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WO2015011438A1 - Appareil de stockage thermique pour applications à cycle rapide - Google Patents

Appareil de stockage thermique pour applications à cycle rapide Download PDF

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Publication number
WO2015011438A1
WO2015011438A1 PCT/GB2014/051863 GB2014051863W WO2015011438A1 WO 2015011438 A1 WO2015011438 A1 WO 2015011438A1 GB 2014051863 W GB2014051863 W GB 2014051863W WO 2015011438 A1 WO2015011438 A1 WO 2015011438A1
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WO
WIPO (PCT)
Prior art keywords
store
thermal
flow
charging
discharging
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.)
Ceased
Application number
PCT/GB2014/051863
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English (en)
Inventor
Jonathan Sebastian Howes
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Isentropic Ltd
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Isentropic Ltd
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Filing date
Publication date
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Publication of WO2015011438A1 publication Critical patent/WO2015011438A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/14—Gas-turbine plants having means for storing energy, e.g. for meeting peak loads
    • F02C6/16—Gas-turbine plants having means for storing energy, e.g. for meeting peak loads for storing compressed air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
    • F28D20/023—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat the latent heat storage material being enclosed in granular particles or dispersed in a porous, fibrous or cellular structure
    • 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
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D9/00—Adaptations of wind motors for special use; Combinations of wind motors with apparatus driven thereby; Wind motors specially adapted for installation in particular locations
    • F03D9/10—Combinations of wind motors with apparatus storing energy
    • F03D9/17—Combinations of wind motors with apparatus storing energy storing energy in pressurised fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D9/00—Adaptations of wind motors for special use; Combinations of wind motors with apparatus driven thereby; Wind motors specially adapted for installation in particular locations
    • F03D9/10—Combinations of wind motors with apparatus storing energy
    • F03D9/18—Combinations of wind motors with apparatus storing energy storing heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/0056—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using solid heat storage material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
    • F28D20/028—Control arrangements therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/42—Storage of energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D2020/0065—Details, e.g. particular heat storage tanks, auxiliary members within tanks
    • F28D2020/0069—Distributing arrangements; Fluid deflecting means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D2020/0065—Details, e.g. particular heat storage tanks, auxiliary members within tanks
    • F28D2020/0078—Heat exchanger arrangements
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/14—Thermal energy storage
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/16—Mechanical energy storage, e.g. flywheels or pressurised fluids
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E70/00—Other energy conversion or management systems reducing GHG emissions
    • Y02E70/30—Systems combining energy storage with energy generation of non-fossil origin

Definitions

  • the present invention relates to thermal storage apparatus and methods for operating such apparatus, as well as systems incorporating such apparatus, especially energy storage systems.
  • Thermal energy storage (TES) apparatus (or thermal stores) is used to store thermal energy, which may be heat or cold (including cryogenic temperature energy) until subsequently required, and has found application within many industrial processes, such as chemical processing and metal refinement. More recently, TES apparatus has found application in energy storage systems, including adiabatic compressed air energy storage (ACAES) plants or solar energy or wind based energy plants, especially where back-up capacity is required.
  • TES apparatus is characterised as containing a thermal storage medium i.e. a mass of thermal energy absorbing or rejecting material through which a thermal exchange fluid or heat transfer fluid (HTF) (e.g.
  • the thermal storage medium may be in the form of a porous storage mass, which may be a packed bed of solid particles through which the fluid passes exchanging thermal energy directly, or, it may comprise a solid matrix or monolith provided with HTF channels or interconnecting pores extending therethrough, or, the fluid may pass through a network of heat exchange pipes that separate it from the storage mass, such as a packed bed of particles (e.g. rocks).
  • a 'thermal front' is created in the store, i.e. a rise or a fall in temperature in the thermal storage medium with distance moved downstream, which occurs in the region of the store where thermal transfer is most active.
  • Figure 1 illustrates the formation of a thermal front in a thermal store and shows how the process of charging a thermal store sets up a thermal front within a region of the store that progresses downstream and that is usually initially quite steep but which becomes progressively shallower as charging continues.
  • the front may start with length L1 , but as it moves down the vessel it extends in length to length L2 and then L3.
  • the length of the front can be discussed in terms of the length of the front between TH2 and TA2, these being for example within 3% of the peak temperature and start temperature.
  • a similar front occurs in the heat transfer fluid with distance down the store, with the front of the storage medium inevitably lagging the front in the fluid.
  • a heat store will operate with a hotter end and a colder end so as to minimise exergy loss, whereby hotter heat transfer fluid arrives at the hotter end and passes down the length of the store losing heat until it exits the store at the cooler end in one of a charging or discharging phase, and, in the other phase, cooler heat transfer fluid is passed in the reverse direction through the store before exiting as reheated fluid at the hotter end.
  • the fluid has a hot thermal front moving down the store, and in the other phase, a cooler thermal front will make the return travel.
  • the practice will be to keep the thermal front held within the store by ceasing to charge or discharge just before the front leaves the store such that the HTF emerges at the same temperature as the nose or tail of the front.
  • Applicant's earlier application WO201 1/104556 describes a thermal store in which the size and type of media can be varied through the store to either reduce the irreversibilities that are created when a thermal front is generated or else to help reduce the pressure drop.
  • TES apparatus wherein the storage media is divided up into separate respective downstream sections or layers.
  • the flow path of the heat transfer fluid through the layers can be selectively altered so as to access only certain layers at selected times, so as to avoid pressure losses through inactive sections upstream or downstream of the sections where the thermal front is located.
  • TES apparatus typically operates in a charging phase, storage phase (e.g. part of fully charging) and discharging phase and, as mentioned above, usually operates such that HTF flow reverses between charging and discharging phases.
  • the TES may be subject to "rapid cycling" i.e. short cycle (or low amplitude) flow reversals (e.g. such that a single direction flow pulse will only move a thermal front over a distance in a store that is very much less than the available front travel within that store).
  • Sensible heat stores (as opposed to latent heat stores) within any rapid cycling system are prone to a loss of effectiveness over successive cycles.
  • the thermal front behaviour associated with this class of heat store will reduce in gradient (dT/dx where x is distance along the store) with each successive flow reversal until a stable condition is achieved, in which each end of the thermal front reaches the store end on every flow reversal.
  • dT/dx where x is distance along the store
  • Applicant's earlier application WO 2009/044139 discloses an energy storage system using thermal stores, namely, a Pumped Heat Energy Storage system (PHES) which, in addition to being cycled between long phases of charging and discharging, may need to be cycled through a small amplitude (e.g. short period of charge followed by a short period of discharge).
  • PHES Pumped Heat Energy Storage system
  • a hot store and a cold store are connected to each other by a compressor and expander acting on a working gas circulating in a circuit.
  • heat is effectively pumped from one store to the other by the working gas so as to heat the "hot store” (i.e. charging it with heat) and cool the "cold store” (i.e.
  • the process is reversed with the "cold store” being used to cool gas prior to compression (i.e. discharging its cold) before the gas is heated in the "hot store” (i.e. discharging its heat) and expanded to generate power.
  • the system can use a variety of different types of compressors and expanders, some examples are reciprocating, rotary screw, sliding vane, axial or centrifugal.
  • the present Applicant has identified the need for an improved thermal storage apparatus that is better suited to applications where there may be rapid cycling.
  • thermal storage apparatus for storing and returning thermal energy to a heat transfer fluid passing through the apparatus, comprising:
  • each thermal store comprising fluid-permeable thermal storage media disposed in a chamber for transferring thermal energy to or from the heat transfer fluid
  • flow controllers for selectively altering the flow path of the heat transfer fluid through the apparatus
  • the apparatus is configured to be operable in different respective flow modes, wherein in at least one flow mode the apparatus is operable in alternative phases of charging and discharging as the nature of the incoming heat transfer fluid changes, and at least one store is selectively configured to perform the charging while at least one other store is selectively configured to perform the discharging, thereby minimising or avoiding switching of those individual stores between charging and discharging in that flow mode and the thermal front reversals associated therewith.
  • Operable in alternative phases of charging and discharging as the nature of the incoming heat transfer fluid changes is intended to mean that the apparatus as a whole in that flow mode (or flow set-up) is operable in, and able to switch between, a charging function or discharging function depending on the changing nature of the incoming heat transfer fluid requirement (e.g. temperature/direction); however, in addition to those active phases, the apparatus may also switch into other phases e.g. an inactive storing phase.
  • Charge can mean to charge with heat (or store heat) in which case the discharging is discharging or returning of the heat, or, it can mean to charge with cold (return heat), in which case the discharging is discharging of that cold (or storing heat).
  • heat or store heat
  • cold return heat
  • the storage medium heats in one phase and cools in the other phase, but the charging and discharging nomenclature is of assistance when discussing thermal storage that forms part of energy storage systems.
  • the at least one store may be selectively configured only to perform charging while the at least one other store may be selectively configured only to perform the discharging, so as to avoid any switching of those individual stores between charging and discharging and the thermal front reversals associated therewith.
  • the present invention is concerned with the problem of protecting the integrity of thermal fronts within a thermal storage apparatus required to switch between charging and discharging, i.e. as alternative active operational phases, and where the thermal fronts in individual stores would normally reverse their direction whenever the function of the individual store changes between charging and discharging, such that especially low amplitude, rapid cycling switching of the apparatus per se would cause degradation of the steepness of the thermal front (i.e. undesirable front lengthening) in those individual stores.
  • stores are not caused to switch their individual charging or discharging functions (causing front reversal) every time the apparatus per se is required to switch its charging/discharging function (e.g. due to the heat transfer fluid reversing its direction through the thermal storage apparatus).
  • the apparatus has at least one flow mode that protects individual stores from rapid, low amplitude cycling (i.e. where the apparatus is prone to frequent switching between charging and discharging) by virtue of the fact that, within that one flow mode, the selected at least one store and at least one other store have their dedicated respective charging and discharging roles.
  • a thermal front may progress steadily in one direction (e.g. in the discharging store in increments corresponding to the respective bursts of required discharging activity) along the store, usually from near or at one end of the store towards the other, without reversing.
  • both the at least one store and the at least one other store are each configured such that a thermal front is only allowed to progress in a single direction along each respective store, without reversal, during the at least one flow mode.
  • the apparatus is configured to switch from the at least one flow mode to a different flow mode when a selected end condition is reached in the at least one store or at least one other store. While the at least one flow mode may be interrupted before either store has become fully charged or discharged, ideally, the flow mode is maintained for as long as possible until one (or simultaneously both) of the selected stores is about to exceed a preselected maximum capacity (i.e. selected end condition) such that the apparatus cannot continue in that mode. Ideally, the apparatus is configured to switch from the at least one flow mode to a different mode just as a thermal front approaches the end of a thermal store, so as to retain and preserve that front in that store, for when the store is next required to perform the alternative charging/discharging function.
  • the apparatus is configured such that, in the at least one flow mode, it can switch between charging and discharging without altering the setting of flow controllers that control the flow to the respective at least one store and at least one other store.
  • the apparatus may be able to switch between charging and discharging merely by reversing the direction of the heat transfer fluid through the thermal storage apparatus.
  • the apparatus comprises two thermal stores, wherein the apparatus is also operable in a second flow mode in which the at least one store is selectively configured to perform the discharging while the at least one other store is selectively configured to perform the charging.
  • the two stores reverse their functions between the two flow modes.
  • stores may also be present and may be allocated those functions so that different respective pairs of stores are used in different respective flow modes.
  • two or three or more stores may be allocated the respective charging and discharging functions in each mode, and they may be selected on the basis of differing physical characteristics between different stores.
  • the heat transfer fluid may be a liquid or gas/vapour; the latter may apply where the fluid acts as a working fluid in a gas based thermodynamic cycle.
  • Thermal transfer will usually occur under isobaric conditions.
  • the at least one thermal store and at least one other thermal store may be configured to receive a heat transfer fluid at substantially similar pressures.
  • the fluid-permeable thermal storage medium may comprise any materials suitable for direct thermal exchange with the heat transfer fluid at the temperatures and pressures contemplated.
  • the media may comprise a monolithic porous structure provided with through passageways and/or a network of interconnecting pores, or, may comprise a particulate material.
  • the gas-permeable thermal storage medium comprises particulate material.
  • the particulate material may comprises solid particles and/or porous media and/or fibres and or foamed material (e.g. metallic, mineral or ceramic particles and/or fibres and/or foam) packed to form a gas-permeable thermal storage structure.
  • the invention is applicable to thermal stores in which the media is arranged as a continuous mass (e.g. single monolithic porous mass or particulate media), or where it is separated into respective downstream layers, as described above in relation to Applicant's layered store application.
  • a continuous mass e.g. single monolithic porous mass or particulate media
  • the apparatus is operable both to charge and discharge as alternative active modes (i.e. modes where flow occurs), so that charging or discharging is conducted sequentially; there will, however, be other inactive modes e.g. where the apparatus is left in a fully charged, part charged or fully discharged state.) It is applicable to systems or equipment in which the working fluid flows through the thermal storage apparatus in one direction upon charging and the opposite direction upon discharging (e.g. where the thermal storage apparatus has an inlet/outlet at one end and an outlet/inlet at the opposed end), and to systems or equipment in which the heat transfer fluid acts as a working fluid (i.e. undergoing compression and/or expansion) doing work within a thermodynamic cycle.
  • alternative active modes i.e. modes where flow occurs
  • inactive modes e.g. where the apparatus is left in a fully charged, part charged or fully discharged state.
  • the thermal storage apparatus may be located within and may charge and discharge the heat transfer fluid to a single primary (closed) circuit (e.g. a pumped heat energy storage system) or limb (open circuit), which may form part of an energy storage system, or, may charge the heat transfer fluid to a primary circuit and discharge the heat transfer fluid to a secondary circuit of the system of which it forms a part.
  • a single primary (closed) circuit e.g. a pumped heat energy storage system
  • limb open circuit
  • the thermal storage apparatus may form part of an energy storage system. This may be powered by electricity in a charging phase and/or return electricity (e.g. to the electricity grid) in a discharging phase.
  • the energy storage system may be powered by solar power or wind power.
  • Thermal storage apparatus as configured above is particularly suited for use in an energy system powered by wind, solar or other power sources prone to fluctuating behaviour.
  • the energy storage system may comprise a compressed air energy storage CAES system, especially an adiabatic CAES.
  • the energy storage system may comprise a pumped heat energy storage system for storing and returning energy comprising:
  • a first engine stage configured to act as a compressor during a charging phase of a cycle and as an expander during a discharging phase of the cycle;
  • a first thermal storage arrangement for receiving and storing thermal energy from gas compressed by the first engine stage during the charging phase
  • a second engine stage configured to act as an expander during the charging phase to expand gas received from the first thermal store and as a compressor during the discharging phase;
  • thermo storage arrangement for transferring thermal energy to gas expanded by the expander during the charging phase; wherein one or both of the first and second thermal storage arrangements comprises thermal storage apparatus as defined above.
  • thermal storage apparatus for storing and returning thermal energy to a heat transfer fluid passing through the apparatus, comprising:
  • each thermal store comprising fluid-permeable thermal storage media disposed in a chamber for transferring thermal energy to or from the heat transfer fluid, and, flow controllers for selectively altering the flow path of the heat transfer fluid through the apparatus,
  • the apparatus is configured such that heat transfer fluid will pass through each store in a first direction if that store is storing thermal energy and in the reverse direction if that store is returning thermal energy, and
  • the apparatus is configured to be operable in at least one flow mode wherein the apparatus is operable both to store thermal energy and return thermal energy, but not simultaneously, and at least one store is selectively configured only to store the thermal energy while at least one other store is selectively configured only to return the thermal energy, thereby minimising or avoiding switching of those individual stores between the storing and returning functions and the thermal front reversals associated therewith.
  • thermo storage apparatus to store and return thermal energy to a heat transfer fluid passing through the apparatus, wherein the apparatus comprises:
  • each thermal store comprising fluid-permeable thermal storage media disposed in a chamber for transferring thermal energy to or from the heat transfer fluid
  • the apparatus switches between operating in alternative charging and discharging phases, and at least one store is selectively configured to perform the charging while at least one other store is selectively configured to perform the discharging, thereby minimising or avoiding switching of those individual stores between charging and discharging and the thermal front reversals associated therewith.
  • the thermal storage apparatus may cycle between phases of charging and discharging activity (i.e. that activity is not simultaneous) in the at least one flow mode while in each store a thermal front advances progressively in only a single direction relative to each respective store in steps corresponding to the respective phases of activity.
  • the apparatus may switch to a different flow mode in response to a thermal front reaching the other end of one of the respective stores.
  • the apparatus comprises two or more thermal stores connected in parallel with each other, each thermal store comprising fluid-permeable thermal storage media disposed in a chamber for transfer of thermal energy to or from a heat transfer fluid passing through the media, and flow controllers for selectively altering the flow path of the heat transfer fluid through the apparatus,
  • the apparatus is configured such that heat transfer fluid will pass through each store in a first direction if that store is storing thermal energy and in the reverse direction if that store is returning thermal energy, and
  • the method comprising operating the apparatus in at least one flow mode in which the apparatus switches alternately between storing thermal energy and returning thermal energy and at least one store is assigned solely for storing thermal energy and at least one other store is assigned solely for returning thermal energy such that, during that flow mode, the heat transfer fluid does not reverse direction within either store when the apparatus switches.
  • apparatus for storing and returning energy comprising:
  • a first engine stage configured to act as a compressor during a charging phase of a cycle and as an expander during a discharging phase of the cycle;
  • a first thermal storage arrangement for receiving and storing thermal energy from gas compressed by the first engine stage during the charging phase
  • a second engine stage configured to act as an expander during the charging phase to expand gas received from the first thermal store and as a compressor during the discharging phase;
  • thermo storage arrangement for transferring thermal energy to gas expanded by the expander during the charging phase; wherein at least one of the first and second thermal storage arrangements comprise:
  • the apparatus in a first mode of operation the apparatus is operative to pass gas through the first thermal store during the charging phase and to pass gas through the second thermal store during the discharging phase;
  • the apparatus in a second mode of operation the apparatus is operative to pass gas through the first thermal store during the discharging phase and to pass gas through the second thermal store, or through a further thermal store connected in parallel to the first and second thermal stores, during the charging phase.
  • apparatus for storing energy in which the at least one of the first and second thermal storage arrangements may be switched between a charging phase and discharging phase without the need to reverse gas flow through a partially discharged/charged thermal store.
  • the apparatus is operative to: charge the first thermal store from a substantially uncharged configuration to a substantially fully charged configuration without any intermediate discharging of the first thermal store; or, to discharge the second thermal store from a substantially fully charged configuration to a substantially uncharged configuration without any intermediate charging the second thermal store.
  • the first and second engine stages comprise separate apparatus.
  • the apparatus may comprise separate apparatus for respectively compressing and expanding gas, or may comprise a device operable in a first mode to compressor gas and operable in a second mode to expand gas.
  • first and second engine stages may involve the use of the same apparatus for compressing and expanding gas (e.g. with compression and expansion occurring sequentially by alternative connections).
  • the apparatus comprises: a valve arrangement operative to configure the apparatus between the first and second modes of operation; and a controller (e.g. mechanical or electronic controller) operative to control operation of the valve arrangement to switch between the first and second modes of operation.
  • a controller e.g. mechanical or electronic controller
  • the apparatus is configured to generate gas flow in a first direction during charging and in a second direction, opposed to the first direction, during discharging, and the valve arrangement is operable:
  • the valve arrangement comprises first and second valves (e.g. first and second interruptible non-return valves) for controlling gas flow through one of the first and second thermal stores, the first and second valves being connected in series and being configurable between:
  • first valve mode in which flow is permitted through the first valve in the first direction only and through the second valve in both the first and second directions
  • a second valve mode in which flow is permitted through the second valve in the second direction only and through the first valve mode in both the first and second directions
  • the one of the first and second thermal stores is positioned in series between the first and second valves.
  • the apparatus comprises a circuit configured to allow gas to pass cyclically between the first and second stages during at least one of the charging phase and the discharging phase.
  • the first and second thermal stores are configured to receive gas at substantially similar pressures.
  • At least one of the first and second thermal stores comprise: a chamber for receiving gas; and a gas-permeable thermal storage medium housed in the chamber (i.e. to allow direct heat transfer between the gas flow and the thermal storage medium).
  • the second thermal store comprises first and second thermal sub-stores connected in parallel and the apparatus is configured to pass gas through either the first thermal sub-store or through second thermal sub-store.
  • the apparatus is operative to pass gas through the first thermal sub-store when a temporary change between the charging and discharging phases is determined to last for a time period below a predetermined threshold and operative to pass gas through the second thermal sub-store when a temporary change between the charging and discharging phase is determined to last for a time period above the predetermined threshold.
  • the second thermal sub-store is configured to provide a thermal charge/discharge efficiency which is higher (e.g. substantially higher) than that of the first thermal sub-store.
  • first and second thermal storage arrangements comprise: a first thermal store
  • Figure 1 is a graph illustrating thermal front progression within a storage vessel
  • Figures 2a and 2b show thermal storage apparatus according to a first embodiment of the present invention operating in two respective flow modes;
  • FIGS. 3a to 3h are schematic illustrations of the thermal storage apparatus of Figure 2 in a plurality of charging configurations during use in two flow modes;
  • Figure 4 shows a schematic illustration of an energy storage system according to a second embodiment of the present invention
  • Figures 5a to 5e illustrate the energy storage system of Figure 4 in a plurality of charging configurations during use
  • FIGS. 6a to 6c illustrate in more detail the operation of a hot storage arrangement of Figure 4;
  • Figures 7a and 7b illustrate the operation of the hot storage arrangement of 5 Figure 4 in a first flow mode
  • Figures 8a and 8b illustrate the operation of the hot storage arrangement of Figure 4 in a second flow mode
  • Figure 9 is a schematic illustration of a hot storage arrangement according to a further embodiment of the invention.
  • FIGS 2a and 2b show thermal storage apparatus 81 according to a first embodiment of the present invention for storing and returning thermal energy, especially in applications where the apparatus may be subjected to successive part charge/part discharge cycles.
  • Such apparatus may, for example, form part of a chemical processing 15 plant or an energy storage system.
  • Figures 2a and 2b respectively depict two respective flow modes (or flow set-ups) in which the apparatus 81 may operate, with the apparatus being able to both charge and discharge in each respective flow mode.
  • the apparatus 81 comprises two pressure vessels 82, 84 20 acting as thermal stores arranged in parallel.
  • the apparatus and stores are arranged vertically between a downward Hot Feed HF, such that hot working fluid approaches the apparatus from above and moves downwardly through the apparatus/stores, and an upward Cold Feed CF, whereby, alternatively, relatively colder working fluid approaches the apparatus from below and moves upwardly 25 through the apparatus/stores.
  • a hot front bringing relatively hotter fluid
  • a cold front bringing relatively colder fluid
  • each store 82, 84 has an upper port branching into two 30 conduits each containing a non-return valve NRV 88, which valves are in opposed arrangements so that they permit fluid flow in opposed directions in the respective conduits.
  • the conduits rejoin into a single upward conduit 83 at a junction provided with a selector valve 86 which, as depicted, can be alternatively adjusted so that one or other of the conduits is in open communication with conduit 83.
  • Conduits 83 from each store 82, 35 84 meet and join in a single upper conduit 85 through which the Hot Feed would be supplied.
  • a conduit 87 supplying the Cold Feed branches into respective conduits leading to the lower port of each store without any valving present to inhibit flow.
  • the two thermal stores 82, 84 are provided in parallel with this valving with the aim of maintaining a common flow direction (thermal front direction) within each individual store despite periodic reversing of the flow direction within the apparatus per se, which would otherwise cause undesired lengthening of the thermal front due to the successive flow reversals in a single store.
  • a system including a heat storage function may exist in two HTF flow conditions defined by reversal of a flow of heat transfer fluid across the heat storage element, where the flow in one direction will be arriving as a hotter flow and the flow in the other direction will be arriving as a relatively cooler flow. These may be defined as “HTF flow condition one" and “HTF flow condition two" and relate to the heat transfer fluid.
  • the heat storage element may comprise two heat stores connected to the system fluid flow circuit in parallel (but further stores in parallel could also be used). Each heat store may be either heated by the fluid flow, thus cooling the flow, or the store cooled by the flow, hence heating the flow and these states are referred to as HS “heating store” or CS “cooling store” respectively.
  • HTF flow condition one store A is a cooling store and flow is prevented (eg by a valve) from passing through store B.
  • HTF flow condition two store B is a heating store and flow is prevented from passing through store A. Therefore, if the system flow is repeatedly changed or cycled between HTF flow conditions one and two, store A only acts as a cooling store and store B only acts as a heating store with the thermal fronts in each store progressing intermittently in a single direction on each cycle of switching between flow conditions one and two, as the direction (and nature) of the heat transfer fluid changes.
  • the system can be regarded as being in a first flow mode of operation, where flow controllers have assigned the store A and B the above respective functions. If the system alters to a different flow mode of operation (upon reaching the selected end condition) where the flow controllers now assign the opposite functionality to the stores, then store A becomes the heating store under HTF flow condition two, while store B becomes a cooling store under HTF flow condition one (i.e. as heat transfer fluid direction changes).
  • Figure 2a shows a first flow mode of operation where selector valves 86 have assigned store 82 and 84 the respective functionalities of CS Cooling Store and HS Heating Store, regardless under which HTF flow condition the heat transfer fluid is operating (i.e. whether HF or CF is arriving).
  • fluid flow CF from bottom to top of the diagram is prevented from passing through the right hand store 84 (acting as the "heating store” HS) by the right hand selector valve 86 blocking feed from the relevant non-return valve.
  • the flow CF will pass through the left hand cooling store 82 CS as the left hand selector valve 86 has opened the flow path to flow in this direction via the appropriate non-return valve.
  • valve combination on the left prevents flow from passing through the cooling store 82 CS but allows it to pass through the heating store 84 HS.
  • the system Upon reaching the selected end condition in the first flow mode of operation, the system needs to alter to a different flow mode of operation and this is accomplished in this embodiment merely by adjustment of the selector valves 86, without adjustment of the parallel NRV's.
  • Figure 2b shows a second flow mode of operation where selector valves 86 have assigned store 82 and 84 the now respective reverse functionalities of HS Heating Store and CS Cooling Store, regardless under which flow condition the heat transfer fluid is operating (i.e. whether HF or CF is arriving).
  • the thermal front directions change and the left hand store becomes the "heating store” while the right hand store becomes the "cooling store”.
  • the arrows in the stores in both figures are intended merely to indicate the respective directions of the thermal fronts in each store; there is no simultaneous reverse flow in both stores.
  • a selected end condition should be chosen for each store since either may reach that condition first.
  • the selected end condition may be chosen to be such that the thermal front is close to but has not yet exited the store (it being desirable to keep a front within a store, rather than needing to create a new one), and it may be detected, for example, by monitoring for a certain rise or fall in exit gas temperature from the system.
  • a selected end condition may only correspond for example to -50-75% of the full theoretical capacity of the storage medium (if 100% corresponds to the whole store rising to say close to the entry temperature of a hotter transfer fluid), with steeper fronts leading to higher capacities.
  • the switching of the selector valves 86 may be made automatic by sensing of the store downstream temperatures. When these show a variation beyond a limit acceptable to the system, then both selector valves are switched and the fronts in each store change direction while the stores swap roles from “cooling” to “heating” and vice versa.
  • references to heating and cooling may involve both heating and cooling of the store, and in the context of the present specification, references to charging should be understood to mean either charging with heat, in which case discharging will be discharging of that heat, or, charging with cold, in which case the discharging will be discharging of that cold.
  • thermal storage apparatus comprising at least two parallel thermal stores that are assigned respective charge and discharge roles within at least one flow mode, together with appropriate associated flow controllers, it is possible to maintain thermal front quality in situations where the apparatus is subjected to rapid cycling.
  • the "heating" and “cooling” stores may then be configured to switch function by the flow controllers switching the apparatus to a different flow mode, as and when either store is incapable of preserving its original function due to its charge state; in the different flow mode, the same pair of stores may be assigned the reverse functionality, or one or more different new stores may be assigned that functionality.
  • FIGs 3a to 3h are schematic illustrations of the thermal storage apparatus of Figure 2 illustrating how it progresses through a plurality of charging states during use in two flow modes M1 and M2.
  • flow mode M1 (corresponding to Figure 2a flow mode)
  • Cooler Fluid flow can only pass up through the apparatus via left hand store 82.
  • Cooler Fluid flow can only pass up through the apparatus via right hand 5 store 84. Hatching denotes charging with heat with thermal fronts 82a and 84a in stores 82 and 84 shown as horizontal borders for simplicity (although their profiles would more resemble those of Figure 1).
  • Figure 3a shows that in operative mode M 1 store 82 is fully charged with heat and is assigned as Cooling Store CS, while store 84 is empty of heat (although preferably with
  • Figure 3e shows the two stores have reached a point where the flow mode needs to switch to flow mode M2 because the selected end condition for the Heating Store HS 84 has been reached with the hot front just adjacent the end of that store so that any further charging of that store would
  • Flow mode M2 is therefore selected by the selector valves so that stores 82 and 84 swap such that they are assigned as HS and CS respectively, as shown in Figure 2b. It will be noted that the front in Figure 3e is therefore forced to change direction before it reaches the end of that store.
  • Figure 3g shows a hot front moving down store 82 as it acts as HS. If the pair of stores is not thereafter subjected to a requirement to discharge heat, it is possible for the hot front in store 82 to reach the end such that both stores become fully charged with heat. Thereafter no further charging is possible.
  • 35 mode M2 can trigger the apparatus swapping back to flow mode M1 so store 82 acts as Cooling Store CS.
  • the apparatus could remain in flow mode M2, such that store 84 continues in its function of Cooling Store CS.
  • flow mode switching may be initiated, or, in the event that no further (e.g. third parallel store) functionality of that type is available, the apparatus may remain in the same mode, or swap to a further flow mode in which, for example, functionality is not assigned to preserve front quality but where, for example, stores are used in parallel to achieve a high charge or discharge rate.
  • operation of the at least two parallel stores in the at least one flow mode may be expressed as:-
  • thermal fronts have remained static in each store or progressed in increments in only one direction in that store.
  • Thermal front reversal in each store is not therefore linked to a change of direction of the heat transfer fluid through the apparatus (i.e. associated with a change in requirement between the alternative functions of charging and discharging of the apparatus), but rather is linked to a change of flow mode preferably initiated by the reaching of a selected end condition in one store, and achieved by a change of valving.
  • FIG. 4 shows an electricity storage system 10 comprising a hot storage arrangement 20, a cold storage arrangement 30, first and second compressor/expanders 40, 50, interruptible non-return valves (NRVs) 60, and an arrangement of interconnecting pipes 70 for conveying working gas around the system to form a gas circuit 80.
  • Hot storage arrangement 20 comprises first and second insulated hot storage vessels 22, 24 each housing a gas-permeable particulate thermal storage structure 22a, 24a respectively.
  • Cold storage arrangement 30 comprises first and second insulated cold storage vessels 32, 34 each housing a gas-permeable particulate thermal storage structure 32a, 34a respectively.
  • gas that may be near ambient temperature or at a different temperature, but at a higher pressure exits hot storage arrangement 20 and is expanded by second compressor/expander 50 to a lower pressure.
  • the gas is cooled during this expansion and passes to cold storage arrangement 30 where the cooled gas is heated (thereby cooling the cold storage arrangement 30).
  • the now hotter gas leaves cold storage arrangement 30 at a temperature that may be around ambient or a temperature that is different to ambient.
  • the gas then enters first compressor/expander 40 where the gas is compressed to the higher pressure. As the gas is compressed the temperature rises and the gas leaves the compressor at a higher temperature and passes into hot storage arrangement 20 where the gas is cooled (thereby heating the hot storage arrangement 20).
  • the now cooler gas leaves hot storage arrangement 20.
  • the process can continue until the hot and cold stores are 'fully charged' (i.e. fully heated and cooled respectively) or stop earlier if required.
  • This overall charging process absorbs energy that is normally supplied from other generating devices via the electric grid.
  • the compressor/expanders 40, 50 are driven by a mechanical device, such as an electric motor (not shown).
  • cold storage arrangement 30 is charged with cold with the flow entering from the bottom and travelling upwards and discharged of cold with the flow entering from the top and travelling downwards.
  • Hot storage arrangement 20 is charged with heat with the flow entering from the top and travelling downwards and discharged of heat with the flow entering from the bottom and travelling upwards.
  • the overall discharging process generates energy that is normally supplied in an electrical form (e.g. back to the electric grid).
  • the compressor/expanders 40, 50 drive a mechanical device, such as an electric generator (not shown).
  • Figures 5a)-e) show in more detail a preferred manner in which hot and cold storage arrangements 20, 30 of a PHES system are charged/discharged.
  • fully charged configurations A and B refer to respective operatively linked fully charged pairs of stores (e.g. 22 and 34, or, 32 and 24); in fact, in this example, only half of the total thermal storage capacity of the four stores is ever used in order to ensure that any low amplitude cycling can be met without any thermal front reversals in individual stores. Further a fully discharged store in this example may have some thermal energy still remaining in that store due to deliberate retention of a region of thermal front: the creation of a new thermal front can create losses so that it may be more efficient to 'keep' it to use with the next charge cycle.
  • Figure 5a shows the electricity storage system 10 in a first charged configuration
  • first insulated hot storage vessel 22 of hot storage arrangement 20 and second insulated cold storage vessel 34 of cold storage arrangement 30 are each fully charged and second insulated hot storage vessel 24 of hot storage arrangement 20 and first insulated cold storage vessel 32 of cold storage arrangement 30 are each fully discharged.
  • Figure 5b shows electricity storage system 10 during a subsequent charging phase in which charging of the second insulated hot storage vessel 24 and first insulated cold storage vessel 32 has begun.
  • Figure 5c shows electricity storage system 10 during a subsequent short discharging phase triggered (e.g. by a sudden brief demand for electricity to be generated by the system 10) before charging of the second insulated hot storage vessel 24 and first insulated cold storage vessel 32 is complete.
  • the flow of gas is not reversed through second insulated hot storage vessel 24 and first insulated cold storage vessel 32 but instead is reversed through first insulated hot storage vessel 22 and second insulated cold storage vessel 34 that are each primed for discharge.
  • Figure 5e shows electricity storage system 10 in a second fully charged configuration "B" in which second insulated hot storage vessel 24 and first insulated cold storage vessel 32 are each fully charged and first insulated hot storage vessel 22 and second insulated cold storage vessel 34 are each fully discharged.
  • Figures 6a to 6c, 7a, 7b, 8a and 8b show in more detail the operation of the electricity storage system 10, and in particular, the operation of NRVs 60 to control gas flow through hot storage arrangement 20 (operation of the apparatus on the cold storage side is equivalent).
  • an NRV 60 is positioned at each end of each of insulated hot storage vessels 22, 24 and each of insulated cold storage vessels 32, 34 (with each NRV 60 being operative when acting to restrict the direction of gas flow to allow gas flow into its respective storage vessel).
  • NRVs 60 have two modes of operation: a first mode in which they are configured to act as conventional non-return valves and permit gas flow in one direction only; and a second mode in which the operation of the valves is "interrupted" to permit gas flow in opposed directions.
  • each NRV 60 may be a simple mechanical flap valve 62 that pivots around a pivot point "P" with a lever 64 also attached at the pivot point and capable of being acted upon by an actuating force as shown in Figure 6c so as to hold the valve 62 open ("the interrupted" state).
  • first insulated hot storage vessel 22 is defined as being in a "charge” state, as shown, whilst second insulated hot storage vessel 24 is assigned the opposed functionality i.e. is in a "discharge” state.
  • the valve states remain the same regardless of whether system 10 is charging ( Figure 7b) or discharging ( Figure 7a).
  • the "charge" store 22 the NRV 60 that prevents flow in a hot to cold direction is interrupted (i.e. held open) and the NRV 60 that prevents flow in a cold to hot direction will allow flow in a hot to cold direction (i.e. charge direction).
  • the NRV 60 that prevents flow in a hot to cold direction will allow flow in a cold to hot direction (i.e. discharge direction) and the NRV 60 that prevents flow in a cold to hot direction is interrupted (i.e. held open). In this way, working gas entering the manifold at the hot end of the stores will 5 only pass through the "charge” store 22, as shown. If, on the other hand, working gas enters the manifold at the cold end of the stores, it will only pass through the "discharge” store 24 (not shown). When the gas flows are intermittent and reversed frequently, the thermal fronts within "charge” and "discharge” stores 22, 24 will nevertheless progress steadily along their respective stores over the course of multiple cycles without any
  • the stores are swapped over to a different operative flow mode by changing the flow controllers, namely, the interrupted NRVs 60 are released to normal operation (e.g. by an electronic or mechanical controller) and the previously active NRVs
  • valve states again remain the same regardless of whether system 10 is charging (Figure 8b) or discharging (Figure 8a), since those valve states only needed to alter when a requirement for further capacity (e.g. a front in one of the 5 stores approaching a store end) caused them to reverse the two stores 22, 24 respective functions.
  • a requirement for further capacity e.g. a front in one of the 5 stores approaching a store end
  • Figure 9 shows a modified hot storage arrangement 20' including an alternative 35 valve arrangement in which pairs of NRVs 60' are located at one end of the stores 22, 24. As illustrated, the NRVs 60' of each pair are of opposed directionality when operative to restrict flow to one direction with each NRV 60' of the pair facing the other NRV 60' of the pair. Operation of this valve arrangement is equivalent to valve arrangement discussed in relation to Figure 6a and this alternative valve arrangement is equally suitable for use with cold storage arrangement 30.
  • the charging and discharging functions may be shared among more stores e.g. three or four stores; further, the at least one store and at least one other store may each comprise sub-stores connected in series or in parallel.

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Abstract

Appareil de stockage thermique (81) destiné à stocker et à renvoyer l'énergie thermique à un fluide de transfert de chaleur traversant l'appareil, comprenant deux, ou plus, accumulateurs thermiques (82, 84) reliés parallèlement l'un à l'autre, comprenant chacun un milieu de stockage thermique perméable au fluide disposé dans une chambre pour transférer l'énergie thermique vers le fluide ou depuis ce dernier, et, des régulateurs d'écoulement (86, 88) destinés à modifier sélectivement la voie d'écoulement du fluide dans l'appareil, l'appareil fonctionnant dans différents modes d'écoulement respectifs, dans au moins un mode d'écoulement l'appareil fonctionnant en phase de charge et de décharge en alternance quand la nature du fluide de transfert de chaleur entrant change, et au moins un autre accumulateur est sélectivement configuré pour réaliser la charge tandis qu'au moins un autre accumulateur est sélectivement configuré pour réaliser la décharge, ce qui permet de réduire au minimum la commutation de ces accumulateurs individuels entre charge et décharge dans ce mode d'écoulement et les inversions avant thermiques associées. Un tel agencement est utilisé lorsque l'appareil est soumis à des cycles de charge ou décharge partiels successifs.
PCT/GB2014/051863 2013-07-22 2014-06-17 Appareil de stockage thermique pour applications à cycle rapide Ceased WO2015011438A1 (fr)

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CN108692309A (zh) * 2018-05-04 2018-10-23 清华大学 一种固介储热系统和热电厂换热系统
CN113167548A (zh) * 2018-12-07 2021-07-23 伊沃克-X有限公司 用于实施循环储能的方法及其设备
EP4160131A1 (fr) * 2021-09-30 2023-04-05 Siemens Gamesa Renewable Energy GmbH & Co. KG Ensemble de stockage d'énergie thermique avec concept de mélange de fluides

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FR3036177B1 (fr) * 2015-05-13 2017-04-21 Commissariat Energie Atomique Dispositif de stockage d'energie thermique
DE102015009256A1 (de) * 2015-07-16 2017-01-19 Linde Aktiengesellschaft Festbettkältespeicher und Verfahren zur Speicherung von thermischer Energie
EP3303967B2 (fr) 2015-09-30 2022-10-19 Siemens Gamesa Renewable Energy A/S Système d'échange de chaleur avec au moins deux chambres d'échange de chaleur, et procédé d'échange de chaleur utilisant le système d'échange de chaleur
US10260820B2 (en) 2016-06-07 2019-04-16 Dresser-Rand Company Pumped heat energy storage system using a conveyable solid thermal storage media
CN106556277A (zh) * 2017-01-06 2017-04-05 北京大学邯郸创新研究院 一种应用于温室的相变储能装置
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CN111238281A (zh) * 2020-01-20 2020-06-05 天津大学 一种可调节的梯级相变储热装置及控制方法
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CN108692309A (zh) * 2018-05-04 2018-10-23 清华大学 一种固介储热系统和热电厂换热系统
CN113167548A (zh) * 2018-12-07 2021-07-23 伊沃克-X有限公司 用于实施循环储能的方法及其设备
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