US20140033714A1 - Regenerative thermal energy system and method of operating the same - Google Patents

Regenerative thermal energy system and method of operating the same Download PDF

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Publication number
US20140033714A1
US20140033714A1 US13/563,142 US201213563142A US2014033714A1 US 20140033714 A1 US20140033714 A1 US 20140033714A1 US 201213563142 A US201213563142 A US 201213563142A US 2014033714 A1 US2014033714 A1 US 2014033714A1
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United States
Prior art keywords
heat exchange
thermal energy
exchange reactor
fluid
solid particles
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Abandoned
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US13/563,142
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English (en)
Inventor
Miguel Angel Gonzalez Salazar
Matthias Finkenrath
Mathilde Bieber
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General Electric Co
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General Electric Co
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Priority to US13/563,142 priority Critical patent/US20140033714A1/en
Assigned to GENERAL ELECTRIC COMPANY reassignment GENERAL ELECTRIC COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BIEBER, Mathilde, FINKENRATH, MATTHIAS, GONZALEZ SALAZAR, MIGUEL ANGEL
Priority to JP2015525526A priority patent/JP2015527526A/ja
Priority to BR112015002205A priority patent/BR112015002205A2/pt
Priority to PCT/US2013/052810 priority patent/WO2014022451A1/en
Priority to EP13748194.1A priority patent/EP2895706A1/en
Priority to CA2879405A priority patent/CA2879405A1/en
Priority to AU2013296592A priority patent/AU2013296592A1/en
Priority to RU2015101907A priority patent/RU2015101907A/ru
Priority to CN201380040843.8A priority patent/CN104508257A/zh
Priority to MX2015001504A priority patent/MX2015001504A/es
Priority to KR20157005203A priority patent/KR20150038481A/ko
Publication of US20140033714A1 publication Critical patent/US20140033714A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • 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
    • F01K27/00—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
    • 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
    • F01K3/02—Use of accumulators and specific engine types; Control thereof
    • 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
    • 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
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/08—Heating air supply before combustion, e.g. by exhaust gases
    • F02C7/10—Heating air supply before combustion, e.g. by exhaust gases by means of regenerative heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28C—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA COME INTO DIRECT CONTACT WITHOUT CHEMICAL INTERACTION
    • F28C3/00—Other direct-contact heat-exchange apparatus
    • F28C3/10—Other direct-contact heat-exchange apparatus one heat-exchange medium at least being a fluent solid, e.g. a particulate material
    • F28C3/12—Other direct-contact heat-exchange apparatus one heat-exchange medium at least being a fluent solid, e.g. a particulate material the heat-exchange medium being a particulate material and a gas, vapour, or liquid
    • F28C3/14—Other direct-contact heat-exchange apparatus one heat-exchange medium at least being a fluent solid, e.g. a particulate material the heat-exchange medium being a particulate material and a gas, vapour, or liquid the particulate material moving by gravity, e.g. down a tube
    • 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
    • F28D19/00—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium
    • F28D19/02—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium using granular particles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/0056—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using solid heat storage material
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • 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

Definitions

  • the field of the invention relates generally to energy storage and, more particularly, to regenerative thermal energy storage (TES) systems associated with adiabatic compressed air energy storage (A-CAES) systems.
  • TES regenerative thermal energy storage
  • A-CAES adiabatic compressed air energy storage
  • At least some known A-CAES systems use expansive containments, e.g., pressure vessels or underground caverns to store hot, compressed air. Storage facilities using man-made pressure vessels require sufficient containment wall strength to withstand high pressures induced by compressed air for extended periods of time. Also, these known pressure vessels are exposed to high temperatures due to the compression of the air stored within. Therefore, some known pressure vessels are fabricated from expensive metal alloys with thick walls to withstand temperatures of approximately 450 degrees Celsius (° C.) (842 degrees Fahrenheit (° F.)). Other known containments include thick concrete walls with complex structures to facilitate gas tightness at high pressures. Such concrete walls are typically constructed to withstand temperatures of approximately 100° C. (212° F.), and therefore, require an active cooling system.
  • expansive containments e.g., pressure vessels or underground caverns to store hot, compressed air. Storage facilities using man-made pressure vessels require sufficient containment wall strength to withstand high pressures induced by compressed air for extended periods of time. Also, these known pressure vessels are exposed to high temperatures due to the
  • thermal energy storage within A-CAES systems requires a substantial capital investment to merely reduce heat transfer from the stored, compressed gases.
  • At least some known A-CAES systems include fixed-matrix regenerators within a stand-alone vessel that includes an inventory of solid mass.
  • the solid mass stores thermal energy as hot air is channeled over the solid mass. Also, the solid mass releases thermal energy as cold air is channeled over the solid mass.
  • the walls of these stand-alone vessels must provide sufficient strength to withstand the pressures of the air channeled therethrough. Therefore, strengthening the walls will increase the capital construction costs of the A-CAES systems. Also, at least some known A-CAES systems include indirect heat transfer systems that use equipment to facilitate substantial heat losses.
  • a regenerative thermal energy system in one aspect, includes a heat exchange reactor that includes a top entry portion, a lower entry portion, and a bottom discharge portion.
  • the system also includes at least one fluid source coupled in flow communication with the at least one heat exchange reactor at the lower entry portion.
  • the system also includes at least one cold particle storage source coupled in flow communication with the at least one heat exchange reactor at the top entry portion.
  • the system further includes at least one thermal energy storage (TES) vessel coupled in flow communication with the heat exchange reactor at each of the bottom discharge portion and the top entry portion.
  • TES thermal energy storage
  • the heat exchange reactor is configured to facilitate direct contact and counter-flow heat exchange between solid particles and a fluid.
  • a power generation facility in a further aspect, includes at least one power generation apparatus and at least one regenerative thermal energy system coupled to the at least one power generation apparatus.
  • the at least one regenerative thermal energy system includes a heat exchange reactor that includes a top entry portion, a lower entry portion, and a bottom discharge portion.
  • the system also includes at least one fluid source coupled in flow communication with the at least one heat exchange reactor at the lower entry portion.
  • the system further includes at least one cold particle storage source coupled in flow communication with the at least one heat exchange reactor at the top entry portion.
  • the system also includes at least one thermal energy storage (TES) vessel coupled in flow communication with the heat exchange reactor at each of the bottom discharge portion and the top entry portion, wherein the heat exchange reactor is configured to facilitate direct contact and counter-flow heat exchange between solid particles and a fluid and channel hot pressurized air to the at least one power generation apparatus.
  • TES thermal energy storage
  • a method of operating a power generation facility includes channeling solid particles downward through a heat exchange reactor and channeling pressurized air upward through the heat exchange reactor.
  • the method also includes transferring heat from the pressurized air to the solid particles through direct contact.
  • the method further includes channeling the solid particles into at least one thermal energy storage (TES) vessel.
  • TES thermal energy storage
  • FIG. 1 is a schematic view of a first portion of an exemplary regenerative thermal energy system.
  • FIG. 2 is a flow chart of a method of charging the regenerative thermal energy system shown in FIG. 1 .
  • FIG. 3 is a schematic view of a second portion of the regenerative thermal energy system partially shown in FIG. 1 .
  • FIG. 4 is a flow chart of a method of discharging the regenerative thermal energy system shown in FIG. 3 .
  • FIG. 5 is a schematic view of an exemplary power generation facility that uses the regenerative thermal energy system shown in FIGS. 1 and 3 .
  • Approximating language may be applied to modify any quantitative representation that could permissibly vary without resulting in a change in the basic function to which it is related. Accordingly, a value modified by a term or terms, such as “about” and “substantially”, are not to be limited to the precise value specified. In at least some instances, the approximating language may correspond to the precision of an instrument for measuring the value.
  • range limitations may be combined and/or interchanged, such ranges are identified and include all the sub-ranges contained therein unless context or language indicates otherwise.
  • FIG. 1 is a schematic view of a first portion 102 of an exemplary regenerative thermal energy system 100 .
  • First portion 102 includes the components of system 100 used during a charging operation, i.e., when a solid mass (described further below) is charged with thermal energy for storage.
  • regenerative thermal energy system 100 includes a heat exchange reactor 110 including a plurality of walls 112 that define a fully enclosed heat transfer cavity 114 . Walls 112 also define a top entry portion 116 coupled in flow communication with at least one cold particle storage source 118 .
  • Cold particle storage source 118 is any containment and delivery system that enables operation of regenerative thermal energy system 100 as described herein, including, without limitation, hoppers, bins, silos, solids transfer devices, and gravity-feed devices.
  • Storage source 118 and top entry portion 116 cooperate to inject small, cold, solid particles 119 into heat transfer cavity 114 .
  • Particles 119 are any solids that enable operation of regenerative thermal energy system 100 as described herein, including, without limitation, sand.
  • walls 112 define a lower entry portion 120 that is coupled in flow communication with at least one fluid source, i.e., an air compressor 122 , e.g., without limitation, a multi-stage air compressor.
  • an air compressor 122 e.g., without limitation, a multi-stage air compressor.
  • system 100 includes a staged air compression system (not shown) with a plurality of air compressors 122 coupled in series.
  • lower entry portion 120 defines a plurality of air inlet ports (not shown) that may be coupled to an air inlet manifold (not shown).
  • Air compressor 122 is coupled to an electric motor 124 .
  • air compressor 122 is driven by any mechanism that enables operation of regenerative thermal energy system 100 as described herein, including, without limitation, a steam turbine, a gas turbine, a water turbine, a wind turbine, a gasoline combustion engine, and a diesel engine, all with geared couplings as necessary.
  • Air compressor 122 is configured to receive cold, ambient air 126 and discharge hot, compressed air 128 into heat transfer cavity 114 , as described further below.
  • regenerative thermal energy system 100 includes moisture removal apparatus configured to remove moisture from compressed air prior to injection of hot, compressed air 128 into heat transfer cavity 114 .
  • moisture removal apparatus includes at least one of an upstream moisture separator 123 coupled in flow communication with air compressor 122 upstream of air compressor 122 , downstream moisture separator 125 coupled in flow communication with air compressor 122 downstream of air compressor 122 , and a plurality of interstage moisture separators 127 within air compressor 122 .
  • Each of upstream moisture separator 123 , downstream moisture separator 125 , and interstage moisture separators 127 facilitate removal of water 129 from the air.
  • walls 112 define an inwardly inclined bottom discharge portion 130 configured to facilitate storage of hot solid particles 132 .
  • Bottom discharge portion 130 is also configured to facilitate discharge of hot solid particles 132 out of heat transfer cavity 114 with the assistance of gravity.
  • regenerative thermal energy system 100 includes at least one cyclone filter 140 coupled in flow communication with heat transfer cavity 114 through an air extraction conduit 142 .
  • Conduit 142 is positioned between top entry portion 116 and lower entry portion 120 , and is configured to direct cold, pressurized air 144 and entrained particles 146 from heat transfer cavity 114 to cyclone filter 140 .
  • At least one cold, pressurized air storage vessel 148 is coupled in flow communication with cyclone filter 140 .
  • cyclone filter 140 includes a sloped portion 150 configured to retain entrained particles 146 .
  • Storage source 118 is coupled in flow communication with sloped portion 150 .
  • regenerative thermal energy system 100 includes at least one thermal energy storage (TES) vessel 160 coupled in flow communication with heat exchange reactor 110 at bottom discharge portion 130 .
  • TES vessel 160 defines a particle storage cavity 162 configured to receive and store hot solid particles 132 therein. Cavity 162 is sufficiently sized to enable operation of regenerative thermal energy system 100 through one full cycle as described herein.
  • TES vessel 160 includes an insulation layer 164 that is sufficient to enable maintaining hot solid particles 132 within a predetermined temperature range through one full cycle of regenerative thermal energy system 100 as described herein. For example, and without limitation, insulation layer 164 facilitates maintaining hot solid particles 132 within the predetermined temperature range for 12 to 24 hours.
  • TES vessel 160 is configured to operate at approximately atmospheric pressure.
  • regenerative thermal energy system 100 includes at least one solids transfer pump 166 coupled in flow communication with TES vessel 160 .
  • Pump 166 is configured to transfer hot particles 168 from TES vessel 160 as described further below.
  • solids transfer pump 166 is a GE Posimetric® pump commercially available from GE Energy, Atlanta, Ga., USA. Alternatively, any pumping device that enables operation of regenerative thermal energy system 100 as described herein is used.
  • regenerative thermal energy system 100 includes at least one device configured to increase a residence time of solid particles 119 and hot, compressed air 128 .
  • a plurality of air and particle deflector devices 163 are coupled to walls 112 within heat transfer cavity 114 and extend inward therefrom.
  • air and particle deflector devices 163 and walls 112 define a tortuous heat transfer channel 165 .
  • heat transfer projections 167 e.g., without limitation, heat fins, are positioned within channel 165 . Deflector devices 163 , channel 165 , and projections 167 facilitate increasing the residence time to further facilitate heat transfer between particles 119 and air 128 .
  • FIG. 2 is a flow chart of a method 200 of charging regenerative thermal energy system 100 (shown in FIG. 1 ).
  • small, cold, solid particles 119 (shown in FIG. 1 ) are injected 202 into heat transfer cavity 114 from storage source 118 through top entry portion 116 (all shown in FIG. 1 ).
  • Particles 119 are injected within a temperature range between approximately 0 degrees Celsius (° C.) (32 degrees Fahrenheit (° F.)) and approximately 49° C. (120° F.).
  • particles 119 are injected within any temperature range that enables operation of regenerative thermal energy system 100 as described herein.
  • Particles 119 are injected at any pressures that enable operation of regenerative thermal energy system 100 as described herein.
  • particles 119 are directed 204 downward through heat exchange reactor 110 (shown in FIG. 1 ) with the assistance of gravity.
  • Cold, ambient air 126 (shown in FIG. 1 ) is received and compressed 206 by air compressor 122 (shown in FIG. 1 ).
  • Ambient air 126 is in a temperature range between approximately 0° C. (32° F.) and approximately 49° C. (120° F.), and has an atmospheric pressure of approximately one atmosphere, i.e., 1.015 bar, 101.353 kilo-Pascal (kPa), and 14.7 pounds per square inch (psi).
  • inlet air 126 to air compressor 122 has temperatures and pressures in any range that enables operation of regenerative thermal energy system 100 as described herein.
  • air compressor 122 discharges 208 hot, compressed air 128 (shown in FIG. 1 ) into heat transfer cavity 114 with a temperature range between approximately 250° C. (482° F.) and approximately 700° C. (1292° F.), and a pressure range between approximately 20 bar (2000 kPa, 290 psi) and approximately 70 bar (7000 kPa, 1015 psi).
  • hot, compressed air 128 discharged from air compressor 122 has temperatures and pressures in any range that enables operation of regenerative thermal energy system 100 as described herein.
  • Hot, compressed air 128 is channeled 210 upward through heat transfer cavity 114 .
  • particles 119 and air 128 flow counter to each other, particles 119 and air 128 come into direct contact with each other within heat transfer cavity 114 .
  • Such direct contact between air 128 and particles 119 facilitates heat exchange therebetween such that air 128 transfers 212 thermal energy to particles 119 .
  • the heat exchange generates hot solid particles 132 , cold, pressurized air 144 , and entrained particles 146 (all shown in FIG. 1 ).
  • Deflector devices 163 , channel 165 , and projections 167 facilitate increasing the residence time to further facilitate heat transfer between particles 119 and air 128 .
  • air 144 is directed 218 to at least one cold, pressurized air storage vessel 148 .
  • Air 144 has a temperature value within a range between approximately 20° C. (68° F.) and 60° C. (140° F.) and within a pressure range between approximately 20 bar (2000 kPa, 290 psi) and approximately 70 bar (7000 kPa, 1015 psi).
  • air 144 is within any temperature range that enables operation of regenerative thermal energy system 100 as described herein.
  • entrained particles 146 are directed 220 downward through cyclone filter 140 with the assistance of gravity and are stored at sloped portion 150 (shown in FIG. 1 ) of cyclone filter 140 .
  • Particles 146 have a temperature value within a range between approximately 20° C. (68° F.) and approximately 60° C. (140° F.). Alternatively, particles 146 are within any temperature range that enables operation of regenerative thermal energy system 100 as described herein. Particles 146 are channeled to cold particle storage source 118 for regenerative use.
  • hot solid particles 132 are deposited at inwardly inclined bottom discharge portion 130 .
  • Hot solid particles 132 are transferred 222 out of heat transfer cavity 114 to TES vessel 160 with the assistance of gravity.
  • TES vessel 160 receives and stores hot solid particles 132 within particle storage cavity 162 .
  • Hot solid particles 132 are maintained 224 within a predetermined temperature range between approximately 240° C. (464° F.) and approximately 690° C. (1274° F.) through one full cycle of regenerative thermal energy system 100 as described herein.
  • hot solid particles 132 are maintained within the exemplary temperature range for approximately 12 to approximately 24 hours.
  • TES vessel 160 is maintained at approximately atmospheric pressure.
  • FIG. 3 is a schematic view of a second portion 170 of regenerative thermal energy system 100 .
  • Second portion 170 includes the components of system 100 used during a discharging operation, i.e., when thermal energy stored within a hot solid mass (described further below) is liberated to generate power.
  • Many of the same components of system 100 used in first portion 102 (shown in FIG. 1 ) for charging operations described above are also used for discharging operations.
  • regenerative thermal energy system 100 includes at least one solids transfer pump 166 coupled in flow communication with TES vessel 160 .
  • Solids transfer pump 166 is also coupled in flow communication with heat transfer cavity 114 of heat exchange reactor 110 through top entry portion 116 .
  • Solids transfer pump 166 is configured to transfer hot particles 168 from TES vessel 160 into heat transfer cavity 114 .
  • stored, cold, pressurized air 144 is contained in air storage vessel 148 within a pressure range between approximately 20 bar (2000 kPa, 290 psi) and approximately 70 bar (7000 kPa, 1015 psi). Therefore, solids transfer pump 166 is configured to inject particles 168 into heat exchange reactor 110 with sufficient pressure to overcome the pressure of air 144 .
  • cyclone filter 140 is coupled in flow communication with heat transfer cavity 114 through air extraction conduit 142 .
  • Cyclone filter 140 is further coupled in flow communication with heat transfer cavity 114 through an entrained particle return conduit 175 .
  • regenerative thermal energy system 100 includes at least one expander 180 rotatably coupled to a machine, e.g., without limitation, a generator 182 .
  • Expander 180 is coupled in flow communication with cyclone filter 140 .
  • regenerative thermal energy system 100 includes at least one combustion apparatus 181 coupled in flow communication with cyclone filter 140 and expander 180 .
  • Combustion apparatus 181 includes a hot air extension line 183 coupled to cyclone filter 140 .
  • Combustion apparatus 181 also includes a fuel line 185 .
  • Combustion apparatus 181 further includes an air/fuel mixer 186 coupled to hot air extension line 183 and fuel line 185 .
  • Combustion apparatus 181 also includes a combustion chamber 187 coupled to air/fuel mixer 186 and hot air extension line 183 .
  • Combustion apparatus 181 further includes a heat exchange device 188 coupled to combustion chamber 187 , hot air extension line 183 , and expander 180 .
  • Combustion apparatus 181 further includes an exhaust conduit 189 coupled to heat exchange device 188 .
  • FIG. 4 is a flow chart of a method 300 of discharging regenerative thermal energy system 100 (shown in FIG. 3 ).
  • hot solid particles 132 (shown in FIG. 3 ) are maintained 302 within a predetermined temperature range between approximately 240° C. (464° F.) and approximately 690° C. (1274° F.) through one full cycle of regenerative thermal energy system 100 as described herein.
  • hot solid particles 132 are maintained within the exemplary temperature range for 12 to 24 hours.
  • TES vessel 160 (shown in FIG. 3 ) is maintained at approximately atmospheric pressure.
  • Hot particles 168 (shown in FIG. 3 ) are transferred from TES vessel 160 into heat transfer cavity 114 (shown in FIG. 3 ) through top entry portion 116 (shown in FIG. 3 ) within a similar temperature range.
  • cold, pressurized air 144 is contained 304 in air storage vessel 148 (shown in FIG. 3 ).
  • Air 144 has a temperature value within a range between approximately 20° C. (68° F.) and 60° C. (140° F.) and within a pressure range between approximately 20 bar (2000 kPa, 290 psi) and approximately 70 bar (7000 kPa, 1015 psi).
  • Stored, cold, pressurized air 144 is discharged 306 into heat transfer cavity 114 .
  • Air 144 is directed 308 upward through heat transfer cavity 114 .
  • Solids transfer pump 166 (shown in FIG. 3 ) injects 310 particles 168 into heat exchange reactor 110 with sufficient pressure to overcome the pressure of air 144 .
  • particles 168 and air 144 flow counter to each other, particles 168 and air 144 come into direct contact with each other within heat transfer cavity 114 .
  • Such direct contact between air 144 and particles 168 facilitates heat exchange therebetween such that particles 168 transfers 312 thermal energy to air 144 .
  • the heat exchange generates hot, pressurized air 172 , entrained particles 174 , and cold particles 190 (all shown in FIG. 3 ).
  • hot, pressurized air 172 and entrained particles 174 are extracted 314 from heat transfer cavity 114 to cyclone filter 140 (shown in FIG. 3 ) that uses cyclonic action to separate 316 air 172 from particles 174 .
  • Hot, pressurized air 172 and entrained particles 174 are within a temperature range of approximately 240° C. (464° F.) and approximately 690° C. (1274° F.).
  • entrained particles 174 are directed 318 downward through cyclone filter 140 with the assistance of gravity and are stored at sloped portion 150 (shown in FIG. 3 ) of cyclone filter 140 .
  • Some reusable, i.e., still transferable, thermal energy may reside within particles 174 . Therefore, such particles 174 within a temperature range between approximately 240° C. (464° F.) and approximately 690° C. (1274° F.) are reinjected 320 into heat transfer cavity 114 for further thermal energy transfer to air 144 .
  • particles 174 are reinjected into heat transfer cavity 114 within any temperature range that enables operation of regenerative thermal energy system 100 as described herein.
  • particles 174 are transferred 322 to cold particle storage source 118 for regenerative use.
  • particles 174 are channeled to cold particle storage source 118 within any temperature range that enables operation of regenerative thermal energy system 100 as described herein.
  • some cold particles 190 that have been substantially exhausted of transferrable thermal energy are deposited at inwardly inclined bottom discharge portion 130 (shown in FIG. 3 ).
  • Particles 190 are transferred 324 , with the assistance of gravity, out of heat transfer cavity 114 to TES vessel 160 in a manner that reduces a probability of cannibalizing thermal energy stored in hot particles 132 .
  • TES vessel 160 receives and stores cold particles 190 within particle storage cavity 162 .
  • Cold particles 190 are transferred 326 to cold particle storage source 118 for regenerative use.
  • hot, pressurized air 172 having a temperature value within a range between approximately 240° C. (464° F.) and approximately 690° C. (1274° F.) and within a pressure range between approximately 20 bar (2000 kPa, 290 psi) and approximately 70 bar (7000 kPa, 1015 psi) is directed 328 to expander 180 (shown in FIG. 3 ).
  • air 172 is within any temperature range and any pressure range that enables operation of regenerative thermal energy system 100 as described herein.
  • Expander 180 (shown in FIG. 3 ) drives 330 generator 182 (shown in FIG. 3 ) and expended air 184 (shown in FIG. 3 ) is discharged to any place that enables operation of regenerative thermal energy system 100 as described herein.
  • the hot air from cyclone filter 140 is channeled to combustion apparatus 181 through conduit 183 .
  • Some of the hot air and fuel are channeled to air/fuel mixer 186 through conduit 183 and fuel line 185 , respectively, where they are mixed.
  • the air/fuel mixture is channeled to combustion chamber 187 and additional hot air in injected into combustion chamber 187 from conduit 183 .
  • Hot gases are generated and are channeled to heat exchange device 188 . Heat transfer from the gases to hot air channeled from conduit 183 further increases the temperature of air 172 prior to expander 180 .
  • the combustion gases are channeled through exhaust conduit 189
  • FIG. 5 is a schematic view of an exemplary power generation facility 500 that uses regenerative thermal energy system 100 .
  • power generation facility 500 includes a plurality of power generators 502 , including, without limitation, steam turbine generators, gas turbine generators, water turbine generators, wind turbine generators, gasoline combustion engine-driven generators, and diesel engine generators, and any combination thereof.
  • operating power generation facility 500 includes storing thermal energy during non-peak periods and expending the stored thermal energy during peak periods.
  • an own/operator of power generation facility anticipates a need for additional power generation during a future peaking period.
  • Power generators 502 transmit electric power to electric motors 124 of air compressors 122 (shown in FIG. 1 ) and thermal energy is stored in regenerative thermal energy system 100 as described above.
  • regenerative thermal energy system 100 substantially recovers the stored thermal energy and electric power that is generated by generators 182 is added to the electric power generated by power generators 502 for transmission.
  • Such regenerative operation represents a full cycle of regenerative thermal energy system 100 .
  • such cycles may occur twice on weekdays, i.e., discharging operations are performed between approximately 5:00 AM and approximately 9:00 AM, and again approximately 5:00 PM and approximately 10:00 PM.
  • Charging operations are performed between those two time periods when discharging operations are not in progress.
  • some embodiments of power generation facility 500 may include multiple iterations of regenerative thermal energy system 100 such that one system 100 is charging and feeding a second system 100 that is discharging.
  • the above-described regenerative thermal energy system provides a cost-effective method for generating and storing thermal energy for later use.
  • the embodiments described herein facilitate storing thermal energy in a thermal energy storage vessel during low power usage periods for future use during peak power usage periods.
  • the devices, systems, and methods described herein facilitate transferring heat from hot compressed air to and the assistance of gravity small, cold, solid particles through direct contact.
  • the devices, systems, and methods described herein facilitate using a power generation facility to use at least some of the power generated therein to drive air compressors during low power usage periods.
  • the thermal energy now contained in the hot, small particles is stored with the particles in an insulated vessel configured to maintain the particles within a specific temperature range for a certain period of time at atmospheric pressure.
  • the cold, pressurized air is channeled to a storage vessel.
  • the hot particles are channeled to mix with the stored, cold, pressurized air to transfer the thermal energy back into the air.
  • the reheated air is channeled to an expander coupled to a generator. Therefore, since the small hot particles are stored in a smaller vessel than that use to store the air, use of more robust structural materials and insulation for air storage is no longer required. Moreover, since the particles and air are in direct contact, equipment necessary to facilitate indirect thermal energy transfer is not required.
  • An exemplary technical effect of the methods, systems, and apparatus described herein includes at least one of: (a) decreasing the volume of a vessel used to store thermal energy; and (b) directly contacting cold particles with hot air and hot particles with cold air to regeneratively transfer thermal energy therebetween.
  • regenerative thermal energy system for power generation facilities and methods for operating are described above in detail.
  • the regenerative thermal energy system, power generation facilities, and methods of operating such systems and facilities are not limited to the specific embodiments described herein, but rather, components of systems and/or steps of the methods may be utilized independently and separately from other components and/or steps described herein.
  • the methods may also be used in combination with other systems requiring thermal energy storage and methods, and are not limited to practice with only the regenerative thermal energy system, power generation facilities, and methods as described herein. Rather, the exemplary embodiment can be implemented and utilized in connection with many other thermal energy storage and transfer applications.
US13/563,142 2012-07-31 2012-07-31 Regenerative thermal energy system and method of operating the same Abandoned US20140033714A1 (en)

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Application Number Priority Date Filing Date Title
US13/563,142 US20140033714A1 (en) 2012-07-31 2012-07-31 Regenerative thermal energy system and method of operating the same
KR20157005203A KR20150038481A (ko) 2012-07-31 2013-07-31 재생 열 에너지 시스템, 그러한 시스템을 포함하는 발전 설비 및 그 작동 방법
EP13748194.1A EP2895706A1 (en) 2012-07-31 2013-07-31 Regenerative thermal energy system, a power generating facility comprising such a system and a method of operating the same
BR112015002205A BR112015002205A2 (pt) 2012-07-31 2013-07-31 sistema de energia térmica regenerativo, instalação de geração de potência e método para operar uma instalação de geração de potência
PCT/US2013/052810 WO2014022451A1 (en) 2012-07-31 2013-07-31 Regenerative thermal energy system, a power generating facility comprising such a system and a method of operating the same
JP2015525526A JP2015527526A (ja) 2012-07-31 2013-07-31 再生式熱エネルギーシステム、そのようなシステムを備えた発電設備、および発電設備を動作させる方法
CA2879405A CA2879405A1 (en) 2012-07-31 2013-07-31 Regenerative thermal energy system, a power generating facility comprising such a system and a method of operating the same
AU2013296592A AU2013296592A1 (en) 2012-07-31 2013-07-31 Regenerative thermal energy system, a power generating facility comprising such a system and a method of operating the same
RU2015101907A RU2015101907A (ru) 2012-07-31 2013-07-31 Система рекуперации тепловой энергии, энергетическая установка, содержащая такую систему, и способ ее эксплуатации
CN201380040843.8A CN104508257A (zh) 2012-07-31 2013-07-31 再生热能系统、具有再生热能系统的发电设施及其操作方法
MX2015001504A MX2015001504A (es) 2012-07-31 2013-07-31 Sistema de energia termica regenerativa, una instalacion generadora de energia que comprende dicho sistema y metodo para operar el mismo.

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KR20150038481A (ko) 2015-04-08
CA2879405A1 (en) 2014-02-06
RU2015101907A (ru) 2016-09-27
BR112015002205A2 (pt) 2017-08-01
AU2013296592A1 (en) 2015-02-05
JP2015527526A (ja) 2015-09-17
MX2015001504A (es) 2015-04-08
EP2895706A1 (en) 2015-07-22
WO2014022451A1 (en) 2014-02-06

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