WO2009096028A1 - Système de fourniture de puissance motrice pour centrale, procédé pour son exploitation et procédé pour sa modification - Google Patents

Système de fourniture de puissance motrice pour centrale, procédé pour son exploitation et procédé pour sa modification Download PDF

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Publication number
WO2009096028A1
WO2009096028A1 PCT/JP2008/051573 JP2008051573W WO2009096028A1 WO 2009096028 A1 WO2009096028 A1 WO 2009096028A1 JP 2008051573 W JP2008051573 W JP 2008051573W WO 2009096028 A1 WO2009096028 A1 WO 2009096028A1
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WIPO (PCT)
Prior art keywords
plant
steam
turbine equipment
power supply
gas turbine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2008/051573
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English (en)
Japanese (ja)
Inventor
Yukinori Katagiri
Kouichi Chino
Yasuo Fukushima
Mutsumi Horitsugi
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Hitachi Ltd
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Hitachi Ltd
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Priority to JP2009506827A priority Critical patent/JP4910042B2/ja
Priority to PCT/JP2008/051573 priority patent/WO2009096028A1/fr
Publication of WO2009096028A1 publication Critical patent/WO2009096028A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
    • F01K17/02—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic
    • F01K17/025—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic in combination with at least one gas turbine, e.g. a combustion gas turbine
    • 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
    • F01K23/101—Regulating means specially adapted therefor
    • 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
    • F25J1/0022—Hydrocarbons, e.g. natural gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
    • F25J1/0047—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle
    • F25J1/0052—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle by vaporising a liquid refrigerant stream
    • F25J1/0055—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle by vaporising a liquid refrigerant stream originating from an incorporated cascade
    • 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
    • F25J1/0211—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 a multi-component refrigerant [MCR] fluid in a closed vapor compression cycle
    • F25J1/0212—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 a multi-component refrigerant [MCR] fluid in a closed vapor compression cycle as a single flow MCR 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
    • 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
    • F25J1/0257—Construction and layout of liquefaction equipments, e.g. valves, machines
    • F25J1/0262—Details of the cold heat exchange system
    • F25J1/0264—Arrangement of heat exchanger cores in parallel with different functions, e.g. different cooling streams
    • F25J1/0265—Arrangement of heat exchanger cores in parallel with different functions, e.g. different cooling streams comprising cores associated exclusively with the cooling of a refrigerant stream, e.g. for auto-refrigeration or economizer
    • F25J1/0268—Arrangement of heat exchanger cores in parallel with different functions, e.g. different cooling streams comprising cores associated exclusively with the cooling of a refrigerant stream, e.g. for auto-refrigeration or economizer using a dedicated refrigeration means
    • 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
    • F25J1/0279—Compression of refrigerant or internal recycle fluid, e.g. kind of compressor, accumulator, suction drum etc.
    • F25J1/0281—Compression of refrigerant or internal recycle fluid, e.g. kind of compressor, accumulator, suction drum etc. characterised by the type of prime driver, e.g. hot gas expander
    • F25J1/0284—Electrical motor as the prime mechanical driver
    • 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
    • F25J2240/70—Steam turbine, e.g. used in a Rankine 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
    • F25J2240/00—Processes or apparatus involving steps for expanding of process streams
    • F25J2240/80—Hot exhaust gas turbine combustion engine
    • F25J2240/82—Hot exhaust gas turbine combustion engine with waste heat recovery, e.g. in a combined cycle, i.e. for generating steam used in a Rankine 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
    • F25J2270/00—Refrigeration techniques used
    • F25J2270/12—External refrigeration with liquid vaporising 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
    • F25J2270/00—Refrigeration techniques used
    • F25J2270/60—Closed external refrigeration cycle with single component refrigerant [SCR], e.g. C1-, C2- or C3-hydrocarbons
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P80/00—Climate change mitigation technologies for sector-wide applications
    • Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier
    • Y02P80/15—On-site combined power, heat or cool generation or distribution, e.g. combined heat and power [CHP] supply

Definitions

  • the present invention relates to a power supply system for a plant that supplies power to a plant, and an operation method and a modification method thereof.
  • An example of this type of plant is a natural gas liquefaction plant that purifies and liquefies natural gas extracted from a gas field.
  • this plant continuous and stable power supply is indispensable in order to maintain the quality of natural gas and maximize the production volume.
  • the necessary power is supplied within the plant by using a combined cycle facility in order to cope with constraints such as the location of the well being located in an area away from other industrial facilities. There is something.
  • combined cycle equipment has the characteristic that the power generation output fluctuates due to daytime and nighttime or annual atmospheric temperature fluctuations.
  • the gas turbine output is relatively decreased during warm weather such as daytime or summer, because the atmospheric temperature relatively increases as compared with other times and seasons.
  • a method has been proposed in which water is sprayed on the gas turbine intake air during warm weather to increase the gas turbine output (see JP 2003-206750 A).
  • the cooling performance of a heat exchanger or the like used for cooling natural gas or refrigerant is relatively improved during cold weather. Therefore, the required power of the compressor that pressurizes and compresses the refrigerant is reduced, and the power required by the plant tends to be reduced. This characteristic is opposite to the characteristic of the combined cycle facility in which the output increases in cold weather, and the efficiency decrease due to surplus steam during cold weather becomes even more remarkable.
  • An object of the present invention is to provide a power supply system for a plant that can suppress a decrease in efficiency when the atmospheric temperature is lowered while supplying continuous and stable power to the plant.
  • the present invention provides a gas turbine facility driven by combustion gas obtained by burning fuel and intake air, an exhaust heat recovery boiler that generates steam from exhaust gas from the gas turbine facility, Steam turbine equipment driven by steam from the exhaust heat recovery boiler, extraction piping for supplying steam extracted from the steam turbine facility to the steam utilization facility, extraction flow rate control valve provided in the extraction piping, air
  • the output command value (MWD) from the plant that changes with the daily change in temperature is lower than the rated output value (MWD0) of the gas turbine equipment and the steam turbine equipment
  • the total output of the gas turbine equipment and the steam turbine equipment ( MW) is based on a deviation ( ⁇ MW) between the rated output value (MWD0) and the output command value (MWD) so that the output command value (MWD) approaches.
  • a control device for determining a steam flow rate (GblsD) extracted from the steam turbine equipment via the extraction piping and setting the extraction flow rate control valve at an opening degree (CVbls) determined based on the steam flow rate (GblsD).
  • the gas turbine equipment can be operated near the rating even when the atmospheric temperature decreases, the efficiency of the power supply system for the plant can be improved.
  • FIG. 1 is a schematic view of a natural gas liquefaction plant provided with a plant power supply system according to a first embodiment of the present invention.
  • the natural gas liquefaction plant is a facility for producing liquefied natural gas (LNG) 48 by refining and liquefying natural gas extracted from a gas field.
  • the natural gas liquefaction plant (hereinafter referred to as appropriate plant) shown in this figure mainly includes a main heat exchanger 40, a gas-liquid separator 41 (separator), a first refrigeration cycle system (mixed refrigerant refrigeration cycle system) 60, A second refrigeration cycle system (propane refrigeration cycle system) 61 is provided.
  • the main heat exchanger 40 cools and liquefies natural gas (source gas 49) from which impurities have been separated by a natural gas refining facility (not shown) with the first refrigerant from the first refrigeration cycle system 60. .
  • a natural gas introduction pipe 62 from a natural gas purification facility is introduced.
  • the natural gas introduction pipe 62 circulates the source gas 49 and passes through the main heat exchanger 40 and extends to the outside of the main heat exchanger 40.
  • the main heat exchanger 40 is connected to a gas-liquid separator 41 into which the first refrigerant cooled by the first refrigeration cycle system 60 is introduced.
  • the liquid phase portion and the gas phase portion of the first refrigerant separated by the gas-liquid separator 41 are separately led to the main heat exchanger 40 and used for cooling the raw material gas 49.
  • the raw material gas 49 supplied from the natural gas refining facility is cooled by the first refrigerant when passing through the main heat exchanger 40, and then further cooled to pass through the expansion valve 65 to liquefy natural gas 48. It becomes.
  • the first refrigeration cycle system (mixed refrigerant refrigeration cycle system) 60 compresses and cools the first refrigerant to be supplied to the main heat exchanger 40.
  • the working fluid (first refrigerant) of the first refrigeration cycle system 60 in the present embodiment is a mixed refrigerant (MCR) mainly composed of methane, ethane, and propane.
  • MCR mixed refrigerant
  • the first refrigeration cycle system 60 cools the first refrigerant compressed by the low-pressure refrigerant compressor 10a and the low-pressure refrigerant compressor 10a that compresses the first refrigerant used for cooling the natural gas in the main heat exchanger 40.
  • An intermediate cooler 47a a high-pressure refrigerant compressor 10b that compresses the first refrigerant cooled by the intermediate cooler 47a, a post-cooler 47b that cools the first refrigerant compressed by the high-pressure refrigerant compressor 10b, and a plant
  • an electric motor 16 that drives the low-pressure refrigerant compressor 10a and the high-pressure refrigerant compressor 10b with electric power supplied from a power supply system 80 (described later) via a power system 18 (see FIG. 2).
  • the inlet of the low-pressure refrigerant compressor 10a is connected to the main heat exchanger 40.
  • the outlet of the post-cooler 47b is connected to the gas-liquid separator 41 after passing through the cooler group (the first cooler 43, the second cooler 44, and the third cooler 45) of the second refrigeration cycle system 61. ing.
  • the low-pressure refrigerant compressor 10a and the high-pressure refrigerant compressor 10b are collectively referred to as the first refrigerant compressor 10 and the gas-liquid separator 41 is cooled through the cooler group of the second refrigeration cycle system 61.
  • the first refrigerant is subjected to gas-liquid separation, and is connected to the outlet of the third cooler 45.
  • the gas-liquid separator 41 supplies the separated liquid phase portion and gas phase portion of the first refrigerant to the main heat exchanger 40 separately.
  • the second refrigeration cycle system (propane refrigeration cycle system) 61 compresses and cools the second refrigerant for cooling the first refrigerant, and cools the first refrigerant from the first refrigeration cycle system 60 with the second refrigerant.
  • the second refrigeration cycle system 61 includes a refrigerant compressor (second refrigerant compressor) 11, an electric motor 17, a condenser 46, a liquid receiver 42, a first cooler 43, a second cooler 44, and A third cooler 45 is provided.
  • the working fluid (second refrigerant) of the second refrigeration cycle system 61 in the present embodiment is propane.
  • the refrigerant compressor 11 compresses the second refrigerant and is driven by an electric motor 17 connected to a drive shaft.
  • the refrigerant compressor 11 has a high pressure stage portion connected to the first cooler 43, an intermediate pressure stage portion connected to the second cooler 44, and a low pressure stage portion connected to the third cooler 45.
  • the second refrigerant (gas) supplied from the coolers 43, 44, 45 to the refrigerant compressor 11 via this connection path cools the second refrigerant in the refrigerant compressor 11.
  • Electric power of the electric motor 17 is supplied from a power supply system 80 via an electric power system 18 (see FIG. 2).
  • the condenser 46 is connected to the outlet of the refrigerant compressor 11 and cools and condenses the second refrigerant compressed by the refrigerant compressor 11.
  • the liquid receiver 42 is connected to the outlet of the condenser 46 and receives the second refrigerant condensed by the condenser 46.
  • a second refrigerant condensed and liquefied is stored in the liquid receiver 42.
  • the first cooler 43 is connected to the outlet of the liquid receiver 42, and receives the second refrigerant that has been expanded under reduced pressure and reduced in temperature via an expansion valve.
  • the second cooler 44 is connected to the first cooler 43, and receives the second refrigerant further reduced in temperature via the expansion valve.
  • the third cooler 45 is connected to the second cooler 44, and receives the second refrigerant whose temperature has been further reduced via the expansion valve.
  • first cooler 43 Inside the first cooler 43, the second cooler 44, and the third cooler 45, a pipe through which the first refrigerant (mixed refrigerant) flows is arranged.
  • the second refrigerant (propane) received in the coolers 43, 44, and 45 takes heat from the first refrigerant and evaporates, thereby cooling the first refrigerant stepwise.
  • the mixed refrigerant (first refrigerant) is cooled to about ⁇ 35 ° C., for example, when it passes through the third cooler 45 and supplied to the gas-liquid separator 41.
  • coolant is determined by the heat exchange amount of the condenser 46, the intermediate
  • the blower air volume and cooling water volume of these heat exchangers 46, 47a, 47b are increased, and the temperature and pressure of the refrigerant are controlled to be constant.
  • the power required by the entire plant or the first refrigerant compressor 10 and the second refrigerant compressor 11 (output command value MWD described later) also changes.
  • FIG. 2 is a schematic diagram of a power supply system for a plant according to the first embodiment of the present invention.
  • the plant power supply system (power supply system) 80 shown in this figure includes a gas turbine facility 20, an intake spray device 6, a water amount adjustment valve 8, a water tank 31, an exhaust heat recovery boiler 3, and a steam turbine facility. 25, a condenser 35, a water production device 30, a power system 18, and a control device 110.
  • the gas turbine facility 20 includes a turbine 1, a compressor 2, and a combustor (not shown).
  • the intake air and fuel compressed by the compressor 2 are burned by the combustor to generate combustion gas.
  • the turbine 1 is rotationally driven by the combustion gas.
  • a generator 14 is connected to the turbine 1 and supplies power to the plant via the power system 18.
  • the power system 18 supplies the power generated by the power supply system to the plant, and the main power supply destination is the motor 16 that drives the first refrigerant compressor and the second refrigerant compressor 11. There is a motor 17 to perform.
  • An intake spray device 6 and a temperature measuring device 7 are provided on the upstream side of the compressor 2.
  • the intake spray device 6 sprays water on the intake air of the gas turbine equipment 20, and is connected to the water tank 31 via the spray water pipe 63.
  • the spray water pipe 63 is provided with a water amount adjustment valve 8 that adjusts the amount of water supplied to the intake spray device 6 according to the atmospheric temperature, and a water transfer pump 32 that pumps up water in the water tank 31.
  • the opening degree of the water amount adjustment valve 8 in the present embodiment is adjusted by an opening degree command (CVwac) output from a combined cycle auxiliary control unit 101 (described later).
  • CVwac opening degree command
  • pure water is preferable in order to suppress corrosion and the like of piping.
  • the temperature measuring device 7 measures the atmospheric temperature, and outputs the measured atmospheric temperature Ta to the combined cycle auxiliary control unit 101.
  • the water tank 31 stores water supplied to the intake spray device 6. Pure water is supplied from the water production apparatus 30 to the water tank 31 of the present embodiment. In addition to the water production apparatus 30, the condenser 35 and other supply sources may be used as the pure water supply source.
  • the exhaust heat recovery boiler 3 heats the water supplied from the condenser 35 via the makeup water pump 34 with the exhaust gas from the gas turbine facility 20 to generate steam.
  • the exhaust heat recovery boiler 3 is provided on the downstream side in the direction in which the exhaust gas from the gas turbine equipment 20 flows. Most of the steam generated in the exhaust heat recovery boiler 3 is supplied to the steam turbine equipment 25 via the flow rate control valve 23, and the rest is discharged to the outside via the chimney 4.
  • the steam turbine facility 25 has a turbine 5 driven by steam from the exhaust heat recovery boiler 3.
  • a generator 15 is connected to the turbine 5, and the steam turbine facility 25 supplies power to the plant via the power system 18.
  • the steam turbine facility 25 is attached with an extraction pipe 64 for extracting a part of the steam flowing through the steam turbine facility 25.
  • the extraction pipe 64 of the present embodiment is connected to a so-called intermediate stage portion between the first stage and the last stage of the turbine 5.
  • the extraction pipe 64 is connected to the water production facility (steam utilization facility) 30 and supplies the steam extracted from the steam turbine facility 25 to the water production facility 30.
  • the extraction pipe 64 is provided with an extraction flow rate adjusting valve 9 that adjusts the extraction flow rate of steam from the turbine 5 in accordance with the atmospheric temperature.
  • the opening degree of the extraction flow rate adjusting valve 9 in the present embodiment is adjusted by an opening degree command (CVbls) output from a combined cycle auxiliary control unit 101 (described later).
  • the water production device 30 produces pure water from seawater, river water, etc. using steam from the extraction pipe 64.
  • Seawater or river water which is a raw material of pure water, is supplied to the water production apparatus 30 by a water intake pump 33.
  • seawater or river water pumped up by the intake pump 33 is also supplied to the condenser 35, and is used for condensing steam from the steam turbine equipment 25 by the condenser 35.
  • the pure water produced by the water production apparatus 30 is supplied to the water tank 31 and the condenser 35 and used as intake spray or steam.
  • the control device 110 controls the entire plant, and includes a plant control unit 102, a combined cycle control unit (hereinafter referred to as CC control unit) 100, and a combined cycle auxiliary control unit (hereinafter referred to as CC auxiliary control unit) 101. is doing.
  • CC control unit combined cycle control unit
  • CC auxiliary control unit combined cycle auxiliary control unit
  • the plant control unit 102 includes a CC control unit 100 and a CC auxiliary control unit that output a total output (output command value MWD) required by the entire plant and a signal SW that instructs the power supply system to execute the optimum control according to the present invention.
  • 101 is connected to the CC control unit 100 and the CC auxiliary control unit 101.
  • the output command value MWD changes with the daily change of the atmospheric temperature Ta, as shown in FIGS.
  • the signal SW indicates the start of the optimum operation of the plant based on the atmospheric temperature change according to the present invention after the combined cycle facility including the gas turbine facility 20, the steam turbine facility 25, and the exhaust heat recovery boiler 3 reaches the rated operation state. Or it is a control signal for instruct
  • the CC control unit 100 is connected to the fuel flow control valve 22.
  • the CC control unit 100 calculates the opening degree of the fuel flow control valve 22 based on the output command value MWD, and holds the calculated opening degree.
  • the degree command CVfuel is output to the fuel flow control valve 22.
  • the opening degree command CVfuel determines the amount of fuel supplied to the combustor of the gas turbine equipment 20, and thereby the output of the gas turbine equipment 20 and the turbine rotational speed, and the amount of steam generated in the exhaust heat recovery boiler 3 (that is, The amount of steam supplied to the steam turbine equipment 25) is controlled.
  • the CC auxiliary control unit 101 is connected to the temperature measuring device 7, the water amount adjustment valve 8, and the extraction flow rate adjustment valve 9.
  • the CC auxiliary control unit 101 receives a signal to start control by the signal SW from the plant control unit 102, the CC auxiliary control unit 101 sums the actual outputs of the gas turbine facility 20 and the steam turbine facility 25 (that is, the actual total output of the power supply system ( Hereinafter, based on the output command value MWD and the atmospheric temperature Ta so that the output MW)) approaches the output command value (MWD), the amount of spray water (GwacD) supplied to the intake spray device 6 and the extraction from the steam turbine equipment 25 The steam flow rate (GblsD) to be adjusted is adjusted.
  • gas turbine facility 20 only one gas turbine facility 20 is shown, but a plurality of gas turbine facilities may be connected to the power system 18 according to the power required by the plant.
  • the output of any of the multiple gas turbine facilities decreases due to failure or inspection.
  • the necessary power can be supplemented by the output from other gas turbine equipment.
  • a combined cycle system may be constructed by appropriately providing steam turbine equipment that cooperates with a plurality of gas turbine equipment.
  • FIG. 3 is a circuit diagram of the CC auxiliary control unit 101 of the power supply system according to the first embodiment of the present invention.
  • the CC auxiliary control unit 101 shown in this figure supplies a subtraction unit 50 that calculates an output command value deviation ⁇ MW0 (described later), a maximum selection unit 51 that selects the maximum value of the output command value deviation ⁇ MW0, and an intake spray device 6.
  • a water amount control unit 52 for calculating the amount of water to be calculated, a valve opening degree control unit 53 for adjusting the opening amount of the water amount control valve 8, a minimum selection unit 54 for selecting the minimum value of the output command value deviation ⁇ MW0, and steam turbine equipment 25, a steam flow rate control unit 55 for calculating the steam flow rate to be extracted from the air flow rate 25 and a valve opening degree control unit 56 for adjusting the opening degree of the extraction flow rate control valve 9 are provided.
  • the rated output value MWD0 that is the sum of the rated outputs of the gas turbine facility 20 and the steam turbine facility 25 (that is, the combined cycle facility) and the output command value MWD are input to the subtracting unit 50.
  • the subtracting unit 50 subtracts the rated output value MWD0 from the output command value MWD, and calculates a deviation (output command value deviation) ⁇ MW0 between the output command value MWD and the rated output value MWD0.
  • the output command deviation value ⁇ MW0 calculated by the subtraction unit 50 is output to the maximum selection unit 51 and the minimum selection unit 54.
  • the maximum selection unit 51 compares the output command deviation value ⁇ MW0 with a numerical value 0 (zero), and when the output command deviation value ⁇ MW0 is positive (that is, the output command value MWD exceeds the rated output value MWD0, the demand (MWD) On the other hand, when the output (MWD0) is insufficient), the maximum value ⁇ MWH of the deviation value ⁇ MW0 is output to the water amount control unit 52.
  • the atmospheric temperature Ta is input from the temperature measuring device 7 to the water amount control unit 52.
  • the water amount control unit 52 calculates the water amount GwacD from the deviation maximum value ⁇ MWH by proportional-integral calculation so that the actual output MW of the power supply system approaches the output command value MWD.
  • the water amount control unit 52 corrects the value of the water amount GwacD according to the atmospheric temperature Ta.
  • amendment according to atmospheric temperature Ta is added to the water quantity GwacD, the motive power fall of the compressor 2 by an air temperature fluctuation
  • the water amount GwacD calculated by the water amount control unit 52 is output to the valve opening degree control unit 53.
  • a signal SW from the plant control unit 102 is input to the valve opening degree control unit 53.
  • the valve opening degree control unit 53 determines the opening degree of the water amount adjustment valve 8 based on the water amount GwacD, and calculates an opening degree command CVwac that holds the calculated opening degree.
  • the opening degree command CVwac calculated by the valve opening degree control unit 53 is output to the water amount adjustment valve 8.
  • the minimum selection unit 54 compares the output command deviation value ⁇ MW0 with the numerical value 0 (zero), and when the output command deviation value ⁇ MW0 is negative (that is, the output command value MWD falls below the rated output value MWD0, the demand (MWD) ) (When the output (MWD0) becomes excessive), the minimum value (absolute value maximum value in a negative number) ⁇ MWL of the deviation value ⁇ MW0 is output to the steam flow rate controller 55.
  • the atmospheric temperature Ta is input from the temperature measuring device 7 to the steam flow rate control unit 55.
  • the steam flow rate control unit 55 calculates the extraction flow rate GblsD from the minimum deviation value ⁇ MWL by proportional integration so that the actual output MW of the power supply system approaches the output command value MWD.
  • the steam flow rate control unit 55 corrects the value of the extraction flow rate GblsD according to the atmospheric temperature Ta.
  • amendment according to atmospheric temperature Ta is added to extraction flow GblsD, the output excess of the steam turbine equipment 25 by temperature fluctuation can be suppressed.
  • the extraction flow rate GblsD calculated by the steam flow rate control unit 55 is output to the valve opening degree control unit 56.
  • a signal SW from the plant control unit 102 is input to the valve opening degree control unit 56.
  • the valve opening degree control unit 56 determines the opening degree of the extraction flow rate adjusting valve 9 based on the extraction flow rate GblsD, and calculates an opening degree command CVbls that holds the calculated opening degree.
  • the opening degree command CVbls calculated by the valve opening degree control unit 56 is output to the extraction flow rate adjusting valve 9.
  • the opening degree command CVbls that outputs the opening degree 0 is output. Then, steam extraction is stopped.
  • FIG. 4 is a diagram showing an example of plant operation characteristics when the optimum operation is not performed.
  • the upper diagram is a diagram showing the daily change of the atmospheric temperature Ta
  • the lower diagram is a diagram showing the daily change of the output command value MWD and the output MW of the power supply system at that time.
  • the fuel flow rate supplied to the gas turbine equipment of the power supply system and the steam flow rate supplied to the steam turbine equipment are constant.
  • the output command value MWD required by the plant rises in the daytime (10 to 22:00) and increases at night (0 (10:00 to 20:00 to 24:00).
  • the total MW of the actual output of the gas turbine facility and the steam turbine facility that is, the actual output of the combined cycle facility
  • the total MW of the actual output of the gas turbine facility and the steam turbine facility tends to decrease in the daytime and increase in the night as opposed to the atmospheric temperature change.
  • a heat exchanger or the like used for cooling natural gas or the first and second refrigerants during cold weather (for example, at night).
  • 47b because the cooling performance of the condenser 46) is relatively improved, the required power of the refrigerant compressors 10 and 11 for heating and compressing the first and second refrigerants is reduced, and the output command value MWD tends to be reduced.
  • This characteristic is opposite to the characteristic of the combined cycle facility in which the output increases in cold weather, and the efficiency decrease due to surplus steam during cold weather becomes even more remarkable. For example, in the example shown in FIG. 4, a deviation of ⁇ MW occurs at the maximum in the power supply and demand due to the daily change in the atmospheric temperature Ta.
  • the power supply system has an extraction pipe 64 that supplies steam extracted from the steam turbine facility 25 to the water production apparatus 30, an extraction flow rate control valve 9, and an output from the plant.
  • the command value MWD is lower than the rated output value MWD0 of the gas turbine equipment 20 and the steam turbine equipment 25, the rated output value MWD0 is set so that the total output MW of the gas turbine equipment 20 and the steam turbine equipment 25 approaches the output command value MWD.
  • a control device 110 determines a steam flow rate GblsD to be extracted from the steam turbine equipment 25 based on the deviation ⁇ MW of the output command value MWD, and holds the extraction flow rate adjustment valve 9 at the opening degree CVbls determined based on the steam flow rate GblsD. ing.
  • the CC auxiliary control unit 101 of the control device 110 first calculates the extraction flow rate GblsD from the output command deviation value ⁇ MW0 and the atmospheric temperature Ta, and based on the calculated extraction flow rate GblsD, the opening degree command CVbls. Is calculated. Next, the CC auxiliary control unit 101 outputs the calculated opening degree command CVbls to the extraction flow rate adjustment valve 9, and the opening degree of the extraction flow rate adjustment valve 9 so that the output MW follows the change in the output command value MWD. Adjust.
  • the output MW can be brought close to the output command value MWD while the gas turbine facility 20 is operated near the rating.
  • the steam extracted from the steam turbine facility 25 is supplied to the water production device 30 to produce pure water required by the intake spray device 6 when the temperature rises. The generated steam can be used effectively.
  • the output MW can follow the change in the output command value MWD while operating the gas turbine facility 20 near the rating even when the atmospheric temperature is lowered. Efficiency can be improved.
  • FIG. 5 is a diagram showing an example of plant operation characteristics when the optimum operation is performed.
  • the upper diagram shows the daily change of the output MW when the atmospheric temperature Ta changes as shown in the upper diagram of FIG. 4, and the lower diagram shows the water amount adjustment valve 8 and the bleed flow rate at that time. It is a figure which shows the opening degree (%) of the control valve.
  • output command value MWD ⁇ rated output value MWD0 (ie, output command deviation value ⁇ MW0 ⁇ 0)” is established between 0-10 o'clock and 22-24 o'clock, and “output command value MWD> rated rating between 10-22 o'clock”.
  • the rated output value MWD0 of the power supply system is set so that the output value MWD0 (that is, the output command deviation value ⁇ MW0> 0) is established.
  • the output command deviation value ⁇ MW0 is negative between midnight and morning (0-10 o'clock, 22-24 o'clock) when the atmospheric temperature Ta is relatively low, so the output of the steam turbine equipment 25 is reduced.
  • control is performed to bring the output MW closer to the output command value MWD.
  • control is performed to keep the output MW constant from 0 to 8 o'clock, and the opening degree of the extraction flow rate adjusting valve 9 is held at ⁇ .
  • the output of the steam turbine equipment 25 can be reduced from the rating by ⁇ MWbld (see the upper part of FIG. 5).
  • the output MW can be brought close to the output command value MWD while operating the facility 20 near the rating.
  • the power supply system of the present embodiment includes an intake spray device 6 that sprays water on the intake air of the gas turbine equipment 20, a water tank 31 that stores water supplied to the intake spray device 6, and a water tank 31.
  • Spray water pipe 63 that connects to the intake spray device 6, a water amount adjustment valve 8 provided in the spray water pipe 63, a temperature measuring device 7 that measures the atmospheric temperature, and an output command value MWD from the plant is the gas turbine equipment 20 and the rated output value MWD0 of the steam turbine equipment 25, the deviation ⁇ MW between the rated output value MWD0 and the output command value MWD so that the total output MW of the gas turbine equipment 20 and the steam turbine equipment 25 approaches the output command value MWD.
  • the water amount GwacD supplied from the water tank 31 to the intake spray device 6 is determined, and the water amount Gwa is determined. Further comprising a control device 110 for holding the water amount adjusting valve 8 to an opening CVwac determined based on D.
  • the CC auxiliary control unit 101 of the control device 110 determines the amount of water GwacD supplied to the intake spray device 6 based on the deviation ⁇ MW of the output command value MWD and the atmospheric temperature Ta. Then, the CC auxiliary control unit 101 outputs the opening degree command CVwac determined based on the water amount GwacD to the water amount adjustment valve 8, and opens the water amount adjustment valve 8 so that the output MW follows the change in the output command value MWD. Adjust the degree.
  • the water amount adjustment valve 8 is held at the opening degree ⁇ at 12 to 20:00 when the atmospheric temperature rises, and the intake spray is performed on the inlet of the compressor 2.
  • the output of the combined cycle facility increases by ⁇ MWwac, so that the output MW can be made to follow the output command value MWD required by the plant even when the atmospheric temperature increases.
  • control is performed to keep the output MW constant at 0-8 o'clock and 12-20 o'clock, but the deviation between the output command value MWD and the output MW approaches zero over the entire time period.
  • the output MW may be controlled. In this case, the efficiency of the power supply system can be further improved.
  • the output MW while operating the gas turbine equipment 20 near the rating can be made constant, and the efficient operation of the entire plant becomes possible.
  • FIG. 6 is a schematic diagram of a plant power supply system according to a second embodiment of the present invention.
  • the same parts as those in the previous figure are denoted by the same reference numerals and description thereof is omitted.
  • the power supply system of the present embodiment is different from that of the first embodiment in that the drive shaft of the first refrigerant compressor 10A is connected to the turbine 1, and the second refrigerant compressor 11A is connected to the turbine 5.
  • the drive shaft is connected.
  • the power supply system shown in FIG. 6 directly drives the first refrigerant compressor 10 with the power obtained by the gas turbine equipment 20, and the second refrigerant compressor 11 with the power obtained by the steam turbine equipment 25. Is driving directly.
  • the opening degree command CVwac to the water amount adjusting valve 8 can be calculated from the deviation of the output of the gas turbine equipment 20 and the necessary power of the first refrigerant compressor 10.
  • the opening degree command CVbls to the extraction flow rate adjusting valve 9 can be calculated from the deviation of the output of the steam turbine equipment 25 and the necessary power of the second refrigerant compressor 11. Therefore, according to the present embodiment, the outputs of the gas turbine facility 20 and the steam turbine facility 25 can be individually controlled by controlling the opening degree commands CVwac and CVbls. Thereby, it can respond flexibly also when the required motive power of the 1st refrigerant
  • the configuration in which the first refrigerant compressor 10 is driven by the gas turbine equipment 20 and the second refrigerant compressor 11 is driven by the steam turbine equipment 25 has been taken up.
  • the second refrigerant compressor 11 may be driven by 20 and the first refrigerant compressor 10 may be driven by the steam turbine equipment 25.
  • a generator (not shown) is added to the rotating shaft of the gas turbine equipment 20 or the rotating shaft of the steam turbine 25 shown in FIG. 6, and the first refrigerant compressor 10 or the second refrigerant compressor 11 becomes redundant. Electric power may be generated with a different driving force. If the generator is added in this way, the surplus output that is not used for driving the refrigerant compressors 10 and 11 can be supplied as electric power to other equipment in the plant, so that the output generated by the combined cycle equipment can be used. Efficiency can be further improved.
  • the supply destination of the steam extracted from the steam turbine facility 25 is the water production apparatus 30, but one end of the extraction pipe 64 is connected to a steam utilization facility such as a heat pump or district heating / cooling, and extraction
  • a steam utilization facility such as a heat pump or district heating / cooling
  • the power supply system of the natural gas liquefaction plant has been described as an example, but besides this, the power supply consistent with the power demand of the plant is always required due to the nature of the plant, and the The present invention can be applied to any plant that requires stable power.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

L'invention concerne un système destiné à fournir une puissance motrice à une centrale et comprenant une machine (20) à turbine à gaz, une chaudière (3) à récupération de chaleur d'échappement servant à générer de la vapeur à l'aide des gaz d'échappement provenant de la machine à turbine à gaz, une machine (25) à turbine à vapeur actionnée par la vapeur provenant de la chaudière à récupération de chaleur d'échappement, une canalisation (64) de prélèvement servant à fournir de la vapeur prélevée à partir de la machine à turbine à vapeur à une machine (30) de production d'eau, une soupape (9) de régulation du débit d'air de prélèvement installée sur la canalisation de prélèvement, et un régulateur (110) destiné à fixer un débit (GblsD) de vapeur prélevée à partir de la machine à turbine à vapeur en accord avec un écart (?MW0) par rapport à la consigne de puissance de sortie de telle sorte qu'une puissance totale de sortie (MW) de la machine à turbine à gaz et de la machine à turbine à vapeur s'approche d'une valeur de consigne de puissance de sortie (MWD) de la centrale lorsque ladite valeur, qui change avec la variation quotidienne de température ambiante, tombe au-dessous des valeurs nominales (MWD0) de puissance de sortie de la machine à turbine à gaz et de la machine à turbine à vapeur. Une telle configuration assure l'exploitation de la machine à turbine à gaz au voisinage de sa puissance nominale de sortie même en cas de chute de la température ambiante, permettant ainsi d'améliorer le rendement du système de fourniture de puissance motrice de la centrale.
PCT/JP2008/051573 2008-01-31 2008-01-31 Système de fourniture de puissance motrice pour centrale, procédé pour son exploitation et procédé pour sa modification Ceased WO2009096028A1 (fr)

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JP2011189894A (ja) * 2010-03-16 2011-09-29 Hitachi Plant Technologies Ltd 真空環境試験装置
WO2012032557A1 (fr) * 2010-09-06 2012-03-15 株式会社 日立製作所 Système de production d'électricité à turbine à gaz
JP2012140959A (ja) * 2011-01-03 2012-07-26 General Electric Co <Ge> 発電設備（ｐｏｗｅｒｇｅｎｅｒａｔｉｏｎａｐｐａｒａｔｕｓ）
EP2792858A3 (fr) * 2013-03-15 2015-03-25 Mitsubishi Hitachi Power Systems, Ltd. Centrale électrique à turbine à vapeur
US10126048B2 (en) 2014-04-07 2018-11-13 Mitsubishi Heavy Industries Compressor Corporation Floating liquefied-gas production facility
JP2019503840A (ja) * 2015-12-02 2019-02-14 ランドバーグ・エルエルシー 電気集塵を用いてタービンの動作を改善するためのシステム、装置、及び方法
JP2023067442A (ja) * 2021-11-01 2023-05-16 株式会社東芝 蒸気供給設備

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JPH10266812A (ja) * 1997-03-25 1998-10-06 Mitsubishi Heavy Ind Ltd 熱併給ガスタ−ビンコンバインドプラントの電力制御方法
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Publication number Priority date Publication date Assignee Title
JP2011189894A (ja) * 2010-03-16 2011-09-29 Hitachi Plant Technologies Ltd 真空環境試験装置
WO2012032557A1 (fr) * 2010-09-06 2012-03-15 株式会社 日立製作所 Système de production d'électricité à turbine à gaz
JPWO2012032557A1 (ja) * 2010-09-06 2013-10-31 株式会社日立製作所 ガスタービン発電システム
JP2012140959A (ja) * 2011-01-03 2012-07-26 General Electric Co <Ge> 発電設備（ｐｏｗｅｒｇｅｎｅｒａｔｉｏｎａｐｐａｒａｔｕｓ）
EP2792858A3 (fr) * 2013-03-15 2015-03-25 Mitsubishi Hitachi Power Systems, Ltd. Centrale électrique à turbine à vapeur
US10126048B2 (en) 2014-04-07 2018-11-13 Mitsubishi Heavy Industries Compressor Corporation Floating liquefied-gas production facility
JP2019503840A (ja) * 2015-12-02 2019-02-14 ランドバーグ・エルエルシー 電気集塵を用いてタービンの動作を改善するためのシステム、装置、及び方法
JP2023067442A (ja) * 2021-11-01 2023-05-16 株式会社東芝 蒸気供給設備

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