WO2012021285A2 - Adiabatic compressed air energy storage process - Google Patents

Adiabatic compressed air energy storage process Download PDF

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Publication number
WO2012021285A2
WO2012021285A2 PCT/US2011/045275 US2011045275W WO2012021285A2 WO 2012021285 A2 WO2012021285 A2 WO 2012021285A2 US 2011045275 W US2011045275 W US 2011045275W WO 2012021285 A2 WO2012021285 A2 WO 2012021285A2
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WO
WIPO (PCT)
Prior art keywords
process gas
heat transfer
thermal mass
unit
electric heater
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/US2011/045275
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English (en)
French (fr)
Other versions
WO2012021285A3 (en
Inventor
H. Allan Kidd
Harry F. Miller
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Dresser Rand Co
Original Assignee
Dresser Rand Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Dresser Rand Co filed Critical Dresser Rand Co
Priority to EP11816782.4A priority Critical patent/EP2603684B1/en
Priority to CA2807502A priority patent/CA2807502C/en
Priority to JP2013524090A priority patent/JP5893025B2/ja
Priority to AU2011289781A priority patent/AU2011289781C1/en
Priority to CN201180046211.3A priority patent/CN103237970B/zh
Publication of WO2012021285A2 publication Critical patent/WO2012021285A2/en
Publication of WO2012021285A3 publication Critical patent/WO2012021285A3/en
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
    • 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
    • F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
    • F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
    • 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
    • F02C6/18—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants
    • 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
    • F02C7/12—Cooling of plants
    • F02C7/14—Cooling of plants of fluids in the plant, e.g. lubricant or fuel
    • F02C7/141—Cooling of plants of fluids in the plant, e.g. lubricant or fuel of working fluid
    • F02C7/143—Cooling of plants of fluids in the plant, e.g. lubricant or fuel of working fluid before or between the compressor stages
    • 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
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/14—Combined heat and power generation [CHP]
    • 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
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P80/00—Climate change mitigation technologies for sector-wide applications
    • Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier
    • Y02P80/15—On-site combined power, heat or cool generation or distribution, e.g. combined heat and power [CHP] supply

Definitions

  • the present disclosure relates to systems and methods for compressed air energy storage (CAES), and more particularly to adiabatic CAES.
  • CAES compressed air energy storage
  • peak hours may include 8-12 daytime hours
  • off-peak hours may include the remaining 12-16 hours of the day and/or night.
  • CAES is a way to store energy generated during off- peak hours for use during peak hours.
  • Embodiments of the disclosure may provide a compressed air energy storage system.
  • the system may include a compressor adapted to receive a process gas and output a compressed process gas.
  • a heat transfer unit may be coupled to the compressor and adapted to receive the compressed process gas and a heat transfer medium and to output a cooled process gas and a heated heat transfer medium.
  • a compressed gas storage unit may be coupled to the heat transfer unit and adapted to receive and store the cooled process gas.
  • a waste heat recovery unit may be coupled to the heat transfer unit and adapted to receive the heated heat transfer medium.
  • a thermal mass may be coupled to the waste heat recovery unit and the compressed gas storage unit, and the thermal mass may be adapted to be heated by the waste heat recovery unit, to receive the cooled process gas from the compressed gas storage unit, to heat the cooled process gas, and to output a heated process gas.
  • a power generation unit may be coupled to the thermal mass and adapted to receive the heated process gas and generate a power output.
  • Embodiments of the disclosure may further provide a method of generating power.
  • the method may include compressing a process gas with a compressor to produce a compressed process gas.
  • the method may also include transferring heat from the compressed process gas to a heat transfer medium with a heat transfer unit to produce a cooled process gas and a heated heat transfer medium.
  • the method may further include storing the cooled process gas in a compressed gas storage unit.
  • the method may further include transporting the heated heat transfer medium to a waste heat recovery unit.
  • the method may further include heating a thermal mass with the waste heat recovery unit.
  • the method may further include transporting the cooled process gas from the compressed gas storage unit to the thermal mass.
  • the method may further include heating the cooled process gas with the thermal mass to produce a heated process gas.
  • the method may further include transporting the heated process gas from the thermal mass to a power generation unit.
  • the method may further include generating a power output with the power generation unit.
  • Embodiments of the disclosure may further provide a compressed air energy storage system.
  • a compressor may be coupled to and driven by a driver, and the compressor may be adapted to compress a process gas.
  • a first heat transfer unit may be coupled to the compressor and adapted receive the process gas from the compressor and transfer heat from the process gas to a first heat transfer medium.
  • a first waste heat recovery unit may be coupled to the first heat transfer unit and adapted to receive the first heat transfer medium from the first heat transfer unit and generate a first power output.
  • a process cooler may be coupled to the first heat transfer unit and adapted to receive the process gas from the first heat transfer unit and cool the process gas.
  • a compressed gas storage unit may be coupled to the process cooler and adapted to receive process gas from the process cooler and store the process gas.
  • An electric heater may be coupled to the first waste heat recovery unit and adapted to receive the first power output.
  • a thermal mass may be coupled to the electric heater and the compressed gas storage unit and adapted to be heated by the electric heater, to receive the process gas from the compressed gas storage unit, and to heat the process gas.
  • a power generation unit may be coupled to the thermal mass and adapted to receive the process gas from the thermal mass and generate a second power output.
  • Figure 1 depicts a block diagram of an illustrative adiabatic CAES system, according to one or more embodiments described.
  • Figure 2 depicts a block diagram of another illustrative adiabatic CAES system including a supersonic compressor train, according to one or more embodiments described.
  • Figure 3 depicts a flow chart of an illustrative method of generating power using stored compressed air energy, according to one or more embodiments described.
  • first and second features are formed in direct contact
  • additional features may be formed interposing the first and second features, such that the first and second features may not be in direct contact.
  • exemplary embodiments presented below may be combined in any combination of ways, i.e., any element from one exemplary embodiment may be used in any other exemplary embodiment, without departing from the scope of the disclosure.
  • FIG. 1 depicts a block diagram of an illustrative adiabatic CAES system 100, according to one or more embodiments described.
  • the CAES system 100 may include a compressor train 104 having one or more compressors 106,126, 146,166 adapted to compress a process gas.
  • the process gas may be ambient air.
  • the compressors 106,126,146,166 may be supersonic compressors, centrifugal compressors, axial flow compressors, reciprocating compressors, rotary screw compressors, rotary vane compressors, scroll compressors, diaphragm compressors, or the like.
  • the compressor train 104 may also include one or more drivers 105,125, 145,165 coupled to and adapted to drive the compressors 106,126,146,166.
  • the drivers 105,125,145,165 may be electric motors, turbines, or any other device known in the art to drive a compressor 106, 126, 146, 166.
  • four drivers 105, 125, 145,165 and four compressors 106, 126,146,166 are depicted in Figure 1 , any number of drivers 105,125, 145, 165 and/or compressors 106, 126, 146, 166 may be used in the compressor train 104 of the CAES system 100.
  • the first driver 105 may drive the first compressor 106
  • the second driver 125 may drive the second compressor 126
  • the third driver 145 may drive the third compressor 146
  • the fourth driver 165 may drive the fourth compressor 166.
  • at least one of the drivers 105, 125, 145,165 and compressors 106, 126, 146, 166 may be disposed together in a hermetically sealed casing (not shown).
  • at least one of the drivers 105, 125, 145,165 and compressors 106, 126, 146, 166 may include a DATUM ® centrifugal compressor unit commercially-available from Dresser-Rand of Olean, New York.
  • at least one of the compressors 106,126, 146, 166 may include Rampressors ® developed by Ramgen Power Systems, LLC of Bellevue, Washington.
  • the compressor train 104 may compress the process gas, and the process gas may be introduced to and stored in a compressed gas storage unit 185.
  • the compressed gas storage unit 185 may be a cavern or a vessel.
  • the compressed gas storage unit 185 may be a rock cavern, a salt cavern, an aquifer, an abandoned mine, a depleted gas field, a container stored under water or above ground, or the like.
  • other compressed gas storage units 185 are contemplated herein.
  • Heat transfer units 109,1 15,129,135, 149, 155,169, 175 may be disposed between compressors and/or stages 106,126,146,166 of the compressor train 104.
  • the heat transfer units 109,1 15, 129, 135,149,155, 169, 175 may include a coil system, a shell-and-tube system, a direct contact system, or other heat transfer system known in the art.
  • a heat transfer medium may flow through the heat transfer units 109,1 15, 129, 135, 149,155, 169,175 and absorb heat from the process gas.
  • the heat transfer medium has a higher temperature when it exits the heat transfer units 109, 1 15,129, 135, 149, 155,169, 175 than when it enters the heat transfer units 109, 1 15, 129, 135,149,155, 169, 175, i.e., the heat transfer medium is heated, and the process gas has a lower temperature when it exits the heat transfer units 109,1 15, 129,135,149,155, 169,175 than when it enters the heat transfer units 109,1 15, 129,135, 149, 155,169,175, i.e., the process gas is cooled.
  • the heat transfer medium may be water, steam, a suitable refrigerant, a process gas such as C02 or propane, a combination thereof, or any other suitable heat transfer medium.
  • Heat transfer units 109,129,149,169 may be high grade heat transfer units, and heat transfer units 1 15, 135,155,175 may be low grade heat transfer units.
  • Each high grade heat transfer unit 109, 129, 149, 169 may be disposed upstream of one or more of the low grade heat transfer units 1 15, 135, 155, 175.
  • the process gas introduced to each high grade heat transfer unit 109, 129, 149, 169 may have a higher temperature than the process gas introduced to each adjacent low grade heat transfer unit 1 15,135,155, 175.
  • one or more of the heat transfer units 109,1 15, 129,135,149,155, 169, 175 may, in addition to extracting energy from the process stream, introduce cooling to the process thereby lowering the temperature of the process stream to a temperature lower than ambient.
  • process coolers 121 , 141 , 161 and 181 are not required.
  • Each heat transfer unit 109,1 15,129,135, 149, 155, 169,175 may be coupled to a waste heat recovery unit (WHRU) 1 12, 1 18, 132, 138,152,158, 172, 178. After the heat transfer medium flows through and is heated in a heat transfer unit 109, 1 15, 129, 135, 149, 155, 169, 175, it may be introduced to the waste heat recovery unit (WHRU) 1 12, 1 18, 132, 138, 152, 158, 172, 178 coupled to it.
  • the WHRUs 1 12,1 18,132,138,152,158, 172,178 may each include a turbine (not shown), such as a high pressure turbine expander, and a generator (not shown).
  • the heat transfer medium may directly drive the turbine expander or may be used to transfer thermal energy to another gas to drive the turbine expander, and the turbine expander may power the generator, which may generate electrical power.
  • WHRUs 1 12,132,152,172 may be high grade WHRUs, and WHRUs 1 18, 138, 158,178 may be low grade WHRUs.
  • the high grade WHRUs 1 12, 132, 152,172 may receive the heat transfer medium from the high grade heat transfer units 109,129,149,169, and the low grade WHRUs 1 18,138, 158, 178 may receive the heat transfer medium from the low grade heat transfer units 1 15, 135, 155, 175.
  • the WH RUs 1 12, 1 18, 132, 138, 152, 158, 172, 178 may recover between about 10% and about 30%, about 20% and about 40%, about 25% and about 50%, or more of the energy put into the system depending on the temperature of the process stream and the design of the WHRU. The amount of energy recovered is directly dependent on the temperature of the process stream.
  • the high grade WHRUs 1 12, 132, 152, 172 may generate between about 5M W and about 15MW of electrical power
  • the low grade WHRUs 1 18,138,158,178 may generate between about 1 MW and about 5MW.
  • the high grade WHRUs 1 12,132,152, 172 may generate between about 8.5MW and about 12MW of electrical power
  • the low grade WHRUs 1 18, 138, 158, 178 may generate between about 2MW and about 4 MW.
  • Process coolers 121 , 141 , 161 , 181 may be disposed between the compressors 106, 126, 146, 166 and/or compressor stages in the compressor train 104.
  • the process coolers 121 ,141 ,161 , 181 may be aftercoolers or intercoolers.
  • the process coolers 121 , 141 ,161 ,181 may remove the remaining heat from the air that did not get removed by the heat transfer units 109, 1 15,129,135,149,155,169, 175 and reject that residual heat to the atmosphere.
  • An energy extraction scheme may be used that returns air to the next stage compressor that is colder than ambient.
  • the electrical power generated by the WHRUs 1 12,1 18, 132, 138,152,158, 172, 178 may power one or more electric heaters (one is shown) 189 disposed on or in a thermal mass 188.
  • heat energy from the process gas compressed by the compressor train 104 may be used to heat the thermal mass 188.
  • the thermal mass 188 may include a solid mass, a liquid mass, hot salt, or the like.
  • the thermal mass 188 may include water, earth, rammed earth, mud, rocks, stones, concrete, or wood.
  • the thermal mass 188 may be disposed within a man-made insulated vessel (not shown).
  • An energy source 187 may be used to augment the power supplied to the electric heater 189.
  • the energy source 187 may be a gas generator or the electrical grid.
  • the energy source 187 may also be a renewable energy source such as wind energy, solar energy, geothermal energy, or any other renewable energy source known in the art.
  • the compressed process gas may be drawn from the compressed gas storage unit 185 and used to power a power generation unit 192. Prior to reaching the power generation unit 192, the compressed process gas may be introduced to the thermal mass 188, and heat from the thermal mass 188 may be transferred to the compressed process gas. In at least one embodiment, the compressed process gas may be injected free flow into the thermal mass 188.
  • the heated process gas may be supplied from the thermal mass 188 to the power generation unit 192.
  • the power generation unit 192 may include an expander 194 and an electrical generator 195.
  • the heated process gas may expand in the expander 194 generating mechanical power to drive the electrical generator 195.
  • the heated process gas from the thermal mass 188 may be combined with fuel and combusted in a combustor 193 prior to entering the expander 194.
  • the fuel may include a hydrocarbon feed or other fuel known in the art.
  • the electrical generator 195 may generate and supply power to the electrical grid 101 during peak hours.
  • the power generation unit 192 may generate between 10MW and 170MW.
  • a heat transfer unit 196 may be configured to recover thermal energyfrom the exhaust from at least one of the combustor 193, the expander 194, and the electrical generator 195.
  • a WHRU 197 may be coupled to the heat transfer unit 196 and configured to generate electrical power. The electrical power generated by the WHRU 197 may be supplied to the electric heater 189 and/or at least one of the drivers 105,125,145,165.
  • the heat transfer unit 196 may be the same as any of heat transfer units 109, 1 15,129,135, 149,155,169, 175 or may be different, and the WHRU 197 may be the same as any of the WHRUs 1 12,1 18,132,138, 152,158, 172,178 or may be different.
  • the process gas may be introduced to the first compressor 106 via line 107.
  • the process gas in line 107 may have a pressure between about 10 psia and about 20 psia, a temperature between about 40 °F and about 1 10°F, a relative humidity (RH) between about 50% and about 70%, and a flow rate between about 370 lbs/sec and about 470 lbs/sec.
  • RH relative humidity
  • the RH could be between about 0% and about 100% and the flow rate could be between about 25 lbs/sec and about 100 lbs/sec.
  • the process gas in line 107 may have a pressure of about 14.7 psia, a temperature of about 95°F, a RH of about 60%, and a flow rate of about 420 lbs/sec.
  • the first compressor 106 may compress the process gas and output the compressed process gas in line 108.
  • the compressed process gas in line 108 may have a pressure between about 60 psia and about 90 psia and a temperature between about 350°F and about 450°F.
  • the compressed process gas in line 108 may have a pressure of about 75 psia and a temperature of about 400°F.
  • the compressed process gas may be introduced to the first heat transfer unit 109 via line 108, and the heat transfer medium may be introduced to the first heat transfer unit 109 via line 1 10.
  • the heat transfer unit 109 transfers heat from the compressed process gas to the heat transfer medium and outputs the process gas in line 1 14 and the heat transfer medium in line 1 1 1.
  • the heat transfer medium in line 1 1 1 may be introduced to the first WHRU 1 12.
  • the first WHRU 1 12 may generate electrical power in line 1 13 that powers the electric heater 189.
  • the first WHRU 1 12 may generate electrical power that is supplied to the first driver 105 via line 122.
  • heat energy from the compressed process gas in line 108 may be used to heat the thermal mass 188 and/or power the first driver 105.
  • the process gas in line 1 14 may have a pressure between about 50 psia and about 80 psia and a temperature between about 300°F and about 500°F.
  • the process gas in line 1 14 may have a pressure of about 73 psia and a temperature of about 250°F.
  • the process gas may be introduced to the second heat transfer unit 1 15 via line 1 14, and the heat transfer medium may be introduced to the second heat transfer unit 1 15 via line 1 16.
  • the heat transfer unit transfers heat from the process gas to the heat transfer medium and outputs the process gas in line 120 and the heat transfer medium in line 1 17.
  • the heat transfer medium in line 1 17 may be introduced to the second WHRU 1 18.
  • the second WHRU 1 18 may generate electrical power in line 1 19 that powers the electric heater 189.
  • the second WHRU 1 18 may generate electrical power that is supplied to the first driver 105 via line 123.
  • heat energy from the process gas in line 1 14 may be used to heat the thermal mass 188 and/or powerthe first driver 105.
  • the process gas in line 120 may have a pressure between about 50 psia and about 80 psia and a temperature between about 300°F and about 500°F
  • the process gas in line 120 may have a pressure of about 73 psia and a temperature of about 150 °F.
  • the process gas in line 120 may be introduced to the first process cooler 121 , which may further cool the process gas and output the process gas in line 127.
  • the process gas in line 127 may have a pressure between about 55 psia and 85 psia and a temperature between about 100°F and about 160°F.
  • the process gas in line 120 may have a pressure between about 50 psia and about 80 psia and a temperature between about 300°F and about 500°F
  • the process gas in line 120 may have a pressure of about 73 psia and a temperature of about 150 °F.
  • the process gas in line 120 may be introduced to the first process cooler 121 , which may further
  • 127 may have a pressure of about 70 psia and a temperature of about 130°F.
  • the process gas in line 127 may be introduced to the second compressor 126.
  • the second compressor 126 may compress the process gas in line 127 and output a second compressed process gas in line 128.
  • the second compressed process gas in line 128 may have a pressure between about 200 psia and about 300 psia and a temperature between about 250°F and about 350°F.
  • the second compressed process gas in line 128 may have a pressure of about 250 psia and a temperature of about 300°F.
  • the second compressed process gas may be introduced to the third heat transfer unit 129 via line 128, and the heat transfer medium may be introduced to the third heat transfer unit 129 via line 130.
  • the third heat transfer unit 129 transfers heat from the second compressed process gas to the heat transfer medium and outputs the process gas in line 134 and the heat transfer medium in line 131.
  • the heat transfer medium in line 131 may be introduced to the third WHRU 132.
  • the third WHRU 132 may generate electrical power in line 133 that powers the electric heater 189.
  • the third WHRU 132 may generate electrical power that is supplied to the second driver 125 via line 142.
  • heat energy from the second compressed process gas in line 128 may be used to heat the thermal mass 188 and/or power the second driver 125.
  • the process gas in line 134 may have a pressure between about 200 psia and about 500 psia and a temperature between about 100°F and about 300°F.
  • the process gas in line 134 may have a pressure of about 250 psia and a temperature of about 200°F.
  • the process gas may be introduced to the fourth heat transfer unit 135 via line 134, and the heat transfer medium may be introduced to the fourth heat transfer unit 135 via line 136.
  • the fourth heat transfer unit 135 may transfer heat from the process gas to the heat transfer medium and output the process gas in line 140 and the heat transfer medium in line 137.
  • the heat transfer medium in line 137 may be introduced to the fourth WHRU 138.
  • the fourth WHRU 138 may generate electrical power in line 139 that powers the electric heater 189.
  • the fourth WHRU 138 may generate electrical power that is supplied to the second driver 125 via line 143.
  • heat energy from the process gas in line 134 may be used to heat the thermal mass 188 and/or power the second driver 125.
  • the process gas in line 140 may have a pressure between about 200 psia and about 500 psia and a temperature between about 100°F and about 300°F.
  • the process gas in line 140 may have a pressure of about 245 psia and a temperature of about 125°F.
  • the process gas in line 140 may be introduced to the second process cooler 141 , which further cools the process gas and outputs the process gas in line 147.
  • the process gas in line 147 may have a pressure between about 195 psia and about 295 psia and a temperature between about 100°F and about 160°F.
  • the process gas in line 147 may have a pressure of about 245 psia and a temperature of about 130°F.
  • the process gas in line 147 may be introduced to the third compressor 146.
  • the third compressor 146 may compress the process gas and output a third compressed process gas in line 148.
  • the third compressed process gas in line 148 may have a pressure between about 500 PSIA and about 600 PSIA and a temperature between about 250°F and about 350°F.
  • the third compressed process gas in line 148 may have a pressure of about 550 PSIA and a temperature of about 300°F.
  • the third compressed process gas may be introduced to the fifth heat transfer unit 149 via line 148, and the heat transfer medium may be introduced to the fifth heat transfer unit 149 via line 150.
  • the fifth heat transfer unit transfers heat from the third compressed process gas to the heat transfer medium and outputs the process gas in line 154 and the heat transfer medium in line 151
  • the heat transfer medium in line 151 may be introduced to the fifth WHRU 152.
  • the fifth WHRU 152 may generate electrical power in line 153 that powers the electric heater 189.
  • the fifth WHRU 152 may generate electrical power that is supplied to the third driver 145 via line 162.
  • heat energy from the third compressed process gas in line 148 may be used to heat the thermal mass 188 and/or power the third driver 145.
  • the process gas in line 154 may have a pressure between about 300 psia and about 600 psia and a temperature between about 200°F and about 500°F.
  • the process gas in line 154 may have a pressure of about 545 psia and a temperature of about 175°F.
  • the process gas may be introduced to the sixth heat transfer unit 155 via line 154, and the heat transfer medium may be introduced to the sixth heat transfer unit 155 via line 156.
  • the sixth heat transfer unit transfers heat from the process gas to the heat transfer medium and outputs the process gas in line 160 and the heat transfer medium in line 157
  • the heat transfer medium in line 157 may be introduced to the sixth WHRU 158.
  • the sixth WHRU 158 may generate electrical power in line 159 that powers the electric heater 189.
  • the sixth WHRU 158 may generate electrical power that is supplied to the third driver 145 via line 163.
  • heat energy from the process gas in line 154 may be used to heat the thermal mass 188 and/or power the third driver 145.
  • the process gas in line 160 may have a pressure between about 300 psia and about 600 psia and a temperature between about 100°F and about 200°F.
  • the process gas in line 160 may have a pressure of about 540 psia and a temperature of about 100°F.
  • the process gas in line 160 may be introduced to the third process cooler 161 , which may further cool the process gas and output the process gas in line 167.
  • the process gas in line 167 may have a pressure between about 495 psia and about 595 psia and a temperature between about 100°F and 160°F.
  • the process gas in line 167 may have a pressure of about 545 psia and a temperature of about 130°F.
  • the process gas in line 167 may be introduced to the fourth compressor 166.
  • the fourth compressor 166 may compress the process gas and output a fourth compressed process gas in line 168.
  • the fourth compressed process gas in line 168 may have a pressure between about 1320 psia and about 1720 psia and a temperature between about 250°F and about 350°F.
  • the fourth compressed process gas in line 168 may have a pressure of about 1520 psia and a temperature of about 300°F.
  • the fourth compressed process gas may be introduced to the seventh heat transfer unit 169 via line 168, and the heat transfer medium may be introduced to the seventh heat transfer unit 169 via line 170.
  • the seventh heat transfer unit 169 transfers heat from the fourth compressed process gas to the heat transfer medium and outputs and the process gas in line 174 and the heat transfer medium in line 171.
  • the heat transfer medium in line 171 may be introduced to the seventh WHRU 172.
  • the seventh WHRU 172 may generate electrical power in line 173 that powers the electric heater 189.
  • the seventh WHRU 172 may generate electrical power that is supplied to the fourth driver 165 via line 182.
  • heat energy from the fourth compressed process gas in line 168 may be used to heat the thermal mass 188 and/or power the fourth driver 165.
  • the process gas in line 174 may have a pressure between about 1250 psia and about 1800 psia and a temperature between about 200°F and about 300°F.
  • the process gas in line 174 may have a pressure of about 1515 psia and a temperature of about 185°F.
  • the process gas may be introduced to the eighth heat transfer unit 175 via line 174, and the heat transfer medium may be introduced to the eighth heat transfer unit 175 via line 176.
  • the eighth heat transfer unit transfers heat from the process gas to the heat transfer medium and outputs and the process gas in line 180 and the heat transfer medium in line 177.
  • the heat transfer medium in line 177 may be introduced to the eighth WHRU 178.
  • the eighth WHRU 178 may generate electrical power in line 179 that powers the electric heater 189.
  • the eighth WHRU 178 may generate electrical power that is supplied to the fourth driver 165 via line 183.
  • heat energy from the process gas in line 174 may be used to heat the thermal mass 188 and/or power the fourth driver 165.
  • the process gas in line 180 may have a pressure between about 1250 psia and about 1800 psia and a temperature between about 100°F and about 200°F.
  • the process gas in line 180 may have a pressure of about 1510 psia and a temperature of about 120°F.
  • the process gas in line 180 may be introduced to the fourth process cooler 181 , which further cools process gas and outputs the process gas in line 184.
  • the process gas in line 184 may have a pressure between about 1300 psia and about 1700 psia and a temperature between about 70°F and 100°F.
  • the process gas in line 184 may have a pressure of about 1500 psia and a temperature of about 85°F.
  • the process gas in line 184 may be introduced to and stored in the compressed gas storage unit 185 during off-peak hours. During peak hours, the process gas may be drawn from the compressed gas storage unit 185 and used to power the power generation unit 192. Prior to being introduced to the power generation unit 192, the process gas may be introduced to the thermal mass 188 via line 186. The thermal mass may transfer heat to the process gas. The thermal mass 188 may heat the compressed process gas to a temperature between about 600°F and about 1400°F. For example, the thermal mass 188 may heat the compressed process gas to a temperature between about 800°F and about 1000°F.
  • the process gas may be transported from the thermal mass 188 to the power generation unit 192 via line 190.
  • the process gas may expand in the expander 194 generating mechanical power to drive the electrical generator 195.
  • the process gas is combined with fuel and combusted in a combustor 193 prior to being introduced to the expander 194.
  • the electrical generator 195 may generate and supply power to the electrical grid 101 during peak hours.
  • at least a portion of the electrical power generated by the electrical generator 195 may be introduced to the electric heater 189 via line 191 .
  • Figure 2 depicts a block diagram of another illustrative adiabatic CAES system 200 including a supersonic compressor train 204, according to one or more embodiments described.
  • the components in Figure 2 may be substantially similar to the corresponding components in Figure 1 , except, the compressors 206,226 in Figure 2 may be supersonic compressors.
  • the supersonic compressors 206,226 in the supersonic compressor train 204 may achieve the desired temperature and pressure with fewer compressors than a subsonic compressor train 104 (see Figure 1 ).
  • the supersonic compressors 206,226 may be Rampressors ® developed by Ramgen Power Systems, LLC of Bellevue, Washington.
  • the first compressor 206 may be a supersonic compressor having about a 60 inch wheel
  • the second compressor may be a supersonic compressor having about a 34 inch wheel. Any number of supersonic compressors 206,226 may be used in the supersonic compressor train 204.
  • the supersonic compressors 206,226 may be driven by drivers 205,225.
  • the first driver 205 may be about a 71 MW electric motor
  • the second driver 225 may be about a 69 MW electric motor.
  • other motor sizes are contemplated herein.
  • the process gas may be introduced to the first supersonic compressor 206 via line 207.
  • the process gas in line 207 may have a pressure between about 10 psia and 20 psia, a temperature between about 80°F and about 1 10°F, a RH between about 50% and about 70%, and a flow rate between about 370 lbs/sec and about 470 lbs/sec.
  • the process gas in line 207 may have a pressure of about 14.7 PSIA, a temperature of about 95°F, a RH of about 60%, and a flow rate of about 420 lbs/sec.
  • the first supersonic compressor 206 may compress the process gas and output a first compressed process gas in line 208.
  • the first compressed process gas in line 208 may have a pressure between about 100 psia and about 200 psia and a temperature between about 600°F and about 800°F.
  • the first compressed process gas in line 208 may have a pressure of about 152.5 psia and a temperature of about 700°F.
  • the first compressed process gas may be introduced to the first heat transfer unit 209 via line 208, and the heat transfer medium may be introduced to the first heat transfer unit 209 via line 210.
  • the first heat transfer unit 209 transfers heat from the first compressed process gas to the heat transfer medium and outputs and the process gas in line 214 and the heat transfer medium in line 21 1
  • the heat transfer medium in line 21 1 may be introduced to the first WHRU 212.
  • the first WHRU 212 may generate electrical power in line 213 that powers the electric heater 289.
  • the first WHRU 212 may generate electrical power that is supplied to the first driver 205 via line 222.
  • heat energy from the first compressed process gas in line 208 may be used to heat the thermal mass 288 and/or power the first driver 205.
  • the process gas in line 214 may have a pressure between about 120 psia and about 220 psia and a temperature between about 160°F and about 360°F.
  • the process gas in line 214 may have a pressure of about 170 psia and a temperature of about 260°F.
  • the process gas may be introduced to the second heat transfer unit 215 via line 214, and the heat transfer medium may be introduced to the second heat transfer unit 215 via line 216.
  • the second heat transfer unit 215 transfers heat from the process gas to the heat transfer medium and outputs the process gas in line 220 and the heat transfer medium in line 217.
  • the heat transfer medium in line 217 may be introduced to the second WHRU 218.
  • the second WHRU 218 may generate electrical power in line 219 that powers the electric heater 289.
  • the second WHRU 218 may generate electrical power that is supplied to the first driver 205 via line 223.
  • heat energy from the process gas in line 214 may be used to heat the thermal mass 288 and/or powerthe first driver205.
  • the process gas in line 220 may have a pressure between about 1 10 psia and about 180 psia and a temperature between about 100°F and about 250°F.
  • the process gas in line 220 may have a pressure of about 145 psia and a temperature of about 120°F.
  • the gas in line 220 may be introduced to a first process cooler 221 , which further cools the process gas and outputs the process gas in line 227.
  • the process gas in line 227 may have a pressure between about 100 psia and 200 psia and a temperature between about 50°F and about 130°F.
  • the first cooled process gas may have a pressure of about 149 psia and a temperature of about 93°F.
  • the process gas in line 227 may be introduced to the second supersonic compressor 226.
  • the second supersonic compressor 226 may compress the process gas and output a second compressed process gas in line 228.
  • the second compressed process gas in line 228 may have a pressure between about 1325 psia and about 1725 psia and a temperature between about 600°F and about 800°F.
  • the second compressed process gas in line 228 may have a pressure of about 1525 psia and a temperature of about 699°F.
  • the second compressed process gas may be introduced to the third heat transfer unit 229 via line 228, and the heat transfer medium may be introduced to the third heat transfer unit 229 via line 230.
  • the third heat transfer unit transfers heat from the second compressed process gas to the heat transfer medium and outputs the process gas in line 234 and the heat transfer medium in line 231.
  • the heat transfer medium in line 231 may be introduced to the third WHRU 232.
  • the third WHRU 232 may generate electrical power in line 233 that powers the electric heater 289.
  • the third WHRU 232 may generate electrical power that is supplied to the second driver 225 via line 242.
  • heat energy from the second compressed process gas in line 228 may be used to heat the thermal mass 288 and/or power the second driver 225.
  • the process gas in line 234 may have a pressure between about 1250 psia and about 1800 psia and a temperature between about 160°F and about 360°F.
  • the process gas in line 234 may have a pressure of about 1520 psia and a temperature of about 260°F.
  • the process gas may be introduced to the fourth heat transfer unit 235 via line 234, and the heat transfer medium may be introduced to the fourth heat transfer unit 235 via line 236.
  • the fourth heat transfer unit transfers heat from the process gas to the heat transfer medium and outputs the process gas in line 240 and the heat transfer medium in line 237.
  • the heat transfer medium in line 237 may be introduced to the fourth WHRU 238.
  • the fourth WHRU 238 may generate electrical power in line 239 that powers the electric heater 289.
  • the fourth WHRU 238 may generate electrical power that is supplied to the second driver 225 via line 243.
  • heat energy from the process gas in line 234 may be used to heat the thermal mass 288 and/or power the second driver 225.
  • the process gas in line 240 may have a pressure between about 1250 psia and about 1800 psia and a temperature between about 160°F and about 360°F.
  • the process gas in line 240 may have a pressure of about 1515 psia and a temperature of about 120°F.
  • the process gas in line 240 may be introduced to the second process cooler 241 , which may further cool the process gas and output the process gas in line 284.
  • the process gas in line 284 may have a pressure between about 1300 psia and about 1700 psia and a temperature between about 70°F and about 100°F.
  • the process gas in line 284 may have a pressure of about 1500 psia and a temperature of about 85°F.
  • the process gas in line 284 may be introduced to and stored in the compressed gas storage unit 285 during off-peak hours. During peak hours, the process gas may be drawn from the compressed gas storage unit 285 and used to power the power generation unit 292. Prior to being introduced to the power generation unit 292, the process gas may be introduced to the thermal mass 288 via line 286.
  • the thermal mass 288 may heat the process gas in line 286. In at least one embodiment, thermal mass 288 may heat the process gas in line 286 to a temperature between about 800°F and about 1400°F. For example, the thermal mass 288 may heat the process gas to a temperature between about 800°F and about 1000°F.
  • the process gas may be transported from the thermal mass 288 to the power generation unit 292 via line 290.
  • the process gas in line 290 may power the expander 294.
  • the process gas in line 290 may be combined with fuel and combusted in a combustor 293 prior to being introduced to the expander 294.
  • the expander 294 may drive an electrical generator 295, and the electrical generator 295 may generate and supply power to the electrical grid 201 during peak hours.
  • at least a portion of the electrical power generated by the electrical generator 295 may be introduced to the electric heater 289 via line 291.
  • a heat transfer unit 296 may be configured to recover thermal energy from the exhaust from at least one of the combustor 293, the expander 294, and the electrical generator 295.
  • a WHRU 297 may be coupled to the heat transfer unit 296 and configured to generate electrical power. The electrical power generated by the WHRU 297 may be supplied to the electric heater 289 and/or at least one of the drivers 205,225.
  • FIG. 3 depicts a flowchart of an illustrative method 300 of generating power using stored compressed air energy.
  • the method 300 includes compressing a process gas with a compressor to produce a compressed process gas, as shown at 302.
  • the method 300 also includes transferring heat from the compressed process gas to a heat transfer medium with a heat transfer unit to produce a cooled process gas and a heated heat transfer medium, as shown at 304.
  • the method 300 also includes storing the cooled process gas in a compressed gas storage unit, as shown at 306.
  • the method 300 also includes transporting the heated heat transfer medium to a waste heat recovery unit, as shown at 308.
  • the method 300 also includes heating a thermal mass with the waste heat recovery unit, as shown at 310.
  • the method 300 also includes transporting the cooled process gas from the compressed gas storage unit to the thermal mass, as shown at 312.
  • the method 300 also includes heating the cooled process gas with the thermal mass to produce a heated process gas, as shown at 314.
  • the method 300 also includes transporting the heated process gas from the thermal mass to a power generation unit, as shown at 316.
  • the method 300 also includes generating a power output with the power generation unit, as shown at 318.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
PCT/US2011/045275 2010-08-10 2011-07-26 Adiabatic compressed air energy storage process Ceased WO2012021285A2 (en)

Priority Applications (5)

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EP11816782.4A EP2603684B1 (en) 2010-08-10 2011-07-26 Adiabatic compressed air energy storage process
CA2807502A CA2807502C (en) 2010-08-10 2011-07-26 Adiabatic compressed air energy storage process
JP2013524090A JP5893025B2 (ja) 2010-08-10 2011-07-26 断熱的圧縮エア・エネルギー蓄積方法
AU2011289781A AU2011289781C1 (en) 2010-08-10 2011-07-26 Adiabatic compressed air energy storage process
CN201180046211.3A CN103237970B (zh) 2010-08-10 2011-07-26 绝热式压缩空气蓄能处理

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US37225210P 2010-08-10 2010-08-10
US61/372,252 2010-08-10
US13/050,781 US8978380B2 (en) 2010-08-10 2011-03-17 Adiabatic compressed air energy storage process
US13/050,781 2011-03-17

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8978380B2 (en) 2010-08-10 2015-03-17 Dresser-Rand Company Adiabatic compressed air energy storage process
US9938895B2 (en) 2012-11-20 2018-04-10 Dresser-Rand Company Dual reheat topping cycle for improved energy efficiency for compressed air energy storage plants with high air storage pressure
CN110446839A (zh) * 2017-03-29 2019-11-12 株式会社神户制钢所 压缩空气储能发电装置

Families Citing this family (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2687702A1 (en) * 2012-07-20 2014-01-22 Alstom Technology Ltd Energy storage system and method for energy storage
US20140033714A1 (en) * 2012-07-31 2014-02-06 General Electric Company Regenerative thermal energy system and method of operating the same
US9551279B2 (en) * 2013-03-14 2017-01-24 Dresser-Rand Company CAES plant using steam injection and bottoming cycle expander
US9010117B2 (en) * 2013-03-15 2015-04-21 Cummins Inc. Multi-stage turbocharger system with intercooling and aftercooling
WO2014161065A1 (en) * 2013-04-03 2014-10-09 Sigma Energy Storage Inc. Compressed air energy storage and recovery
CN103410616B (zh) * 2013-08-22 2015-10-21 华北电力大学 大容量压缩空气储能高效发电系统
US9790847B2 (en) 2014-04-07 2017-10-17 Cummins Inc. Multi-stage turbocharger system with off-engine low pressure stage
JP6411221B2 (ja) * 2014-08-27 2018-10-24 株式会社神戸製鋼所 圧縮流体貯蔵発電装置
JP6614878B2 (ja) * 2014-12-25 2019-12-04 株式会社神戸製鋼所 圧縮空気貯蔵発電装置及び圧縮空気貯蔵発電方法
US10514210B2 (en) * 2014-12-31 2019-12-24 Ingersoll-Rand Company Fin-tube heat exchanger
JP6510876B2 (ja) 2015-05-01 2019-05-08 株式会社神戸製鋼所 圧縮空気貯蔵発電方法および圧縮空気貯蔵発電装置
JP6373794B2 (ja) 2015-05-08 2018-08-15 株式会社神戸製鋼所 圧縮空気貯蔵発電装置及び圧縮空気貯蔵発電方法
JP6456236B2 (ja) 2015-05-11 2019-01-23 株式会社神戸製鋼所 圧縮空気貯蔵発電装置
JP6343587B2 (ja) 2015-05-18 2018-06-13 株式会社神戸製鋼所 圧縮空気貯蔵発電方法及び圧縮空気貯蔵発電装置
JP6511378B2 (ja) 2015-09-29 2019-05-15 株式会社神戸製鋼所 圧縮空気貯蔵発電装置及び圧縮空気貯蔵発電方法
JP6649141B2 (ja) * 2016-03-18 2020-02-19 株式会社神戸製鋼所 圧縮空気貯蔵発電装置
AU2018212001A1 (en) * 2017-01-30 2019-08-22 The Regents Of The University Of California Storage-combined cold, heat and power
BR112019015745B1 (pt) 2017-02-01 2021-07-13 Hydrostor Inc. Sistema de armazenamento de energia de gás comprimido
EP4382735A3 (en) 2017-03-09 2024-08-28 Hydrostor Inc. A thermal storage apparatus for a compressed gas energy storage system
CN108644607A (zh) * 2018-04-02 2018-10-12 全球能源互联网研究院有限公司 一种深冷液化空气储能系统和方法
WO2019218084A1 (en) 2018-05-17 2019-11-21 Hydrostor Inc. A hydrostatically compressed gas energy storage system
EP3794270A4 (en) 2018-05-17 2022-03-09 Hydrostor Inc. HYDROSTATICALLY COMPENSATED COMPRESSED GAS ENERGY STORAGE SYSTEM
EP3911588B1 (en) 2019-01-15 2025-03-05 Hydrostor Inc. A compressed gas energy storage system
US20230110494A1 (en) 2019-02-08 2023-04-13 Hydrostor Inc. Reversible heat exchangers in compressed air energy storage systems
CA3128774A1 (en) 2019-02-27 2020-09-03 Hydrostor Inc. A hydrostatically compensated caes system having an elevated compensation liquid reservoir
CN111396162B (zh) * 2020-04-20 2024-05-07 贵州电网有限责任公司 一种高效率的先进压缩空气储能系统及方法
CN112459983B (zh) * 2020-11-24 2022-03-01 清华四川能源互联网研究院 一种含压缩空气储能的综合供能系统及方法
FR3117165B1 (fr) * 2020-12-03 2022-12-09 Ifp Energies Now Système et procédé de stockage et de récupération d’énergie par gaz comprimé avec récupération de liquide
US12253020B2 (en) * 2021-12-29 2025-03-18 Mark Patton Electrical power generating system

Family Cites Families (147)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2421387A (en) 1943-04-02 1947-06-03 Ljungstroms Angturbin Ab Hot air turbine power plant with automatic air supply control
GB1275753A (en) 1968-09-14 1972-05-24 Rolls Royce Improvements in or relating to gas turbine engine power plants
CH599460A5 (enExample) 1975-12-23 1978-05-31 Bbc Brown Boveri & Cie
CH593423A5 (enExample) 1976-03-15 1977-11-30 Bbc Brown Boveri & Cie
GB1583648A (en) 1976-10-04 1981-01-28 Acres Consulting Services Compressed air power storage systems
US4094148A (en) 1977-03-14 1978-06-13 Stone & Webster Engineering Corporation Thermal storage with molten salt for peaking power
US4158145A (en) 1977-10-20 1979-06-12 The United States Of America As Represented By The United States Department Of Energy Combined compressed air storage-low BTU coal gasification power plant
US4348863A (en) 1978-10-31 1982-09-14 Taylor Heyward T Regenerative energy transfer system
US4281256A (en) * 1979-05-15 1981-07-28 The United States Of America As Represented By The United States Department Of Energy Compressed air energy storage system
US4275310A (en) 1980-02-27 1981-06-23 Summers William A Peak power generation
US4347706A (en) 1981-01-07 1982-09-07 The United States Of America As Represented By The United States Department Of Energy Electric power generating plant having direct coupled steam and compressed air cycles
US4593202A (en) 1981-05-06 1986-06-03 Dipac Associates Combination of supercritical wet combustion and compressed air energy storage
US4391552A (en) 1981-08-24 1983-07-05 Bechtel International Corp. Apparatus and method for eliminating champagne effect in compressed air energy storage systems
DE3139567A1 (de) 1981-10-05 1983-04-21 Bautz, Wilhelm, 6000 Frankfurt Verfahren zur speicherung von elektrischer energie unter verwendung von fluessiggasen, insbesondere fluessiger luft
CH659855A5 (de) * 1981-11-16 1987-02-27 Bbc Brown Boveri & Cie Luftspeicher-kraftwerk.
HU202958B (en) 1984-01-11 1991-04-29 Energiagazdalkodasi Intezet Method for combined electric power and heat producing at power plants operating with boilers of heat utilization
US4644202A (en) * 1985-04-15 1987-02-17 Rockwell International Corporation Sealed and balanced motor and fluid pump system
US4765142A (en) 1987-05-12 1988-08-23 Gibbs & Hill, Inc. Compressed air energy storage turbomachinery cycle with compression heat recovery, storage, steam generation and utilization during power generation
US4870816A (en) 1987-05-12 1989-10-03 Gibbs & Hill, Inc. Advanced recuperator
US4885912A (en) 1987-05-13 1989-12-12 Gibbs & Hill, Inc. Compressed air turbomachinery cycle with reheat and high pressure air preheating in recuperator
US4872307A (en) 1987-05-13 1989-10-10 Gibbs & Hill, Inc. Retrofit of simple cycle gas turbines for compressed air energy storage application
US4936098A (en) 1987-05-13 1990-06-26 Gibbs & Hill, Inc. Utilization of circulating fluidized bed combustors for compressed air energy storage application
US4849648A (en) 1987-08-24 1989-07-18 Columbia Energy Storage, Inc. Compressed gas system and method
RU2029119C1 (ru) 1988-05-04 1995-02-20 Гришин Александр Николаевич Газотурбинная установка
JPH0245622A (ja) * 1988-08-08 1990-02-15 Mitsubishi Heavy Ind Ltd 圧縮空気貯蔵発電装置
US4942736A (en) 1988-09-19 1990-07-24 Ormat Inc. Method of and apparatus for producing power from solar energy
US4995234A (en) 1989-10-02 1991-02-26 Chicago Bridge & Iron Technical Services Company Power generation from LNG
US5181376A (en) 1990-08-10 1993-01-26 Fluor Corporation Process and system for producing power
JP3040442B2 (ja) * 1990-09-20 2000-05-15 三菱重工業株式会社 ガスタービン発電設備
WO1992022741A1 (en) 1991-06-17 1992-12-23 Electric Power Research Institute, Inc. Power plant utilizing compressed air energy storage and saturation
US5406786A (en) * 1993-07-16 1995-04-18 Air Products And Chemicals, Inc. Integrated air separation - gas turbine electrical generation process
JPH0742573A (ja) * 1993-07-30 1995-02-10 Mitsubishi Heavy Ind Ltd 圧縮空気エネルギー貯蔵式電力平準化システム
IL108546A (en) 1994-02-03 1997-01-10 Israel Electric Corp Ltd Compressed air energy storage method and system
US5384489A (en) 1994-02-07 1995-01-24 Bellac; Alphonse H. Wind-powered electricity generating system including wind energy storage
US5442904A (en) 1994-03-21 1995-08-22 Shnaid; Isaac Gas turbine with bottoming air turbine cycle
US5632143A (en) 1994-06-14 1997-05-27 Ormat Industries Ltd. Gas turbine system and method using temperature control of the exhaust gas entering the heat recovery cycle by mixing with ambient air
US5495709A (en) 1994-08-05 1996-03-05 Abb Management Ag Air reservoir turbine
US5634340A (en) 1994-10-14 1997-06-03 Dresser Rand Company Compressed gas energy storage system with cooling capability
US5660037A (en) 1995-06-27 1997-08-26 Siemens Power Corporation Method for conversion of a reheat steam turbine power plant to a non-reheat combined cycle power plant
JP3696931B2 (ja) * 1995-07-03 2005-09-21 三菱重工業株式会社 液体空気利用発電設備
US6920759B2 (en) 1996-12-24 2005-07-26 Hitachi, Ltd. Cold heat reused air liquefaction/vaporization and storage gas turbine electric power system
JP3639404B2 (ja) * 1997-02-26 2005-04-20 株式会社タクマ 廃棄物の乾留熱分解溶融燃焼装置
US5778675A (en) 1997-06-20 1998-07-14 Electric Power Research Institute, Inc. Method of power generation and load management with hybrid mode of operation of a combustion turbine derivative power plant
US5931021A (en) 1997-06-24 1999-08-03 Shnaid; Isaac Straightforward method and once-through apparatus for gas liquefaction
US5845479A (en) 1998-01-20 1998-12-08 Electric Power Research Institute, Inc. Method for providing emergency reserve power using storage techniques for electrical systems applications
JPH11257096A (ja) * 1998-03-17 1999-09-21 Hitachi Ltd ガスタービン発電プラント
JP2000008878A (ja) * 1998-06-26 2000-01-11 Ishikawajima Harima Heavy Ind Co Ltd コージェネレーション設備
US6038849A (en) 1998-07-07 2000-03-21 Michael Nakhamkin Method of operating a combustion turbine power plant using supplemental compressed air
US5934063A (en) 1998-07-07 1999-08-10 Nakhamkin; Michael Method of operating a combustion turbine power plant having compressed air storage
US6053699A (en) 1998-07-27 2000-04-25 General Electric Company Steam turbine having a brush seal assembly
US6512305B1 (en) 1999-05-26 2003-01-28 Active Power, Inc. Method and apparatus having a turbine working in different modes for providing an uninterruptible supply of electric power to a critical load
JP2001115859A (ja) * 1999-10-19 2001-04-24 Toshiba Corp Ｃａｅｓ発電システム
US6442941B1 (en) 2000-09-11 2002-09-03 General Electric Company Compressor discharge bleed air circuit in gas turbine plants and related method
US6276123B1 (en) 2000-09-21 2001-08-21 Siemens Westinghouse Power Corporation Two stage expansion and single stage combustion power plant
DE10050248A1 (de) 2000-10-11 2002-04-18 Alstom Switzerland Ltd Brenner
JP2002250023A (ja) * 2001-02-23 2002-09-06 Kubota Corp 制水扉
JP2002250234A (ja) * 2001-02-23 2002-09-06 Mitsubishi Heavy Ind Ltd 液体空気製造装置
GB2373299B (en) 2001-03-12 2004-10-27 Alstom Power Nv Re-fired gas turbine engine
US6708500B2 (en) 2001-08-17 2004-03-23 Alstom Technology Ltd Turbogroup of a power generating plant
DE10236294A1 (de) 2001-08-17 2003-02-27 Alstom Switzerland Ltd Gasversorgungskontrolleinrichtung einer Gasspeicherkraftanlage
DE10236323A1 (de) 2001-08-17 2003-03-06 Alstom Switzerland Ltd Kraftwerksanlage und zugehöriges Startverfahren
DE10236501A1 (de) 2001-08-17 2003-04-03 Alstom Switzerland Ltd Startverfahren für eine Kraftwerksanlage
DE10236324A1 (de) * 2001-08-17 2003-03-06 Alstom Switzerland Ltd Verfahren zum Kühlen von Turbinenschaufeln
US6694722B2 (en) 2001-08-17 2004-02-24 Alstom Technology Ltd Recuperator for thermal power installation
DE10236326A1 (de) 2001-08-17 2003-03-06 Alstom Switzerland Ltd Gasspeicherkraftanlage
US6637207B2 (en) 2001-08-17 2003-10-28 Alstom (Switzerland) Ltd Gas-storage power plant
WO2003031813A1 (en) 2001-10-05 2003-04-17 Ben Enis Method and apparatus for using wind turbines to generates and supply uninterrupted power to locations remote from the power grid
GB2382847A (en) 2001-12-06 2003-06-11 Alstom Gas turbine wet compression
US6745569B2 (en) 2002-01-11 2004-06-08 Alstom Technology Ltd Power generation plant with compressed air energy system
US6725665B2 (en) 2002-02-04 2004-04-27 Alstom Technology Ltd Method of operation of gas turbine having multiple burners
US20080196429A1 (en) 2002-02-11 2008-08-21 The Trustees Of Dartmouth College Pulse Electrothermal And Heat-Storage Ice Detachment Apparatus And Method
US6851265B2 (en) 2002-02-19 2005-02-08 Siemens Westinghouse Power Corporation Steam cooling control for a combined cycle power plant
US6792760B2 (en) 2002-03-11 2004-09-21 Alstom Technology Ltd Method for operating a turbine
US6848259B2 (en) 2002-03-20 2005-02-01 Alstom Technology Ltd Compressed air energy storage system having a standby warm keeping system including an electric air heater
DE10219948A1 (de) 2002-05-03 2003-11-13 Alstom Switzerland Ltd Dampfturbine
US7669419B2 (en) 2002-12-07 2010-03-02 Energetix Group Limited Electrical power supply system
US7127895B2 (en) 2003-02-05 2006-10-31 Active Power, Inc. Systems and methods for providing backup energy to a load
US7086231B2 (en) 2003-02-05 2006-08-08 Active Power, Inc. Thermal and compressed air storage system
DE10307374A1 (de) 2003-02-21 2004-09-02 Alstom Technology Ltd Verfahren zum Betrieb eines teilgeschlossenen, aufgeladenen Gasturbinenkreislaufs sowie Gasturbinensystem zur Durchführung des Verfahrens
FR2852358B1 (fr) 2003-03-13 2006-06-09 Procede et un dispositif de cogeneration par turbine a gaz avec chambre de postcombustion
US6863474B2 (en) 2003-03-31 2005-03-08 Dresser-Rand Company Compressed gas utilization system and method with sub-sea gas storage
SE0301585D0 (sv) 2003-05-30 2003-05-30 Euroturbine Ab Förfarande för drift av en gasturbingrupp
DE102004040890A1 (de) 2003-09-04 2005-03-31 Alstom Technology Ltd Kraftwerksanlage, und Verfahren zum Betrieb
EP1512855A1 (de) 2003-09-04 2005-03-09 ALSTOM Technology Ltd Kraftwerksanlage, und Verfahren zum Betrieb
US6931856B2 (en) 2003-09-12 2005-08-23 Mes International, Inc. Multi-spool turbogenerator system and control method
WO2005027302A1 (de) 2003-09-12 2005-03-24 Alstom Technology Ltd Modulare kraftwerksanlage mit kompressor- und turbineneinheit sowie druckspeichervolumen
US6955050B2 (en) 2003-12-16 2005-10-18 Active Power, Inc. Thermal storage unit and methods for using the same to heat a fluid
DE10360951A1 (de) 2003-12-23 2005-07-28 Alstom Technology Ltd Wärmekraftanlage mit sequentieller Verbrennung und reduziertem CO2-Ausstoß sowie Verfahren zum Betreiben einer derartigen Anlage
DE102004007482B4 (de) 2004-02-13 2010-06-24 Alstom Technology Ltd. Kraftwerksanlage
US7325401B1 (en) 2004-04-13 2008-02-05 Brayton Energy, Llc Power conversion systems
JP4469222B2 (ja) 2004-05-19 2010-05-26 東京電力株式会社 複合発電プラント
DE102004028531A1 (de) 2004-06-11 2006-01-05 Alstom Technology Ltd Verfahren zum Betrieb einer Kraftwerksanlage, und Kraftwerksanlage
US7719127B2 (en) 2004-06-15 2010-05-18 Hamilton Sundstrand Wind power system for energy production
US7471010B1 (en) 2004-09-29 2008-12-30 Alliance For Sustainable Energy, Llc Wind turbine tower for storing hydrogen and energy
US7693402B2 (en) 2004-11-19 2010-04-06 Active Power, Inc. Thermal storage unit and methods for using the same to heat a fluid
CA2592456C (en) 2004-12-23 2015-01-06 Alstom Technology Ltd. Method for the operation of a pressure accumulator plant, and pressure accumulator plant
WO2006084809A1 (de) 2005-02-10 2006-08-17 Alstom Technology Ltd Verfahren zum start einer druckspeicheranlage, und druckspeicheranlage
JP2008534851A (ja) 2005-03-30 2008-08-28 アルストム テクノロジー リミテッド 接続可能な補助グループから成るタービン装置を始動する方法
EP1917428B1 (de) 2005-08-23 2017-12-13 General Electric Technology GmbH Verfahren zum betrieb einer kraftwerksanlage mit einem druckspeicher
US20070095069A1 (en) 2005-11-03 2007-05-03 General Electric Company Power generation systems and method of operating same
US20090282840A1 (en) 2006-02-27 2009-11-19 Highview Enterprises Limited Energy storage and generation
US7856843B2 (en) 2006-04-05 2010-12-28 Enis Ben M Thermal energy storage system using compressed air energy and/or chilled water from desalination processes
CA2650981A1 (en) 2006-05-02 2007-11-08 Firebox Energy Systems Ltd. Indirect-fired gas turbine power plant
WO2007141101A1 (de) 2006-06-07 2007-12-13 Alstom Technology Ltd Verfahren zum betrieb einer gasturbine, anwendung des verfahrens in einem kombikraftwerk und kombikraftwerk zur durchführung des verfahrens
US7753646B1 (en) 2006-08-01 2010-07-13 Active Power, Inc. Systems and methods for cooling bearings
KR100792790B1 (ko) 2006-08-21 2008-01-10 한국기계연구원 압축공기저장발전시스템 및 이를 이용한 발전방법
US7918091B1 (en) 2006-09-20 2011-04-05 Active Power, Inc. Systems and methods for controlling humidity
US7389644B1 (en) 2007-01-19 2008-06-24 Michael Nakhamkin Power augmentation of combustion turbines by injection of cold air upstream of compressor
US7669423B2 (en) 2007-01-25 2010-03-02 Michael Nakhamkin Operating method for CAES plant using humidified air in a bottoming cycle expander
US20080178601A1 (en) 2007-01-25 2008-07-31 Michael Nakhamkin Power augmentation of combustion turbines with compressed air energy storage and additional expander with airflow extraction and injection thereof upstream of combustors
US7640643B2 (en) 2007-01-25 2010-01-05 Michael Nakhamkin Conversion of combined cycle power plant to compressed air energy storage power plant
US7614237B2 (en) 2007-01-25 2009-11-10 Michael Nakhamkin CAES system with synchronous reserve power requirements
US8011189B2 (en) 2007-01-25 2011-09-06 Michael Nakhamkin Retrofit of simple cycle gas turbine for compressed air energy storage application having expander for additional power generation
US8261552B2 (en) 2007-01-25 2012-09-11 Dresser Rand Company Advanced adiabatic compressed air energy storage system
DE102007015309B4 (de) 2007-03-27 2023-01-05 Ansaldo Energia Switzerland AG Betriebsverfahren für eine Turbogruppe
JP4371278B2 (ja) 2007-08-07 2009-11-25 株式会社日立製作所 高湿分利用ガスタービン設備
US8156725B2 (en) 2007-12-21 2012-04-17 Palo Alto Research Center Incorporated CO2 capture during compressed air energy storage
JP5022887B2 (ja) 2007-12-25 2012-09-12 株式会社東芝 蒸気弁装置および蒸気タービンプラント
US7963097B2 (en) 2008-01-07 2011-06-21 Alstom Technology Ltd Flexible assembly of recuperator for combustion turbine exhaust
ATE530771T1 (de) * 2008-01-18 2011-11-15 Ramgen Power Systems Llc Verfahren und vorrichtung zum starten von überschallverdichtern
US8024928B2 (en) 2008-01-24 2011-09-27 Enis Ben M Method and apparatus for using solar energy to enhance the operation of a compressed air energy storage system
US7743609B1 (en) 2008-02-06 2010-06-29 Florida Turbine Technologies, Inc. Power plant with energy storage deep water tank
US8037678B2 (en) 2009-09-11 2011-10-18 Sustainx, Inc. Energy storage and generation systems and methods using coupled cylinder assemblies
US7802426B2 (en) 2008-06-09 2010-09-28 Sustainx, Inc. System and method for rapid isothermal gas expansion and compression for energy storage
US7958731B2 (en) 2009-01-20 2011-06-14 Sustainx, Inc. Systems and methods for combined thermal and compressed gas energy conversion systems
US8225606B2 (en) 2008-04-09 2012-07-24 Sustainx, Inc. Systems and methods for energy storage and recovery using rapid isothermal gas expansion and compression
US20110266810A1 (en) 2009-11-03 2011-11-03 Mcbride Troy O Systems and methods for compressed-gas energy storage using coupled cylinder assemblies
US7874036B2 (en) 2008-09-16 2011-01-25 Carlos Wong Energy storage bridge
US8176724B2 (en) 2008-09-18 2012-05-15 Smith Douglas W P Hybrid Brayton cycle with solid fuel firing
US8137054B2 (en) * 2008-12-23 2012-03-20 General Electric Company Supersonic compressor
US8104274B2 (en) 2009-06-04 2012-01-31 Sustainx, Inc. Increased power in compressed-gas energy storage and recovery
US8196395B2 (en) 2009-06-29 2012-06-12 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8146354B2 (en) 2009-06-29 2012-04-03 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US8436489B2 (en) 2009-06-29 2013-05-07 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
US20110016864A1 (en) 2009-07-23 2011-01-27 Electric Power Research Institute, Inc. Energy storage system
US8347628B2 (en) 2009-08-18 2013-01-08 Gerard Henry M Power generation directly from compressed air for exploiting wind and solar power
US20110094231A1 (en) 2009-10-28 2011-04-28 Freund Sebastian W Adiabatic compressed air energy storage system with multi-stage thermal energy storage
US20110100010A1 (en) 2009-10-30 2011-05-05 Freund Sebastian W Adiabatic compressed air energy storage system with liquid thermal energy storage
US8347629B2 (en) 2009-10-30 2013-01-08 General Electric Company System and method for reducing moisture in a compressed air energy storage system
US8572972B2 (en) 2009-11-13 2013-11-05 General Electric Company System and method for secondary energy production in a compressed air energy storage system
US8171728B2 (en) 2010-04-08 2012-05-08 Sustainx, Inc. High-efficiency liquid heat exchange in compressed-gas energy storage systems
US8534058B2 (en) 2010-05-14 2013-09-17 Southwest Research Institute Energy storage and production systems, apparatus and methods of use thereof
EP2586121B1 (en) 2010-06-23 2019-12-11 Synchrony, Inc. Split magnetic thrust bearing
US8978380B2 (en) 2010-08-10 2015-03-17 Dresser-Rand Company Adiabatic compressed air energy storage process
US8261522B2 (en) * 2010-09-09 2012-09-11 The Toro Company Reel gang mower having reel cutting units with adjustable pull point locations
US8863519B2 (en) 2011-08-15 2014-10-21 Powerphase Llc High output modular CAES (HOMC)
US9938895B2 (en) 2012-11-20 2018-04-10 Dresser-Rand Company Dual reheat topping cycle for improved energy efficiency for compressed air energy storage plants with high air storage pressure

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of EP2603684A4 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8978380B2 (en) 2010-08-10 2015-03-17 Dresser-Rand Company Adiabatic compressed air energy storage process
US9938895B2 (en) 2012-11-20 2018-04-10 Dresser-Rand Company Dual reheat topping cycle for improved energy efficiency for compressed air energy storage plants with high air storage pressure
CN110446839A (zh) * 2017-03-29 2019-11-12 株式会社神户制钢所 压缩空气储能发电装置

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EP2603684A2 (en) 2013-06-19
US8978380B2 (en) 2015-03-17
JP2013536357A (ja) 2013-09-19
US20120036853A1 (en) 2012-02-16
AU2011289781A1 (en) 2013-03-21
CA2807502A1 (en) 2012-02-16
CA2807502C (en) 2017-10-24
AU2011289781B2 (en) 2016-01-28
CN103237970A (zh) 2013-08-07
WO2012021285A3 (en) 2012-04-12
EP2603684B1 (en) 2019-03-20
AU2011289781C1 (en) 2016-06-02
CN103237970B (zh) 2015-09-30
JP5893025B2 (ja) 2016-03-23

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