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WO2020261559A1 - Power generation system and power generation method - Google Patents

Power generation system and power generation method Download PDF

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Publication number
WO2020261559A1
WO2020261559A1 PCT/JP2019/025925 JP2019025925W WO2020261559A1 WO 2020261559 A1 WO2020261559 A1 WO 2020261559A1 JP 2019025925 W JP2019025925 W JP 2019025925W WO 2020261559 A1 WO2020261559 A1 WO 2020261559A1
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WO
WIPO (PCT)
Prior art keywords
air
power generation
supply line
liquid
generation system
Prior art date
Application number
PCT/JP2019/025925
Other languages
French (fr)
Japanese (ja)
Inventor
雄介 小西
謙 角谷
安達　修
篤志 神谷
Original Assignee
日揮グローバル株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 日揮グローバル株式会社 filed Critical 日揮グローバル株式会社
Priority to PCT/JP2019/025925 priority Critical patent/WO2020261559A1/en
Priority to JP2021527296A priority patent/JP7375014B2/en
Publication of WO2020261559A1 publication Critical patent/WO2020261559A1/en

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Classifications

    • 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
    • F25J1/0002—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
    • 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
    • F25J1/003—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"
    • F25J1/0045—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
    • F25J1/02—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
    • F25J1/0221—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 using the cold stored in an external cryogenic component in an open refrigeration loop
    • 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
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0244—Operation; Control and regulation; Instrumentation
    • F25J1/0245—Different modes, i.e. 'runs', of operation; Process control
    • F25J1/0251—Intermittent or alternating process, so-called batch process, e.g. "peak-shaving"
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • 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
    • F25J2210/00—Processes characterised by the type or other details of the feed stream
    • F25J2210/62—Liquefied natural gas [LNG]; Natural gas liquids [NGL]; Liquefied petroleum gas [LPG]
    • 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
    • F25J2230/00—Processes or apparatus involving steps for increasing the pressure of gaseous process streams
    • F25J2230/30—Compression of the feed 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
    • F25J2240/00—Processes or apparatus involving steps for expanding of process streams
    • F25J2240/90—Hot gas waste turbine of an indirect heated gas for power generation
    • 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
    • F25J2290/00—Other details not covered by groups F25J2200/00 - F25J2280/00
    • F25J2290/62—Details of storing a fluid in a tank

Definitions

  • the present invention relates to a power generation system and a power generation method using stored liquid air.
  • a storage battery for the purpose of securing the adjustment allowance for the amount of power generation. That is, when the amount of power generated by renewable energy becomes surplus, a storage battery for storing the surplus power is provided, and when the demand for power increases and the amount of power generated by thermal power generation or the like cannot be covered, the storage battery is provided. It is conceivable to respond by discharging from.
  • many of them including NaS (sodium-sulfur) batteries, have various problems such as safety concerns, practical concerns, location restrictions, high cost, and short life. Is a concern.
  • LAES Liquid Air Energy Storage
  • Patent Document 1 describes this LAES system, and shows that when necessary, liquid air is released from a storage tank in the system to drive a turbine to discharge.
  • the present invention has been made in view of such circumstances, and an object of the present invention is to provide a technique relating to a power generation system capable of reliably supplying electric power in response to an electric power demand.
  • the power generation system of the present invention includes a liquid air generator that compresses and cools air to generate liquid air.
  • the storage unit that stores the liquid air and A vaporization unit that vaporizes the liquid air supplied from the storage unit to generate compressed air,
  • An expander that expands the compressed air supplied from the vaporization unit,
  • a first generator driven by the expansion of air in the expander,
  • the first in a power plant including a gas turbine generator which is a second generator and a first air supply line for supplying air to the gas turbine generator by expanding and cooling the air in the expander.
  • a second air supply line connecting the first air supply line and the expander in order to lower the temperature of the air supplied to the air supply line of the gas turbine generator and taken in by the gas turbine generator.
  • the compressed air obtained by vaporizing the stored liquid air is expanded to generate electricity by the first generator, and the air cooled by the power generation is used by the second generator.
  • the gas turbine generator By supplying the gas turbine generator, the amount of power generated by the gas turbine generator is increased. Therefore, a large amount of power generation can be obtained from the power generation system of the present invention, and the amount of power generation can be changed significantly, so that power supply can be performed with high certainty in response to a change in power demand.
  • FIG. Figure 1 shows an overview of the system configuration, the flow of natural gas (NG: Natural Gas) generated from liquefied natural gas (LNG: Liquefied Natural Gas), and the flow of air (including liquid air) used for power generation.
  • NG Natural Gas
  • LNG Liquefied Natural Gas
  • air including liquid air
  • normal temperature air is 20 ° C to 30 ° C air
  • ultra-low temperature air is -160 ° C to -100 ° C air
  • low temperature air is -100 ° C to 5 ° C air
  • cold air is assumed that the air is at 5 ° C to 25 ° C.
  • the power generation system 1 includes a thermal power plant 2 having an LNG receiving terminal and performing a GTCC (gas turbine combined cycle). Therefore, the thermal power plant 2 includes an LNG vaporizer 21 and a power generation facility that generates power using the natural gas generated by the LNG vaporizer 21, and the gas turbine generator 3 is provided as the power generation facility. included. Further, the power generation system 1 includes a LAES plant facility 4, a cold heat recovery facility 5, and a power generation facility 6 using room temperature air. In the present specification, LAES is assumed to be a system including components for generating liquid air, storing liquid air, and taking out liquid air stored from a storage facility for power generation, and obtains electric power from the liquid air. It is shown separately from the cold heat recovery facility 5 composed of the power generation facility 6 and the heat exchanger provided for the purpose.
  • the LAES plant facility 4 is configured as a liquid air storage battery, and includes an air rectification facility 41 and a liquid air storage facility 42 composed of a tank, a pump, and the like.
  • the air rectification facility 41 is a facility that takes in the outside air of the LAES plant facility 4 as room temperature air for producing liquid air, rectifies the taken-in air and pressurizes it to make compressed air, and supplies it to the above-mentioned LNG vaporizer 21. is there.
  • the cold heat recovery facility 5 recovers the cold heat of the air flowing through the power generation system 1 and heats and cools the air (including liquid air) at various places in the system.
  • the compressed air supplied to the LNG vaporizer 21 as described above is cooled by heat exchange with the LNG in the LNG vaporizer 21 to become cryogenic air, and then further cooled by the cold heat recovery facility 5. It becomes liquid air, is supplied to the storage facility 42, and is stored.
  • the power generation facility 6 is provided with an expander (expansion turbine) including a turbine, and the compressed air generated by vaporizing liquid air is adiabatically expanded to rotate the turbine to form a turbine. Electricity is obtained by driving a connected generator. Further, the power generation facility 6 is configured such that the cryogenic air generated from the compressed air by this power generation is transported (supplied) to the thermal power plant 2 as described later.
  • the flow of air (including liquid air) from the storage facility 42 will be described in order.
  • the liquid air in the storage facility 42 is heated by the cold heat recovery facility 5 and supplied to the power generation facility 6 in a state of being compressed air at room temperature.
  • ultra-low temperature air is generated from the compressed air at room temperature.
  • This cryogenic air mixes with the outside air (normal temperature air) of the thermal power plant 2 and lowers the temperature of the normal temperature air.
  • the cold air is cooled by the cold heat recovery facility 5 and becomes cold air in the gas turbine. It is supplied to the generator 3.
  • the power generation system 1 power is generated using room temperature air generated from liquid air, and the temperature of the air taken into the gas turbine generator 3 is lowered by the ultra-low temperature air generated by this power generation.
  • the density of air supplied to the gas turbine generator 3 is increased, the mass of air per unit volume is increased, the combustibility of natural gas as a fuel is enhanced, and the output of the gas turbine generator 3 is increased. Is raised, and the amount of power generation is greatly increased.
  • FIG. 2 shows a more detailed configuration of the power generation system 1.
  • the thermal power plant 2, 31, 32, 33, and 34 in the figure are air compressors, combustors, turbines, and generators that each constitute a gas turbine generator 3 (second generator), and generate power.
  • the machine 34 is driven by the rotation of the turbine 33.
  • 35 is a line for supplying natural gas, which is a fuel for the gas turbine generator 3, from the LNG vaporizer 21 to the combustor 32.
  • Reference numeral 36 denotes a duct (first air supply line) provided in the thermal power plant 2, and a heat exchanger 37 (first heat exchanger) is interposed.
  • the downstream side of the duct 36 is connected to the gas turbine generator 3, and the room temperature air, which is the outside air of the thermal power plant 2 taken in from the upstream side, is taken into the air compressor 31.
  • the thermal power plant 2 performs GTCC, but the display of the equipment for performing steam power generation is omitted.
  • the single-point chain line arrow extending from the heat exchanger 37 indicates a discharge path for moisture in the air that condenses and liquefies around the heat exchanger 37 by supplying ultra-low temperature air to the duct 36. ..
  • the LAES plant facility 4 includes an air rectification facility 41 and a liquid air storage facility (including a pumping facility) 42 as described above.
  • the storage facility 42 includes a tank 40 and a refrigeration pump 43.
  • the air rectification facility 41 includes a compressor for boosting the air pressure to obtain compressed air.
  • the rectification performed by the air rectification facility 41 specifically includes, for example, removal of CO 2 (carbon dioxide) and water.
  • the above-mentioned renewable energy can be used for the operation of each device such as the compressor in the LAES plant facility 4.
  • the compressed air supplied to the LNG vaporizer 21 is cooled by heat exchange with the LNG as described above to become cryogenic air.
  • the heat exchange between LNG and air in the LNG vaporizer 21 is performed, for example, via an intermediate heat medium. That is, heat exchange is performed between LNG and the intermediate heat medium, and heat exchange is performed between the intermediate heat medium and air.
  • the cryogenic air generated in the LNG vaporizer 21 is cooled by the heat exchanger 51 (fourth heat exchanger) to become liquid air, which is supplied to the tank 40 (storage unit) of the LAES plant equipment 4 for storage. Will be done.
  • the air line from the air rectification facility 41 to the tank 40 via the LNG vaporizer 21 and the heat exchanger 51 is shown as 44.
  • the air flowing through the air supply line 44 and the air supply line 45 described later is liquid air depending on the circulation location. That is, it is assumed that the air flowing through the air supply line includes liquid air.
  • the liquid air stored in the tank 40 is sucked into the refrigeration pump 43, pressurized, and pumped to the subsequent stage.
  • the liquid air is warmed by the influence of the outside air of the power generation system 1 and vaporized to become cryogenic air, which is supplied to the heat exchanger 51.
  • the cryogenic air is heated by the heat exchanger 51 and its temperature rises.
  • the cryogenic air whose temperature has risen is supplied to the heat exchanger 55 (second heat exchanger) and further heated.
  • An air supply line 45 is provided which connects the tank 40 and the power generation facility 6 and is provided with a refrigeration pump 43 and heat exchangers 51 and 52.
  • the power generation facility 6 includes an expander and a generator (first generator), respectively, and is shown in FIG. 2 as 61 and 62, respectively.
  • the above air supply line 45 is connected to the inflator 61.
  • the expander 61 is connected to the upstream end of the cryogenic air supply line (second air supply line) 63.
  • the downstream end of the cryogenic air supply line 63 is connected to the duct 36 described above.
  • the compressed air at room temperature supplied to the expander 61 is lowered and stepped down to drive the generator 62 and generate ultra-low temperature air.
  • the extremely low temperature air generated by the expander 61 is, for example, large.
  • the heat exchanger 51 is interposed in the air supply lines 44 and 45 as described above, and in the heat exchanger 51, the extremely low temperature air cooled by the LNG vaporizer 21 and heading for the tank 40 and the refrigeration pump. Heat exchange is performed with the extremely low temperature air supplied from 43 to the subsequent stage. Further, a circulation in which the heat medium is moved by the pump 53 between the heat exchanger 37 at the end of the duct 36 through which the normal temperature air is guided and the heat exchanger 52 at the air (including liquid air) supply line 45. A line 54 (first fluid circulation line) is provided.
  • the cold heat recovery facility 5 described with reference to FIG. 1 is composed of the heat exchangers 51, 52, and 37 described above.
  • An antifreeze solution such as ethylene glycol is used as the heat medium (fluid for heat exchange) of each heat exchanger, and the heat exchanger 52 has an appropriate configuration in order to prevent the flow from being stopped due to freezing of the heat medium.
  • a known heat exchanger called a shell and tube type can be used.
  • the air rectification facility 41, the LNG vaporizer 21, and the heat exchanger 51 of the LAES plant facility 4 form a liquid air generating section, and the heat exchangers 51 and 52 form a vaporizing section. Therefore, the heat exchanger 51 is shared by the liquid air generating section and the vaporizing section.
  • the duck curve is a graph in which the horizontal axis is the time of day and the vertical axis is the power demand in a specific area, and the transition of the power demand is shown in a duck-shaped curve. Is.
  • the problem of this duck curve is that the amount of solar power generation peaks in the daytime, while the demand for electricity is in a time zone (dawn and evening) that deviates significantly from this daytime time zone. It reaches its peak. For example, it has peaks from 6:00 to 8:00 at dawn and from 18:00 to 21:00 in the evening. Due to this, there is a concern about power shortage during these times.
  • the power generation system 1 can be operated so as to solve the problem of the duck curve.
  • an operation example of the power generation system 1 after noon will be described.
  • the power generation system 1 is in a state where liquid air power generation (power generation by the power generation facility 6) and ultra-low temperature air are not supplied to the gas turbine generator 3.
  • the time zone approaches the evening, the amount of power generated by photovoltaic power generation drops sharply due to the decrease in the amount of sunshine, while the demand for power peaks as described above, so it is necessary to secure a large amount of power generation.
  • the temperature of the outside air of the thermal power plant 2 is relatively high.
  • the output of the gas turbine generator 3 is affected by the temperature of the intake air. Therefore, when only this outside air is used, the output of the gas turbine generator 3 cannot be sufficiently improved. There is a fear.
  • liquid air power generation is started, and at the same time, ultra-low temperature air is supplied to the duct 36 connected to the gas turbine generator 3, and the amount of power generated from the thermal power plant 2 increases. To do.
  • the amount of power generated from the power generation system 1 in this way, power is supplied so as to correspond to the peak of power demand in the evening, and the supply and demand of power is balanced.
  • the liquid air power generation and the supply of cryogenic air will be stopped in response to the decrease in the demand for electric power.
  • the power generation system 1 can be operated to accommodate the peak of dawn when people's behavior becomes active.
  • liquid air power generation and cryogenic air supply are performed so as to avoid daytime when the amount of power generated by photovoltaic power generation is large, but liquid air power generation and cryogenic air supply during the daytime are prohibited. It's not something. While the liquid air power generation is performed at an arbitrary timing according to the demand in this way, the generation of the liquid air by the LAES plant equipment 4 and the supply of the generated liquid air to the tank 40 are, for example, the time when the liquid air power generation is not performed. Do it with a belt.
  • the amount of power generation in the thermal power plant 2 in addition to performing liquid air power generation, the amount of power generation in the thermal power plant 2 can be increased.
  • the amount of power generated by the thermal power plant 2 that has decreased due to the temperature of the outside air is restored, and the amount of power generated is high so that the influence of the temperature of the outside air can be suppressed. Will be obtained. Since the amount of power generated by the thermal power plant 2 can be increased at the same time as the liquid air power generation is performed in this way, the power generation system 1 can obtain a high amount of power generation at an arbitrary timing and the amount of power generation is relatively rapid. Can be raised and lowered.
  • the power generation system 1 power generation can be performed so as to respond with high certainty to changes in the amount of power demand.
  • the power generation system 1 is located in an area where there is a need for power storage due to a surplus of power generated using renewable energy, the air temperature is high, and GTCC power generation cannot produce the rated output. It is effective to provide.
  • the power generation system 1 includes the LAES plant equipment 4, but it is generally considered that the plant equipment has a relatively long service life of 40 years. That is, since the power generation system 1 is expected to be able to be operated for a relatively long time after construction, it is advantageous as compared with the case of using a storage battery having a short life such as a NaS battery. Further, since the power generation system 1 uses air, there is an advantage that it is a clean system that does not need to use chemical substances that affect the environment.
  • the compressed air for generating the liquid air is cooled by heat exchange with the LNG in the LNG vaporizer 21, so that the power required for generating the liquid air can be reduced. It is advantageous.
  • a heat exchanger that cools the compressed air using liquid nitrogen as a heat medium may be provided in the power generation system 1 to generate liquid air.
  • the heat exchanger 37 is provided in the duct 36 in which the ultra-low temperature air and the normal temperature air are mixed, so that the temperature of the air supplied to the gas turbine generator 3 becomes lower. Therefore, the amount of power generated at the thermal power plant 2 can be set to a higher value.
  • the power generation system 1 has a configuration in which a heat medium is distributed between the heat exchanger 37 and the heat exchanger 52. That is, the heat transfer when cooling the air in the duct 36 and the heat transfer when vaporizing the liquid air are mutually used. Therefore, the energy required for cooling the air in the duct 36 and vaporizing the liquid air is exchanged, so that the operating cost and power of the power generation system 1 can be reduced.
  • the power generation system 1 heat exchange is performed between liquid air and air in the heat exchanger 51. Therefore, the heat transfer for vaporizing the liquid air and the heat transfer for generating the liquid air from the air are mutually utilized. As a result, in the power generation system 1, the energy required for the generation of liquid air and the vaporization of liquid air is exchanged, so that the operating cost and power of the system can be reduced.
  • the configuration of the air and liquid air lines is not limited to the above-described example.
  • the liquid air supplied from the refrigeration pump 43 is supplied to the heat exchanger 52 without passing through the heat exchanger 51. It may be.
  • the cryogenic air from the LNG vaporizer 21 to the tank 40 may be liquefied air using a heat exchanger that uses liquid nitrogen or the like as a heat medium.
  • the heat exchangers 51 and 52 are supplied with the ultra-low temperature air vaporized from the liquid air, the liquid air before vaporization is supplied and the heat exchanger 51 or the heat exchanger 52 liquids. The air may be vaporized.
  • the power generation system 7 of the second embodiment of the present invention will be described with reference to FIG. 3, focusing on the differences from the power generation system 1 of the first embodiment.
  • the power generation system 7 is not provided with the heat exchanger 37 and the pump 53 for the heat medium.
  • an exhaust flow having a relatively high temperature is supplied to the heat exchanger 52 from the thermal power plant 2, and the extremely low temperature air is heated by heat exchange between the exhaust flow and the extremely low temperature air. It becomes normal temperature air and is supplied to the expander 61.
  • the duct 36 may be configured so that the heat exchanger 37 is not provided.
  • the outside air is defined as room temperature air taken in from the upstream side of the duct 36 and flowing through the duct 36.
  • the extremely low temperature air discharged from the expander 61 can be sufficiently mixed with the outside air to sufficiently lower the temperature of the air supplied to the gas turbine generator 3.
  • a mixing portion is provided in order to mix the cryogenic air flowing in the duct 36 with high certainty.
  • the mixing portion is composed of, for example, an annular body 71.
  • the arrow of the chain line extending from the annular body 71 in FIG. 3 indicates a water discharge path like the arrow extending from the heat exchanger 37 of FIG. 1, and is generated by cooling the air around the annular body 71. Remove the water.
  • FIGS. 4 and 5 are a longitudinal side view and a cross-sectional plan view of the annular body 71, respectively.
  • a through hole 72 is formed in the central portion of the annular body 71 when viewed in the direction of the flow path of the duct 36, and the through hole 72 forms a flow path for the outside air.
  • a plurality of discharge ports 73 are provided on the front surface of the annular body 71 toward the downstream side of the duct 36 at equal intervals along the circumferential direction of the annular body 71. That is, the discharge ports 73 are opened at different positions in the circumferential direction.
  • the downstream side of the cryogenic air supply line 63 is branched and connected to the annular body 71 so that the cryogenic air can be supplied to each discharge port 73.
  • cryogenic air is discharged toward the downstream side of the duct 36 and toward the central portion of the plan view annular body 71.
  • the mixing portion for reliably mixing the above-mentioned cryogenic air flowing in the duct 36 is not limited to the above configuration, and as shown in FIG. 6, the nozzle 81 is inside the duct 36 as the mixing portion. May be provided.
  • the nozzle 81 is, for example, a porous nozzle, that is, a nozzle having a large number of discharge ports.
  • the upstream side of the nozzle 81 is connected to the cryogenic air supply line 63. Then, the nozzle 81 sprays the ultra-low temperature air supplied from the supply line 63 toward the downstream side of the flow path in the duct 36 so as to radiate from the nozzle 81 along the flow path direction.
  • the ultra-low temperature air is highly mixed with the outside air, that is, the ultra-low temperature air is configured to be uniformly dispersed with respect to the outside air.
  • the cryogenic air is ejected from the discharge port of the nozzle 81 and the discharge port 73 of the annular body 71, respectively, due to the pressure of the nozzle 81 and the annular body 71.
  • the moisture generated by cooling the air around the annular body 71 can be removed by a plurality of corrugated plates 74 provided in the duct 36 as shown in FIG. 6, and water droplets hit the corrugated plate 74. It is possible to remove water efficiently. That is, although FIG. 6 shows an example in which a corrugated plate 74 is provided as a moisture removing portion on the downstream side of the nozzle 81 in the duct 36, the annular body is also provided in the duct 36 provided with the annular body 71 in FIG. A corrugated plate 74 is provided on the downstream side of the 71, and water droplets accompanying the air hit the corrugated plate 74 and fall to be discharged from the inside of the duct 36 to the outside of the duct 36. The reason for removing the water droplets in this way is to prevent the impeller of the air compressor built in the gas turbine generator 3 from being worn by being hit by a large amount of water droplets.
  • the power generation system 82 of the third embodiment of the present invention will be described with reference to FIG. 7, focusing on the differences from the power generation system 1.
  • a heat exchanger 83 (third heat exchanger) is interposed in the cryogenic air supply line 63.
  • a heat medium circulation line 84 (second fluid circulation line) is provided, which is partly in common with the heat medium circulation line 54 and in which heat exchangers 37 and 83 are interposed.
  • the portion of the circulation line 54 on the downstream side of the pump 53 that sends the heat medium from the heat exchanger 37 to the heat exchanger 52 branches.
  • a heat exchanger 83 is interposed in this branched line, and the end of the branched line is a portion of the circulation line 54 where the heat medium flows from the heat exchanger 52 to the heat exchanger 37. It is connected.
  • This branched line constitutes the circulation line 84.
  • the heat exchanger 83 warms the cryogenic air to, for example, cold air before it is supplied to the duct 36.
  • the temperature of the extremely low temperature air is too low, so that the outside air flowing through the duct 36 (taken in from the upstream of the duct 36) at the connection portion of the duct 36 with the supply line 63 of the extremely low temperature air. This is to prevent the (normal temperature air) from freezing and preventing the extremely low temperature air from being sufficiently mixed with the outside air.
  • FIG. 8 shows a modified example of the power generation system 1 described above.
  • a valve 85 is interposed between the heat exchanger 51 and the refrigeration pump 43 in the air supply line 45, and one end of the liquid air recirculation line 86 is connected between the valve 85 and the refrigeration pump 43. ing.
  • the other end of the reflux line 86 is connected to the liquid air tank 40 via a valve 87.
  • the refrigerating pump 43 always operates to supply liquid air from the tank 40 toward the rear stage side of the supply line 63.
  • valve 85 When liquid air power generation is not performed, the valve 85 is slightly opened and the valve 87 is opened, the liquid air is returned to the tank 40, and the delivery system (heat exchangers 51 and 52, and thus the heat exchangers 51 and 52) is sent as a cold insulation circulation. It is sent to the inflator 61).
  • the valve 85 When performing liquid air power generation, the valve 85 is opened and the valve 87 is closed, and the liquid air is not sent to the tank 40 but is supplied to the heat exchanger 51 and the expander 61. Therefore, the valves 85 and 87 form a switching unit that switches the main supply destination of the liquid air between the heat exchanger 51 and the tank 40.

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Abstract

[Problem] To provide a technology which pertains to a power generation system capable of definitively supplying power which corresponds to the demand for power. [Solution] A power generation system configured so as to be equipped with: a liquid air generation unit for generating liquid air by compressing and cooling air; a storage unit for storing the liquid air; a vaporization unit for generating compressed air by vaporizing the liquid air which was supplied from the storage unit; an expander for expanding the compressed air which was supplied by the vaporization unit; a first power generator which drives as a result of the expansion of air by the expander; and a second air supply line for connecting the expander and a first air supply line to one another in order to decrease the temperature of air which is drawn in by a gas turbine power generator via the supply of cooled air which has been expanded by the expander to the first air supply line, which is provided to a power station equipped with the gas turbine power generator, which is a second power generator, and the first air supply line, which supplies air to the gas turbine power generator.

Description

発電システム及び発電方法Power generation system and power generation method
　本発明は、貯蔵した液体空気を用いる発電システム及び発電方法に関する。 The present invention relates to a power generation system and a power generation method using stored liquid air.
　温室効果ガスを排出しない利点が有ることから、太陽光、風力、地熱などの再生可能エネルギーを用いる発電が有望視され、その導入が進められている。しかし再生可能エネルギーによる発電のうちで主要な太陽光発電、風力発電については気象条件により、その発電量が左右されてしまう。この問題についてより具体的に述べると、電力系統から安定した周波数で電気を利用者に供給するためには、電力の需給のバランスをとることが求められる。言い換えれば、電力の需給バランスをとることで、供給される電気の周波数の調整がなされている。再生可能エネルギーによる発電と併用される他の発電による発電量、特に火力発電による発電量を調整することによって、この需給バランスを取ることが図られている。 Since it has the advantage of not emitting greenhouse gases, power generation using renewable energy such as solar power, wind power, and geothermal power is seen as promising, and its introduction is being promoted. However, among the power generation by renewable energy, the amount of power generated by major solar power generation and wind power generation depends on the weather conditions. More specifically, in order to supply electricity to users at a stable frequency from the electric power system, it is necessary to balance the supply and demand of electric power. In other words, the frequency of the supplied electricity is adjusted by balancing the supply and demand of electric power. This supply-demand balance is being achieved by adjusting the amount of power generated by other power generation used in combination with the power generated by renewable energy, especially the amount of power generated by thermal power generation.
しかし、上記のように気象条件の影響を受けるので、太陽光発電及び風力発電の発電量の調整は困難である。従って、これら太陽光発電及び風力発電を中心とする再生可能エネルギーを用いた発電システムの電力系統への導入が進むと、当該再生可能エネルギーによる発電量が大きくなるときには上記の他の発電による発電量を低下させたとしても、電力系統の電力の供給量が電力の需要量を超えて、余剰電力が生じてしまう懸念が有る。 However, it is difficult to adjust the amount of power generated by solar power generation and wind power generation because it is affected by the weather conditions as described above. Therefore, if the introduction of power generation systems using renewable energy such as solar power generation and wind power generation into the power system progresses, when the amount of power generated by the renewable energy increases, the amount of power generated by the other power generations described above Even if it is reduced, there is a concern that the amount of power supplied to the power system will exceed the amount of power demand and surplus power will be generated.
また、再生可能エネルギーを用いた発電システムの導入が進んだ電力系統においては１日のうちの特定の時間帯で、当該再生可能エネルギーによる発電量が急激に、大きく変動してしまう。そのため、このような再生可能エネルギーの発電量の変動に対して、火力発電などの他の発電による発電量の変動が追従しきれず、上記の電力の需給バランスが保てなくなる懸念が有る。このような懸念が生じる背景には、火力発電の発電量が気温の影響を受けてしまうことで、再生可能エネルギーの発電量が低下したときに、当該火力発電からは高い発電量が得られない場合が有るというという理由も存在する。 Further, in an electric power system in which the introduction of a power generation system using renewable energy has progressed, the amount of power generated by the renewable energy suddenly and greatly fluctuates in a specific time zone of the day. Therefore, there is a concern that the fluctuation of the power generation amount due to other power generation such as thermal power generation cannot keep up with the fluctuation of the power generation amount of the renewable energy, and the above-mentioned power supply-demand balance cannot be maintained. The background to this concern is that the amount of power generated by thermal power generation is affected by the temperature, and when the amount of power generated by renewable energy declines, it is not possible to obtain a high amount of power generation from the thermal power generation. There is also a reason that there are cases.
　そこで、発電量の調整代を確保する目的で、蓄電池を設けることが考えられる。即ち、再生可能エネルギーによる発電量が余剰となるときに、その余剰の電力を蓄電する蓄電池を設け、電力の需要が増加して火力発電等による発電量の増加でまかないきれないときに、当該蓄電池からの放電によって対応することが考えられる。ただし、各種の蓄電池のうちＮａＳ（ナトリウム・硫黄）電池をはじめとして、その多くは、安全性の不安、実用上の不安、立地上の制約、高コスト、低寿命などの各種の問題が有ることが懸念されている。 Therefore, it is conceivable to install a storage battery for the purpose of securing the adjustment allowance for the amount of power generation. That is, when the amount of power generated by renewable energy becomes surplus, a storage battery for storing the surplus power is provided, and when the demand for power increases and the amount of power generated by thermal power generation or the like cannot be covered, the storage battery is provided. It is conceivable to respond by discharging from. However, among various storage batteries, many of them, including NaS (sodium-sulfur) batteries, have various problems such as safety concerns, practical concerns, location restrictions, high cost, and short life. Is a concern.
上記した各種の問題が解消された蓄電池として、ＬＡＥＳ（Liquid Air Energy Storage）と呼ばれる、液体空気を生成して貯蔵する設備を含むシステムが期待される。特許文献１には、このＬＡＥＳのシステムについて記載されており、必要時に当該システムにおける貯蔵タンクから液体空気を開放し、タービンを駆動して放電させることが示されている。しかし、上記の再生可能エネルギーの変動に関わらず、電力の需要に確実に対応して電力を供給するためには、そのようにして得られる電力よりも、より多くの電力が得られるシステムが望まれる。 As a storage battery that solves the above-mentioned various problems, a system called LAES (Liquid Air Energy Storage) including a facility for generating and storing liquid air is expected. Patent Document 1 describes this LAES system, and shows that when necessary, liquid air is released from a storage tank in the system to drive a turbine to discharge. However, in order to reliably meet the demand for electric power and supply electric power regardless of the above-mentioned fluctuation of renewable energy, it is desirable to have a system that can obtain more electric power than the electric power obtained in this way. Is done.
特開２０１６－５１７９４８（段落０００５）JP 2016-517948 (paragraph 0005)
　本発明はこのような事情に鑑みてなされたものであり、その課題は、電力の需要に対応した電力供給を確実に行うことができる発電システムに関する技術を提供することを目的とする。 The present invention has been made in view of such circumstances, and an object of the present invention is to provide a technique relating to a power generation system capable of reliably supplying electric power in response to an electric power demand.
本発明の発電システムは、空気の圧縮及び冷却を行い、液体空気を生成する液体空気生成部と、
　前記液体空気を貯蔵する貯蔵部と、
　前記貯蔵部から供給された前記液体空気を気化させて圧縮空気を生成する気化部と、
　前記気化部から供給された圧縮空気を膨張させる膨張機と、
　前記膨張機における空気の膨張により駆動する第１の発電機と、
　前記膨張機において膨張して冷却された空気を、第２の発電機であるガスタービン発電機と前記ガスタービン発電機に空気を供給する第１の空気供給ラインとを備える発電所における前記第１の空気供給ラインに供給して前記ガスタービン発電機が吸気する空気の温度を低下させるために、当該第１の空気供給ラインと前記膨張機とを接続する第２の空気供給ラインと、
を備える発電システム The power generation system of the present invention includes a liquid air generator that compresses and cools air to generate liquid air.
The storage unit that stores the liquid air and
A vaporization unit that vaporizes the liquid air supplied from the storage unit to generate compressed air,
An expander that expands the compressed air supplied from the vaporization unit,
A first generator driven by the expansion of air in the expander,
The first in a power plant including a gas turbine generator which is a second generator and a first air supply line for supplying air to the gas turbine generator by expanding and cooling the air in the expander. A second air supply line connecting the first air supply line and the expander in order to lower the temperature of the air supplied to the air supply line of the gas turbine generator and taken in by the gas turbine generator.
Power generation system equipped with
　本発明によれば、貯蔵した液体空気を気化させて得た圧縮空気を膨張させることで第１の発電機による発電を行い、さらにその発電に用いられて降温された空気を第２の発電機であるガスタービン発電機に供給することで、当該ガスタービン発電機による発電量を増加させる。従って、本発明の発電システムからは大きな発電量を得ることができると共に、その発電量を大きく変化させることができるため、電力の需要の変化に対応した電力供給を確実性高く行うことができる。 According to the present invention, the compressed air obtained by vaporizing the stored liquid air is expanded to generate electricity by the first generator, and the air cooled by the power generation is used by the second generator. By supplying the gas turbine generator, the amount of power generated by the gas turbine generator is increased. Therefore, a large amount of power generation can be obtained from the power generation system of the present invention, and the amount of power generation can be changed significantly, so that power supply can be performed with high certainty in response to a change in power demand.
本発明の発電システムの概略図である。It is the schematic of the power generation system of this invention. 本発明の第１の実施形態に係る発電システムの構成図である。It is a block diagram of the power generation system which concerns on 1st Embodiment of this invention. 本発明の第２の実施形態に係る発電システムの構成図である。It is a block diagram of the power generation system which concerns on 2nd Embodiment of this invention. 前記発電システムを構成するダクトに設けられる環状部材の縦断側面図である。It is a longitudinal side view of the annular member provided in the duct constituting the power generation system. 前記環状部材の横断平面図である。It is a cross-sectional plan view of the annular member. 前記ダクトに設けられる多孔式ノズルの側面図である。It is a side view of the porous nozzle provided in the duct. 本発明の第３の実施形態に係る発電システム及びガスタービン発電機に供給される空気を熱媒体により冷却するシステムの構成図である。It is a block diagram of the power generation system which concerns on 3rd Embodiment of this invention, and the system which cools the air supplied to a gas turbine generator by a heat medium. 前記発電システムの液体空気の供給ラインの構成の一例、及びガスタービン発電機に供給される空気を直接冷却するシステムの構成図である。It is an example of the configuration of the liquid air supply line of the power generation system, and the configuration diagram of the system that directly cools the air supplied to the gas turbine generator.
　本発明の第１の実施形態に係る発電システム１の概略構成について、図１を参照しながら説明する。この図１はシステムの構成の概要と、液化天然ガス（ＬＮＧ：Liquefied Natural Gas）から生じる天然ガス（ＮＧ：Natural Gas）の流れと、発電に用いるための空気（液体空気も含む）の流れと、を示すブロックフロー図である。なお以下の説明で、常温空気とは２０℃～３０℃の空気、極低温空気とは－１６０℃～－１００℃の空気、低温空気とは－１００℃～５℃の空気、冷空気とは５℃～２５℃の空気であるものとする。 The schematic configuration of the power generation system 1 according to the first embodiment of the present invention will be described with reference to FIG. Figure 1 shows an overview of the system configuration, the flow of natural gas (NG: Natural Gas) generated from liquefied natural gas (LNG: Liquefied Natural Gas), and the flow of air (including liquid air) used for power generation. It is a block flow diagram which shows. In the following explanation, normal temperature air is 20 ° C to 30 ° C air, ultra-low temperature air is -160 ° C to -100 ° C air, low temperature air is -100 ° C to 5 ° C air, and cold air is. It is assumed that the air is at 5 ° C to 25 ° C.
発電システム１は、ＬＮＧの受け入れ基地を備えると共にＧＴＣＣ（ガスタービンコンバインドサイクル）を行う火力発電所２を含む。従って、この火力発電所２としては、ＬＮＧ気化器２１と、ＬＮＧ気化器２１で生じた天然ガスを用いて発電を行う発電設備と、を備えており、この発電設備としてガスタービン発電機３が含まれる。また発電システム１は、ＬＡＥＳプラント設備４、冷熱回収設備５及び常温空気を用いる発電設備６を備えている。なお、本明細書ではＬＡＥＳは、液体空気の生成、液体空気の貯蔵、発電のために貯蔵設備から貯蔵された液体空気を取り出す各構成要素を含むシステムであるものとし、液体空気から電力を得るために設けられる発電設備６及び熱交換器から構成される冷熱回収設備５とは区別して示している。 The power generation system 1 includes a thermal power plant 2 having an LNG receiving terminal and performing a GTCC (gas turbine combined cycle). Therefore, the thermal power plant 2 includes an LNG vaporizer 21 and a power generation facility that generates power using the natural gas generated by the LNG vaporizer 21, and the gas turbine generator 3 is provided as the power generation facility. included. Further, the power generation system 1 includes a LAES plant facility 4, a cold heat recovery facility 5, and a power generation facility 6 using room temperature air. In the present specification, LAES is assumed to be a system including components for generating liquid air, storing liquid air, and taking out liquid air stored from a storage facility for power generation, and obtains electric power from the liquid air. It is shown separately from the cold heat recovery facility 5 composed of the power generation facility 6 and the heat exchanger provided for the purpose.
ＬＡＥＳプラント設備４は液体空気の蓄電池として構成されており、空気精留設備４１と、タンク及びポンプなどにより構成される液体空気の貯蔵設備４２とを備えている。空気精留設備４１は、液体空気製造用の常温空気としてＬＡＥＳプラント設備４の外気を取り込み、取り込んだ空気を精留すると共に昇圧させて圧縮空気とし、上記のＬＮＧ気化器２１に供給する設備である。 The LAES plant facility 4 is configured as a liquid air storage battery, and includes an air rectification facility 41 and a liquid air storage facility 42 composed of a tank, a pump, and the like. The air rectification facility 41 is a facility that takes in the outside air of the LAES plant facility 4 as room temperature air for producing liquid air, rectifies the taken-in air and pressurizes it to make compressed air, and supplies it to the above-mentioned LNG vaporizer 21. is there.
冷熱回収設備５は、この発電システム１中を流通する空気の冷熱を回収し、システム中の各所で当該空気（液体空気も含む）の加熱及び冷却を行う。上記のようにＬＮＧ気化器２１に供給された圧縮空気は、ＬＮＧ気化器２１におけるＬＮＧとの間の熱交換により冷却されて、極低温空気となった後に、冷熱回収設備５でさらに冷却されて液体空気となり、貯蔵設備４２に供給されて貯蔵される。 The cold heat recovery facility 5 recovers the cold heat of the air flowing through the power generation system 1 and heats and cools the air (including liquid air) at various places in the system. The compressed air supplied to the LNG vaporizer 21 as described above is cooled by heat exchange with the LNG in the LNG vaporizer 21 to become cryogenic air, and then further cooled by the cold heat recovery facility 5. It becomes liquid air, is supplied to the storage facility 42, and is stored.
そして、発電システム１においては所望のタイミングにおいて、貯蔵設備４２に貯蔵された液体空気を用いた、上記の常温空気を用いる発電設備６による発電（放電）が行われる。この発電設備６について述べると、発電設備６は、タービンを含む膨張機（膨張タービン）を備えており、液体空気が気化されて生成する圧縮空気を断熱膨張させて当該タービンを回転させ、タービンに接続される発電機を駆動させることにより電力が得られる。また発電設備６は、後述のようにこの発電によって圧縮空気から生じた極低温空気が、火力発電所２へ輸送（供給）されるように構成されている。 Then, in the power generation system 1, power generation (discharge) is performed by the power generation facility 6 using the room temperature air described above using the liquid air stored in the storage facility 42 at a desired timing. Regarding the power generation facility 6, the power generation facility 6 is provided with an expander (expansion turbine) including a turbine, and the compressed air generated by vaporizing liquid air is adiabatically expanded to rotate the turbine to form a turbine. Electricity is obtained by driving a connected generator. Further, the power generation facility 6 is configured such that the cryogenic air generated from the compressed air by this power generation is transported (supplied) to the thermal power plant 2 as described later.
貯蔵設備４２からの空気（液体空気を含む）の流れを順に述べると、貯蔵設備４２の液体空気は冷熱回収設備５により加熱されて、常温の圧縮空気となった状態で発電設備６に供給される。上記のように断熱膨張されること及び仕事（タービンの回転）を行い、エネルギーを電力に変換する過程で降圧されることで、上記の常温の圧縮空気から極低温空気が生じる。この極低温空気が、火力発電所２の外気（常温空気）に混ざり、この常温空気の温度を低下させる。そして、温度が低下した常温空気（極低温空気と火力発電所２の外気との混合空気）がガスタービン発電機３に向かう途中、冷熱回収設備５によって冷却されて、冷空気となってガスタービン発電機３に供給される。 The flow of air (including liquid air) from the storage facility 42 will be described in order. The liquid air in the storage facility 42 is heated by the cold heat recovery facility 5 and supplied to the power generation facility 6 in a state of being compressed air at room temperature. To. By performing adiabatic expansion and work (rotation of the turbine) as described above and stepping down in the process of converting energy into electric power, ultra-low temperature air is generated from the compressed air at room temperature. This cryogenic air mixes with the outside air (normal temperature air) of the thermal power plant 2 and lowers the temperature of the normal temperature air. Then, on the way to the gas turbine generator 3, the cold air is cooled by the cold heat recovery facility 5 and becomes cold air in the gas turbine. It is supplied to the generator 3.
このように発電システム１においては、液体空気から生じた常温空気を用いて発電を行うと共に、この発電によって生じた極低温空気により、ガスタービン発電機３に吸気される空気の温度を低下させる。それにより、ガスタービン発電機３に供給される空気の密度を高くし、単位体積あたりの空気の質量を増加させ、燃料である天然ガスの燃焼性を高めて、当該ガスタービン発電機３の出力を高くし、その発電量を大幅に大きくしている。 In this way, in the power generation system 1, power is generated using room temperature air generated from liquid air, and the temperature of the air taken into the gas turbine generator 3 is lowered by the ultra-low temperature air generated by this power generation. As a result, the density of air supplied to the gas turbine generator 3 is increased, the mass of air per unit volume is increased, the combustibility of natural gas as a fuel is enhanced, and the output of the gas turbine generator 3 is increased. Is raised, and the amount of power generation is greatly increased.
図２は発電システム１について、より詳細な構成を示している。火力発電所２について説明すると、図中３１、３２、３３、３４は、夫々ガスタービン発電機３（第２の発電機）を構成する空気圧縮機、燃焼器、タービン、発電機であり、発電機３４は、タービン３３の回転によって駆動する。図中３５は、ＬＮＧ気化器２１からガスタービン発電機３の燃料である天然ガスを、燃焼器３２に供給するラインである。３６は火力発電所２に設けられるダクト（第１の空気供給ライン）であり、熱交換器３７（第１の熱交換器）が介設されている。このダクト３６の下流側はガスタービン発電機３に接続され、上流側から取り込んだ火力発電所２の外気である常温空気が、空気圧縮機３１に吸気される。なお、上記したように火力発電所２はＧＴＣＣを行うが、汽力発電を行うための設備の表示は省略している。なお、熱交換器３７から伸びる一点鎖線の矢印は、極低温空気がダクト３６に供給されることで、熱交換器３７の周囲にて凝縮、液化する空気中の水分の排出路を示している。 FIG. 2 shows a more detailed configuration of the power generation system 1. Explaining the thermal power plant 2, 31, 32, 33, and 34 in the figure are air compressors, combustors, turbines, and generators that each constitute a gas turbine generator 3 (second generator), and generate power. The machine 34 is driven by the rotation of the turbine 33. In the figure, 35 is a line for supplying natural gas, which is a fuel for the gas turbine generator 3, from the LNG vaporizer 21 to the combustor 32. Reference numeral 36 denotes a duct (first air supply line) provided in the thermal power plant 2, and a heat exchanger 37 (first heat exchanger) is interposed. The downstream side of the duct 36 is connected to the gas turbine generator 3, and the room temperature air, which is the outside air of the thermal power plant 2 taken in from the upstream side, is taken into the air compressor 31. As described above, the thermal power plant 2 performs GTCC, but the display of the equipment for performing steam power generation is omitted. The single-point chain line arrow extending from the heat exchanger 37 indicates a discharge path for moisture in the air that condenses and liquefies around the heat exchanger 37 by supplying ultra-low temperature air to the duct 36. ..
続いて、ＬＡＥＳプラント設備４について説明する。ＬＡＥＳプラント設備４は、上記したように空気精留設備４１及び液体空気の貯蔵設備（圧送設備を含む）４２を備えている。貯蔵設備４２は、タンク４０と、冷凍ポンプ４３とを備えている。上記のように液体空気による発電を行う際には、当該冷凍ポンプ４３が駆動して、後段に液体空気を圧送して発電が行われる。また、空気精留設備４１について補足して説明すると、当該空気精留設備４１は、空気を昇圧させて圧縮空気とするための圧縮機を含む。また、空気精留設備４１で行われる精留としては、具体的には例えばＣＯ２（二酸化炭素）及び水の除去が含まれる。ＬＡＥＳプラント設備４における、上記の圧縮器などの各機器の動作には、例えば既述の再生可能エネルギーを用いることができる。 Subsequently, the LAES plant equipment 4 will be described. The LAES plant facility 4 includes an air rectification facility 41 and a liquid air storage facility (including a pumping facility) 42 as described above. The storage facility 42 includes a tank 40 and a refrigeration pump 43. When power generation is performed by liquid air as described above, the refrigerating pump 43 is driven to pump liquid air to the subsequent stage to generate power. Further, to explain the air rectification facility 41 as a supplement, the air rectification facility 41 includes a compressor for boosting the air pressure to obtain compressed air. Further, the rectification performed by the air rectification facility 41 specifically includes, for example, removal of CO 2 (carbon dioxide) and water. For example, the above-mentioned renewable energy can be used for the operation of each device such as the compressor in the LAES plant facility 4.
ＬＮＧ気化器２１に供給された圧縮空気は、上記のようにＬＮＧとの熱交換により冷却されて、極低温空気となる。このＬＮＧ気化器２１におけるＬＮＧと空気との熱交換は、例えば中間熱媒体を介して行われる。つまり、ＬＮＧと中間熱媒体との間で熱交換が行われ、中間熱媒体と空気との間で熱交換が行われる。このＬＮＧ気化器２１において生じた極低温空気が、熱交換器５１（第４の熱交換器）にて冷却されて液体空気となり、ＬＡＥＳプラント設備４のタンク４０（貯蔵部）に供給されて貯蔵される。なお、図中では空気精留設備４１からＬＮＧ気化器２１、熱交換器５１を順に介してタンク４０に至る空気のラインを４４として示している。この空気の供給ライン４４及び後述の空気の供給ライン４５を流通する空気は、その流通する箇所によっては液体空気となっている。つまり、空気の供給ラインを流通する空気としては、液体空気も含むものとする。 The compressed air supplied to the LNG vaporizer 21 is cooled by heat exchange with the LNG as described above to become cryogenic air. The heat exchange between LNG and air in the LNG vaporizer 21 is performed, for example, via an intermediate heat medium. That is, heat exchange is performed between LNG and the intermediate heat medium, and heat exchange is performed between the intermediate heat medium and air. The cryogenic air generated in the LNG vaporizer 21 is cooled by the heat exchanger 51 (fourth heat exchanger) to become liquid air, which is supplied to the tank 40 (storage unit) of the LAES plant equipment 4 for storage. Will be done. In the figure, the air line from the air rectification facility 41 to the tank 40 via the LNG vaporizer 21 and the heat exchanger 51 is shown as 44. The air flowing through the air supply line 44 and the air supply line 45 described later is liquid air depending on the circulation location. That is, it is assumed that the air flowing through the air supply line includes liquid air.
そして上記の発電設備６による発電を行うにあたり、タンク４０に貯蔵された液体空気は、冷凍ポンプ４３に吸引され加圧されて、後段に圧送される。この冷凍ポンプ４３による圧送中に液体空気は発電システム１の外気の影響により暖められて、気化して極低温空気となって熱交換器５１に供給される。そして、この極低温空気は、当該熱交換器５１にて加熱されてその温度が上昇する。温度が上昇した極低温空気は、熱交換器５５（第２の熱交換器）に供給されてさらに加熱される。このように冷凍ポンプによる圧送と熱交換器５１、５２による加熱とによって、液体空気は常温の圧縮空気となって、発電設備６に供給される。タンク４０と発電設備６とを接続すると共に、冷凍ポンプ４３、熱交換器５１、５２が介設された空気の供給ライン４５が設けられている。 Then, when the power generation facility 6 is used to generate electricity, the liquid air stored in the tank 40 is sucked into the refrigeration pump 43, pressurized, and pumped to the subsequent stage. During the pumping by the refrigeration pump 43, the liquid air is warmed by the influence of the outside air of the power generation system 1 and vaporized to become cryogenic air, which is supplied to the heat exchanger 51. Then, the cryogenic air is heated by the heat exchanger 51 and its temperature rises. The cryogenic air whose temperature has risen is supplied to the heat exchanger 55 (second heat exchanger) and further heated. By pumping by the refrigeration pump and heating by the heat exchangers 51 and 52 in this way, the liquid air becomes compressed air at room temperature and is supplied to the power generation facility 6. An air supply line 45 is provided which connects the tank 40 and the power generation facility 6 and is provided with a refrigeration pump 43 and heat exchangers 51 and 52.
続いて発電設備６について述べる。既述したように発電設備６は、膨張機、発電機（第１の発電機）を夫々含んでおり、夫々６１、６２として図２中に示している。膨張機６１に上記の空気の供給ライン４５が接続されている。また、膨張機６１には、極低温空気の供給ライン（第２の空気供給ライン）６３の上流端が接続されている。そして、この極低温空気の供給ライン６３の下流端は、既述のダクト３６に接続されている。既述したように膨張機６１に供給される常温の圧縮空気が降温、降圧されて発電機６２が駆動すると共に極低温空気が生じるが、この膨張機６１にて生じた極低温空気は例えば大気圧よりも高い残圧を有しており、その残圧により供給ライン６３を流れて上記のダクト３６へ流通し、図１で説明したように当該ダクト３６を上流側から流れる常温空気と共にガスタービン発電機３に供給される。 Next, the power generation facility 6 will be described. As described above, the power generation facility 6 includes an expander and a generator (first generator), respectively, and is shown in FIG. 2 as 61 and 62, respectively. The above air supply line 45 is connected to the inflator 61. Further, the expander 61 is connected to the upstream end of the cryogenic air supply line (second air supply line) 63. The downstream end of the cryogenic air supply line 63 is connected to the duct 36 described above. As described above, the compressed air at room temperature supplied to the expander 61 is lowered and stepped down to drive the generator 62 and generate ultra-low temperature air. The extremely low temperature air generated by the expander 61 is, for example, large. It has a residual pressure higher than the atmospheric pressure, and the residual pressure causes it to flow through the supply line 63 and flow to the above duct 36, and as described in FIG. 1, the gas turbine together with the room temperature air flowing from the upstream side of the duct 36. It is supplied to the generator 3.
発電システム１に設けられる各熱交換器について述べる。熱交換器５１は、上記のように空気の供給ライン４４、４５に共に介設され、当該熱交換器５１においては、ＬＮＧ気化器２１で冷却されてタンク４０に向かう極低温空気と、冷凍ポンプ４３から後段に供給される極低温空気との間で熱交換が行われる。また、常温空気が導かれるダクト３６の先にある熱交換器３７と、空気（液体空気を含む）の供給ライン４５にある熱交換器５２との間で、ポンプ５３により熱媒体が移動する循環ライン５４（第１の流体循環ライン）が設けられている。そして、熱交換器３７においての常温空気の冷却、熱交換器５２においての極低温空気の加熱が、循環する当該熱媒体により夫々行われる。図１で説明した冷熱回収設備５は、以上に述べた熱交換器５１、５２、３７により構成される。 Each heat exchanger provided in the power generation system 1 will be described. The heat exchanger 51 is interposed in the air supply lines 44 and 45 as described above, and in the heat exchanger 51, the extremely low temperature air cooled by the LNG vaporizer 21 and heading for the tank 40 and the refrigeration pump. Heat exchange is performed with the extremely low temperature air supplied from 43 to the subsequent stage. Further, a circulation in which the heat medium is moved by the pump 53 between the heat exchanger 37 at the end of the duct 36 through which the normal temperature air is guided and the heat exchanger 52 at the air (including liquid air) supply line 45. A line 54 (first fluid circulation line) is provided. Then, the cooling of the normal temperature air in the heat exchanger 37 and the heating of the extremely low temperature air in the heat exchanger 52 are performed by the circulating heat medium, respectively. The cold heat recovery facility 5 described with reference to FIG. 1 is composed of the heat exchangers 51, 52, and 37 described above.
なお、各熱交換器の熱媒体（熱交換用の流体）としては例えばエチレングリコールなどの不凍液が用いられ、熱交換器５２については熱媒体の氷結による流通の停止を防ぐために、適切な構成なもの（例えば公知のシェルアンドチューブタイプと呼ばれる熱交換器）を用いることができる。また、ＬＡＥＳプラント設備４の空気精留設備４１、ＬＮＧ気化器２１、熱交換器５１は液体空気生成部を構成し、熱交換器５１、５２は気化部を構成する。従って、熱交換器５１は液体空気生成部、気化部に共有される。 An antifreeze solution such as ethylene glycol is used as the heat medium (fluid for heat exchange) of each heat exchanger, and the heat exchanger 52 has an appropriate configuration in order to prevent the flow from being stopped due to freezing of the heat medium. (For example, a known heat exchanger called a shell and tube type) can be used. Further, the air rectification facility 41, the LNG vaporizer 21, and the heat exchanger 51 of the LAES plant facility 4 form a liquid air generating section, and the heat exchangers 51 and 52 form a vaporizing section. Therefore, the heat exchanger 51 is shared by the liquid air generating section and the vaporizing section.
　ところで近年、太陽光発電システムの普及に伴い、ダックカーブと言われる明け方と夕方の電力不足が問題となりつつある。ダックカーブとは、横軸に１日の時間、縦軸に特定の地域における電力の需要量を夫々設定したグラフにおいて、アヒルの形のカーブを描くように電力の需要量の推移が示されることである。そして、このダックカーブの問題とは具体的には、太陽光発電量が昼間にピークを迎えることに対して、電力需要はこの昼間の時間帯から大幅にずれた時間帯（明け方と夕方）にピークを迎える。例えば、明け方として６時～８時、夕方として１８時～２１時に夫々ピークを持つ。このことにより、これらの時間帯の電力不足が懸念される。 By the way, in recent years, with the spread of photovoltaic power generation systems, power shortages at dawn and evening, which are called duck curves, are becoming a problem. The duck curve is a graph in which the horizontal axis is the time of day and the vertical axis is the power demand in a specific area, and the transition of the power demand is shown in a duck-shaped curve. Is. And, specifically, the problem of this duck curve is that the amount of solar power generation peaks in the daytime, while the demand for electricity is in a time zone (dawn and evening) that deviates significantly from this daytime time zone. It reaches its peak. For example, it has peaks from 6:00 to 8:00 at dawn and from 18:00 to 21:00 in the evening. Due to this, there is a concern about power shortage during these times.
上記の発電システム１は、上記のダックカーブの問題が解消されるように動作することができる。以下、昼以降の発電システム１の動作例を説明する。電力需要が少ない昼頃には発電システム１において、液体空気発電（発電設備６による発電）及びガスタービン発電機３への極低温空気の供給が行われていない状態となっている。そして、時間帯が夕方に向かうにつれ、日照量の低下により太陽光発電による発電量は急激に低下する一方で、既述のように電力の需要はピークを迎えるため、大きな発電量を確保する必要が有る。しかし、日中であるため火力発電所２の外気の温度は比較的高い。既述したようにガスタービン発電機３の出力は吸気される空気の温度に影響されるので、この外気のみを用いた場合には、ガスタービン発電機３の出力を十分に向上させることができない恐れが有る。 The power generation system 1 can be operated so as to solve the problem of the duck curve. Hereinafter, an operation example of the power generation system 1 after noon will be described. Around noon when the demand for electric power is low, the power generation system 1 is in a state where liquid air power generation (power generation by the power generation facility 6) and ultra-low temperature air are not supplied to the gas turbine generator 3. Then, as the time zone approaches the evening, the amount of power generated by photovoltaic power generation drops sharply due to the decrease in the amount of sunshine, while the demand for power peaks as described above, so it is necessary to secure a large amount of power generation. There is. However, since it is daytime, the temperature of the outside air of the thermal power plant 2 is relatively high. As described above, the output of the gas turbine generator 3 is affected by the temperature of the intake air. Therefore, when only this outside air is used, the output of the gas turbine generator 3 cannot be sufficiently improved. There is a fear.
そこで、上記の発電システム１において、液体空気発電が開始されると共に、ガスタービン発電機３に接続されるダクト３６への極低温空気の供給が行われ、火力発電所２からの発電量が増大する。このように発電システム１からの発電量が増加する結果として、夕方の電力の需要のピークに対応するように電力が供給され、電力の需給バランスが取られる。その後は電力の需要の低下に対応して、この液体空気発電及び極低温空気の供給が停止する。同様に、人々の行動が活発になる明け方のピークに対応するように、発電システム１を動作することができる。 Therefore, in the above power generation system 1, liquid air power generation is started, and at the same time, ultra-low temperature air is supplied to the duct 36 connected to the gas turbine generator 3, and the amount of power generated from the thermal power plant 2 increases. To do. As a result of the increase in the amount of power generated from the power generation system 1 in this way, power is supplied so as to correspond to the peak of power demand in the evening, and the supply and demand of power is balanced. After that, the liquid air power generation and the supply of cryogenic air will be stopped in response to the decrease in the demand for electric power. Similarly, the power generation system 1 can be operated to accommodate the peak of dawn when people's behavior becomes active.
上述の例では、太陽光発電による発電量が多くなる昼間を避けるように液体空気発電及び極低温空気の供給を行うように示したが、昼間における液体空気発電及び極低温空気の供給が禁止されるものではない。このように需要に応じた任意のタイミングで液体空気発電を行う一方で、ＬＡＥＳプラント設備４による液体空気の生成及び生成した液体空気のタンク４０への供給は、例えば液体空気発電を行っていない時間帯で行う。 In the above example, it is shown that liquid air power generation and cryogenic air supply are performed so as to avoid daytime when the amount of power generated by photovoltaic power generation is large, but liquid air power generation and cryogenic air supply during the daytime are prohibited. It's not something. While the liquid air power generation is performed at an arbitrary timing according to the demand in this way, the generation of the liquid air by the LAES plant equipment 4 and the supply of the generated liquid air to the tank 40 are, for example, the time when the liquid air power generation is not performed. Do it with a belt.
このように発電システム１においては液体空気発電を行うことに加えて、火力発電所２における発電量を増加させることができる。上記の作用例のように外気の温度が比較的高いときには、その外気の温度によって低下している火力発電所２の発電量を回復させ、この外気の温度の影響が抑えられるように高い発電量が得られることになる。このように液体空気発電を行うと同時に、火力発電所２の発電量を増加させることができるため、この発電システム１においては任意のタイミングにおいて高い発電量を得ること、及び発電量を比較的急激に上昇、下降させることができる。従って、発電システム１によれば、電力の需要量の変化に確実性高く対応するように発電を行うことができる。特に、再生可能エネルギーを用いた発電電力が余剰となるような状況が生じて電力貯蔵の必要性が有り、空気温度が高く、ＧＴＣＣ発電が定格の出力を出せないような地域に当該発電システム１を設けることが有効である。 In this way, in the power generation system 1, in addition to performing liquid air power generation, the amount of power generation in the thermal power plant 2 can be increased. When the temperature of the outside air is relatively high as in the above example of action, the amount of power generated by the thermal power plant 2 that has decreased due to the temperature of the outside air is restored, and the amount of power generated is high so that the influence of the temperature of the outside air can be suppressed. Will be obtained. Since the amount of power generated by the thermal power plant 2 can be increased at the same time as the liquid air power generation is performed in this way, the power generation system 1 can obtain a high amount of power generation at an arbitrary timing and the amount of power generation is relatively rapid. Can be raised and lowered. Therefore, according to the power generation system 1, power generation can be performed so as to respond with high certainty to changes in the amount of power demand. In particular, the power generation system 1 is located in an area where there is a need for power storage due to a surplus of power generated using renewable energy, the air temperature is high, and GTCC power generation cannot produce the rated output. It is effective to provide.
なお、火力発電所２における外気の温度が高いときに極低温空気がダクト３６に供給される例を示したが、そのように火力発電所２の外気の温度が高いときのみならず、外気の温度が低いときにも極低温空気のダクト３６への供給により、ガスタービン発電機３に供給される空気の温度を低下させて、ガスタービン発電機３の出力を高めることができる。つまり、火力発電所２の外気の温度が高いときのみに限られることなく、既述した発電システム１の効果が得られる。 An example is shown in which extremely low temperature air is supplied to the duct 36 when the temperature of the outside air in the thermal power plant 2 is high, but not only when the temperature of the outside air in the thermal power plant 2 is high, but also in the outside air. Even when the temperature is low, the temperature of the air supplied to the gas turbine generator 3 can be lowered by supplying the ultra-low temperature air to the duct 36, and the output of the gas turbine generator 3 can be increased. That is, the effect of the power generation system 1 described above can be obtained without being limited to only when the temperature of the outside air of the thermal power plant 2 is high.
また、発電システム１はＬＡＥＳプラント設備４を含むが、一般にプラント設備については耐用年数が４０年と、比較的長いものと考えられている。つまり発電システム１は建設後、比較的長く運用することができることが見込まれるので、ＮａＳ電池などの寿命が短い蓄電池を用いる場合に比べて、有利である。さらに、この発電システム１は空気を用いるため、環境に影響を与える化学物質を使用する必要が無いクリーンなシステムであるという利点も有る。 The power generation system 1 includes the LAES plant equipment 4, but it is generally considered that the plant equipment has a relatively long service life of 40 years. That is, since the power generation system 1 is expected to be able to be operated for a relatively long time after construction, it is advantageous as compared with the case of using a storage battery having a short life such as a NaS battery. Further, since the power generation system 1 uses air, there is an advantage that it is a clean system that does not need to use chemical substances that affect the environment.
また、発電システム１によれば、液体空気を生成するための圧縮空気の冷却を、ＬＮＧ気化器２１においてＬＮＧとの熱交換により行うので、この液体空気の生成に必要な電力を削減できるため、有利である。ただしこのようなＬＮＧの冷熱によらず、例えば液体窒素などを熱媒体として圧縮空気の冷却を行う熱交換器を発電システム１に設けて、液体空気を生成してもよい。 Further, according to the power generation system 1, the compressed air for generating the liquid air is cooled by heat exchange with the LNG in the LNG vaporizer 21, so that the power required for generating the liquid air can be reduced. It is advantageous. However, regardless of the cold heat of LNG, for example, a heat exchanger that cools the compressed air using liquid nitrogen as a heat medium may be provided in the power generation system 1 to generate liquid air.
さらに発電システム１によれば、極低温空気と常温空気とが混合されるダクト３６に熱交換器３７が設けられることで、ガスタービン発電機３に供給される空気の温度がより低い温度となるので、火力発電所２における発電量をより高い値とすることができる。また、発電システム１に関しては、上記の熱交換器３７と熱交換器５２との間で熱媒体が流通する構成としている。つまり、ダクト３６における空気の冷却を行うときの熱移動と、液体空気の気化を行うときの熱移動とが相互に利用される。従って、ダクト３６における空気の冷却と、液体空気の気化との夫々に要するエネルギーが交換されるので、発電システム１の運用コストや用力を削減することができる。 Further, according to the power generation system 1, the heat exchanger 37 is provided in the duct 36 in which the ultra-low temperature air and the normal temperature air are mixed, so that the temperature of the air supplied to the gas turbine generator 3 becomes lower. Therefore, the amount of power generated at the thermal power plant 2 can be set to a higher value. Further, the power generation system 1 has a configuration in which a heat medium is distributed between the heat exchanger 37 and the heat exchanger 52. That is, the heat transfer when cooling the air in the duct 36 and the heat transfer when vaporizing the liquid air are mutually used. Therefore, the energy required for cooling the air in the duct 36 and vaporizing the liquid air is exchanged, so that the operating cost and power of the power generation system 1 can be reduced.
また、発電システム１においては、熱交換器５１において液体空気と、空気との間で熱交換を行っている。従って、液体空気を気化するための熱移動と、空気から液体空気を生成させるための熱移動とが相互に利用される。それにより、発電システム１においては液体空気の生成と、液体空気の気化との夫々に要するエネルギーが交換されるので、当該システムの運用コストや用力を削減することができる。 Further, in the power generation system 1, heat exchange is performed between liquid air and air in the heat exchanger 51. Therefore, the heat transfer for vaporizing the liquid air and the heat transfer for generating the liquid air from the air are mutually utilized. As a result, in the power generation system 1, the energy required for the generation of liquid air and the vaporization of liquid air is exchanged, so that the operating cost and power of the system can be reduced.
なお、空気、液体空気のラインの構成としては既述した例には限られず、例えば冷凍ポンプ４３から供給された液体空気が熱交換器５１を通過せずに熱交換器５２に供給される構成であってもよい。その場合は、ＬＮＧ気化器２１からタンク４０に向かう極低温空気は液体窒素などを熱媒体として用いる熱交換器を利用して液化空気とすればよい。また、熱交換器５１、５２には、液体空気から気化した極低温空気が供給されるものとして説明したが、気化前の液体空気が供給され、当該熱交換器５１または熱交換器５２で液体空気が気化されてもよい。 The configuration of the air and liquid air lines is not limited to the above-described example. For example, the liquid air supplied from the refrigeration pump 43 is supplied to the heat exchanger 52 without passing through the heat exchanger 51. It may be. In that case, the cryogenic air from the LNG vaporizer 21 to the tank 40 may be liquefied air using a heat exchanger that uses liquid nitrogen or the like as a heat medium. Further, although it has been described that the heat exchangers 51 and 52 are supplied with the ultra-low temperature air vaporized from the liquid air, the liquid air before vaporization is supplied and the heat exchanger 51 or the heat exchanger 52 liquids. The air may be vaporized.
続いて、本発明の第２の実施形態の発電システム７について、図３を参照して、第１の実施形態の発電システム１との差異点を中心に説明する。発電システム７においては、発電システム１と異なり、熱交換器３７、熱媒体用のポンプ５３が設けられていない。そして、熱交換器５２には、例えば火力発電所２から比較的高い温度の排気流が供給され、この排気流と極低温空気との間で熱交換されることにより、極低温空気が加熱されて常温空気となり、膨張機６１に供給される。このようにダクト３６において熱交換器３７が設けられない構成とされてもよい。 Subsequently, the power generation system 7 of the second embodiment of the present invention will be described with reference to FIG. 3, focusing on the differences from the power generation system 1 of the first embodiment. Unlike the power generation system 1, the power generation system 7 is not provided with the heat exchanger 37 and the pump 53 for the heat medium. Then, for example, an exhaust flow having a relatively high temperature is supplied to the heat exchanger 52 from the thermal power plant 2, and the extremely low temperature air is heated by heat exchange between the exhaust flow and the extremely low temperature air. It becomes normal temperature air and is supplied to the expander 61. In this way, the duct 36 may be configured so that the heat exchanger 37 is not provided.
以下の説明では特に記載無い限り、外気とはダクト３６の上流側から取込まれ、当該ダクト３６内を流れる常温空気のことであるものとする。膨張機６１から放出される極低温空気は、外気と十分に混ざることで、ガスタービン発電機３に供給される空気の温度を十分に低下させることができる。この発電システム７のダクト３６においては、当該ダクト３６内を流れる外気に極低温空気を確実性高く混合させるために、混合部が介設されている。その混合部は、例えば環状体７１により構成されている。なお、図３中の環状体７１から伸びる鎖線の矢印は、図１の熱交換器３７から伸びる矢印と同様に水の排出路を示しており、環状体７１の周囲の空気が冷却されて生じた水分を除去する。 In the following description, unless otherwise specified, the outside air is defined as room temperature air taken in from the upstream side of the duct 36 and flowing through the duct 36. The extremely low temperature air discharged from the expander 61 can be sufficiently mixed with the outside air to sufficiently lower the temperature of the air supplied to the gas turbine generator 3. In the duct 36 of the power generation system 7, a mixing portion is provided in order to mix the cryogenic air flowing in the duct 36 with high certainty. The mixing portion is composed of, for example, an annular body 71. The arrow of the chain line extending from the annular body 71 in FIG. 3 indicates a water discharge path like the arrow extending from the heat exchanger 37 of FIG. 1, and is generated by cooling the air around the annular body 71. Remove the water.
環状体７１の縦断側面図、横断平面図である図４、図５を夫々参照しながら説明を続ける。ダクト３６の流路方向に見て、環状体７１の中央部には貫通孔７２が形成されており、当該貫通孔７２は、外気の流路をなす。環状体７１におけるダクト３６の下流側に向かう正面には、当該環状体７１の周方向に沿って等間隔を空けて複数の吐出口７３が設けられている。つまり、当該周方向の互いに異なる位置に各吐出口７３が開口している。極低温空気の供給ライン６３は、各吐出口７３に極低温空気を供給できるようにその下流側が分岐して環状体７１に接続されている。例えば各吐出口７３から、ダクト３６の下流側且つ平面視環状体７１の中央部に向かうように極低温空気が吐出される。このように貫通孔７２を通過する外気に互いに離れた位置から極低温空気が供給されることで、極低温空気の外気への混合性を高くすることができる。 The description will be continued with reference to FIGS. 4 and 5 which are a longitudinal side view and a cross-sectional plan view of the annular body 71, respectively. A through hole 72 is formed in the central portion of the annular body 71 when viewed in the direction of the flow path of the duct 36, and the through hole 72 forms a flow path for the outside air. A plurality of discharge ports 73 are provided on the front surface of the annular body 71 toward the downstream side of the duct 36 at equal intervals along the circumferential direction of the annular body 71. That is, the discharge ports 73 are opened at different positions in the circumferential direction. The downstream side of the cryogenic air supply line 63 is branched and connected to the annular body 71 so that the cryogenic air can be supplied to each discharge port 73. For example, from each discharge port 73, cryogenic air is discharged toward the downstream side of the duct 36 and toward the central portion of the plan view annular body 71. By supplying the cryogenic air from positions separated from each other by the outside air passing through the through hole 72 in this way, the mixing property of the cryogenic air with the outside air can be improved.
ところで、ダクト３６内を流れる外気に上記の極低温空気を確実に混合させるための混合部としては上記の構成には限られず、図６に示すように、当該混合部としてダクト３６内にノズル８１が設けられていてもよい。このノズル８１は例えば多孔式ノズル、即ち吐出口を多数備えるノズルである。ノズル８１の上流側は、極低温空気の供給ライン６３に接続されている。そしてノズル８１は、供給ライン６３から供給された極低温空気を、ダクト３６内の流路の下流側に向かって、流路方向に沿って当該ノズル８１から放射状に拡散するようにスプレーすることで、極低温空気の外気への混合性が高くなる、即ち極低温空気が外気に対して均一に分散するように構成されている。なお、ノズル８１及び上記の環状体７１において、極低温空気はそれ自体が持つ圧力により、ノズル８１の吐出口、環状体７１の吐出口７３から夫々噴出する。 By the way, the mixing portion for reliably mixing the above-mentioned cryogenic air flowing in the duct 36 is not limited to the above configuration, and as shown in FIG. 6, the nozzle 81 is inside the duct 36 as the mixing portion. May be provided. The nozzle 81 is, for example, a porous nozzle, that is, a nozzle having a large number of discharge ports. The upstream side of the nozzle 81 is connected to the cryogenic air supply line 63. Then, the nozzle 81 sprays the ultra-low temperature air supplied from the supply line 63 toward the downstream side of the flow path in the duct 36 so as to radiate from the nozzle 81 along the flow path direction. , The ultra-low temperature air is highly mixed with the outside air, that is, the ultra-low temperature air is configured to be uniformly dispersed with respect to the outside air. In the nozzle 81 and the annular body 71, the cryogenic air is ejected from the discharge port of the nozzle 81 and the discharge port 73 of the annular body 71, respectively, due to the pressure of the nozzle 81 and the annular body 71.
さらに、環状体７１の周囲の空気が冷却されて生じた水分は、図６に示すようにダクト３６に設けられた複数の波板７４により除去することができ、波板７４に水滴が当ることで効率的に水分を取り除くことが可能となる。つまり、図６においてダクト３６内のノズル８１の下流側に、水分の除去部として波板７４を設けた例を示しているが、図４の環状体７１を設けたダクト３６内においても環状体７１の下流側に波板７４を設け、空気に随伴する水滴が波板７４に当り、落下することでダクト３６内からダクト３６外へ排出されるようにすることができる。このように水滴を除去するのは、ガスタービン発電機３に内蔵されるエアコンプレッサのインペラが、多量の水滴が当ることによって摩耗することを防ぐためである。 Further, the moisture generated by cooling the air around the annular body 71 can be removed by a plurality of corrugated plates 74 provided in the duct 36 as shown in FIG. 6, and water droplets hit the corrugated plate 74. It is possible to remove water efficiently. That is, although FIG. 6 shows an example in which a corrugated plate 74 is provided as a moisture removing portion on the downstream side of the nozzle 81 in the duct 36, the annular body is also provided in the duct 36 provided with the annular body 71 in FIG. A corrugated plate 74 is provided on the downstream side of the 71, and water droplets accompanying the air hit the corrugated plate 74 and fall to be discharged from the inside of the duct 36 to the outside of the duct 36. The reason for removing the water droplets in this way is to prevent the impeller of the air compressor built in the gas turbine generator 3 from being worn by being hit by a large amount of water droplets.
続いて、本発明の第３の実施形態の発電システム８２について、発電システム１との差異点を中心に、図７を参照して説明する。なお、発電システム８２において、発電システム１と同様に構成されている箇所のうちの一部については、図示を省略している。この発電システム８２においては、極低温空気の供給ライン６３に熱交換器８３（第３の熱交換器）が介設されている。そして、熱媒体の循環ライン５４と一部が共通であると共に、熱交換器３７、８３が介設される熱媒体の循環ライン８４（第２の流体循環ライン）が設けられる。より詳しく循環ライン５４、８４の構成を説明すると、循環ライン５４における熱交換器３７から熱交換器５２へ熱媒体を送るポンプ５３の下流側の部位が分岐する。この分岐したラインには熱交換器８３が介設されており、当該分岐したラインの端部は、循環ライン５４のうち熱交換器５２から熱交換器３７へ向けて熱媒体が流通する部位に接続されている。この分岐したラインが循環ライン８４を構成する。 Subsequently, the power generation system 82 of the third embodiment of the present invention will be described with reference to FIG. 7, focusing on the differences from the power generation system 1. In the power generation system 82, some of the parts configured in the same manner as the power generation system 1 are not shown. In the power generation system 82, a heat exchanger 83 (third heat exchanger) is interposed in the cryogenic air supply line 63. A heat medium circulation line 84 (second fluid circulation line) is provided, which is partly in common with the heat medium circulation line 54 and in which heat exchangers 37 and 83 are interposed. Explaining the configuration of the circulation lines 54 and 84 in more detail, the portion of the circulation line 54 on the downstream side of the pump 53 that sends the heat medium from the heat exchanger 37 to the heat exchanger 52 branches. A heat exchanger 83 is interposed in this branched line, and the end of the branched line is a portion of the circulation line 54 where the heat medium flows from the heat exchanger 52 to the heat exchanger 37. It is connected. This branched line constitutes the circulation line 84.
発電システム８２の構成では、熱交換器８３により、ダクト３６に供給される前に極低温空気が例えば低温空気になるように暖められる。このような構成とするのは、極低温空気の温度が低すぎることにより、ダクト３６における極低温空気の供給ライン６３との接続部で、ダクト３６を流れる外気（ダクト３６の上流から取り込まれた常温空気）が氷結し、極低温空気と外気とが十分に混ざらなくなることを確実に防ぐためである。 In the configuration of the power generation system 82, the heat exchanger 83 warms the cryogenic air to, for example, cold air before it is supplied to the duct 36. In such a configuration, the temperature of the extremely low temperature air is too low, so that the outside air flowing through the duct 36 (taken in from the upstream of the duct 36) at the connection portion of the duct 36 with the supply line 63 of the extremely low temperature air. This is to prevent the (normal temperature air) from freezing and preventing the extremely low temperature air from being sufficiently mixed with the outside air.
また、図８は、既述の発電システム１の変形例を示している。空気の供給ライン４５において熱交換器５１と冷凍ポンプ４３との間にバルブ８５が介設されており、バルブ８５と冷凍ポンプ４３との間には液体空気の還流用ライン８６の一端が接続されている。還流用ライン８６の他端はバルブ８７を介して、液体空気のタンク４０に接続されている。冷凍ポンプ４３は常時動作して、タンク４０から液体空気を供給ライン６３の後段側へ向けて供給する。 Further, FIG. 8 shows a modified example of the power generation system 1 described above. A valve 85 is interposed between the heat exchanger 51 and the refrigeration pump 43 in the air supply line 45, and one end of the liquid air recirculation line 86 is connected between the valve 85 and the refrigeration pump 43. ing. The other end of the reflux line 86 is connected to the liquid air tank 40 via a valve 87. The refrigerating pump 43 always operates to supply liquid air from the tank 40 toward the rear stage side of the supply line 63.
液体空気発電を行わないときは、バルブ８５を微開にすると共にバルブ８７が開かれた状態となり、液体空気はタンク４０に還流されると共に、保冷循環として送出系統（熱交換器５１、５２ひいては膨張機６１）へ送られる。液体空気発電を行うときは、バルブ８５が開かれると共にバルブ８７が閉じられた状態となり、液体空気はタンク４０へは送られず、熱交換器５１及び膨張機６１へ供給される。従って、バルブ８５、８７は、液体空気の主な供給先を熱交換器５１とタンク４０との間で切り替える切り替え部を構成する。このような構成とするのは、冷凍ポンプ４３、熱交換器５１、５２、膨張機６１及び機器回りの配管に常時少量の液体空気が送られるようにすることで、当該機器及び配管の温度を低温に維持するためである。それにより、これらの機器及び配管の温度変化による動作性能の変動を確実に防ぐことができる。 When liquid air power generation is not performed, the valve 85 is slightly opened and the valve 87 is opened, the liquid air is returned to the tank 40, and the delivery system ( heat exchangers 51 and 52, and thus the heat exchangers 51 and 52) is sent as a cold insulation circulation. It is sent to the inflator 61). When performing liquid air power generation, the valve 85 is opened and the valve 87 is closed, and the liquid air is not sent to the tank 40 but is supplied to the heat exchanger 51 and the expander 61. Therefore, the valves 85 and 87 form a switching unit that switches the main supply destination of the liquid air between the heat exchanger 51 and the tank 40. In such a configuration, a small amount of liquid air is constantly sent to the refrigeration pump 43, the heat exchangers 51 and 52, the expander 61, and the piping around the equipment, so that the temperature of the equipment and the piping can be adjusted. This is to keep the temperature low. As a result, fluctuations in operating performance due to temperature changes in these devices and pipes can be reliably prevented.
なお、今回開示された実施形態は、全ての点で例示であって制限的なものではないと考えられるべきである。上記の各実施形態は、添付の特許請求の範囲及びその趣旨を逸脱することなく、様々な形態で省略、置換、変更、組み合わせが行われてもよい。 It should be noted that the embodiments disclosed this time are exemplary in all respects and are not considered to be restrictive. Each of the above embodiments may be omitted, replaced, changed, or combined in various forms without departing from the scope and purpose of the appended claims.
１　　　　　発電システム
２　　　　　火力発電所
２１　　　　ＬＮＧ気化器
３　　　　　ガスタービン発電機
３６　　　　ダクト
３７　　　　熱交換器
４　　　　　ＬＡＥＳプラント設備
６１　　　　膨張機
６３　　　　極低温空気の供給ライン
 

  1 Power generation system 2 Thermal power plant 21 LNG vaporizer 3 Gas turbine generator 36 Duct 37 Heat exchanger 4 LAES plant equipment 61 Expander 63 Very low temperature air supply line

Claims (10)

  1. 　空気の圧縮及び冷却を行い、液体空気を生成する液体空気生成部と、
    　前記液体空気を貯蔵する貯蔵部と、
    　前記貯蔵部から供給された前記液体空気を気化させて圧縮空気を生成する気化部と、
    　前記気化部から供給された圧縮空気を膨張させる膨張機と、
    　前記膨張機における空気の膨張により駆動する第１の発電機と、
    　前記膨張機において膨張して冷却された空気を、第２の発電機であるガスタービン発電機と前記ガスタービン発電機に空気を供給する第１の空気供給ラインとを備える発電所における前記第１の空気供給ラインに供給して前記ガスタービン発電機が吸気する空気の温度を低下させるために、当該第１の空気供給ラインと前記膨張機とを接続する第２の空気供給ラインと、
    を備える発電システム。     A liquid air generator that compresses and cools air to generate liquid air,
    The storage unit that stores the liquid air and
    A vaporization unit that vaporizes the liquid air supplied from the storage unit to generate compressed air,
    An expander that expands the compressed air supplied from the vaporization unit,
    A first generator driven by the expansion of air in the expander,
    The first in a power plant including a gas turbine generator which is a second generator and a first air supply line for supplying air to the gas turbine generator by expanding and cooling the air in the expander. A second air supply line connecting the first air supply line and the expander in order to lower the temperature of the air supplied to the air supply line of the gas turbine generator and taken in by the gas turbine generator.
    Power generation system equipped with.
  2. 　前記第１の空気供給ラインには前記ガスタービン発電機へ供給される空気の温度を低下させるための第１の熱交換器が設けられ、
    　前記気化部は、前記液体空気または当該液体空気から生成した空気を加熱するための第２の熱交換器を備え、
    　当該第１の熱交換器に供給される空気、当該第２の熱交換器に供給される液体空気または空気の各々と熱交換するための熱交換用の流体が、前記第１の熱交換器と前記第２の熱交換器との間で移動するように、当該流体を循環させる第１の流体循環ラインが設けられる請求項１記載の発電システム。     The first air supply line is provided with a first heat exchanger for lowering the temperature of the air supplied to the gas turbine generator.
    The vaporizer includes a second heat exchanger for heating the liquid air or air generated from the liquid air.
    The heat exchange fluid for heat exchange with each of the air supplied to the first heat exchanger, the liquid air supplied to the second heat exchanger, or the air is the first heat exchanger. The power generation system according to claim 1, wherein a first fluid circulation line for circulating the fluid is provided so as to move between the second heat exchanger and the second heat exchanger.
  3. 　前記第２の空気供給ラインにおいて、前記膨張機から供給される空気の温度を上昇させるための第３の熱交換器が設けられ、
    　前記第１の熱交換器と当該第３の熱交換器との間で前記熱交換用の流体が移動するように、当該流体を循環させる第２の流体循環ラインが設けられる請求項２記載の発電システム。     In the second air supply line, a third heat exchanger for raising the temperature of the air supplied from the expander is provided.
    The second aspect of claim 2, wherein a second fluid circulation line for circulating the fluid is provided so that the fluid for heat exchange moves between the first heat exchanger and the third heat exchanger. Power generation system.
  4. 　前記第１の空気供給ラインにおける空気流に、前記第２の空気供給ラインから供給される空気を混合させるための混合部が設けられる請求項１記載の発電システム。 The power generation system according to claim 1, wherein a mixing unit for mixing the air supplied from the second air supply line is provided in the air flow in the first air supply line.
  5. 　前記混合部は、当該第１の空気供給ラインの空気流に、前記第２の空気供給ラインから供給された空気をスプレーするノズルである請求項４記載の発電システム。 The power generation system according to claim 4, wherein the mixing unit is a nozzle that sprays air supplied from the second air supply line into the air flow of the first air supply line.
  6. 　前記混合部は、前記第１の空気供給ラインの流路方向に見て、中央に上流側から供給された空気を下流側に供給する貫通孔を備えた環状体として構成され、
    　当該環状体の周方向の互いに異なる位置に前記第２の空気供給ラインから供給される空気を各々吐出する吐出口が設けられる請求項５記載の発電システム。     The mixing portion is configured as an annular body having a through hole for supplying air supplied from the upstream side to the downstream side in the center when viewed in the flow path direction of the first air supply line.
    The power generation system according to claim 5, wherein discharge ports for discharging air supplied from the second air supply line are provided at positions different from each other in the circumferential direction of the annular body.
  7. 　前記液体空気生成部は、空気を圧縮して圧縮空気を生成する圧縮機と、
    　燃料として天然ガスを前記ガスタービン発電機に供給するために、液化天然ガスを加熱して気化させる液化天然ガス気化器と、を含み、
    前記液化天然ガス気化器における前記液化天然ガスと、前記圧縮機により生成した圧縮空気との間における熱交換により、当該液化天然ガスの加熱と、当該圧縮空気の冷却とが行われる請求項１記載の発電システム。     The liquid air generator includes a compressor that compresses air to generate compressed air, and
    A liquefied natural gas vaporizer that heats and vaporizes liquefied natural gas in order to supply natural gas as fuel to the gas turbine generator.
    The first aspect of claim 1, wherein the liquefied natural gas is heated and the compressed air is cooled by heat exchange between the liquefied natural gas in the liquefied natural gas vaporizer and the compressed air generated by the compressor. Power generation system.
  8. 前記液体空気生成部及び前記気化部は、共通する第４の熱交換器を備え、
    前記液化天然ガス気化器により冷却された圧縮空気と、前記貯蔵部から前記膨張機へ向けて供給される液体空気または当該液体空気から生成した空気との間で熱交換が行われることで、前記圧縮空気の冷却と前記液体空気または前記空気の加熱とが行われる請求項７記載の発電システム。     The liquid air generating section and the vaporizing section include a common fourth heat exchanger.
    The compressed air cooled by the liquefied natural gas vaporizer and the liquid air supplied from the storage unit to the expander or the air generated from the liquid air exchange heat with each other. The power generation system according to claim 7, wherein the compressed air is cooled and the liquid air or the air is heated.
  9. 前記貯蔵部と前記気化部とを接続する液体空気の供給ラインに設けられ、前記気化部へ液体空気を供給するためのポンプと、
    前記ポンプの下流側で前記液体空気の供給ラインから分岐して設けられ、前記貯蔵部へ当該液体空気を還流させる還流ラインと、
    前記気化部と前記貯蔵部との間で、前記ポンプによる前記液体空気の供給先を切り替える切り替え部と、
    が設けられる請求項１記載の発電システム。     A pump provided in the liquid air supply line connecting the storage unit and the vaporization unit to supply the liquid air to the vaporization unit.
    A recirculation line that is branched from the liquid air supply line on the downstream side of the pump and returns the liquid air to the storage unit.
    A switching unit that switches the supply destination of the liquid air by the pump between the vaporization unit and the storage unit, and a switching unit.
    The power generation system according to claim 1, wherein the power generation system is provided.
  10. 　空気の圧縮及び冷却を行い、液体空気を生成する工程と、
    　前記液体空気を貯蔵部に貯蔵する工程と、
    　前記貯蔵部から供給された前記液体空気を気化部により気化させて圧縮空気を生成する工程と、
    　前記気化部から供給された圧縮空気を膨張機により膨張させる工程と、
    　前記膨張機における空気の膨張によって第１の発電機を駆動する工程と、
    　第２の発電機であるガスタービン発電機と前記ガスタービン発電機に空気を供給する第１の空気供給ラインとを備える発電所における前記ガスタービン発電機が吸気する空気の温度を低下させるために、前記膨張機において膨張して冷却された空気を前記第１の空気供給ラインと前記膨張機とを接続する第２の空気供給ラインに供給する工程と、
    を備える発電方法。

          The process of compressing and cooling air to generate liquid air,
    The process of storing the liquid air in the storage unit and
    A step of vaporizing the liquid air supplied from the storage unit by the vaporization unit to generate compressed air, and
    A process of expanding the compressed air supplied from the vaporization unit by an expander, and
    The process of driving the first generator by the expansion of air in the expander, and
    To reduce the temperature of the air taken in by the gas turbine generator in a power plant including a gas turbine generator which is a second generator and a first air supply line that supplies air to the gas turbine generator. A step of supplying the expanded and cooled air in the inflator to the second air supply line connecting the first air supply line and the inflator.
    Power generation method equipped with.
PCT/JP2019/025925 2019-06-28 2019-06-28 Power generation system and power generation method WO2020261559A1 (en)

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JPH04127850A (en) * 1990-09-19 1992-04-28 Central Res Inst Of Electric Power Ind Liquid air storage power generating system
JPH08312374A (en) * 1995-05-22 1996-11-26 Mitsubishi Heavy Ind Ltd Inlet air cooling device of gas turbine
JPH10238366A (en) * 1996-12-24 1998-09-08 Hitachi Ltd Energy storage type gas turbine power generation system
JP2001193483A (en) * 2000-01-12 2001-07-17 Hitachi Ltd Gas turbine system
US20170058768A1 (en) * 2014-04-11 2017-03-02 Mitsubishi Hitachi Power Systems Europe Gmbh Method And Device For Storing And Recovering Energy

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04127850A (en) * 1990-09-19 1992-04-28 Central Res Inst Of Electric Power Ind Liquid air storage power generating system
JPH08312374A (en) * 1995-05-22 1996-11-26 Mitsubishi Heavy Ind Ltd Inlet air cooling device of gas turbine
JPH10238366A (en) * 1996-12-24 1998-09-08 Hitachi Ltd Energy storage type gas turbine power generation system
JP2001193483A (en) * 2000-01-12 2001-07-17 Hitachi Ltd Gas turbine system
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