelektrischer Energie mit einem internen Wärmetauscher und Verfahren zur Speicherung von thermoelektrischer Energie

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US (1) US20120222423A1 (de)
EP (1) EP2312129A1 (de)
JP (1) JP2013507559A (de)
CN (1) CN102575529A (de)
RU (1) RU2012119524A (de)
WO (1) WO2011045282A2 (de)

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