WO2018218617A1 - 分级蓄冷式超临界压缩空气储能系统及方法 - Google Patents

分级蓄冷式超临界压缩空气储能系统及方法 Download PDF

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Publication number
WO2018218617A1
WO2018218617A1 PCT/CN2017/086877 CN2017086877W WO2018218617A1 WO 2018218617 A1 WO2018218617 A1 WO 2018218617A1 CN 2017086877 W CN2017086877 W CN 2017086877W WO 2018218617 A1 WO2018218617 A1 WO 2018218617A1
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Prior art keywords
cold
storage
cryogenic
energy
supercritical
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PCT/CN2017/086877
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English (en)
French (fr)
Inventor
林曦鹏
王亮
陈海生
谢宁宁
杨征
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中国科学院工程热物理研究所
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Application filed by 中国科学院工程热物理研究所 filed Critical 中国科学院工程热物理研究所
Priority to US16/617,476 priority Critical patent/US11892234B2/en
Priority to PCT/CN2017/086877 priority patent/WO2018218617A1/zh
Priority to EP17911475.6A priority patent/EP3640449B1/en
Priority to JP2019565850A priority patent/JP7169305B2/ja
Priority to AU2017416627A priority patent/AU2017416627A1/en
Publication of WO2018218617A1 publication Critical patent/WO2018218617A1/zh
Priority to ZA2019/08601A priority patent/ZA201908601B/en
Priority to AU2021290222A priority patent/AU2021290222B2/en

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    • 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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0228—Coupling of the liquefaction unit to other units or processes, so-called integrated processes
    • F25J1/0235—Heat exchange integration
    • F25J1/0237—Heat exchange integration integrating refrigeration provided for liquefaction and purification/treatment of the gas to be liquefied, e.g. heavy hydrocarbon removal from natural gas
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
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    • F25J1/0002—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the fluid to be liquefied
    • F25J1/0012—Primary atmospheric gases, e.g. air
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    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
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    • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
    • F25J1/0032—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration"
    • F25J1/0035—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by gas expansion with extraction of work
    • F25J1/0037—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by gas expansion with extraction of work of a return stream
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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    • F25J1/0032—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration"
    • F25J1/0045—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by vaporising a liquid return stream
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
    • F25J1/0047—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle
    • F25J1/005—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle by expansion of a gaseous refrigerant stream with extraction of work
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
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    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
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    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
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    • F25J1/0235—Heat exchange integration
    • F25J1/0242—Waste heat recovery, e.g. from heat of compression
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    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
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    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
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    • F25J1/0244—Operation; Control and regulation; Instrumentation
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    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
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    • F25J2270/00—Refrigeration techniques used
    • F25J2270/04—Internal refrigeration with work-producing gas expansion loop
    • F25J2270/06—Internal refrigeration with work-producing gas expansion loop with multiple gas expansion loops
    • 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 invention relates to the fields of renewable energy, compressed air energy storage, distributed energy, and the like, and particularly relates to a hierarchical cold storage supercritical compressed air energy storage system and method.
  • Compressed air energy storage is the only mature physical energy storage technology for large-scale power grid storage other than pumped storage. It can be used in power grid peak-shaving and stable output of renewable energy such as solar and wind energy.
  • Conventional compressed air storage uses compressors to compress air into large caverns. It uses fossil fuels to burn and reheat to expand work during the energy release phase. It is suitable for large systems, low cost and long life, but its construction site is limited and dependent. The pollution caused by the burning of fossil energy.
  • the regenerative compressed air energy storage recovers the heat of compression generated by the compression process and is used for reheating between the turbine stages during the release process. It belongs to a Stirling cycle and is highly efficient and environmentally friendly. However, its promotion is still subject to Limited to the topography of the gas storage cave.
  • the working fluid in the Liquefied Air Energy Storage System is stored at liquid atmospheric pressure or low pressure, which not only greatly increases the energy storage density, but also greatly reduces the system construction cost and floor space.
  • the early liquid air technology release process still relies on fossil fuel combustion. There is no cold storage design in the system. It relies on external liquid air input, mainly combined with traditional air separation system. The cold energy recovery in the energy release stage is not considered, although the technology maturity. Higher, but the actual electrical efficiency of the system is very low.
  • Some literatures disclose a new liquid air energy storage technology. Compared with the previous technology, it does not contain any combustion process. Only air is used as the working fluid.
  • the heat storage and cold storage technology is added to recover the cold energy from the liquid air evaporation for the air liquefaction process. , improve system efficiency.
  • Some literatures disclose a supercritical compressed air energy storage system that recovers and stores cold energy, combining an air supercritical liquefaction cycle, an energy storage system, and a Rankine cycle.
  • the compressor exits the supercritical air to absorb the cold energy and cool down.
  • ⁇ throttling/isentropic expansion low-pressure liquefied air is stored in a low-temperature adiabatic storage tank, and the liquid air boosted by the cryopump in the release phase absorbs heat and recovers cold energy, then gasifies and reheats through the reheater to enter through Doing work.
  • the cold energy recovery is used in the liquefaction process in the above study, the cold energy utilization rate is still insufficient, and the cold storage capacity of the storage and release process is not closed.
  • the optimized Crowder absorption is considered in the liquefaction process. More cold energy and self-compensation of the system's cold energy.
  • Some literatures disclose a two-fluid cold storage cycle of propane and methanol, and the integration with nuclear power plants keeps the nuclear power plant close to full load operation while meeting the strain demand.
  • the liquid working medium also reduces the irreversible loss of cold energy as heat transfer and cold storage working medium.
  • both methanol and propane are flammable, explosive and toxic hazardous chemicals, which are prone to explosion when exposed to oxygen-rich areas during air liquefaction. Large-scale long-term storage is unimaginable in terms of safety, economy and maintenance costs.
  • the present invention provides a hierarchical cold storage subsystem and a supercritical compressed air energy storage system for solving the problem of insufficient cold energy recovery and the need for large-scale, low-cost, safe and reliable energy storage.
  • An aspect of the invention provides a staged cold storage supercritical compressed air energy storage system comprising a supercritical liquefaction subsystem for converting input gaseous air into liquid air and an evaporative expansion for converting liquid air into gaseous air
  • the subsystem wherein the hierarchical cold storage supercritical compressed air energy storage system further comprises:
  • a staged cold storage subsystem for storing and/or releasing cold energy when gaseous air and liquid air are converted.
  • the hierarchical cold storage subsystem comprises at least one liquefied cold box, at least one cryogenic cold storage cycle and at least one intermediate cold storage cycle;
  • the cryogenic cold storage cycle is connected with the liquefied cold box to release cold energy from a cryogenic temperature to a normal temperature;
  • the medium-cooling cold storage cycle is connected to the liquefied cold box to release the cold energy from the cryogenic temperature to the intermediate cooling temperature.
  • Each of the liquefied cold boxes includes at least one cryogenic cycle internal flow passage, at least one intermediate cooling circulation internal flow passage, at least one supercritical flow passage, at least one cold energy compensation flow passage, and at least one cold energy recovery flow passage. ;
  • Each of the cryogenic cold storage cycles includes at least one cryogenic storage tank, at least one cryogenic circulating fan, and at least one cryogenic circulating external flow passage, each cryogenic circulating external flow passage connecting at least one cryogenic storage tank, at least one a cryogenic circulating fan and connected to a cryogenic cycle internal flow passage in the liquefied cold box to form a complete circulation flow passage;
  • Each of the intercooled cold storage cycles includes at least one intercooled storage tank, at least one intermediate cooling circulating fan, and at least one intermediate cooling circulating external flow passage, and each intermediate cooling circulating external flow passage connects at least one intermediate cooling storage tank, at least one The intercooling circulation fan is connected to an internal cooling passage of the intermediate cooling circuit in the liquefied cold box to form a complete circulation flow passage.
  • the hierarchical cold storage subsystem further comprises at least one evaporative cold box, wherein the evaporative cold box and the liquefied cold box share at least one cryogenic cold storage cycle and at least one intermediate cold storage cycle;
  • the cryogenic cold storage cycle is connected to the evaporative cold box to store cold energy from a cryogenic temperature to a normal temperature;
  • the intercooled cold storage cycle is connected to the evaporative cold box to store the cold energy from the cryogenic temperature to the intermediate cooling temperature.
  • the evaporative cold box comprises at least one cryogenic circulation internal flow passage, at least one intermediate cooling circulation internal flow passage and at least one supercritical flow passage;
  • Each cryogenic cycle external flow passage in the cryogenic cold storage cycle is connected to at least one cryogenic storage tank, at least one cryogenic circulating fan, and is connected to a deep cooling cycle internal flow passage in the evaporation cold box to form a complete circulation flow Road
  • Each of the intermediate cooling circulation external flow passages in the intermediate cooling storage cycle is connected to at least one intermediate cooling storage tank, at least one intermediate cooling circulation fan, and is connected with an internal cooling passage of the intermediate cooling passage in the evaporation cold box to form a complete circulation flow. Road.
  • the liquefied cold box and the evaporative cold box respectively comprise a heat exchanger group, a cold-preserving material and a sealed outer casing;
  • the heat exchanger group is at least one plate fin heat exchanger, or at least one plate heat exchanger, or at least one coiled heat exchanger.
  • the cold insulation material is one or more of a mixture of glass fiber mat, pearl sand, rock wool, and vacuum board.
  • the hierarchical cold storage subsystem comprises at least one cold box, at least one cryogenic cold storage cycle and at least one intermediate cold storage cycle;
  • the cold box is used as a liquefied cold box or an evaporative cold box;
  • the cryogenic cold storage cycle is connected to the cold box, and the cold heat is released to the normal temperature when the cold box is used as the liquefied cold box, and the cold energy is stored to the normal temperature when the cold box is used as the evaporative cold box;
  • the intermediate cooling storage cycle is connected to the cold box, and the cold energy of the cryogenic temperature to the intermediate cooling temperature is released when the cold box is used as the liquefied cold box, and the cold energy of the cryogenic temperature to the intermediate cooling temperature is stored when the cold box is used as the evaporating cold box. .
  • each of the cold boxes includes at least one cryogenic cycle internal flow channel, at least one intermediate cooling cycle internal flow channel, and at least one supercritical flow channel;
  • Each of the cryogenic cold storage cycles includes at least one cryogenic storage tank, at least one cryogenic circulating fan, and at least one cryogenic circulating external flow passage, each cryogenic circulating external flow passage connecting at least one cryogenic storage tank, at least one a cryogenic circulating fan and connected to a cryogenic cycle internal flow passage in the cold box to form a complete circulation flow passage;
  • Each of the intercooled cold storage cycles includes at least one intercooled storage tank, at least one intermediate cooling circulating fan, and at least one intermediate cooling circulating external flow passage, and each intermediate cooling circulating external flow passage connects at least one intermediate cooling storage tank, at least one The intercooling circulation fan is connected to an internal cooling passage of the intermediate cooling circuit in the cold box to form a complete circulation flow path.
  • the at least one intercooled storage tank is two intercooled storage tanks, the two intercooled storage tanks are connected in series or in parallel;
  • one of the intercooled storage tanks is divided into a deep-cooled side and a normal-temperature side, and the cold-storage to normal-temperature cold energy is stored therein;
  • the other medium-cooled storage tank is divided into an intermediate-cooled side and a normal-temperature side.
  • the cold energy stored in the middle to the normal temperature is stored therein, and the intermediate cooling circulating fan is connected in series between the normal temperature sides of the two intermediate cooling storage tanks;
  • the two intercooled storage tanks When two intercooled storage tanks are connected in parallel, the two intercooled storage tanks store cryogenic to intercooled cold energy.
  • cryogenic storage tank and the intermediate cooling storage tank are both fixed packed bed structures, and the fixed packed bed structure is filled with low temperature cold storage material, and the circulating working medium flows in the gap of the filled low temperature cold storage material and exchanges the cooling capacity.
  • the circulating working medium is one or a mixture of air, nitrogen, argon and helium;
  • the low temperature storage material is ceramic, stone, alumina, metal, encapsulated phase change particles, chemical reaction One or more mixtures of particles.
  • cryogenic circulating fan and the medium-cooling circulating fan are both bidirectional circulating fans, the fan runner is sealed, and the air volume is adjustable.
  • the cryogenic temperature does not exceed 30K of the low temperature liquid in the low temperature insulated storage tank, and the intermediate cooling temperature is between the deep cooling temperature and the normal temperature.
  • the supercritical liquefaction subsystem comprises an electric motor, at least one multi-stage compressor, a drying and purifying device, a proportional adjusting device, a liquid expander, a gas-liquid separator and a low-temperature heat insulating storage tank;
  • the motor is connected to the multi-stage compressor shaft, and the connection between the multi-stage compressors includes two paths, one for the shaft connection, one for the pneumatic connection, and the dry purification device is disposed on the multi-stage compressor air passage for reducing the air Water vapor, carbon dioxide, and alkane content;
  • the motor drives the multi-stage compressor to multi-stage compression of the input gaseous air to form supercritical air, and the supercritical air at the outlet of the multi-stage compressor enters the proportional adjustment device to divert, and the supercritical air after the diversion enters the liquefied cold box of the grading storage subsystem.
  • the liquid expander expands and the gas-liquid separator separates to form liquid air, and the liquid air enters the low-temperature insulated storage tank through the liquid side outlet of the gas-liquid separator.
  • the proportional adjustment device of the supercritical liquefaction subsystem is internally provided with a flow regulating mechanism for regulating the flow ratio of the supercritical air in the two circuits of the shunt.
  • the evaporative expansion subsystem comprises at least one cryogenic pump, a multi-stage expander and a generator, and the liquid air outputted by the low-temperature adiabatic storage tank is evaporated by a supercritical flow channel of a cryogenic pump and a staged cold storage subsystem evaporating cold box.
  • Supercritical air, supercritical air formed by evaporation enters the multi-stage expander to work and drives the generator to generate electricity.
  • the generator is connected with the multi-stage expander shaft; the connection of the multi-stage expander includes two paths, one for the shaft connection and one for the gas. road.
  • the evaporative expansion subsystem further comprises a preheater placed at a position before the supercritical air enters the multistage expander, and the exhaust gas at the outlet of the multistage expander enters the preheater to form a gas path circuit; Used to recover high temperature heat energy from the multistage expander outlet.
  • the preheater of the evaporative expansion subsystem is one or a combination of a plate fin type, a plate type, a shell tube type, and a spiral plate type heat exchanger.
  • the compressed air energy storage system further includes a heat storage heat exchange subsystem, and the heat storage heat exchange subsystem includes at least one heat storage tank, at least one normal temperature tank, at least two regenerators, and at least two reheaters, each of which The heaters are independent of each other, and the reheaters are independent of each other.
  • the outlet of the normal temperature tank is connected to one end of each regenerator, and the other end of each regenerator is connected to the inlet of the heat storage tank;
  • the outlet of the heat storage tank is connected to one end of each reheater, and the other end of each regenerator is connected to the inlet of the normal temperature tank;
  • At least one regenerator is simultaneously connected between the multi-stage compressors of the supercritical liquefaction subsystem, and at least one regenerator is simultaneously connected between the multi-stage compressor of the supercritical liquefaction subsystem and the proportional adjustment device;
  • At least one reheater is simultaneously connected to the supercritical air formed by evaporation into the multistage expander, and at least one regenerator is simultaneously connected between the multistage expanders of the evaporative expansion subsystem gas path.
  • the heat storage heat exchange subsystem further comprises a waste heat utilization device, and the waste heat utilization device is located between the reheater outlet and the normal temperature tank inlet for recovering waste heat of the regenerator working fluid at the outlet of the reheater.
  • the waste heat utilization device of the heat storage heat exchange subsystem is a heat supply heat exchanger or a refrigeration unit or a combination of the two.
  • the compressed air energy storage system further comprises a cold energy compensation subsystem
  • the cold energy compensation subsystem comprises a low temperature expansion unit and a mixer
  • the supercritical liquefaction subsystem proportional adjustment device diverts another supercritical air into the classification cold storage subsystem.
  • the cold energy of the liquefaction cold box compensates for the cooling of the flow channel and then enters the low-temperature expansion unit for further cooling, and the low-temperature air at the gas-side outlet of the gas-liquid separator is mixed in the mixer, and the cold energy recovery of the liquefied cold box of the grading storage subsystem is performed.
  • the flow path recovers cold energy and returns to the multi-stage compressor inlet or returns to the gas path between the compressors of the multi-stage compressor.
  • the cold box when connected with the cold energy compensation subsystem, further comprises at least one cold energy compensation flow channel and at least one cold energy recovery flow channel; and another supercritical air after the supercritical liquefaction subsystem proportional adjustment device is diverted
  • the cooling unit After entering the cooling energy compensation channel of the cold storage subsystem of the grading storage subsystem, the cooling unit enters the low temperature expansion unit and further expands, and the low temperature air at the gas side outlet of the gas liquid separator is mixed in the mixer, and then the cold storage box of the grading storage subsystem is cooled.
  • the cold energy recovery flow path recovers cold energy and returns to the multi-stage compressor inlet or returns to the gas path between the compressors of the multi-stage compressor.
  • Another aspect of the present invention provides a tiered regenerative supercritical compressed air energy storage system, which is applied to the tiered regenerative supercritical compressed air energy storage system, including:
  • the supercritical liquefaction subsystem converts the input gaseous air into liquid air
  • An evaporative expansion subsystem converts liquid air into gaseous air
  • the staged cold storage subsystem stores and/or releases cold energy as it is converted from gaseous air to liquid air.
  • the supercritical liquefaction subsystem converts the input gaseous air into liquid air, specifically:
  • the motor drives the multi-stage compressor to form supercritical air into the multi-stage compression of the input air, and the supercritical air at the outlet of the multi-stage compressor enters the proportional adjustment device to divert, and the supercritical air after the split enters the liquefied cold box of the grading storage subsystem.
  • the liquid expander expands and the gas-liquid separator separates to form liquid air, and the liquid air enters the low-temperature insulated storage tank through the liquid side outlet of the gas-liquid separator.
  • the evaporative expansion subsystem converts liquid air into gaseous air, specifically:
  • the liquid air output from the low-temperature insulated storage tank is evaporated by the cryogenic pump and the staged cold storage subsystem to form supercritical air, and the supercritical air formed by evaporation enters the multi-stage expander to work and drive the generator to generate electricity.
  • the graded cold storage subsystem stores and/or releases cold energy when the gaseous air and the liquid air are converted, specifically:
  • the circulating fan drives the circulating working fluid to input the cold energy in the cryogenic storage tank and the intermediate cooling storage tank into the internal circulation passage of the cryogenic cycle and the internal circulation passage of the intermediate cooling cycle, respectively, to provide supercritical air liquefaction in the supercritical flow passage.
  • Cold energy
  • the circulating fan drives the circulating working fluid to input the cold energy in the cryogenic storage tank and the intermediate cooling storage tank into the internal circulation passage of the deep cooling cycle of the evaporative cold box and the internal flow passage of the intermediate cooling cycle to provide supercritical air evaporation in the supercritical flow channel.
  • Thermal energy, storage of cold energy
  • the heat storage heat exchange subsystem further stores the heat storage medium after the temperature rise in the heat storage tank and returns the heat storage medium after the temperature return to the normal temperature tank.
  • the heat storage heat exchange subsystem stores the heat storage medium after the temperature rise in the heat storage tank and returns the heat storage medium after the temperature return to the normal temperature tank, specifically:
  • the heat storage medium at the outlet of the reheater liquid side of each stage further absorbs the heat energy of the heat storage medium through the waste heat utilization device and outputs the cold energy near the normal temperature, and returns the heat storage medium after the temperature reduction to the normal temperature tank.
  • the cold energy compensation subsystem also includes the independent compensation of cold energy.
  • the cold energy compensation subsystem independently compensates the cold energy, specifically: when the stratified cold storage subsystem comprises at least one liquefied cold box and at least one chilling cold box, the supercritical liquefaction subsystem proportional adjusting device diverts another supercritical air into the air
  • the cooling energy of the liquefied cold box of the grading storage subsystem compensates for the cooling channel and then enters the low-temperature expansion unit for further cooling, and is mixed with the low-temperature air at the gas-side outlet of the gas-liquid separator in the mixer, and then liquefied cold box through the grading storage subsystem.
  • the cold energy recovery flow path recovers cold energy and returns to the multi-stage compressor inlet or returns to the gas path between the compressors of the multi-stage compressor stage; or
  • the grading storage subsystem includes at least one cold box for liquefaction and evaporation, the cold box is connected to the cold energy compensation subsystem, and further includes at least one cold energy compensation flow path and at least one cold energy recovery flow path; supercritical liquefied
  • the cold energy recovery flow path of the cold storage tank of the grading storage subsystem recovers the cold energy, and returns to the multi-stage compressor inlet or returns to the gas path between the compressors of the multi-stage compressor.
  • Another aspect of the present invention provides a hierarchical cold storage subsystem, wherein the hierarchical cold storage subsystem includes at least one liquefied cold box, at least one cryogenic cold storage cycle, and at least one intermediate cold storage cycle;
  • the cryogenic cold storage cycle is connected with the liquefied cold box to release cold energy from a cryogenic temperature to a normal temperature;
  • the medium-cooling cold storage cycle is connected to the liquefied cold box to release the cold energy from the cryogenic temperature to the intermediate cooling temperature.
  • the liquefied cold box includes at least one cryogenic circulation internal flow passage, at least one intermediate cooling circulation internal flow passage, at least one supercritical flow passage, at least one cold energy compensation flow passage, and at least one cold energy recovery flow passage;
  • each cryogenic cold storage cycle includes at least one cryogenic storage tank, at least one cryogenic circulating fan, and at least one cryogenic circulating external flow passage, and each cryogenic circulating external flow passage is connected to at least one a cryogenic storage tank, at least one cryogenic circulating fan, and connected to a deep cooling cycle internal flow passage in the liquefied cold box to form a complete circulation flow passage;
  • the at least one intercooled cold storage cycle, each of the intercooled cold storage cycles includes at least one intermediate cooling storage tank, at least one intermediate cooling circulating fan, and at least one intermediate cooling circulating external flow passage, and each of the intermediate cooling circulating flow passages is connected to at least one medium
  • the cold storage tank, the at least one intermediate cooling circulating fan, and the inner flow passage of an intermediate cooling cycle in the liquefied cold box form a complete circulation flow passage.
  • the hierarchical cold storage subsystem further comprises at least one evaporative cold box, the evaporative cold box and the liquefied cold box share at least one cryogenic cold storage cycle and at least one intermediate cold storage cycle;
  • the cryogenic cold storage cycle is connected with the evaporative cold box, The cold energy storing the cryogenic temperature to the normal temperature is stored;
  • the intermediate cooling storage cycle is connected with the evaporating cold box to store the cold energy from the cryogenic temperature to the intermediate cooling temperature.
  • the evaporative cold box comprises at least one cryogenic circulating internal flow passage, at least one intermediate cooling circulating internal flow passage, and at least one supercritical flow passage; each cryogenic circulating external flow passage is connected to at least one cryogenic storage tank, at least a deep-cooling circulation fan connected to a deep-cooling internal flow passage in the evaporative cold box to form a complete circulation flow passage; each of the intermediate cooling circulation flow passages connecting at least one intermediate cooling storage tank and at least one intermediate cooling circulation fan And connecting with an internal cooling passage of the intermediate cooling circuit in the evaporative cold box to form a complete circulation flow path.
  • Still another aspect of the present invention provides a hierarchical cold storage subsystem including a cold box, at least one cryogenic cold storage cycle, and at least one intermediate cold storage cycle, wherein:
  • the cold box is used as a liquefied cold box or an evaporative cold box;
  • the cryogenic cold storage cycle is connected to the cold box, and the cold heat is released to the normal temperature when the cold box is used as the liquefied cold box, and the cold energy is stored to the normal temperature when the cold box is used as the evaporative cold box;
  • the intermediate cooling storage cycle is connected to the cold box, and the cold energy of the cryogenic temperature to the intermediate cooling temperature is released when the cold box is used as the liquefied cold box, and the cold energy of the cryogenic temperature to the intermediate cooling temperature is stored when the cold box is used as the evaporating cold box. .
  • the cold box includes at least one cryogenic circulation internal flow passage, at least one intermediate cooling circulation internal flow passage, and at least one supercritical flow passage;
  • Each of the cryogenic cold storage cycles includes at least one cryogenic storage tank, at least one cryogenic circulating fan, and at least one cryogenic circulating external flow passage, each cryogenic circulating external flow passage connecting at least one cryogenic storage tank, at least one a cryogenic circulating fan and connected to a cryogenic cycle internal flow passage in the cold box to form a complete circulation flow passage;
  • Each of the intercooled cold storage cycles includes at least one intercooled storage tank, at least one intermediate cooling circulating fan, and at least one intermediate cooling circulating external flow passage, and each intermediate cooling circulating external flow passage connects at least one intermediate cooling storage tank, at least one The intercooling circulation fan is connected to an internal cooling passage of the intermediate cooling circuit in the cold box to form a complete circulation flow path.
  • the at least one intercooled storage tank is two intercooled storage tanks, the two intercooled storage tanks are connected in series or in parallel;
  • one of the intercooled storage tanks is divided into a deep-cooled side and a normal-temperature side, and the cold-storage to normal-temperature cold energy is stored therein;
  • the other medium-cooled storage tank is divided into an intermediate-cooled side and a normal-temperature side.
  • the cold energy stored in the middle to the normal temperature is stored therein, and the intermediate cooling circulating fan is connected in series between the normal temperature sides of the two intermediate cooling storage tanks;
  • the two intercooled storage tanks When two intercooled storage tanks are connected in parallel, the two intercooled storage tanks store cryogenic to intercooled cold energy.
  • cryogenic storage tank and the intermediate cooling storage tank are both fixed packed bed structures, and the fixed packed bed structure is filled with low temperature cold storage material, and the circulating working medium flows in the gap of the filled low temperature cold storage material and exchanges the cooling capacity.
  • the circulating working medium is one or a mixture of air, nitrogen, argon and helium;
  • the low temperature storage material is ceramic, stone, alumina, metal, encapsulated phase change particles, chemical reaction One or more mixtures of particles.
  • cryogenic circulating fan and the medium-cooling circulating fan are both bidirectional circulating fans, the fan runner is sealed, and the air volume is adjustable.
  • the cryogenic temperature does not exceed 30K of the low temperature liquid in the low temperature insulated storage tank, and the intermediate cooling temperature is between the deep cooling temperature and the normal temperature.
  • the liquefied cold box and the evaporative cold box respectively comprise a heat exchanger group, a cold-preserving material and a sealed outer casing;
  • the heat exchanger group is at least one plate fin heat exchanger, or at least one plate heat exchanger, or at least one coiled heat exchanger.
  • the cold insulation material is one or more of a mixture of glass fiber mat, pearl sand, rock wool, and vacuum board.
  • the graded cold storage subsystem increases the cooling capacity of the intermediate temperature by adding an intermediate cooling storage cycle, and has the advantages of increasing the recycling efficiency of the cold energy, solving the problem of insufficient cold energy recovery, and thereby improving the system circulation efficiency.
  • the circulating working medium used is one of air, nitrogen, argon, and helium. Or a variety of mixtures, simple and easy to obtain and safe and reliable, with low cost, high efficiency, environmentally friendly, suitable for large-scale applications;
  • the cold energy compensation system and the heat storage heat exchange system are further included, and the independent compensation of the cold energy and the recovery of the compressed heat in the energy storage process are completed, and the high-efficiency independent operation can be realized without the external cold heat source input. , not subject to terrain conditions.
  • FIG. 1 is a flow chart of a staged cold storage supercritical compressed air energy storage method according to an embodiment of the present invention
  • FIG. 2 is a schematic diagram of a hierarchical cold storage supercritical compressed air energy storage system combining a single cryogenic cold storage cycle and an intermediate cooling storage tank according to an embodiment of the present invention
  • FIG. 3 is a schematic diagram of a staged cold storage supercritical compressed air energy storage system in which a medium-cooled storage tank is a two-tank series structure according to an embodiment of the present invention
  • FIG. 4 is a schematic diagram of a hierarchical cold storage supercritical compressed air energy storage system at a higher pressure of a cryogenic liquid storage tank according to an embodiment of the present invention
  • FIG. 5 is a schematic diagram of a hierarchical cold storage supercritical compressed air energy storage system including a cold box according to an embodiment of the present invention.
  • the hierarchical cold storage supercritical compressed air energy storage system of the present invention comprises a supercritical liquefaction subsystem for converting input gaseous air into liquid air; an evaporation expansion subsystem for converting liquid air into gaseous air; A subsystem for storing and/or releasing cold energy when gaseous air and liquid air are converted.
  • the stratified cold storage subsystem comprises at least one liquefied cold box, at least one cryogenic cold storage cycle and at least one intermediate cold storage cycle; the cryogenic cold storage cycle is connected with the liquefied cold box to release the cryogenic temperature to the normal temperature cold energy; the intermediate cold storage cold cycle The liquefied cold box is connected to release the cold energy from the cryogenic temperature to the intermediate cooling temperature.
  • each liquefied cold box comprises at least one cryogenic circulation internal flow passage, at least one intermediate cooling circulation internal flow passage, at least one supercritical flow passage, at least one cold energy compensation flow passage and at least one cold energy recovery flow passage;
  • a cryogenic cold storage cycle includes at least one cryogenic storage tank, at least one cryogenic circulating fan, and at least one cryogenic circulating external flow passage, each cryogenic circulating external flow passage connecting at least one cryogenic storage tank, at least one deep cooling cycle
  • the fan is connected to a deep circulation inner flow passage in the liquefaction cold box to form a complete circulation flow passage;
  • each of the cold storage cold storage cycles includes at least one intermediate cooling storage tank, at least one intermediate cooling circulation fan, and at least one intermediate cooling cycle external
  • the flow channel, each of the intermediate cooling channels is connected to at least one intermediate cooling tank, at least one intermediate cooling circulating fan, and is connected with an internal cooling passage of the intermediate cooling circuit in the liquefied cold box to form a complete circulating flow passage.
  • the stratified cold storage subsystem further comprises at least one evaporative cold box, the evaporative cold box and the liquefied cold box share at least one cryogenic cold storage cycle and at least one intermediate cold storage cycle; the cryogenic cold storage cycle is connected with the evaporative cold box to store the cryogenic temperature to the normal temperature The cold energy; the cold storage cold storage cycle is connected with the evaporative cold box to store the cold energy from the cryogenic temperature to the intermediate cooling temperature.
  • the evaporative cold box comprises at least one cryogenic circulating internal flow passage, at least one intermediate cooling circulating internal flow passage and at least one supercritical flow passage; each cryogenic circulating external flow passage in the cryogenic cold storage cycle is connected to at least one cryogenic storage tank At least one cryogenic circulating fan connected to a deep-cooling internal flow passage in the evaporative cold box to form a complete circulation flow passage; each intermediate cooling passage in the intermediate cooling storage cycle is connected to at least one intermediate-cooled storage tank At least one intermediate-cooling circulation fan is connected to an internal circulation passage of an intermediate cooling cycle in the evaporative cold box to form a complete circulation flow path.
  • the liquefaction cold box and the evaporative cold box respectively comprise a heat exchanger group, a cold storage material and a sealed outer casing;
  • the heat exchanger group is at least one plate fin heat exchanger, or at least one plate heat exchanger, or at least one coil type Heat Exchanger.
  • the cold insulation material is one or more of a mixture of glass fiber mat, pearl sand, rock wool, and vacuum board.
  • the liquefied cold box and the evaporative cold box may share the same cold box, wherein the cold box is used as a liquefied cold box or an evaporative cold box; at least one cryogenic cold storage cycle and at least one medium cold storage cold storage Circulating; each cold box can be used for both releasing cold energy and storing cold energy; each cold box includes at least one deep cooling cycle internal flow passage, at least one intermediate cooling circulation internal flow passage, and at least one supercritical flow passage.
  • the cryogenic cold storage cycle is connected to the cold box to release and/or store the cryogenic temperature to the normal temperature cold water; each cryogenic cold storage cycle includes at least one cryogenic storage tank, at least one cryogenic circulating fan, and at least one cryogenic cycle external
  • the flow channel, each cryogenic cycle external flow channel is connected to at least one cryogenic storage tank, at least one cryogenic circulating fan, and is connected to a cryogenic circulating internal flow passage in the cold box to form a complete circulation flow passage.
  • the intercooled cold storage cycle is connected to the cold box to release and/or store the cold energy from the cryogenic temperature to the intermediate cooling temperature; each of the cold storage cold storage cycles includes at least one intermediate cooling storage tank, at least one intermediate cooling circulating fan, and at least one intercooling
  • the outer flow passage is circulated, and each of the outer circulation passages of the intermediate cooling circuit is connected with at least one intermediate cooling storage tank and at least one intermediate cooling circulation fan, and is connected with an inner cooling passage of the intermediate cooling circuit in the cold box to form a complete circulation flow passage.
  • the number of the intercooling cold storage cycles is greater than 1, the cold energy between different intercooling temperatures is stored in each of the intercooled cold storage cycles.
  • the intercooled storage tanks when at least one of the intercooled storage tanks is two intercooled storage tanks, two of the intercooled storage tanks are connected in series or in parallel; when the two intercooled storage tanks are connected in series, one of the intercooled storage tanks is divided into a deep cold side and a normal temperature side. , which stores cold energy from cryogenic to normal temperature; another medium-cooled storage tank is divided into the intercooled side and the normal temperature side, and the inside storage is moderately cold.
  • the warm cold energy, the intercooled circulation fan is connected in series between the two intermediate storage tanks at the normal temperature side; when the two intercooled storage tanks are connected in parallel, the two intercooled storage tanks store the cryogenic to intercooled cold energy.
  • cryogenic storage tank and the intermediate cooling storage tank are both fixed packed bed structures, and the fixed packed bed structure is filled with low temperature cold storage material, and the circulating working medium flows in the gap of the filled low temperature cold storage material and exchanges the cold amount;
  • the working medium is one or more mixtures of air, nitrogen, argon and helium;
  • the low temperature storage material is one or more of ceramic, stone, alumina, metal, encapsulated phase change particles, chemical reaction particles. a mixture.
  • cryogenic circulating fan and the medium-cooling circulating fan are both bidirectional circulating fans, the fan runner is sealed, and the air volume is adjustable.
  • the cryogenic temperature does not exceed 30K of the low temperature liquid in the low temperature insulated storage tank, and the intermediate cooling temperature is between the deep cooling temperature and the normal temperature.
  • the supercritical liquefaction subsystem comprises an electric motor, at least one multi-stage compressor, a drying and purifying device, a proportional adjusting device, a liquid expander, a gas-liquid separator and a low-temperature heat insulating storage tank; the motor is connected with a multi-stage compressor shaft, and the multi-stage compressor
  • the connection between the two includes two ways, one is the shaft connection, the other is the gas connection, and the drying and purifying device is arranged on the multi-stage compressor gas path to reduce the content of water vapor, carbon dioxide and alkane in the air;
  • the stage compressor compresses the input gaseous air into supercritical air, and the supercritical air at the outlet of the multistage compressor enters the proportional adjustment device to divert, and the supercritical air after the split enters the supercritical flow of the liquefied cold box of the grading storage subsystem.
  • the proportional adjustment device of the supercritical liquefaction subsystem is internally provided with a flow adjustment mechanism for regulating the flow ratio of supercritical air in the two circuits of the split flow.
  • the evaporative expansion subsystem comprises at least one cryogenic pump, a multi-stage expander and a generator, and the liquid air outputted by the low-temperature adiabatic storage tank is evaporated by a cryogenic pump and a staged cold storage subsystem to evaporate the supercritical flow path of the cold box to form supercritical air.
  • the supercritical air formed by evaporation enters the multi-stage expander to work and drives the generator to generate electricity.
  • the generator is connected with the multi-stage expander shaft; the connection of the multi-stage expander includes two paths, one is the shaft connection and the other is the gas path.
  • the evaporative expansion subsystem further includes a preheater placed in a position before the supercritical air enters the multistage expander, and the exhaust gas at the outlet of the multistage expander enters the preheater to form a gas path circuit; Used to recover high temperature heat energy from the multistage expander outlet.
  • the preheater is one or a combination of a plate fin type, a plate type, a shell tube type, and a spiral plate type heat exchanger.
  • the compressed air energy storage system further includes a heat storage heat exchange subsystem including at least one heat storage tank, at least one normal temperature tank, at least two regenerators, at least two reheaters, and each regenerator Independent of each other, each reheater is independent of each other, the outlet of the normal temperature tank is connected with one end of each regenerator, and the other end of each regenerator is connected with the inlet of the heat storage tank; the outlet of the heat storage tank and each reheater Connected at one end, the other end of each regenerator is connected to the inlet of the normal temperature tank; at least one regenerator is simultaneously connected between the multistage compressors of the supercritical liquefaction subsystem, and at least one regenerator is simultaneously connected to the supercritical liquefaction Between the multi-stage compressor of the subsystem and the proportional adjustment device; at least one reheater is simultaneously connected to the supercritical air formed by evaporation before entering the multi-stage expander, and at least one regenerator is simultaneously connected to the gas path of the evaporative expansion subsystem Between multi-stage expanders
  • the heat storage heat exchange subsystem further comprises a waste heat utilization device, and the waste heat utilization device is located between the reheater outlet and the normal temperature tank inlet for recovering the waste heat of the regenerator working fluid at the outlet of the reheater.
  • the waste heat utilization device of the heat storage heat exchange subsystem is a heat supply heat exchanger or a refrigeration unit or a combination of the two.
  • the compressed air energy storage system further comprises a cold energy compensation subsystem
  • the cold energy compensation subsystem autonomously compensates the cold energy, specifically: the supercritical liquefaction when the hierarchical cold storage subsystem comprises at least one liquefied cold box and at least one evaporation cold box
  • the other supercritical air after the subsystem proportional adjustment device is diverted into the cooling energy compensation channel of the liquefied cold box of the grading storage subsystem, and then enters the low temperature expansion unit to expand further, and the low temperature air at the gas side outlet of the gas-liquid separator is
  • the cold energy recovery flow passage of the liquefied cold box of the grading storage subsystem recovers the cold energy, and returns to the multi-stage compressor inlet or returns to the gas path between the compressors of the multi-stage compressor; or
  • the grading storage subsystem includes at least one cold box for liquefaction and evaporation, the cold box is connected to the cold energy compensation subsystem, and further includes at least one cold energy compensation flow path and at least one cold energy recovery flow path; supercritical liquefied
  • the cold energy recovery flow path of the cold storage tank of the grading storage subsystem recovers the cold energy, and returns to the multi-stage compressor inlet or returns to the gas path between the compressors of the multi-stage compressor.
  • the hierarchical cold storage supercritical compressed air energy storage method of the present invention is applied to a hierarchical cold storage supercritical compressed air energy storage system, as shown in FIG. 1 , which is a hierarchical cold storage supercritical compressed air storage according to an embodiment of the present invention.
  • the method flow chart includes:
  • the supercritical liquefaction subsystem converts the input gaseous air into liquid air; specifically: the motor drives the multi-stage compressor to multi-stage compression of the input air to form supercritical air, and the supercritical air inlet ratio adjustment of the multi-stage compressor outlet
  • the device is diverted, and the supercritical air after the diversion enters the supercritical flow channel of the liquefied cold box of the grading and accumulating subsystem, and then expands by the liquid expander, and the gas-liquid separator separates to form liquid air, and the liquid air passes through the liquid of the gas-liquid separator.
  • the side outlet enters the low temperature insulated storage tank.
  • the evaporative expansion subsystem converts the liquid air into gaseous air; specifically: the liquid air outputted by the low-temperature adiabatic storage tank is evaporated by the cryogenic pump and the grading storage subsystem to evaporate the supercritical flow path of the cold box to form supercritical air, and is formed by evaporation.
  • the supercritical air enters the multistage expander to do work and drive the generator to generate electricity.
  • the grading storage subsystem stores and/or releases cold energy when the gaseous air and the liquid air are converted; specifically: the circulating fan drives the circulating working medium to input the cold energy in the cryogenic storage tank and the intermediate cooling storage tank into the liquefied cold box respectively.
  • the inner passage of the cryogenic cycle and the internal flow passage of the intercooled circulation provide cold energy for supercritical air liquefaction in the supercritical flow passage;
  • the circulating fan drives the circulating working fluid to input the cold energy in the cryogenic storage tank and the intermediate cooling storage tank into the internal circulation passage of the deep cooling cycle of the evaporative cold box and the internal flow passage of the intermediate cooling cycle to provide supercritical air evaporation in the supercritical flow channel.
  • Thermal energy, storage of cold energy
  • the hierarchical cold storage supercritical compressed air energy storage method of the present invention further comprises:
  • the heat storage heat exchange subsystem stores the heat storage medium after the temperature rise in the heat storage tank and returns the heat storage medium after the temperature return to the normal temperature tank; specifically: after the heat of absorption is absorbed in the regenerators of the respective stages
  • the heat storage medium is stored in the heat storage tank; and the heat storage medium at the outlet of the reheater liquid side of each stage further absorbs the heat energy of the heat storage medium through the waste heat utilization device and outputs the cold energy near the normal temperature, and then stores the cooling energy after the temperature is lowered.
  • the hot working fluid is returned to the normal temperature tank.
  • the hierarchical cold storage supercritical compressed air energy storage method of the present invention further comprises:
  • the cold energy compensation subsystem autonomously compensates the cold energy; specifically: the cold energy compensation subsystem autonomously compensates the cold energy, specifically: the supercritical liquefied body when the hierarchical cold storage subsystem includes at least one liquefied cold box and at least one evaporation cold box Another supercritical air entering point after the system proportional adjustment device is diverted
  • the cooling energy compensation channel of the liquefaction cold box of the stage cold storage subsystem is cooled and then enters the low temperature expansion unit to expand further, and is mixed with the low temperature air at the gas side outlet of the gas liquid separator in the mixer, and then liquefied cold box through the grading storage subsystem.
  • the cold energy recovery flow path recovers cold energy and returns to the multi-stage compressor inlet or returns to the gas path between the compressors of the multi-stage compressor stage; or
  • the grading storage subsystem includes at least one cold box for liquefaction and evaporation, the cold box is connected to the cold energy compensation subsystem, and further includes at least one cold energy compensation flow path and at least one cold energy recovery flow path; supercritical liquefied
  • the cold energy recovery flow path of the cold storage tank of the grading storage subsystem recovers the cold energy, and returns to the multi-stage compressor inlet or returns to the gas path between the compressors of the multi-stage compressor.
  • FIG. 2 is a schematic diagram of a hierarchical cold storage supercritical compressed air energy storage system combining a single cryogenic cold storage cycle and an intermediate cooling storage tank according to an embodiment of the present invention.
  • the working medium is heat transfer oil
  • the compressor is secondary compression
  • the expander is secondary expansion
  • a single heat storage tank, a single normal temperature tank, a single cryogenic liquid storage tank, and a single graded cold storage subsystem are used;
  • the cold storage subsystem includes a single cryogenic storage tank, a single intercooled storage tank, a single liquefied cold box, a single evaporative cold box, a waste heat utilization device for the absorption refrigeration unit, a low temperature expander for secondary expansion, and a low temperature liquid storage tank with a pressure close to Atmospheric pressure.
  • the gas returned from the cold energy recovery flow path 4035 of the liquefaction cold box of the present embodiment is returned to the inlet of the primary compressor 101.
  • the usage process is:
  • the motor 100 drives the primary compressor 101 to compress the return air of the atmospheric air and the cold energy recovery flow passage 4035.
  • the compressed air is exchanged with heat through the interstage regenerator 203 and then input to the drying and purifying device 102 to lower the water.
  • the content of steam, carbon dioxide, and alkane components, and the dry purified compressed air are further compressed in the final stage compressor 103 and exchanged heat, and then input to the proportional adjustment device 104 in a supercritical state.
  • the heat storage medium which has absorbed the heat of compression in the regenerators 203 and 204 of each stage is stored in the heat storage tank 201.
  • the circulating fans 405 and 406 drive the circulating medium to input the cold energy in the cryogenic storage tank 401 and the intermediate cooling storage tank 402 into the deep cooling circulation internal flow passage 4031 and the intermediate cooling circulation internal flow passage 4032 of the liquefied cold tank 403, respectively.
  • Cryogenic cycle The external flow path 4051 is connected to the cryogenic storage tank 401 and the deep cooling circulation fan 405, and is connected to the deep cooling circulation internal flow passage 4032 in the liquefied cold box 403 to form a complete circulation flow passage; the intermediate cooling circulation external flow passage 4061 is connected to the intermediate cooling storage.
  • the tank 402 and the intermediate cooling circulation fan 406 are connected to the intermediate cooling circulation internal flow path 4031 in the liquefaction cold box 403 to constitute a complete circulation flow path.
  • the supercritical air is diverted by the proportional adjustment device 104 and then output at a certain flow rate. Most of the supercritical flow passages 4033 entering the liquefied cold box absorb the cold energy and then liquefy into high pressure fluid, and another part of the supercritical air enters the liquefied cold box.
  • the cold energy compensating flow channel 4034 after absorbing part of the cold energy to cool down, is further expanded and cooled by the low temperature expansion unit 108 to be a low temperature gas close to the normal pressure, and the low temperature cold energy is compensated for the whole system.
  • the supercritical air After the supercritical air is liquefied, it is expanded into a gas-liquid mixed fluid close to normal pressure by the liquid expander 105 and enters the gas-liquid separator 106, and the separated low-temperature gas and the low-temperature gas after the expansion and cooling of the cold energy compensation circuit 4034 are mixed.
  • the mixture 109 is mixed, and the mixed near normal pressure low temperature gas is supplied to the liquefied cold box cold storage passage 4035 to recover cold energy and compensate for the shortage of cold energy.
  • the liquid air separated in the gas-liquid separator 106 is collected and stored in the low-temperature heat insulating storage tank 107 to complete the storage of energy.
  • the liquid air is pressurized by the cryopump 301 and then input to the evaporative cold box 404.
  • the circulating refrigerant in the cryogenic storage tank 401' and the intercooled storage tank 402' is driven separately by the circulating fans 405' and 406'.
  • the deep cooling circulating internal flow path 4041 of the evaporating cold box and the intermediate cooling circulating internal flow path 4042, the circulating working medium absorbs the cooling amount released by the liquid air evaporation in the evaporating cold channel 4043 in the evaporating cold box, and then enters the cryogenic storage tank 401' respectively.
  • the cold storage tank 402' the recovery and storage of cold energy is completed.
  • the evaporative cold box 404 and the liquefied cold box 403 share a cryogenic cold storage cycle and a medium cold storage cold cycle; wherein the cryogenic storage tank 401 and the cryogenic storage tank 401' are the same cryogenic storage tank, the intermediate cooling storage tank 402 and the medium cooling
  • the storage tank 402' is actually the same intercooled storage tank; the cryogenic circulating fan 405 and the cryogenic circulating fan 405' are the same cryogenic circulating fan; the intermediate cooling circulating fan 406 and the intermediate cooling circulating fan 406' are the same intercooling cycle.
  • the evaporative cold box comprises a deep cooling cycle internal flow channel 4041, an intermediate cooling cycle internal flow channel 4042 and a supercritical flow channel 4043;
  • the cryogenic cycle external flow channel 4051' in the cryogenic cold storage cycle is connected to the cryogenic storage tank 401', cryogenically
  • the circulating fan 405' is connected to the cryogenic circulating internal flow channel 4042 in the evaporating cold box 404 to form a complete circulating flow path;
  • the external flow path 4061' is connected to the intermediate cooling storage tank 402', the intermediate cooling circulation fan 406', and is connected to the intermediate cooling circulation internal flow passage 4041 in the evaporation cold box 404 to constitute a complete circulation flow path.
  • the preheated supercritical air absorbs the heat of the heat storage medium through the reheater 205, enters the primary expander 303 to work and drives the generator 305 to generate electricity, and the primary expander 303 exits the compressed air into the final stage reheater 206 and reheats.
  • the final stage expander 304 is expanded to perform work.
  • the heat storage medium at the liquid side outlets of the reheaters 205 and 206 still have a relatively high temperature, and further absorbs the heat energy of the heat storage medium through the waste heat utilization device 207 and outputs cold energy near the normal temperature, and the heat storage device after the temperature reduction The mass returns to the normal temperature tank 202.
  • FIG. 3 is a schematic diagram of a staged cold storage type supercritical compressed air energy storage system in which a medium-cooled storage tank is a two-tank series structure according to an embodiment of the present invention; as shown in FIG. 3, the improvement of the first embodiment is at least one medium cooling.
  • the storage tank is two intercooled storage tanks, the lower middle cold storage tank 4021 and the upper middle cold storage tank 4022 are connected in series, and the lower middle cold storage tank 4021 stores the cold energy from the intermediate cooling to the normal temperature in the medium and cold storage tank 4022.
  • the cold energy to the normal temperature is cold, and the normal temperature side of the lower and middle cold storage tanks 4021 and the upper and middle cold storage tanks 4022 are connected by the intermediate cooling circulation fan 406.
  • the advantage is that the intermediate cooling circulation fan 406 can be operated at normal temperature to avoid the heat of compression.
  • the lower and middle cooling storage tanks 4021' and the upper and middle cooling storage tanks 4022' are connected in series, and the lower and middle cooling storage tanks 4021' store the cold energy storage tanks 4022' from the medium to the normal temperature to be stored from deep to normal temperature.
  • the cold energy energy, the normal temperature side of the lower middle and cold storage tank 4021' and the upper and middle cold storage tanks 4022' are connected by the intermediate cooling circulation fan 406', and the advantage is that the intermediate cooling circulation fan 406' can be operated at normal temperature to avoid the heat of compression.
  • the intermediate cooling circulating fan 406 and the intermediate cooling circulating fan 406' are actually the same intermediate cooling circulating fan, and the lower intermediate cooling storage tank 4021 and the lower intermediate cooling storage tank 4021' are the same lower intermediate cooling storage tank; the upper middle cooling storage tank The 4022 and the upper and middle cold storage tanks 4022' are the same upper and middle cold storage tanks.
  • Embodiment 4 is a schematic diagram of a hierarchical cold storage supercritical compressed air energy storage system at a higher pressure of a cryogenic liquid storage tank according to an embodiment of the present invention; as shown in FIG. 4, the improvement with respect to Embodiment 1 is:
  • the low-temperature atmospheric gas returned from the liquefaction cold box cold energy recovery flow path 4035 is returned to the gas path between the dry purification device 102 and the final stage compressor, and is not returned to the inlet of the primary compressor 101.
  • the pressure of storing the liquid air in the low-temperature heat insulating storage tank 107 is not close to the normal pressure, but is much higher than the normal pressure.
  • the liquefaction cold box cold energy compensation flow channel 4034 is cooled by the supercritical fluid absorption portion, and then cooled by the two-stage low temperature expander 108 to a low pressure close to the low temperature adiabatic storage tank 107, and the gas liquid separator
  • the internally separated low-temperature gas is mixed in the mixer 109 and then input into the cold energy recovery flow path 4035.
  • the cold energy recovery flow path 4035 is connected to the inlet of the final stage compressor 103, mixed with the compressed air compressed by the primary compressor 101, and then input to the final stage.
  • the compressor 103 is compressed into supercritical air.
  • FIG. 5 is a schematic diagram of a hierarchical cold storage supercritical compressed air energy storage system including a cold box according to an embodiment of the present invention.
  • the improvement of the first embodiment is that the liquefied cold box and the evaporative cold box share the same cold box, that is, only one cold box 407 is provided, which can be used as liquefied cold for releasing cold energy.
  • the box can also be used as an evaporative cold box for storing cold energy.
  • the valve G1 and the valve G3 are opened, the valve 2 G2 and the valve 4 G4 are closed.
  • the supercritical air enters the proportional adjustment device 104 through the valve two G2; the supercritical air is diverted by the proportional adjustment device 104 and mostly enters the supercritical flow passage 4033 of the cold box, and then enters the liquid expander 105 through the valve three G3.
  • valve G1 and valve G3 are closed, valve 2 G2 and valve 4 G4 are open.
  • the liquid air is pressurized by the cryopump 301 and then sent to the supercritical flow channel 4033 of the liquefaction cold box via the valve G4.
  • the supercritical air outputted by the supercritical flow channel 4033 is input into the preheater 302 through the valve 2G2 through the proportional adjustment device 104.

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Abstract

一种超临界压缩空气储能系统，该超临界压缩空气储能系统包括超临界液化子系统、蒸发膨胀子系统、分级蓄冷子系统、储热换热子系统和冷能补偿子系统，其中，分级蓄冷子系统用于实现冷能的分级储存和释放，提高释能和储能过程低温冷能的回收利用效率进而提高系统循环效率。

Description

分级蓄冷式超临界压缩空气储能系统及方法 技术领域
本发明涉及可再生能源、压缩空气储能、分布式能源等领域，尤其涉及一种分级蓄冷式超临界压缩空气储能系统及方法。
背景技术
压缩空气储能是除抽水蓄能以外唯一成熟的大规模电网储电的物理储能技术，可用于电网削峰填谷以及太阳能和风能等可再生能源稳定输出等领域。传统的压缩空气储能利用压缩机将空气压缩进入大型岩洞存储，在释能阶段利用化石燃料燃烧再热从而膨胀做功，适合大型系统、成本低、寿命长，但是其建设地点受限，且依赖于化石能源燃烧造成污染。蓄热式压缩空气储能回收压缩过程产生的压缩热并在释能过程中用于透平级间再热，属于一种斯特林循环，具有效率高，对环境友好，然而其推广仍然受限于储气岩洞地形条件。大规模耐高压容器管道被用于替代大型储气岩洞，摆脱了地形条件的限制，适合于大范围推广，但是采用金属压力容器储存高压空气成本昂贵，且随着储能时间的增大容器成本所占比重越来越大，影响压缩空气储能系统成本回收和大规模推广应用。
液化空气储能系统(LAES)内做功工质以液态常压或低压存储，不仅大大提高了储能密度，同时也大幅降低系统建设成本和占地面积。早期液态空气技术释能过程仍然依靠化石燃料燃烧，系统中无储冷设计，依赖于外部液态空气输入，主要是与传统空分系统结合，未考虑释能阶段冷能的回收，虽然技术成熟度较高，但是系统实际电效率很低。一些文献公开了新型液态空气储能技术，相对于之前的技术，不包含任何燃烧过程，只有空气为工质，增加了储热和储冷技术回收液态空气蒸发时的冷能用于空气液化流程，提高了系统效率。一些文献公开了一种回收并储存冷能的超临界压缩空气储能系统，结合了空气超临界液化循环、储能系统和朗肯循环，储能阶段压缩机出口超临界空气吸收冷能降温并等焓节流/等熵膨胀，低压液化空气储存在低温绝热储罐内，释能阶段经低温泵升压后的液态空气吸收热量并回收冷能后气化并经再热器再热后进入透平做功。还具有建设地点不受限制和零污染排放等优点。此外由于透平进口的压力和流量可 以保持稳定，解决了绝热式压缩空气储能系统储气装置与透平进口之间的压力调节以及压缩机出口变压力运行等缺点，可以保持动力机械在高效点稳定运行。
以上研究中虽然将冷能回收用于液化流程，但是冷能利用率仍不足，且储释过程冷量并不闭合，后续的研究中在液化流程中均考虑了采用优化的克劳德吸收更多冷能并实现系统冷能的自补偿。一些文献公开了丙烷与甲醇双流体蓄冷的循环，并与核电站的集成使核电站维持接近满负荷运行同时满足应变需求，液态工质同时作为传热和储冷工质减少了冷能的不可逆损失，然而甲醇和丙烷均为易燃易爆有毒的危化品，与空气液化过程中存在富氧区域接触容易发生爆炸，其大规模长期储存从安全性、经济性和维护成本上难以想象。
综上，当前的研究中，对于液化过程中冷能利用的研究已经非常充分，但是对于蒸发冷箱内高温液态空气冷能的回收则明显不足，现有发明仍不满足于大规模、低成本和安全可靠储能的需求，仍需要进一步优化。
发明内容
(一)要解决的技术问题
针对上述问题，本发明提供一种分级蓄冷子系统和超临界压缩空气储能系统，用以解决冷能回收不足的问题，以及不满足大规模、低成本和安全可靠储能的需求。
(二)技术方案
本发明的一方面提供一种分级蓄冷式超临界压缩空气储能系统，包括用于将输入的气态空气转化为液态空气的超临界液化子系统和用于将液态空气转化为气态空气的蒸发膨胀子系统，其中，该分级蓄冷式超临界压缩空气储能系统还包括：
分级蓄冷子系统，用于在气态空气与液态空气转化时储存和/或释放冷能。
其中，所述分级蓄冷子系统包括至少一液化冷箱、至少一深冷蓄冷循环和至少一中冷蓄冷循环；
所述深冷蓄冷循环与液化冷箱连接，释放深冷温度到常温的冷能；
所述中冷蓄冷循环与液化冷箱连接，释放深冷温度到中冷温度的冷能。
其中，每一所述液化冷箱包括至少一深冷循环内部流道、至少一中冷循环内部流道、至少一超临界流道、至少一冷能补偿流道和至少一冷能回收流道；
每一所述深冷蓄冷循环包括至少一深冷储罐、至少一深冷循环风机以及至少一深冷循环外部流道，每一深冷循环外部流道连接至少一深冷储罐、至少一深冷循环风机，并与所述液化冷箱中的一深冷循环内部流道连接构成完整循环流道；
每一所述中冷蓄冷循环包括至少一中冷储罐、至少一中冷循环风机以及至少一中冷循环外部流道，每一中冷循环外部流道连接至少一中冷储罐、至少一中冷循环风机，并与所述液化冷箱中的一中冷循环内部流道连接构成完整循环流道。
其中，所述分级蓄冷子系统还包括至少一蒸发冷箱，蒸发冷箱与液化冷箱共用至少一深冷蓄冷循环和至少一中冷蓄冷循环；
所述深冷蓄冷循环与蒸发冷箱连接，储存深冷温度到常温的冷能；
所述中冷蓄冷循环与蒸发冷箱连接，储存深冷温度到中冷温度的冷能。
其中，所述蒸发冷箱包括至少一深冷循环内部流道、至少一中冷循环内部流道和至少一超临界流道；
深冷蓄冷循环中的每一深冷循环外部流道连接至少一深冷储罐、至少一深冷循环风机，并与所述蒸发冷箱中的一深冷循环内部流道连接构成完整循环流道；
中冷蓄冷循环中的每一中冷循环外部流道连接至少一中冷储罐、至少一中冷循环风机，并与所述蒸发冷箱中的一中冷循环内部流道连接构成完整循环流道。
其中，所述液化冷箱和蒸发冷箱均包括换热器组、保冷材料和密闭外壳；
所述换热器组为至少一板翅式换热器、或至少一板式换热器、或至少一绕管式换热器。
所述保冷材料为玻璃纤维毡、珠光砂、岩棉、真空板中的一种或多种混合。
其中，所述分级蓄冷子系统包括至少一冷箱、至少一深冷蓄冷循环和至少一中冷蓄冷循环；
冷箱用于做为液化冷箱或蒸发冷箱；
深冷蓄冷循环，连接于冷箱，在冷箱做为液化冷箱时释放深冷温度到常温的冷能，在冷箱作为蒸发冷箱时储存深冷温度到常温的冷能；
中冷蓄冷循环，连接于冷箱，在冷箱做为液化冷箱时释放深冷温度到中冷温度的冷能，在冷箱作为蒸发冷箱时储存深冷温度到中冷温度的冷能。
其中，每一所述冷箱包括至少一深冷循环内部流道、至少一中冷循环内部流道、至少一超临界流道；
每一所述深冷蓄冷循环包括至少一深冷储罐、至少一深冷循环风机以及至少一深冷循环外部流道，每一深冷循环外部流道连接至少一深冷储罐、至少一深冷循环风机，并与所述冷箱中的一深冷循环内部流道连接构成完整循环流道；
每一所述中冷蓄冷循环包括至少一中冷储罐、至少一中冷循环风机以及至少一中冷循环外部流道，每一中冷循环外部流道连接至少一中冷储罐、至少一中冷循环风机，并与所述冷箱中的一中冷循环内部流道连接构成完整循环流道。
其中，所述中冷蓄冷循环的数量大于1时，各中冷蓄冷循环中储存不同中冷温度间的冷能。
其中，所述至少一中冷储罐为两个中冷储罐时，两个中冷储罐串联或并联；
两个中冷储罐串联时，其中一个中冷储罐分为深冷侧和常温侧，其内储存深冷到常温的冷能；另一个中冷储罐分为中冷侧和常温侧，其内储存中冷到常温的冷能，中冷循环风机串联于两个中冷储罐常温侧之间；
两个中冷储罐并联时，两个中冷储罐内均储存深冷到中冷的冷能。
其中，所述深冷储罐和中冷储罐均为固定式填充床结构，且固定式填充床结构内部填充耐低温蓄冷材料，循环工质在填充的耐低温蓄冷材料间隙流动并交换冷量；
其中，所述循环工质为空气、氮气、氩气、氦气中的一种或多种混合物；所述耐低温蓄冷材料为陶瓷、石子、氧化铝、金属、封装的相变颗粒、化学反应颗粒中的一种或多种混合物。
其中，所述深冷循环风机和中冷循环风机均为双向循环风机，风机流道密封，风量可调。
其中深冷温度不超过低温绝热储罐内低温液体温度30K，中冷温度在深冷温度与常温之间。
其中，所述超临界液化子系统包括电动机、至少一多级压缩机、干燥净化装置、比例调节装置、液体膨胀机、气液分离器和低温绝热储罐；
电动机与多级压缩机轴连接，多级压缩机之间的连接包括两路，一路为轴连接，一路为气路连接，干燥净化装置设置于多级压缩机气路上，用于降低空气中的水蒸气、二氧化碳、烷烃类成分含量；
电动机驱动多级压缩机对输入的气态空气多级压缩形成超临界空气，多级压缩机出口的超临界空气进入比例调节装置分流，分流后的一路超临界空气进入分级蓄冷子系统液化冷箱的超临界流道后，再经过液体膨胀机膨胀、气液分离器分离形成液态空气，液态空气经气液分离器的液侧出口进入低温绝热储罐。
其中，超临界液化子系统的比例调节装置内部设置流量调节机构，用于调节其分流的两个回路中超临界空气的流量比例。
其中，所述蒸发膨胀子系统包括至少一个的低温泵、多级膨胀机和发电机，低温绝热储罐输出的液态空气经低温泵、分级蓄冷子系统蒸发冷箱的超临界流道后蒸发形成超临界空气，蒸发形成的超临界空气进入多级膨胀机做功并驱动发电机发电，发电机与多级膨胀机轴连接；多级膨胀机的连接包括两路，一路为轴连接，一路为气路。
其中，所述蒸发膨胀子系统还包括预热器，所述预热器置于超临界空气进入多级膨胀机之前的位置，并且多级膨胀机出口的尾气进入预热器形成一气路回路；用于回收多级膨胀机出口较高温度热能。
其中，所述蒸发膨胀子系统的预热器，为板翅式、板式、壳管式、螺旋板式换热器中的一种或多种组合。
其中，该压缩空气储能系统还包括储热换热子系统，储热换热子系统包括至少一储热罐、至少一常温罐、至少两个回热器、至少两个再热器，各回热器之间相互独立，各再热器之间相互独立，
常温罐出口与各回热器的一端相连，每个回热器的另一端与储热罐进口连接；
储热罐出口与各再热器的一端相连，每个回热器的另一端与常温罐进口连接；
至少一回热器同时连接于超临界液化子系统的多级压缩机之间，并且至少一回热器同时连接于超临界液化子系统的多级压缩机与比例调节装置之间；
至少一再热器同时连接于蒸发形成的超临界空气进入多级膨胀机之前，并且至少一回热器同时连接于蒸发膨胀子系统气路的多级膨胀机之间。
其中，所述储热换热子系统还包括余热利用装置，余热利用装置位于再热器出口与常温罐进口之间，用于回收再热器出口蓄热工质的余热。
其中，储热换热子系统的余热利用装置，为供热换热器或制冷机组或两种的组合。
其中，该压缩空气储能系统还包括冷能补偿子系统，冷能补偿子系统包括低温膨胀机组和混合器，超临界液化子系统比例调节装置分流后的另一路超临界空气进入分级蓄冷子系统液化冷箱的冷能补偿流道降温后进入低温膨胀机组膨胀进一步降温，并与气液分离器气侧出口的低温空气在混合器内混合后，经分级蓄冷子系统液化冷箱的冷能回收流道回收冷能，并返回多级压缩机进口或返回多级压缩机各级压缩机之间的气路。
其中，所述冷箱，与冷能补偿子系统连接时，还包括至少一冷能补偿流道和至少一冷能回收流道；超临界液化子系统比例调节装置分流后的另一路超临界空气进入分级蓄冷子系统冷箱的冷能补偿流道降温后进入低温膨胀机组膨胀进一步降温，并与气液分离器气侧出口的低温空气在混合器内混合后，经分级蓄冷子系统冷箱的冷能回收流道回收冷能，并返回多级压缩机进口或返回多级压缩机各级压缩机之间的气路。
本发明的另一方面提供一种分级蓄冷式超临界压缩空气储能方法，应用于所述的分级蓄冷式超临界压缩空气储能系统，包括：
超临界液化子系统将输入的气态空气转化为液态空气；
蒸发膨胀子系统将液态空气转化为气态空气；以及
分级蓄冷子系统在气态空气与液态空气转化时储存和/或释放冷能。
其中，所述超临界液化子系统将输入的气态空气转化为液态空气，具体为：
电动机驱动多级压缩机对输入的空气多级压缩形成超临界空气，多级压缩机出口的超临界空气进入比例调节装置分流，分流后的一路超临界空气进入分级蓄冷子系统液化冷箱的超临界流道后，再经过液体膨胀机膨胀、气液分离器分离形成液态空气，液态空气经气液分离器的液侧出口进入低温绝热储罐。
其中，所述蒸发膨胀子系统将液态空气转化为气态空气，具体为：
低温绝热储罐输出的液态空气经低温泵、分级蓄冷子系统蒸发冷箱的超临界流道后蒸发形成超临界空气，蒸发形成的超临界空气进入多级膨胀机做功并驱动发电机发电。
其中，分级蓄冷子系统在气态空气与液态空气转化时储存和/或释放冷能，具体为：
循环风机驱动循环工质将深冷储罐和中冷储罐内的冷能分别输入液化冷箱的深冷循环内部流道和中冷循环内部流道，为超临界流道内超临界空气液化提供冷能；以及
循环风机驱动循环工质将深冷储罐和中冷储罐内的冷能分别输入蒸发冷箱的深冷循环内部流道和中冷循环内部流道，为超临界流道内超临界空气蒸发提供热能，储存冷能。
其中，还包括储热换热子系统将升温后的蓄热工质储存在储热罐以及将降温后的蓄热工质返回常温罐。
其中，所述储热换热子系统将升温后的蓄热工质储存在储热罐以及将降温后的蓄热工质返回常温罐，具体为：
将在各级回热器内吸收压缩热升温后的蓄热工质储存在储热罐内；以及
各级再热器液侧出口的蓄热工质通过余热利用装置进一步吸收蓄热工质热能并输出常温附近的冷能，将降温后的蓄热工质返回常温罐内。
其中，还包括冷能补偿子系统自主补偿冷能。
其中，冷能补偿子系统自主补偿冷能，具体为：分级蓄冷子系统包括至少一液化冷箱和至少一蒸发冷箱时，超临界液化子系统比例调节装置分流后的另一路超临界空气进入分级蓄冷子系统液化冷箱的冷能补偿流道降温后进入低温膨胀机组膨胀进一步降温，并与气液分离器气侧出口的低温空气在混合器内混合后，经分级蓄冷子系统液化冷箱的冷能回收流道回收冷能，并返回多级压缩机进口或返回多级压缩机各级压缩机之间的气路；或
分级蓄冷子系统包括至少一同时用于液化和蒸发的冷箱时，冷箱与冷能补偿子系统连接，还包括至少一冷能补偿流道和至少一冷能回收流道；超临界液化子系统比例调节装置分流后的另一路超临界空气进入分级蓄冷子系统冷箱的冷能补偿流道降温后进入低温膨胀机组膨胀进一步降温，并与气液分离器气侧出口的低温空气在混合器内混合后，经分级蓄冷子系统冷箱的冷能回收流道回收冷能，返回多级压缩机进口或返回多级压缩机各级压缩机之间的气路。
本发明的另一方面还提供一种分级蓄冷子系统，其中，该分级蓄冷子系统包括至少一液化冷箱、至少一深冷蓄冷循环和至少一中冷蓄冷循环；
所述深冷蓄冷循环与液化冷箱连接，释放深冷温度到常温的冷能；
所述中冷蓄冷循环与液化冷箱连接，释放深冷温度到中冷温度的冷能。
其中，所述液化冷箱包括至少一深冷循环内部流道、至少一中冷循环内部流道、至少一超临界流道、至少一冷能补偿流道和至少一冷能回收流道；
所述至少一深冷蓄冷循环，每一深冷蓄冷循环包括至少一深冷储罐、至少一深冷循环风机以及至少一深冷循环外部流道，每一深冷循环外部流道连接至少一深冷储罐、至少一深冷循环风机，并与所述液化冷箱中的一深冷循环内部流道连接构成完整循环流道；
所述至少一中冷蓄冷循环，每个中冷蓄冷循环包括至少一中冷储罐、至少一中冷循环风机以及至少一中冷循环外部流道，每个中冷循环流道连接至少一中冷储罐、至少一中冷循环风机，并与所述液化冷箱中的一中冷循环内部流道连接构成完整循环流道。
其中，所述分级蓄冷子系统还包括至少一蒸发冷箱，蒸发冷箱与液化冷箱共用至少一深冷蓄冷循环和至少一中冷蓄冷循环；所述深冷蓄冷循环与蒸发冷箱连接，储存深冷温度到常温的冷能；所述中冷蓄冷循环与蒸发冷箱连接，储存深冷温度到中冷温度的冷能。
其中，所述蒸发冷箱包括至少一深冷循环内部流道、至少一中冷循环内部流道、至少一超临界流道；每一深冷循环外部流道连接至少一深冷储罐、至少一深冷循环风机，并与所述蒸发冷箱中的一深冷循环内部流道连接构成完整循环流道；每一中冷循环流道连接至少一中冷储罐、至少一中冷循环风机，并与所述蒸发冷箱中的一中冷循环内部流道连接构成完整循环流道。
本发明的再一方面还提供一种分级蓄冷子系统，包括一冷箱、至少一深冷蓄冷循环和至少一中冷蓄冷循环，其中：
冷箱用于做为液化冷箱或蒸发冷箱；
深冷蓄冷循环，连接于冷箱，在冷箱做为液化冷箱时释放深冷温度到常温的冷能，在冷箱作为蒸发冷箱时储存深冷温度到常温的冷能；
中冷蓄冷循环，连接于冷箱，在冷箱做为液化冷箱时释放深冷温度到中冷温度的冷能，在冷箱作为蒸发冷箱时储存深冷温度到中冷温度的冷能。
其中：
所述冷箱包括至少一深冷循环内部流道、至少一中冷循环内部流道、至少一超临界流道；
每一所述深冷蓄冷循环包括至少一深冷储罐、至少一深冷循环风机以及至少一深冷循环外部流道，每一深冷循环外部流道连接至少一深冷储罐、至少一深冷循环风机，并与所述冷箱中的一深冷循环内部流道连接构成完整循环流道；
每一所述中冷蓄冷循环包括至少一中冷储罐、至少一中冷循环风机以及至少一中冷循环外部流道，每一中冷循环外部流道连接至少一中冷储罐、至少一中冷循环风机，并与所述冷箱中的一中冷循环内部流道连接构成完整循环流道。
其中，所述中冷蓄冷循环的数量大于1时，各中冷蓄冷循环中储存不同中冷温度间的冷能。
其中，所述至少一中冷储罐为两个中冷储罐时，两个中冷储罐串联或并联；
两个中冷储罐串联时，其中一个中冷储罐分为深冷侧和常温侧，其内储存深冷到常温的冷能；另一个中冷储罐分为中冷侧和常温侧，其内储存中冷到常温的冷能，中冷循环风机串联于两个中冷储罐常温侧之间；
两个中冷储罐并联时，两个中冷储罐内均储存深冷到中冷的冷能。
其中，所述深冷储罐和中冷储罐均为固定式填充床结构，且固定式填充床结构内部填充耐低温蓄冷材料，循环工质在填充的耐低温蓄冷材料间隙流动并交换冷量；
其中，所述循环工质为空气、氮气、氩气、氦气中的一种或多种混合物；所述耐低温蓄冷材料为陶瓷、石子、氧化铝、金属、封装的相变颗粒、化学反应颗粒中的一种或多种混合物。
其中，所述深冷循环风机和中冷循环风机均为双向循环风机，风机流道密封，风量可调。
其中深冷温度不超过低温绝热储罐内低温液体温度30K，中冷温度在深冷温度与常温之间。
其中，所述液化冷箱和蒸发冷箱均包括换热器组、保冷材料和密闭外壳；
所述换热器组为至少一板翅式换热器、或至少一板式换热器、或至少一绕管式换热器。
所述保冷材料为玻璃纤维毡、珠光砂、岩棉、真空板中的一种或多种混合。
(三)有益效果
从以上技术方案可以看出，本发明的分级蓄冷式超临界压缩空气储能系统及方法，具有下列有益效果：
1)本发明中，分级蓄冷子系统通过增加一个中冷蓄冷循环储存中间温度的冷量，优点是增加了冷能的回收利用效率，解决冷能回收不足的问题，进而提高系统循环效率，同时可以降低压缩机出口压力；
2)本发明中，使用的循环工质为空气、氮气、氩气、氦气中的一种 或多种混合物，简单易得且安全可靠，具有成本低、效率高、对环境友好、适合大规模应用等优点；
3)本发明中，还包含冷能补偿系统和储热换热系统，完成储能过程中冷能的自主补偿和压缩热的回收利用，而且可以在无外界冷热源输入下实现高效独立运行，不受地形条件限制。
附图说明
图1为本发明一具体实施例的分级蓄冷式超临界压缩空气储能方法流程图；
图2为本发明一具体实施例的单深冷蓄冷循环和中冷储罐结合的分级蓄冷式超临界压缩空气储能系统示意图；
图3为本发明一具体实施例的中冷储罐为双罐串联结构的分级蓄冷式超临界压缩空气储能系统示意图；
图4为本发明一具体实施例的低温液体储罐较高压力下的分级蓄冷式超临界压缩空气储能系统示意图；
图5为本发明一具体实施例的包含一冷箱的分级蓄冷式超临界压缩空气储能系统示意图。
附图标记
100  电动机
101  初级压缩机
102  干燥净化装置
103  末级压缩机
104  比例调节装置
105  液体膨胀机
106  气液分离器
107  低温液体储罐
108  低温膨胀机组
109  混合器
201  储热罐
202  常温罐
203  初级回热器
204  末级回热器
205  初级再热器
206  末级再热器
207  余热利用装置
301  低温泵
302  预热器
303  初级膨胀机
304  末级膨胀机
305  发电机
401  401′深冷储罐
402  402′中冷储罐
4021  4021′下中冷储罐
4022  4022′上中冷储罐
403  液化冷箱
4031 液化冷箱深冷循环内部流道
4032 液化冷箱中冷循环内部流道
4033 液化冷箱超临界流道
4034 液化冷箱冷能补偿流道
4035 液化冷箱冷能回收流道
404  蒸发冷箱
4041 蒸发冷箱深冷循环内部流道
4042 蒸发冷箱中冷循环内部流道
4043 蒸发冷箱蒸发流道
405   405′深冷循环风机
4051  4051′深冷循环外部流道
406   406′中冷循环风机
4061  4061′中冷循环外部流道
407   液化蒸发两用冷箱
具体实施方式
为使本发明的目的、技术方案和优点更加清楚明白，以下结合具体实施例，并参照附图，对本发明进一步详细说明。
需要说明的是，在附图或说明书描述中，相似或相同的部分都使用相同的图号。且在附图中，实施例的形状或是厚度可扩大，并以简化或是方便标示。再者，附图中未绘示或描述的元件或实现方式，为所属技术领域中普通技术人员所知的形式。另外，虽然本文可提供包含特定值的参数的示范，但应了解，参数无需确切等于相应的值，而是可在可接受的误差容限或设计约束内近似于相应的值。
以下将在上述实施例的基础上，给出本发明的最优实施例。需要说明的，该最优的实施例仅用于理解本发明，并不用于限制本发明的保护范围。并且，最优实施例中的特征，在无特别注明的情况下，均同时适用于方法实施例和装置实施例，在相同或不同实施例中出现的技术特征在不相互冲突的情况下可以组合使用。
本发明的分级蓄冷式超临界压缩空气储能系统，包括超临界液化子系统，用于将输入的气态空气转化为液态空气；蒸发膨胀子系统，用于将液态空气转化为气态空气；分级蓄冷子系统，用于在气态空气与液态空气转化时储存和/或释放冷能。
分级蓄冷子系统包括至少一液化冷箱、至少一深冷蓄冷循环和至少一中冷蓄冷循环；深冷蓄冷循环与液化冷箱连接，释放深冷温度到常温的冷能；中冷蓄冷循环与液化冷箱连接，释放深冷温度到中冷温度的冷能。其中，每一液化冷箱包括至少一深冷循环内部流道、至少一中冷循环内部流道、至少一超临界流道、至少一冷能补偿流道和至少一冷能回收流道；每一深冷蓄冷循环包括至少一深冷储罐、至少一深冷循环风机以及至少一深冷循环外部流道，每一深冷循环外部流道连接至少一深冷储罐、至少一深冷循环风机，并与液化冷箱中的一深冷循环内部流道连接构成完整循环流道；每一中冷蓄冷循环包括至少一中冷储罐、至少一中冷循环风机以及至少一中冷循环外部流道，每一中冷循环外部流道连接至少一中冷储罐、至少一中冷循环风机，并与液化冷箱中的一中冷循环内部流道连接构成完整循环流道。
分级蓄冷子系统还包括至少一蒸发冷箱，蒸发冷箱与液化冷箱共用至少一深冷蓄冷循环和至少一中冷蓄冷循环；深冷蓄冷循环与蒸发冷箱连接，储存深冷温度到常温的冷能；中冷蓄冷循环与蒸发冷箱连接，储存深冷温度到中冷温度的冷能。蒸发冷箱包括至少一深冷循环内部流道、至少一中冷循环内部流道和至少一超临界流道；深冷蓄冷循环中的每一深冷循环外部流道连接至少一深冷储罐、至少一深冷循环风机，并与蒸发冷箱中的一深冷循环内部流道连接构成完整循环流道；中冷蓄冷循环中的每一中冷循环外部流道连接至少一中冷储罐、至少一中冷循环风机，并与蒸发冷箱中的一中冷循环内部流道连接构成完整循环流道。
其中，液化冷箱和蒸发冷箱均包括换热器组、保冷材料和密闭外壳；换热器组为至少一板翅式换热器、或至少一板式换热器、或至少一绕管式换热器。保冷材料为玻璃纤维毡、珠光砂、岩棉、真空板中的一种或多种混合。
在本发明的实施例中，液化冷箱和蒸发冷箱可以共用同一个冷箱，此时冷箱用于做为液化冷箱或蒸发冷箱；至少一深冷蓄冷循环和至少一中冷蓄冷循环；每一冷箱既可用于释放冷能，又可用于储存冷能；每一冷箱包括至少一深冷循环内部流道、至少一中冷循环内部流道、至少一超临界流道。深冷蓄冷循环与冷箱连接，释放和/或储存深冷温度到常温的冷能；每一深冷蓄冷循环包括至少一深冷储罐、至少一深冷循环风机以及至少一深冷循环外部流道，每一深冷循环外部流道连接至少一深冷储罐、至少一深冷循环风机，并与冷箱中的一深冷循环内部流道连接构成完整循环流道。中冷蓄冷循环与冷箱连接，释放和/或储存深冷温度到中冷温度的冷能；每一中冷蓄冷循环包括至少一中冷储罐、至少一中冷循环风机以及至少一中冷循环外部流道，每一中冷循环外部流道连接至少一中冷储罐、至少一中冷循环风机，并与冷箱中的一中冷循环内部流道连接构成完整循环流道。
中冷蓄冷循环的数量大于1时，各中冷蓄冷循环中储存不同中冷温度间的冷能。
其中，至少一中冷储罐为两个中冷储罐时，两个中冷储罐串联或并联；两个中冷储罐串联时，其中一中冷储罐分为深冷侧和常温侧，其内储存深冷到常温的冷能；另一中冷储罐分为中冷侧和常温侧，其内储存中冷到常 温的冷能，中冷循环风机串联于两个中冷储罐常温侧之间；两个中冷储罐并联时，两个中冷储罐内均储存深冷到中冷的冷能。
其中，深冷储罐和中冷储罐均为固定式填充床结构，且固定式填充床结构内部填充耐低温蓄冷材料，循环工质在填充的耐低温蓄冷材料间隙流动并交换冷量；循环工质为空气、氮气、氩气、氦气中的一种或多种混合物；耐低温蓄冷材料为陶瓷、石子、氧化铝、金属、封装的相变颗粒、化学反应颗粒中的一种或多种混合物。
其中，深冷循环风机和中冷循环风机均为双向循环风机，风机流道密封，风量可调。
其中深冷温度不超过低温绝热储罐内低温液体温度30K，中冷温度在深冷温度与常温之间。
超临界液化子系统包括电动机、至少一多级压缩机、干燥净化装置、比例调节装置、液体膨胀机、气液分离器和低温绝热储罐；电动机与多级压缩机轴连接，多级压缩机之间的连接包括两路，一路为轴连接，一路为气路连接，干燥净化装置设置于多级压缩机气路上，用于降低空气中的水蒸气、二氧化碳、烷烃类成分含量；电动机驱动多级压缩机对输入的气态空气多级压缩形成超临界空气，多级压缩机出口的超临界空气进入比例调节装置分流，分流后的一路超临界空气进入分级蓄冷子系统液化冷箱的超临界流道后，再经过液体膨胀机膨胀、气液分离器分离形成液态空气，液态空气经气液分离器的液侧出口进入低温绝热储罐。超临界液化子系统的比例调节装置内部设置流量调节机构，用于调节其分流的两个回路中超临界空气的流量比例。
蒸发膨胀子系统包括至少一个的低温泵、多级膨胀机和发电机，低温绝热储罐输出的液态空气经低温泵、分级蓄冷子系统蒸发冷箱的超临界流道后蒸发形成超临界空气，蒸发形成的超临界空气进入多级膨胀机做功并驱动发电机发电，发电机与多级膨胀机轴连接；多级膨胀机的连接包括两路，一路为轴连接，一路为气路。
蒸发膨胀子系统还包括预热器，预热器置于超临界空气进入多级膨胀机之前的位置，并且多级膨胀机出口的尾气进入预热器形成一气路回路； 用于回收多级膨胀机出口较高温度热能。预热器，为板翅式、板式、壳管式、螺旋板式换热器中的一种或多种组合。
该压缩空气储能系统还包括储热换热子系统，储热换热子系统包括至少一储热罐、至少一常温罐、至少两个回热器、至少两个再热器，各回热器之间相互独立，各再热器之间相互独立，常温罐出口与各回热器的一端相连，每个回热器的另一端与储热罐进口连接；储热罐出口与各再热器的一端相连，每个回热器的另一端与常温罐进口连接；至少一回热器同时连接于超临界液化子系统的多级压缩机之间，并且至少一回热器同时连接于超临界液化子系统的多级压缩机与比例调节装置之间；至少一再热器同时连接于蒸发形成的超临界空气进入多级膨胀机之前，并且至少一回热器同时连接于蒸发膨胀子系统气路的多级膨胀机之间。其中，储热换热子系统还包括余热利用装置，余热利用装置位于再热器出口与常温罐进口之间，用于回收再热器出口蓄热工质的余热。储热换热子系统的余热利用装置，为供热换热器或制冷机组或两种的组合。
其中，该压缩空气储能系统还包括冷能补偿子系统，冷能补偿子系统自主补偿冷能，具体为：分级蓄冷子系统包括至少一液化冷箱和至少一蒸发冷箱时，超临界液化子系统比例调节装置分流后的另一路超临界空气进入分级蓄冷子系统液化冷箱的冷能补偿流道降温后进入低温膨胀机组膨胀进一步降温，并与气液分离器气侧出口的低温空气在混合器内混合后，经分级蓄冷子系统液化冷箱的冷能回收流道回收冷能，并返回多级压缩机进口或返回多级压缩机各级压缩机之间的气路；或
分级蓄冷子系统包括至少一同时用于液化和蒸发的冷箱时，冷箱与冷能补偿子系统连接，还包括至少一冷能补偿流道和至少一冷能回收流道；超临界液化子系统比例调节装置分流后的另一路超临界空气进入分级蓄冷子系统冷箱的冷能补偿流道降温后进入低温膨胀机组膨胀进一步降温，并与气液分离器气侧出口的低温空气在混合器内混合后，经分级蓄冷子系统冷箱的冷能回收流道回收冷能，返回多级压缩机进口或返回多级压缩机各级压缩机之间的气路。
本发明的分级蓄冷式超临界压缩空气储能方法，应用于分级蓄冷式超临界压缩空气储能系统，如图1所示，为本发明的一具体实施例的分级蓄冷式超临界压缩空气储能方法流程图包括：
S101：超临界液化子系统将输入的气态空气转化为液态空气；具体为：电动机驱动多级压缩机对输入的空气多级压缩形成超临界空气，多级压缩机出口的超临界空气进入比例调节装置分流，分流后的一路超临界空气进入分级蓄冷子系统液化冷箱的超临界流道后，再经过液体膨胀机膨胀、气液分离器分离形成液态空气，液态空气经气液分离器的液侧出口进入低温绝热储罐。
S102：蒸发膨胀子系统将液态空气转化为气态空气；具体为：低温绝热储罐输出的液态空气经低温泵、分级蓄冷子系统蒸发冷箱的超临界流道后蒸发形成超临界空气，蒸发形成的超临界空气进入多级膨胀机做功并驱动发电机发电。
S103：分级蓄冷子系统在气态空气与液态空气转化时储存和/或释放冷能；具体为：循环风机驱动循环工质将深冷储罐和中冷储罐内的冷能分别输入液化冷箱的深冷循环内部流道和中冷循环内部流道，为超临界流道内超临界空气液化提供冷能；以及
循环风机驱动循环工质将深冷储罐和中冷储罐内的冷能分别输入蒸发冷箱的深冷循环内部流道和中冷循环内部流道，为超临界流道内超临界空气蒸发提供热能，储存冷能。
其中，本发明的分级蓄冷式超临界压缩空气储能方法还包括：
S104：储热换热子系统将升温后的蓄热工质储存在储热罐以及将降温后的蓄热工质返回常温罐；具体为：将在各级回热器内吸收压缩热升温后的蓄热工质储存在储热罐内；以及各级再热器液侧出口的蓄热工质通过余热利用装置进一步吸收蓄热工质热能并输出常温附近的冷能，将降温后的蓄热工质返回常温罐内。
其中，本发明的分级蓄冷式超临界压缩空气储能方法还包括：
S105：冷能补偿子系统自主补偿冷能；具体为：冷能补偿子系统自主补偿冷能，具体为：分级蓄冷子系统包括至少一液化冷箱和至少一蒸发冷箱时，超临界液化子系统比例调节装置分流后的另一路超临界空气进入分 级蓄冷子系统液化冷箱的冷能补偿流道降温后进入低温膨胀机组膨胀进一步降温，并与气液分离器气侧出口的低温空气在混合器内混合后，经分级蓄冷子系统液化冷箱的冷能回收流道回收冷能，并返回多级压缩机进口或返回多级压缩机各级压缩机之间的气路；或
分级蓄冷子系统包括至少一同时用于液化和蒸发的冷箱时，冷箱与冷能补偿子系统连接，还包括至少一冷能补偿流道和至少一冷能回收流道；超临界液化子系统比例调节装置分流后的另一路超临界空气进入分级蓄冷子系统冷箱的冷能补偿流道降温后进入低温膨胀机组膨胀进一步降温，并与气液分离器气侧出口的低温空气在混合器内混合后，经分级蓄冷子系统冷箱的冷能回收流道回收冷能，返回多级压缩机进口或返回多级压缩机各级压缩机之间的气路。
实施例1
图2为本发明一具体实施例的单深冷蓄冷循环和中冷储罐结合的分级蓄冷式超临界压缩空气储能系统示意图。
此实施例中，工质为导热油，压缩机为二级压缩，膨胀机为二级膨胀，采用单个储热罐、单个常温罐、单个低温液体储罐、单个分级蓄冷子系统；其中，分级蓄冷子系统包括单个深冷储罐、单个中冷储罐、单个液化冷箱，单个蒸发冷箱，余热利用装置为吸收式制冷机组，低温膨胀机为二级膨胀，低温液体储罐内压力接近常压。本实施例的液化冷箱的冷能回收流道4035回流的气体返回初级压缩机101的进口
使用流程为：
1.在储能开始阶段，电动机100驱动初级压缩机101将常压空气和冷能回收流道4035出口回流空气压缩，压缩空气经级间回热器203交换热量后输入干燥净化装置102降低水蒸气、二氧化碳、烷烃类成分含量，干燥净化的压缩空气在末级压缩机103内进一步压缩并换热后以超临界状态输入比例调节装置104。在各级回热器203和204内吸收压缩热升温后的蓄热工质储存在储热罐201内。
2.循环风机405和406驱动循环工质将深冷储罐401和中冷储罐402内的冷能分别输入液化冷箱403的深冷循环内部流道4031和中冷循环内部流道4032，为超临界流道4033内超临界空气液化提供冷量。深冷循环 外部流道4051连接深冷储罐401、深冷循环风机405，并与液化冷箱403中的深冷循环内部流道4032连接构成完整循环流道；中冷循环外部流道4061连接中冷储罐402、中冷循环风机406，并与液化冷箱403中的中冷循环内部流道4031连接构成完整循环流道。
3.超临界空气通过比例调节装置104分流后以一定流量比例输出，大部分进入液化冷箱的超临界流道4033吸收冷能降温后液化为高压流体，另外一部分超临界空气进入液化冷箱的冷能补偿流道4034，吸收部分冷能降温后经低温膨胀机组108进一步膨胀降温为接近常压的低温气体，为整个系统补偿低温冷能。
4.超临界空气液化后经液体膨胀机105膨胀为接近常压的气液混合流体并进入气液分离器106，分离后的低温气体与冷能补偿回路4034出口膨胀降温后的低温气体在混合器109内混合，混合后的接近常压低温气体输入液化冷箱补冷流道4035以回收冷能并补偿冷能的不足。气液分离器106内分离的液态空气收集并储存在低温绝热储罐107内，完成能量的存储。
5.释能阶段，液态空气经低温泵301提高压力后输入蒸发冷箱404，深冷储罐401′和中冷储罐402′内的循环工质通过循环风机405′和406′驱动分别输入蒸发冷箱的深冷循环内部流道4041和中冷循环内部流道4042，循环工质在蒸发冷箱内吸收蒸发流道4043内液态空气蒸发释放的冷量后分别进入深冷储罐401′和中冷储罐402′内，完成冷能的回收和存储。蒸发冷箱404与液化冷箱403共用深冷蓄冷循环和中冷蓄冷循环；其中，深冷储罐401和深冷储罐401′实为同一深冷储罐，中冷储罐402和中冷储罐402′实为同一中冷储罐；深冷循环风机405和深冷循环风机405′实为同一深冷循环风机；中冷循环风机406和中冷循环风机406′实为同一中冷循环风机；深冷循环外部流道4051和深冷循环外部流道4051′实为同一深冷循环外部流道；中冷循环外部流道4061和中冷循环外部流道4061′实为同一中冷循环外部流道。蒸发冷箱包括深冷循环内部流道4041、中冷循环内部流道4042和超临界流道4043；深冷蓄冷循环中的深冷循环外部流道4051′连接深冷储罐401′、深冷循环风机405′，并与蒸发冷箱404中的深冷循环内部流道4042连接构成完整循环流道；中冷蓄冷循环中的中冷循环 外部流道4061′连接中冷储罐402′、中冷循环风机406′，并与蒸发冷箱404中的中冷循环内部流道4041连接构成完整循环流道。
6.蒸发冷箱蒸发流道4043出口的超临界空气输入预热器302内与末级膨胀机304出口的较高温度尾气交换热量，进一步提高超临界空气温度。预热后的超临界空气经再热器205吸收蓄热工质热量后进入初级膨胀机303做功并驱动发电机305发电，初级膨胀机303出口压缩空气进入末级再热器206内重新加热后进入末级膨胀机304膨胀做功。
7.各级再热器205和206液侧出口的蓄热工质仍有较高温度，通过余热利用装置207进一步吸收蓄热工质热能并输出常温附近的冷能，降温后的蓄热工质返回常温罐202内。
实施例2
图3为本发明一具体实施例的中冷储罐为双罐串联结构的分级蓄冷式超临界压缩空气储能系统示意图；如图3所示，相对实施例1的改进为：至少一中冷储罐为两个中冷储罐时，下中冷储罐4021和上中冷储罐4022串联，下中冷储罐4021内储存从中冷到常温的冷能上中冷储罐4022内储存从深冷到常温的冷能能，下中冷储罐4021和上中冷储罐4022的常温侧通过中冷循环风机406连接起来，其优点在于中冷循环风机406可以常温运行，避免压缩热引起风机出口中冷温度循环工质温度大幅升高而导致的冷能损失。同样地，下中冷储罐4021′和上中冷储罐4022′串联，下中冷储罐4021′内储存从中冷到常温的冷能上中冷储罐4022′内储存从深冷到常温的冷能能，下中冷储罐4021′和上中冷储罐4022′的常温侧通过中冷循环风机406′连接起来，其优点在于中冷循环风机406′可以常温运行，避免压缩热引起风机出口中冷温度循环工质温度大幅升高而导致的冷能损失。其中，中冷循环风机406和中冷循环风机406′实为同一中冷循环风机，下中冷储罐4021和下中冷储罐4021′实为同一下中冷储罐；上中冷储罐4022和上中冷储罐4022′实为同一上中冷储罐。
实施例3
图4为本发明一具体实施例的低温液体储罐较高压力下的分级蓄冷式超临界压缩空气储能系统示意图；如图4所示，相对实施1的改进为：从 液化冷箱冷能回收流道4035回流的低温常压气体返回干燥净化装置102与末级压缩机之间的气路，并非返回初级压缩机101的进口。此时，低温绝热储罐107内储存液态空气的压力并不接近常压，而是远高于常压。
在储能阶段，液化冷箱冷能补偿流道4034内的超临界流体吸收部分冷能降温后经两级低温膨胀机108膨胀至低接近低温绝热储罐107内压力，并与气液分离器内分离的低温气体在混合器109内混合后输入冷能回收流道4035，冷能回收流道4035与末级压缩机103进口连接，与初级压缩机101压缩后的压缩空气混合后输入末级压缩机103压缩为超临界空气。
实施例4
图5为本发明一具体实施例的包含一冷箱的分级蓄冷式超临界压缩空气储能系统示意图。如图5所示，相对实施例1的改进为：液化冷箱和蒸发冷箱是共用同一个冷箱，即仅设置一冷箱407，该冷箱既可作为用于释放冷能的液化冷箱，又可作为用于储存冷能的蒸发冷箱。在储能开始阶段，阀门一G1和阀门三G3开启，阀门二G2和阀门四G4关闭。超临界空气通过阀门二G2进入比例调节装置104；超临界空气通过比例调节装置104分流后大部分进入冷箱的超临界流道4033，后经过阀门三G3进入液体膨胀机105。在释能阶段，阀门一G1和阀门三G3关闭，阀门二G2和阀门四G4开启。液态空气经低温泵301提高压力后经阀门四G4输入液化冷箱的超临界流道4033，超临界流道4033输出的超临界空气通过比例调节装置104经阀门二G2输入预热器302内。
以上所述的具体实施例，对本发明的目的、技术方案和有益效果进行了进一步详细说明，所应理解的是，以上所述仅为本发明的具体实施例而已，并不用于限制本发明，凡在本发明的精神和原则之内，所做的任何修改、等同替换、改进等，均应包含在本发明的保护范围之内。

Claims (43)

  1. 一种分级蓄冷式超临界压缩空气储能系统，包括用于将输入的气态空气转化为液态空气的超临界液化子系统和用于将液态空气转化为气态空气的蒸发膨胀子系统，其中，该分级蓄冷式超临界压缩空气储能系统还包括：
    分级蓄冷子系统，用于在气态空气与液态空气转化时储存和/或释放冷能。
  2. 根据权利要求1所述的分级蓄冷式超临界压缩空气储能系统，其中，所述分级蓄冷子系统包括至少一液化冷箱、至少一深冷蓄冷循环和至少一中冷蓄冷循环；
    所述深冷蓄冷循环与液化冷箱连接，释放深冷温度到常温的冷能；
    所述中冷蓄冷循环与液化冷箱连接，释放深冷温度到中冷温度的冷能。
  3. 根据权利要求2所述的分级蓄冷式超临界压缩空气储能系统，其中，
    每一所述液化冷箱包括至少一深冷循环内部流道、至少一中冷循环内部流道、至少一超临界流道、至少一冷能补偿流道和至少一冷能回收流道；
    每一所述深冷蓄冷循环包括至少一深冷储罐、至少一深冷循环风机以及至少一深冷循环外部流道，每一深冷循环外部流道连接至少一深冷储罐、至少一深冷循环风机，并与所述液化冷箱中的一深冷循环内部流道连接构成完整循环流道；
    每一所述中冷蓄冷循环包括至少一中冷储罐、至少一中冷循环风机以及至少一中冷循环外部流道，每一中冷循环外部流道连接至少一中冷储罐、至少一中冷循环风机，并与所述液化冷箱中的一中冷循环内部流道连接构成完整循环流道。
  4. 根据权利要求3所述的分级蓄冷式超临界压缩空气储能系统，其中，所述分级蓄冷子系统还包括至少一蒸发冷箱，蒸发冷箱与液化冷箱共用至少一深冷蓄冷循环和至少一中冷蓄冷循环；
    所述深冷蓄冷循环与蒸发冷箱连接，储存深冷温度到常温的冷能；
    所述中冷蓄冷循环与蒸发冷箱连接，储存深冷温度到中冷温度的冷能。
  5. 根据权利要求4所述的分级蓄冷式超临界压缩空气储能系统，其中，所述蒸发冷箱包括至少一深冷循环内部流道、至少一中冷循环内部流道和至少一超临界流道；
    深冷蓄冷循环中的每一深冷循环外部流道连接至少一深冷储罐、至少一深冷循环风机，并与所述蒸发冷箱中的一深冷循环内部流道连接构成完整循环流道；
    中冷蓄冷循环中的每一中冷循环外部流道连接至少一中冷储罐、至少一中冷循环风机，并与所述蒸发冷箱中的一中冷循环内部流道连接构成完整循环流道。
  6. 根据权利要求4所述的分级蓄冷式超临界压缩空气储能系统，其中，所述液化冷箱和蒸发冷箱均包括换热器组、保冷材料和密闭外壳；
    所述换热器组为至少一板翅式换热器、或至少一板式换热器、或至少一绕管式换热器。
    所述保冷材料为玻璃纤维毡、珠光砂、岩棉、真空板中的一种或多种混合。
  7. 根据权利要求1所述的分级蓄冷式超临界压缩空气储能系统，其中，所述分级蓄冷子系统包括至少一冷箱、至少一深冷蓄冷循环和至少一中冷蓄冷循环；
    冷箱用于做为液化冷箱或蒸发冷箱；
    深冷蓄冷循环，连接于冷箱，在冷箱做为液化冷箱时释放深冷温度到常温的冷能，在冷箱作为蒸发冷箱时储存深冷温度到常温的冷能；
    中冷蓄冷循环，连接于冷箱，在冷箱做为液化冷箱时释放深冷温度到中冷温度的冷能，在冷箱作为蒸发冷箱时储存深冷温度到中冷温度的冷能。
  8. 根据权利要求7所述的分级蓄冷式超临界压缩空气储能系统，其中，
    每一所述冷箱包括至少一深冷循环内部流道、至少一中冷循环内部流道、至少一超临界流道；
    每一所述深冷蓄冷循环包括至少一深冷储罐、至少一深冷循环风机以及至少一深冷循环外部流道，每一深冷循环外部流道连接至少一深冷储罐、 至少一深冷循环风机，并与所述冷箱中的一深冷循环内部流道连接构成完整循环流道；
    每一所述中冷蓄冷循环包括至少一中冷储罐、至少一中冷循环风机以及至少一中冷循环外部流道，每一中冷循环外部流道连接至少一中冷储罐、至少一中冷循环风机，并与所述冷箱中的一中冷循环内部流道连接构成完整循环流道。
  9. 根据权利要求1至8中任一项所述的分级蓄冷式超临界压缩空气储能系统，其中，所述中冷蓄冷循环的数量大于1时，各中冷蓄冷循环中储存不同中冷温度间的冷能。
  10. 根据权利要求5或8述的分级蓄冷式超临界压缩空气储能系统，其中，所述至少一中冷储罐为两个中冷储罐时，两个中冷储罐串联或并联；
    两个中冷储罐串联时，其中一个中冷储罐分为深冷侧和常温侧，其内储存深冷到常温的冷能；另一个中冷储罐分为中冷侧和常温侧，其内储存中冷到常温的冷能，中冷循环风机串联于两个中冷储罐常温侧之间；
    两个中冷储罐并联时，两个中冷储罐内均储存深冷到中冷的冷能。
  11. 根据权利要求5或8所述的分级蓄冷式超临界压缩空气储能系统，其中，所述深冷储罐和中冷储罐均为固定式填充床结构，且固定式填充床结构内部填充耐低温蓄冷材料，循环工质在填充的耐低温蓄冷材料间隙流动并交换冷量；
    其中，所述循环工质为空气、氮气、氩气、氦气中的一种或多种混合物；所述耐低温蓄冷材料为陶瓷、石子、氧化铝、金属、封装的相变颗粒、化学反应颗粒中的一种或多种混合物。
  12. 根据权利要求5或8所述的分级蓄冷式超临界压缩空气储能系统，其中，所述深冷循环风机和中冷循环风机均为双向循环风机，风机流道密封，风量可调。
  13. 根据权利要求1-12中任一项所述的分级蓄冷式超临界压缩空气储能系统，其中深冷温度不超过低温绝热储罐内低温液体温度30K，中冷温度在深冷温度与常温之间。
  14. 根据权利要求5或8所述的分级蓄冷式超临界压缩空气储能系统，其中，所述超临界液化子系统包括电动机、至少一多级压缩机、干燥净化装置、比例调节装置、液体膨胀机、气液分离器和低温绝热储罐；
    电动机与多级压缩机轴连接，多级压缩机之间的连接包括两路，一路为轴连接，一路为气路连接，干燥净化装置设置于多级压缩机气路上，用于降低空气中的水蒸气、二氧化碳、烷烃类成分含量；
    电动机驱动多级压缩机对输入的气态空气多级压缩形成超临界空气，多级压缩机出口的超临界空气进入比例调节装置分流，分流后的一路超临界空气进入分级蓄冷子系统液化冷箱的超临界流道后，再经过液体膨胀机膨胀、气液分离器分离形成液态空气，液态空气经气液分离器的液侧出口进入低温绝热储罐。
  15. 根据权利要求14所述的分级蓄冷式超临界压缩空气储能系统，其中，超临界液化子系统的比例调节装置内部设置流量调节机构，用于调节其分流的两个回路中超临界空气的流量比例。
  16. 根据权利要求14所述的分级蓄冷式超临界压缩空气储能系统，其中，所述蒸发膨胀子系统包括至少一个的低温泵、多级膨胀机和发电机，低温绝热储罐输出的液态空气经低温泵、分级蓄冷子系统蒸发冷箱的超临界流道后蒸发形成超临界空气，蒸发形成的超临界空气进入多级膨胀机做功并驱动发电机发电，发电机与多级膨胀机轴连接；多级膨胀机的连接包括两路，一路为轴连接，一路为气路。
  17. 根据权利要求16所述的分级蓄冷式超临界压缩空气储能系统，其中，所述蒸发膨胀子系统还包括预热器，所述预热器置于超临界空气进入多级膨胀机之前的位置，并且多级膨胀机出口的尾气进入预热器形成一气路回路；用于回收多级膨胀机出口较高温度热能。
  18. 根据权利要求所述17的分级蓄冷式超临界压缩空气储能系统，其中，所述蒸发膨胀子系统的预热器，为板翅式、板式、壳管式、螺旋板式换热器中的一种或多种组合。
  19. 根据权利要求16所述的分级蓄冷式超临界压缩空气储能系统，其中，该压缩空气储能系统还包括储热换热子系统，储热换热子系统包括 至少一储热罐、至少一常温罐、至少两个回热器、至少两个再热器，各回热器之间相互独立，各再热器之间相互独立，
    常温罐出口与各回热器的一端相连，每个回热器的另一端与储热罐进口连接；
    储热罐出口与各再热器的一端相连，每个回热器的另一端与常温罐进口连接；
    至少一回热器同时连接于超临界液化子系统的多级压缩机之间，并且至少一回热器同时连接于超临界液化子系统的多级压缩机与比例调节装置之间；
    至少一再热器同时连接于蒸发形成的超临界空气进入多级膨胀机之前，并且至少一回热器同时连接于蒸发膨胀子系统气路的多级膨胀机之间。
  20. 根据权利要求19所述的分级蓄冷式超临界压缩空气储能系统，其中，所述储热换热子系统还包括余热利用装置，余热利用装置位于再热器出口与常温罐进口之间，用于回收再热器出口蓄热工质的余热。
  21. 根据权利要求20所述的分级蓄冷式超临界压缩空气储能系统，其中，储热换热子系统的余热利用装置，为供热换热器或制冷机组或两种的组合。
  22. 根据权利要求19所述的分级蓄冷式超临界压缩空气储能系统，其中，该压缩空气储能系统还包括冷能补偿子系统，冷能补偿子系统包括低温膨胀机组和混合器，超临界液化子系统比例调节装置分流后的另一路超临界空气进入分级蓄冷子系统液化冷箱的冷能补偿流道降温后进入低温膨胀机组膨胀进一步降温，并与气液分离器气侧出口的低温空气在混合器内混合后，经分级蓄冷子系统液化冷箱的冷能回收流道回收冷能，并返回多级压缩机进口或返回多级压缩机各级压缩机之间的气路。
  23. 根据权利要求8和22所述的分级蓄冷式超临界压缩空气储能系统，所述冷箱，与冷能补偿子系统连接时，还包括至少一冷能补偿流道和至少一冷能回收流道；超临界液化子系统比例调节装置分流后的另一路超临界空气进入分级蓄冷子系统冷箱的冷能补偿流道降温后进入低温膨胀机组膨胀进一步降温，并与气液分离器气侧出口的低温空气在混合器内混 合后，经分级蓄冷子系统冷箱的冷能回收流道回收冷能，并返回多级压缩机进口或返回多级压缩机各级压缩机之间的气路。
  24. 一种分级蓄冷式超临界压缩空气储能方法，应用于权利要求1至23中任一项所述的分级蓄冷式超临界压缩空气储能系统，包括：
    超临界液化子系统将输入的气态空气转化为液态空气；
    蒸发膨胀子系统将液态空气转化为气态空气；以及
    分级蓄冷子系统在气态空气与液态空气转化时储存和/或释放冷能。
  25. 根据权利要求24所述的分级蓄冷式超临界压缩空气储能方法，其中，所述超临界液化子系统将输入的气态空气转化为液态空气，具体为：
    电动机驱动多级压缩机对输入的空气多级压缩形成超临界空气，多级压缩机出口的超临界空气进入比例调节装置分流，分流后的一路超临界空气进入分级蓄冷子系统液化冷箱的超临界流道后，再经过液体膨胀机膨胀、气液分离器分离形成液态空气，液态空气经气液分离器的液侧出口进入低温绝热储罐。
  26. 根据权利要求24所述的分级蓄冷式超临界压缩空气储能方法，其中，所述蒸发膨胀子系统将液态空气转化为气态空气，具体为：
    低温绝热储罐输出的液态空气经低温泵、分级蓄冷子系统蒸发冷箱的超临界流道后蒸发形成超临界空气，蒸发形成的超临界空气进入多级膨胀机做功并驱动发电机发电。
  27. 根据权利要求24所述的分级蓄冷式超临界压缩空气储能方法，其中，分级蓄冷子系统在气态空气与液态空气转化时储存和/或释放冷能，具体为：
    循环风机驱动循环工质将深冷储罐和中冷储罐内的冷能分别输入液化冷箱的深冷循环内部流道和中冷循环内部流道，为超临界流道内超临界空气液化提供冷能；以及
    循环风机驱动循环工质将深冷储罐和中冷储罐内的冷能分别输入蒸发冷箱的深冷循环内部流道和中冷循环内部流道，为超临界流道内超临界空气蒸发提供热能，储存冷能。
  28. 根据权利要求24所述的分级蓄冷式超临界压缩空气储能方法，其中，还包括储热换热子系统将升温后的蓄热工质储存在储热罐以及将降温后的蓄热工质返回常温罐。
  29. 根据权利要求28所述的分级蓄冷式超临界压缩空气储能方法，其中，所述储热换热子系统将升温后的蓄热工质储存在储热罐以及将降温后的蓄热工质返回常温罐，具体为：
    将在各级回热器内吸收压缩热升温后的蓄热工质储存在储热罐内；以及
    各级再热器液侧出口的蓄热工质通过余热利用装置进一步吸收蓄热工质热能并输出常温附近的冷能，将降温后的蓄热工质返回常温罐内。
  30. 根据权利要求24所述的分级蓄冷式超临界压缩空气储能方法，其中，还包括冷能补偿子系统自主补偿冷能。
  31. 根据权利要求30所述的分级蓄冷式超临界压缩空气储能方法，其中，冷能补偿子系统自主补偿冷能，具体为：分级蓄冷子系统包括至少一液化冷箱和至少一蒸发冷箱时，超临界液化子系统比例调节装置分流后的另一路超临界空气进入分级蓄冷子系统液化冷箱的冷能补偿流道降温后进入低温膨胀机组膨胀进一步降温，并与气液分离器气侧出口的低温空气在混合器内混合后，经分级蓄冷子系统液化冷箱的冷能回收流道回收冷能，并返回多级压缩机进口或返回多级压缩机各级压缩机之间的气路；或
    分级蓄冷子系统包括至少一同时用于液化和蒸发的冷箱时，冷箱与冷能补偿子系统连接，还包括至少一冷能补偿流道和至少一冷能回收流道；超临界液化子系统比例调节装置分流后的另一路超临界空气进入分级蓄冷子系统冷箱的冷能补偿流道降温后进入低温膨胀机组膨胀进一步降温，并与气液分离器气侧出口的低温空气在混合器内混合后，经分级蓄冷子系统冷箱的冷能回收流道回收冷能，返回多级压缩机进口或返回多级压缩机各级压缩机之间的气路。
  32. 一种分级蓄冷子系统，其中，该分级蓄冷子系统包括至少一液化冷箱、至少一深冷蓄冷循环和至少一中冷蓄冷循环；
    所述深冷蓄冷循环与液化冷箱连接，释放深冷温度到常温的冷能；
    所述中冷蓄冷循环与液化冷箱连接，释放深冷温度到中冷温度的冷能。
  33. 根据权利要求32所述的分级蓄冷子系统，其中，
    所述液化冷箱包括至少一深冷循环内部流道、至少一中冷循环内部流道、至少一超临界流道、至少一冷能补偿流道和至少一冷能回收流道；
    所述至少一深冷蓄冷循环，每一深冷蓄冷循环包括至少一深冷储罐、至少一深冷循环风机以及至少一深冷循环外部流道，每一深冷循环外部流道连接至少一深冷储罐、至少一深冷循环风机，并与所述液化冷箱中的一深冷循环内部流道连接构成完整循环流道；
    所述至少一中冷蓄冷循环，每个中冷蓄冷循环包括至少一中冷储罐、至少一中冷循环风机以及至少一中冷循环外部流道，每个中冷循环流道连接至少一中冷储罐、至少一中冷循环风机，并与所述液化冷箱中的一中冷循环内部流道连接构成完整循环流道。
  34. 根据权利要求33所述的分级蓄冷子系统，其中，所述分级蓄冷子系统还包括至少一蒸发冷箱，蒸发冷箱与液化冷箱共用至少一深冷蓄冷循环和至少一中冷蓄冷循环；所述深冷蓄冷循环与蒸发冷箱连接，储存深冷温度到常温的冷能；所述中冷蓄冷循环与蒸发冷箱连接，储存深冷温度到中冷温度的冷能。
  35. 根据权利要求34所述的分级蓄冷子系统，其中，所述蒸发冷箱包括至少一深冷循环内部流道、至少一中冷循环内部流道、至少一超临界流道；每一深冷循环外部流道连接至少一深冷储罐、至少一深冷循环风机，并与所述蒸发冷箱中的一深冷循环内部流道连接构成完整循环流道；每一中冷循环流道连接至少一中冷储罐、至少一中冷循环风机，并与所述蒸发冷箱中的一中冷循环内部流道连接构成完整循环流道。
  36. 一种分级蓄冷子系统，包括一冷箱、至少一深冷蓄冷循环和至少一中冷蓄冷循环，其中：
    冷箱用于做为液化冷箱或蒸发冷箱；
    深冷蓄冷循环，连接于冷箱，在冷箱做为液化冷箱时释放深冷温度到常温的冷能，在冷箱作为蒸发冷箱时储存深冷温度到常温的冷能；
    中冷蓄冷循环，连接于冷箱，在冷箱做为液化冷箱时释放深冷温度到中冷温度的冷能，在冷箱作为蒸发冷箱时储存深冷温度到中冷温度的冷能。
  37. 根据权利要求36所述的分级蓄冷子系统，其中：
    每一所述冷箱包括至少一深冷循环内部流道、至少一中冷循环内部流道、至少一超临界流道；
    每一所述深冷蓄冷循环包括至少一深冷储罐、至少一深冷循环风机以及至少一深冷循环外部流道，每一深冷循环外部流道连接至少一深冷储罐、至少一深冷循环风机，并与所述冷箱中的一深冷循环内部流道连接构成完整循环流道；
    每一所述中冷蓄冷循环包括至少一中冷储罐、至少一中冷循环风机以及至少一中冷循环外部流道，每一中冷循环外部流道连接至少一中冷储罐、至少一中冷循环风机，并与所述冷箱中的一中冷循环内部流道连接构成完整循环流道。
  38. 根据权利要求32至37中任一项所述的分级蓄冷子系统，其中，所述中冷蓄冷循环的数量大于1时，各中冷蓄冷循环中储存不同中冷温度间的冷能。
  39. 根据权利要求33、35或37所述的分级蓄冷子系统，其中，所述至少一中冷储罐为两个中冷储罐时，两个中冷储罐串联或并联；
    两个中冷储罐串联时，其中一个中冷储罐分为深冷侧和常温侧，其内储存深冷到常温的冷能；另一个中冷储罐分为中冷侧和常温侧，其内储存中冷到常温的冷能，中冷循环风机串联于两个中冷储罐常温侧之间；
    两个中冷储罐并联时，两个中冷储罐内均储存深冷到中冷的冷能。
  40. 根据权利要求33、35或37所述的分级蓄冷子系统，其中，所述深冷储罐和中冷储罐均为固定式填充床结构，且固定式填充床结构内部填充耐低温蓄冷材料，循环工质在填充的耐低温蓄冷材料间隙流动并交换冷量；
    其中，所述循环工质为空气、氮气、氩气、氦气中的一种或多种混合物；所述耐低温蓄冷材料为陶瓷、石子、氧化铝、金属、封装的相变颗粒、化学反应颗粒中的一种或多种混合物。
  41. 根据权利要求33、35或37所述的分级蓄冷子系统，其中，所述深冷循环风机和中冷循环风机均为双向循环风机，风机流道密封，风量可调。
  42. 根据权利要求32-41中任一项所述的分级蓄冷子系统，其中深冷温度不超过低温绝热储罐内低温液体温度30K，中冷温度在深冷温度与常温之间。
  43. 根据权利要求33所述的分级蓄冷子系统，其中，所述液化冷箱和蒸发冷箱均包括换热器组、保冷材料和密闭外壳；
    所述换热器组为至少一板翅式换热器、或至少一板式换热器、或至少一绕管式换热器。
    所述保冷材料为玻璃纤维毡、珠光砂、岩棉、真空板中的一种或多种混合。
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