WO2018131654A1 - 制御システム、ガスタービン、発電プラント及び燃料温度の制御方法 - Google Patents

制御システム、ガスタービン、発電プラント及び燃料温度の制御方法 Download PDF

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Publication number
WO2018131654A1
WO2018131654A1 PCT/JP2018/000499 JP2018000499W WO2018131654A1 WO 2018131654 A1 WO2018131654 A1 WO 2018131654A1 JP 2018000499 W JP2018000499 W JP 2018000499W WO 2018131654 A1 WO2018131654 A1 WO 2018131654A1
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WO
WIPO (PCT)
Prior art keywords
flow rate
fuel
valve
heating device
temperature
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/JP2018/000499
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English (en)
French (fr)
Japanese (ja)
Inventor
悠希 中澤
昭彦 齋藤
中川　博之
諒 古藤
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Mitsubishi Power Ltd
Original Assignee
Mitsubishi Hitachi Power Systems Ltd
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Filing date
Publication date
Application filed by Mitsubishi Hitachi Power Systems Ltd filed Critical Mitsubishi Hitachi Power Systems Ltd
Priority to US16/475,246 priority Critical patent/US11125166B2/en
Priority to CN201880006340.1A priority patent/CN110168207B/zh
Priority to KR1020197019728A priority patent/KR102226983B1/ko
Priority to DE112018000394.9T priority patent/DE112018000394B4/de
Publication of WO2018131654A1 publication Critical patent/WO2018131654A1/ja
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
    • 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
    • F01K23/106—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 with water evaporated or preheated at different pressures in exhaust boiler
    • 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
    • F01K17/06—Returning energy of steam, in exchanged form, to process, e.g. use of exhaust steam for drying solid fuel or plant
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/18—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/22—Fuel supply systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/22—Fuel supply systems
    • F02C7/224—Heating fuel before feeding to the burner
    • 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
    • F02C9/00—Controlling gas-turbine plants; Controlling fuel supply in air- breathing jet-propulsion plants
    • F02C9/26—Control of fuel supply
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23K—FEEDING FUEL TO COMBUSTION APPARATUS
    • F23K5/00—Feeding or distributing other fuel to combustion apparatus
    • F23K5/002—Gaseous fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23R—GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY, e.g. GAS-TURBINE COMBUSTION CHAMBERS
    • F23R3/00—Continuous combustion chambers using liquid or gaseous fuel
    • F23R3/28—Continuous combustion chambers using liquid or gaseous fuel characterised by the fuel supply
    • 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
    • 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
    • F01K23/12—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engines being mechanically coupled
    • F01K23/14—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engines being mechanically coupled including at least one combustion engine
    • 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
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/22—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbines having inter-stage steam heating
    • 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]

Definitions

  • the present invention relates to a control system, a gas turbine, a power plant, and a fuel temperature control method.
  • FIG. 14 is a system diagram of a conventional fuel heating apparatus.
  • FIG. 15 is a block diagram showing a conventional water supply control process in the fuel heating device. As shown in FIG. 14, the fuel gas flows in the direction of the arrow (from right to left in the drawing) and is supplied to the combustor of the gas turbine (GT).
  • GTCC Gas Turbine Combined Cycle
  • the feed water HW (heated water) supplied from the exhaust heat recovery boiler flows in the direction of the arrow (from the left to the right of the page), heats the fuel gas with the fuel heating device 70, and the exhaust heat recovery boiler or condenser. It flows to.
  • the water supply flow rate adjustment valve 71 is installed to control the flow rate of the heating water necessary for heating the fuel during the operation of the gas turbine and collect it on the HRSG side (low pressure water supply side).
  • the opening degree control of the feed water flow rate adjustment valve 71 will be described with reference to FIG.
  • the function unit P10 inputs a load (GTMW) of the gas turbine, and calculates a valve opening degree corresponding to GTMW.
  • the opening degree of the feed water flow rate adjustment valve 71 is controlled to be the calculated valve opening degree. In this way, the feed water flow rate adjustment valve 71 is subjected to feedforward control according to the load while considering the valve characteristics through the operation modes of starting, stopping, partial load operation, and rated operation of the gas turbine.
  • the dump valve 72 is installed to control the flow rate of the heated water to the fuel heating device 70 at the time of starting and stopping of the gas turbine, and dump it to the condenser. Control is performed by feedback control with respect to the target flow rate at the time of start and stop, and during high load operation, control is switched to control by the feed water flow rate adjustment valve 71, and the dump valve 72 is fully closed. When the load decreases and the flow rate of the fuel gas passing through the fuel heating device 70 decreases, control is performed to open the dump valve by the above feedback control.
  • FIG. 15B shows the opening degree control logic of the dump valve 72.
  • the function unit D10 inputs the load (GTMW) of the gas turbine and converts it into a target flow rate F1 suitable for GTMW.
  • the subtractor D11 subtracts the flow rate F2 measured by the flow meter 16 from the flow rate F1, and calculates the deviation between the target flow rate F1 and the actual feed water flow rate F2.
  • the controller D12 calculates a valve opening that makes this deviation close to 0 by PI control, and controls the opening of the dump valve 72 to be the calculated valve opening.
  • Patent Document 1 with regard to the adjustment of the feed water temperature for fuel heating at the time of partial load operation in a combined plant, the reduction adjustment of the fuel gas tends to be insufficient with respect to the reduction in the feed water amount accompanying the decrease in the output of the steam turbine. It is described that the supply of water which tends to be deficient is provided by providing a recirculation system or the like for recirculating the water supply in response to the problem of steaming the water supply by operating with excessive fuel.
  • the fuel gas is heated by the heating water from the exhaust heat recovery boiler, but the heating water supplied to the fuel heating device 70 has a flow rate according to the load of the gas turbine. Because of the supplied control, the temperature of the fuel gas on the outlet side of the fuel heating device 70 may not be controlled to a desired value.
  • the present invention provides a control system, a gas turbine, a power plant, and a fuel temperature control method that can solve the above-described problems.
  • the control system adjusts the flow rate of the heating water supplied to the fuel heating device that heats the fuel of the gas turbine, so that the combustion of the gas turbine passes through the fuel heating device.
  • a control system for controlling the temperature of the fuel supplied to the vessel, wherein the fuel is supplied to the fuel heating device according to a deviation between the target temperature of the fuel and the temperature of the fuel on the outlet side of the fuel heating device A water supply flow rate adjusting unit for adjusting the flow rate of the heated water;
  • the control system collects the flow rate of the heating water supplied from the heating water supply device to the fuel heating device to the heating water supply device from the fuel heating device.
  • a temperature control unit wherein the water supply flow rate adjusting unit calculates a first valve opening degree that is an opening degree of the water supply flow rate adjusting valve according to a load of the gas turbine; and the gas turbine
  • a correction amount is calculated according to a deviation between the target temperature of the fuel supplied to the combustor and the temperature of the fuel on the outlet side of the fuel heating device, and the calculated correction amount is added to the first valve opening degree.
  • a third valve opening calculation unit for calculating the third valve opening; Based on the third valve opening, a feed water flow control valve controller that controls the opening of the feed water flow control valve, a target flow of the heating water that is predetermined according to a load of the gas turbine, and an actual A dump valve control unit that controls an opening degree of the dump valve according to a deviation from the flow rate.
  • the third valve opening calculation unit calculates the correction amount based on a deviation between the target temperature of the fuel and the temperature of the fuel on the outlet side of the fuel heating device. Execute by feedback control.
  • the second valve opening is calculated by multiplying the first valve opening by a coefficient corresponding to the temperature of the fuel on the inlet side of the fuel heating device.
  • a third degree of valve opening calculation unit wherein the third valve opening degree calculating unit calculates the third valve opening degree by adding the correction amount to the second valve opening degree instead of the first valve opening degree.
  • the dump valve control unit controls the opening degree of the dump valve with a flow rate smaller than the flow rate of the heated water passing through the feed water flow rate adjustment valve as a target flow rate.
  • the dump valve control unit is less than the flow rate of the heated water that passes through the feed water flow rate adjustment valve when the load of the gas turbine becomes a predetermined value or more. Let the flow rate be the target flow rate.
  • the control system provides the flow rate of the heating water supplied from the heating water supply device to the fuel heating device on the upstream side of the heating water path in the fuel heating device.
  • An opening of the three-way valve that switches between a ratio of the heated water sent to the fuel heating device and a ratio of the heated water sent to a path bypassing the fuel heating device, and the fuel
  • the opening of the feed water flow rate adjustment valve that adjusts the flow rate of the heated water collected from the heating device to the heating water supply device, and the opening amount of the dump valve that adjusts the flow rate of the heated water dumped to the condenser
  • controlling the temperature of the fuel, and the water supply flow rate adjustment unit calculates a first valve opening degree that is an opening degree of the water supply flow rate adjustment valve according to a load of the gas turbine.
  • a dump valve control unit for controlling the opening degree of the dump valve according to the above, and the opening degree of the three-way valve according to a deviation between the target temperature of the fuel and the temperature of the fuel on the outlet side of the fuel heating device A three-way valve control unit for controlling
  • the control system collects the flow rate of the heating water supplied from the heating water supply device to the fuel heating device that heats the fuel of the gas turbine to the heating water supply device.
  • the temperature of the fuel is controlled by controlling the opening of a feed water flow rate adjustment valve that adjusts the flow rate of the heated water and the opening of a dump valve that adjusts the flow rate of the heated water dumped to the condenser.
  • a first valve opening degree calculation unit that calculates a first valve opening degree that is an opening degree of the feed water flow rate adjustment valve according to a load of the gas turbine, and the first valve opening degree.
  • a second valve opening calculation unit for calculating a second valve opening by multiplying by a coefficient corresponding to the temperature of the fuel on the inlet side of the fuel heating device, and the water supply based on the second valve opening
  • a water supply flow rate control valve control unit that controls the opening degree of the flow rate control valve.
  • a gas turbine includes a compressor, a combustor, a turbine, and the control system described in any one of the above.
  • a power plant includes the gas turbine described in the ninth aspect, a steam turbine, and a generator.
  • the flow rate of the heating water supplied to the fuel heating device for heating the fuel of the gas turbine is adjusted to supply the combustor of the gas turbine via the fuel heating device.
  • a control system for controlling the temperature of the fuel adjusts the flow rate of the heating water supplied to the fuel heating device in accordance with a deviation between the target temperature of the fuel and the temperature of the fuel on the outlet side of the fuel heating device. The fuel temperature control method.
  • control system gas turbine, power plant, and fuel temperature control method described above, by controlling the flow rate of feed water supplied to the fuel heating device while monitoring the temperature of the fuel on the outlet side of the fuel heating device.
  • the temperature of the fuel can be controlled to a desired temperature.
  • FIG. 1 is a system diagram of a gas turbine combined cycle plant according to the first and second embodiments of the present invention.
  • the gas turbine combined cycle (GTCC) plant of the present embodiment includes a gas turbine 10, an exhaust heat recovery boiler 20 that generates steam by the heat of exhaust gas exhausted from the gas turbine 10, and exhaust heat.
  • a steam turbine 30 (high-pressure steam turbine 31, intermediate-pressure steam turbine 32, and low-pressure steam turbine 33) driven by steam from the recovery boiler 20, and a generator 34 that generates electric power by driving each turbine 10, 31, 32, 33; , A condenser 35 that returns the steam exhausted from the low-pressure steam turbine 33 to water, and a control device 100 that controls these devices.
  • the gas turbine 10 includes a compressor 11 that compresses outside air to generate compressed air, a combustor 12 that mixes and burns compressed air with fuel gas to generate high-temperature combustion gas, and a turbine driven by the combustion gas. 13.
  • a fuel line R ⁇ b> 1 that supplies fuel from a fuel supply device (not shown) to the combustor 12 is connected to the combustor 12.
  • a fuel heating device 70 is provided in the fuel line.
  • the exhaust port of the turbine 13 is connected to the exhaust heat recovery boiler 20.
  • the fuel heating device 70 is provided to increase the temperature of the fuel gas in order to improve the thermal efficiency in the combustor 12.
  • a fuel gas having a desired flow rate corresponding to the load is supplied to the fuel heating device 70 from a fuel supply device (not shown).
  • a thermometer 14 is provided on the inlet side of the fuel heating device 70 in the fuel line R1, and a thermometer 15 is provided on the outlet side.
  • the thermometer 14 measures the temperature of the fuel gas on the inlet side.
  • the thermometer 15 measures the temperature of the fuel gas on the outlet side.
  • the fuel heating device 70 is connected to an exhaust heat recovery boiler (HRSG) 20 via a heating water supply line L1. From the exhaust heat recovery boiler 20, the heating water passes through the heating water supply line L1 and is supplied to the fuel heating device.
  • HRSG exhaust heat recovery boiler
  • the heated water and the fuel gas supplied from the fuel line R1 exchange heat. At this time, heat moves from the heated water to the fuel gas, and the temperature of the fuel gas rises.
  • the fuel gas controlled to a desired high temperature is supplied to the combustor 12.
  • the temperature of the fuel gas after passing through the fuel heating device 70 may deviate from a desired temperature.
  • the fuel gas temperature on the outlet side of the fuel heating device 70 is controlled to a desired temperature by the control method described below.
  • a flow meter 16 is provided in the heating water supply line L1. The flow meter 16 measures the flow rate of the heating water supplied to the fuel heating device 70.
  • heating water return line L2 is connected to the outlet side of the fuel heating device 70.
  • the other end of the heating water return line L2 is connected to the exhaust heat recovery boiler 20.
  • the heated water after the heat exchange by the fuel heating device 70 is recovered to the exhaust heat recovery boiler 20 through the heated water return line L2.
  • a feed water flow rate adjustment valve 71 is provided in the heating water return line L2.
  • the heating water return line L2 branches to the condensate line L3 at the branch point DC.
  • the condensate line L3 is connected to the condenser 35.
  • a dump valve 72 is provided in the condensate line L3.
  • part of the heated water recovered from the fuel heating device 70 to the exhaust heat recovery boiler 20 is dumped to the condenser 35 via the condensate line L3.
  • the opening degree of the feed water flow rate adjustment valve 71 and the dump valve 72 is controlled by the control device 100.
  • An exhaust heat recovery boiler (HRSG) 20 includes a high-pressure steam generator 21 that generates high-pressure steam supplied to the high-pressure steam turbine 31, and an intermediate-pressure steam generator 22 that generates intermediate-pressure steam supplied to the intermediate-pressure steam turbine 32.
  • the low-pressure steam generator 24 that generates the low-pressure steam to be supplied to the low-pressure steam turbine 33 and the reheating unit 23 that heats the steam exhausted from the high-pressure steam turbine 31 are provided.
  • the high-pressure steam generator 21 of the exhaust heat recovery boiler 20 and the steam inlet of the high-pressure steam turbine 31 are connected by a high-pressure main steam line 41 that guides the high-pressure steam to the high-pressure steam turbine 31, and the steam outlet of the high-pressure steam turbine 31 and the medium pressure
  • the steam inlet of the steam turbine 32 is connected by an intermediate pressure steam line 44 that guides the steam exhausted from the high pressure steam turbine 31 to the steam inlet of the intermediate pressure steam turbine 32 via the reheating unit 23 of the exhaust heat recovery boiler 20.
  • the low pressure steam generator 24 of the exhaust heat recovery boiler 20 and the steam inlet of the low pressure steam turbine 33 are connected by a low pressure main steam line 51 that guides the low pressure steam to the low pressure steam turbine 33.
  • the steam outlet of the intermediate pressure steam turbine 32 and the steam inlet of the low pressure steam turbine 33 are connected by an intermediate pressure turbine exhaust line 54.
  • a condenser 35 is connected to the steam outlet of the low-pressure steam turbine 33.
  • the condenser 35 is connected to a water supply line 55 that guides the condensate to the exhaust heat recovery boiler 20.
  • An intermediate pressure main steam line 61 connects the intermediate pressure steam generation unit 22 of the exhaust heat recovery boiler 20 and the upstream side portion of the intermediate pressure steam line 44 from the reheating unit 23.
  • the high-pressure main steam line 41 is provided with a high-pressure steam stop valve 42 and a high-pressure main steam control valve 43 that adjusts the amount of steam flowing into the high-pressure steam turbine 31.
  • the intermediate pressure steam line 44 is provided with an intermediate pressure steam stop valve 45 and an intermediate pressure steam control valve 46 that adjusts the amount of steam flowing into the intermediate pressure steam turbine 32.
  • the low-pressure main steam line 51 is provided with a low-pressure steam stop valve 52 and a low-pressure main steam control valve 53 that adjusts the amount of steam flowing into the low-pressure steam turbine 33.
  • the control device 100 adjusts the opening of the feed water flow rate adjustment valve 71 and the dump valve 72 and controls the flow rate of the heated water that exchanges heat with the fuel gas in the fuel heating device 70. Thereby, the control device 100 controls the fuel gas temperature on the outlet side of the fuel heating device 70 to a desired temperature.
  • the control device 100 receives various types of operation data, instruction data, and the like, performs output control of the gas turbine 10, output control of the steam turbine 30, and the like to generate power by the generator 34.
  • FIG. 2 is a block diagram of the control device according to the first embodiment of the present invention.
  • the control device 100 controls the flow rate of the heated water supplied from the exhaust heat recovery boiler 20 to the fuel heating device 70 by adjusting the opening degree of the feed water flow rate adjustment valve 71 and the opening degree of the dump valve 72. .
  • the control device 100 controls the temperature of the fuel gas supplied to the combustor 12 of the gas turbine 10 via the fuel heating device 70 by controlling the flow rate of the heated water.
  • the control device 100 is configured by a computer. As illustrated, the control device 100 includes an operation data acquisition unit 101, a first valve opening calculation unit 102, a second valve opening calculation unit 103, a third valve opening calculation unit 104, and a feed water flow rate adjustment valve.
  • a control unit 105, a dump valve control unit 106, and a storage unit 107 are provided.
  • the operation data acquisition unit 101 acquires operation data (state quantity, target control value, etc.) of each GTCC device (gas turbine 10, exhaust heat recovery boiler 20, etc.). For example, the operation data acquisition unit 101 acquires the gas turbine load (GTMW), the measured values of the thermometers 14 and 15, the measured value of the flow meter 16, and the target temperature of the fuel gas.
  • the first valve opening calculation unit 102 calculates the valve opening (first valve opening) of the feed water flow rate adjustment valve 71 according to the load (GTMW) of the gas turbine 10.
  • the second valve opening calculation unit 103 calculates the second valve opening by multiplying the first valve opening by a coefficient corresponding to the temperature of the fuel on the inlet side of the fuel heating device 70 measured by the thermometer 14. To do.
  • the third valve opening calculation unit 104 adds a correction amount corresponding to a deviation between a predetermined target temperature of the fuel gas and the temperature of the fuel gas on the outlet side of the fuel heating device 70 to the second valve opening. Then, the third valve opening is calculated.
  • the water supply flow rate adjustment valve control unit 105 controls the opening degree of the water supply flow rate adjustment valve 71 based on the third valve opening degree.
  • the dump valve control unit 106 controls the opening degree of the dump valve 72 by feedback control according to the deviation between the target heating water flow rate corresponding to the load (GTMW) of the gas turbine 10 and the actual heating water flow rate.
  • the storage unit 107 stores various information related to the opening control of the feed water flow rate adjustment valve 71 and the dump valve 72.
  • the control device 100 has various other functions related to GTCC control, but descriptions of functions not related to the present embodiment are omitted.
  • FIG. 3 is a system diagram of the fuel heating device according to the first embodiment of the present invention.
  • the fuel gas is supplied to the fuel heating device 70 via the fuel line R1, and the heating water is supplied via the heating water supply line L1.
  • the deviation is set to 0 in accordance with the deviation between the target temperature of the fuel gas (target fuel temperature) on the outlet side of the fuel heating device 70 and the actual measured value of the fuel gas. It is characterized by adjusting the flow rate of the heating water supplied to the fuel heating device 70 by performing control so as to be close.
  • a characteristic configuration of the present embodiment is shown in a portion surrounded by a broken line.
  • the control of the dump valve 72 is the same as that described with reference to FIG.
  • the function unit D10 included in the dump valve control unit 106 calculates a target flow rate for controlling the dump valve 72.
  • the function unit D10 calculates a small target flow rate for a large load and calculates a large target flow rate for a small load.
  • the subtractor D11 included in the dump valve control unit 106 calculates a deviation between the target flow rate by the function unit D10 and the flow rate measurement value of the heating water by the flow meter 16.
  • the controller D12 with which the dump valve control part 106 is provided controls the opening degree of the dump valve 72 by feedback control so that this deviation may be brought close to zero. With this control, when the load of the gas turbine 10 is high, the dump valve 72 is controlled to be fully closed (0%). When the load of the gas turbine 10 is low, for example, when starting, stopping, or during partial load operation, the opening degree is adjusted by the above control to ensure the diversion of the heating water.
  • the first valve opening calculation unit 102 includes a function unit P10 that converts a load of the gas turbine into a valve opening.
  • the function unit P10 is created in consideration of the valve characteristics of the feed water flow rate adjustment valve 71.
  • the first valve opening calculation unit 102 acquires the load (GTMW) of the gas turbine 10 from the operation data acquisition unit 101.
  • the function unit P10 inputs the load of the gas turbine 10, and calculates the opening degree of the feed water flow rate adjustment valve 71 according to this load.
  • the function unit P10 calculates a large valve opening for a large load, and calculates a small valve opening for a small load.
  • the function device P10 calculates the valve opening degree (first valve opening degree) according to the valve characteristic of the feed water flow rate adjustment valve 71.
  • the second valve opening calculation unit 103 includes a function unit P11 and a multiplier P12.
  • the second valve opening calculation unit 103 acquires the temperature of the fuel gas on the inlet side of the fuel heating device 70 measured by the thermometer 14 from the operation data acquisition unit 101.
  • the function unit P11 inputs the temperature of the fuel gas at the inlet side and calculates a coefficient corresponding to this temperature.
  • the multiplier P12 receives the coefficient calculated by the function unit P11 and the valve opening calculated by the function unit P10, and multiplies these two values. That is, the multiplier P12 multiplies the valve opening degree according to the load of the gas turbine 10 by a coefficient corresponding to the inlet side fuel temperature by the function unit P11 (the coefficient becomes larger as the temperature of the fuel gas is lower). Thus, the valve opening (second valve opening) of the feed water flow rate adjustment valve 71 corresponding to the load of the gas turbine 10 and the temperature of the fuel gas is calculated.
  • the third valve opening calculation unit 104 includes a subtracter P13 and an adder P14.
  • the third valve opening calculation unit 104 acquires the temperature of the fuel gas on the outlet side of the fuel heating device 70 measured by the thermometer 15 from the operation data acquisition unit 101.
  • the third valve opening calculation unit 104 acquires the target temperature of the fuel gas from the operation data acquisition unit 101.
  • the target temperature of the fuel gas may be stored in the storage unit 107, or the control device 100 may calculate the target temperature according to the load of the gas turbine 10, for example.
  • the subtractor P13 inputs the temperature of the fuel gas on the outlet side of the fuel heating device 70 and the target fuel temperature, subtracts the temperature of the fuel gas on the outlet side of the fuel heating device 70 from the target fuel temperature, and the deviation between the two. Is calculated.
  • the third valve opening calculation unit 104 calculates a correction amount of the valve opening corresponding to the deviation so that the deviation approaches 0. For example, a function for converting the deviation into a correction amount for the valve opening is stored in the storage unit 107, and the third valve opening calculation unit 104 calculates the correction amount for the valve opening using this function.
  • the adder P14 inputs the second valve opening calculated by the multiplier P12 and the correction amount of the valve opening calculated by the third valve opening calculation unit 104, and adds the two values. That is, the valve opening degree of the feed water flow rate adjustment valve 71 corresponding to the load of the gas turbine 10 and the temperature of the fuel gas is corrected by a correction amount corresponding to the deviation between the target temperature of the fuel gas and the actual temperature of the fuel gas (first). 3 valve opening).
  • the feed water flow rate adjustment valve control unit 105 performs control to adjust the opening degree of the feed water flow rate adjustment valve 71 to the third valve opening degree.
  • FIG. 5 is a flowchart showing an example of a feed water flow rate control process in the first embodiment according to the present invention.
  • the operation data acquisition unit 101 acquires operation data during operation of the GTCC (step S11). Specifically, the operation data acquisition unit 101 calculates the load size of the gas turbine 10, the measured value of the thermometer 14, the measured value of the thermometer 15, the measured value of the flow meter 16, and the target fuel temperature. get.
  • the 1st valve opening calculation part 102 calculates the 1st valve opening according to the magnitude
  • the first valve opening degree calculation unit 102 outputs the first valve opening degree to the second valve opening degree calculation unit 103.
  • the second valve opening calculation unit 103 calculates the second valve opening using the function unit P11 and the multiplier P12 (step S13).
  • the second valve opening degree calculation unit 103 outputs the first valve opening degree to the third valve opening degree calculation unit 104.
  • the third valve opening calculation unit 104 calculates the third valve opening using the subtracter P13 and the adder P14 (step S14).
  • the third valve opening calculation unit 104 outputs the third valve opening to the feed water flow rate adjustment valve control unit 105.
  • the feed water flow rate adjustment valve control unit 105 outputs the third valve opening degree as a command value to the feed water flow rate adjustment valve 71, and controls the opening degree of the feed water flow rate adjustment valve 71 (step S15).
  • the dump valve control unit 106 performs the following processing. First, the dump valve control unit 106 calculates a target flow rate by the function unit D10, and calculates a deviation between the target flow rate and the actual flow rate measured by the flow meter 16 (step S16). Next, the dump valve control unit 106 calculates the valve opening of the dump valve 72 such that the calculated deviation is zero, and controls the opening of the dump valve 72 with the calculated valve opening (step S17). The dump valve control unit 106 continues the processing from step S16 to step S17 by feedback control (for example, PI control).
  • feedback control for example, PI control
  • the temperature of the fuel gas on the outlet side of the fuel heating device 70 is monitored, and the heating supplied from the exhaust heat recovery boiler 20 to the fuel heating device 70 so that this temperature approaches the target fuel temperature. Control water flow. That is, if the temperature of the fuel gas on the outlet side is high, the opening of the feed water flow rate adjustment valve 71 is reduced to reduce the flow rate. On the other hand, if the temperature of the fuel gas on the outlet side is low, the feed water flow rate adjustment valve 71 is opened to increase the flow rate of the heated water so that the fuel gas is heated. Thereby, the temperature of fuel gas can be made into desired temperature.
  • the second valve opening calculation unit 103 can control the feed water flow rate adjustment valve 71 with an opening more suitable for the current situation by multiplying the coefficient according to the fuel temperature on the inlet side of the fuel heating device 70.
  • the present embodiment is not limited to the above configuration. For example, the following embodiments are also conceivable.
  • the third valve opening calculation unit 104 calculates a valve opening correction amount according to the deviation between the measured temperature of the fuel gas and the target fuel temperature, and adjusts this correction amount by feedback control such as PI control.
  • the temperature of the fuel gas at the outlet side of the fuel heating device 70 may be made closer to the target fuel temperature.
  • the second valve opening calculation unit 103 may not be provided. That is, the first valve opening calculation unit 102 calculates the opening (first valve opening) of the feed water flow rate adjustment valve 71 according to the load of the gas turbine 10. Next, the third valve opening calculation unit 104 calculates a correction amount of the valve opening corresponding to the deviation between the fuel gas temperature and the target fuel temperature, adds this correction amount to the first valve opening, Calculate the 3 valve opening.
  • the feed water flow rate adjustment valve control unit 105 performs control to set the opening degree of the feed water flow rate adjustment valve 71 to the third valve opening degree.
  • the third valve opening calculation unit 104 may not be provided. That is, the first valve opening calculation unit 102 calculates the opening (first valve opening) of the feed water flow rate adjustment valve 71 according to the load of the gas turbine 10. Next, the second valve opening calculation unit 103 calculates the second valve opening by multiplying the first valve opening by a coefficient corresponding to the temperature of the fuel gas on the inlet side of the fuel heating device 70. The feed water flow rate adjustment valve control unit 105 performs control to set the opening degree of the feed water flow rate adjustment valve 71 to the second valve opening degree.
  • the control device 100A controls the dump valve 72 by a method different from that of the first embodiment.
  • the dump valve control unit 106 calculates the target flow rate using the function unit D10.
  • the dump valve control unit 106 ⁇ / b> A switches the target flow rate for controlling the dump valve 72 according to the load of the gas turbine 10.
  • FIG. 6 is a block diagram of a control device according to the second embodiment of the present invention.
  • the control device 100A includes an operation data acquisition unit 101, a first valve opening calculation unit 102, a second valve opening calculation unit 103, a third valve opening calculation unit 104, and a feed water flow rate adjustment valve.
  • a control unit 105, a dump valve control unit 106A, and a storage unit 107 are provided.
  • the dump valve control unit 106A sets a flow rate smaller than the flow rate of the feed water passing through the feed water flow rate adjustment valve 71 as a target flow rate, and the load on the gas turbine 10 has a predetermined value.
  • the flow rate calculated using the function unit D10 is set as the target flow rate as in the first embodiment.
  • the dump valve control unit 106A calculates the opening degree of the dump valve 72 by feedback control based on the deviation between the target flow rate and the actual feed water flow rate (measured value by the flow meter 16).
  • FIG. 7 is a diagram illustrating a method for controlling the feed water flow rate to the fuel heating device according to the second embodiment of the present invention.
  • the dump valve control unit 106A includes a function unit D10, a subtractor D11, a controller D12, a function unit D13, a controller D14, a multiplier D15, and a switch D16.
  • the function unit D10 inputs the load of the gas turbine 10 and calculates a target flow rate according to the load.
  • the subtractor D11 calculates the deviation between the two by subtracting the actual feed water flow rate from the target flow rate.
  • the controller D12 calculates the valve opening degree of the dump valve 72 that brings the deviation calculated by the subtractor D11 close to 0 by PI control.
  • the function unit D13 receives the valve opening command value to the feed water flow rate adjustment valve 71 and calculates the CV value of the feed water flow rate adjustment valve 71.
  • the controller D14 inputs the CV value calculated by the function unit D13 and the differential pressure of the feed water flow rate adjustment valve 71, and calculates the flow rate of the heated water flowing through the feed water flow rate adjustment valve 71.
  • the calculated flow rate is described as a flow rate command value.
  • the controller D14 acquires the measured value of the pressure gauge 17 provided on the upstream side of the feed water flow rate adjustment valve 71 and the measured value of the pressure gauge 18 provided on the downstream side, and calculates the differential pressure of the feed water flow rate adjustment valve 71. Calculate (measured value of pressure gauge 17 ⁇ measured value of pressure gauge 18).
  • the multiplier D15 inputs the flow rate command value of the feed water flow rate adjustment valve 71 calculated by the controller D14, and calculates the target flow rate for high load by 0.95 times (95%).
  • the switch D16 switches the target flow rate between the target flow rate by the function unit D10 and the target flow rate (for high load) by the multiplier D15 in accordance with the magnitude of the load of the gas turbine 10.
  • the function unit D10 inputs a gas turbine load and calculates a target flow rate.
  • the function unit D10 outputs the target flow rate to the switch D16.
  • This target flow rate is a target flow rate at the time of medium to low load.
  • the target flow rate at the time of high load is calculated as follows.
  • the function unit D13 calculates the CV value of the feed water flow rate adjustment valve 71 at the current opening.
  • the controller D14 calculates a flow rate command value flowing through the feed water flow rate adjustment valve 71 based on the CV value and the differential pressure before and after the feed water flow rate adjustment valve 71.
  • the controller D14 outputs the calculated flow rate to the multiplier D15.
  • the multiplier D15 calculates a target flow rate at a high load corresponding to 95% of the flow rate.
  • the multiplier D15 outputs the target flow rate to the switch D16.
  • the switch D16 receives the load (GTMW) of the gas turbine 10 and outputs a target flow for high load to the subtracter D11 when the load exceeds, for example, 80% of the rated load. When the load is 80% or less, the target flow rate for medium and low loads is output to the subtracter D11.
  • the feed water flow rate adjustment valve 71 is controlled based on the fuel temperature, while the dump valve 72 is controlled based on the feed water flow rate. May not settle to the value of.
  • the target flow rate is switched to a flow rate command value calculated from an opening degree command for the feed water flow rate control valve 71 in a high load operation (for example, a load of 80% or more). Furthermore, by setting 95% of the calculated flow rate command value as the target flow rate of the dump valve 72, the target flow rate of the feed water flow rate adjustment valve 71 is not exceeded. For this reason, it is possible to appropriately control the fuel temperature without interfering with the feed water flow rate control.
  • the load is low, such as when starting or stopping, feedback control is performed using a function unit D10 that calculates a target flow rate according to the load of the gas turbine 10 as usual.
  • 95% of the flow rate command value of the feed water flow rate adjustment valve 71 is set as the target flow rate.
  • the value calculated by the container D11 is a negative value, and the dump valve 72 is controlled to be fully closed (opening degree 0%).
  • the dump valve 72 is controlled with an opening (> 0%) that compensates for the insufficient flow rate.
  • FIG. 8 is a flowchart showing an example of a water supply control process in the second embodiment according to the present invention.
  • the operation data acquisition unit 101 acquires operation data during operation of the GTCC (step S21). Specifically, the operation data acquisition unit 101 acquires the magnitude of the load of the gas turbine 10, the measurement value of the flow meter 16, and the opening command value of the feed water flow rate adjustment valve 71.
  • the dump valve control unit 106A determines whether the load exceeds 80% of the rated load based on the magnitude of the load of the gas turbine 10 (step S22). Specifically, the switch D16 inputs the value of the gas turbine load and performs the above determination.
  • the dump valve control unit 106A calculates a target flow rate according to the load (step S24). Specifically, the function unit D10 provided in the dump valve control unit 106A receives the load value and calculates a target flow rate corresponding to the magnitude of the load. The function unit D10 outputs the calculated target flow rate to the switch D16. The switch D16 outputs the input target flow rate to the subtracter D11.
  • the dump valve control unit 106A calculates the flow rate command value of the feed water flow rate adjustment valve 71, and sets a flow rate (for example, 95%) smaller than the flow rate command value as the target flow rate (Ste S23).
  • the function unit D13 calculates the CV value from the opening command value of the feed water flow rate adjustment valve 71
  • the controller D14 calculates the feed water flow rate control valve from the CV value and the differential pressure.
  • the flow rate command value of 71 is calculated
  • the multiplier D15 calculates the target flow rate of the dump valve 72 corresponding to 95% of the flow rate command value.
  • the multiplier D15 outputs the calculated target flow rate to the switch D16.
  • the switch D16 outputs the input target flow rate to the subtracter D11.
  • the dump valve controller 106A performs feedback control based on the deviation between the target flow rate and the actual flow rate (step S25). Specifically, the subtractor D11 acquires a measurement value obtained by the flow meter 16 from the operation data acquisition unit 101, and calculates a value obtained by subtracting the measurement value from the target flow rate. The controller D12 calculates the opening degree of the dump valve 72 that brings the deviation between the target flow rate and the measured value close to zero. The controller D12 repeats the process of step S25 by PI control.
  • interference between the fuel temperature control and the feed water flow rate control can be prevented by setting the target flow rate at the time of high load to be lower than the conventional one.
  • the dump valve 72 the function of ensuring the feed water flow rate can be exhibited during the start, stop, and partial load operation of the gas turbine 10, and the backup function can be exhibited during the high load operation of the gas turbine 10, as is conventional.
  • the above numerical values such as 80% and 95% are examples, and can be changed according to the operating conditions.
  • a method of controlling the feed water flow rate to the fuel heating apparatus according to the third embodiment of the present invention will be described with reference to FIGS.
  • the control device 100B according to the third embodiment will be described.
  • the control device 100B controls the flow rate of the heated water supplied to the fuel heating device 70 by a method different from the first embodiment and the second embodiment.
  • a three-way valve is provided on the upstream side of the fuel heating device 70, and a bypass path that connects the three-way valve to the downstream side of the fuel heating device 70 without passing through the fuel heating device 70 is provided.
  • control device 100B adjusts the opening degree of the three-way valve on the fuel heating device 70 side according to the deviation between the target temperature of the fuel gas and the measured value of the fuel gas temperature on the outlet side of the fuel heating device 70, The flow rate of the heating water passing through the fuel heating device 70 is controlled.
  • FIG. 9 is a block diagram of a control device according to the third embodiment of the present invention.
  • the control device 100B includes an operation data acquisition unit 101, a first valve opening calculation unit 102, a feed water flow rate adjustment valve control unit 105, a dump valve control unit 106, a storage unit 107, and a three-way valve. And a control unit 108.
  • the three-way valve control unit 108 controls the opening degree of the three-way valve 73 according to the deviation between the target temperature of the fuel gas and the fuel gas temperature on the outlet side of the fuel heating device 70.
  • FIG. 10 is a system diagram of the fuel heating device according to the third embodiment of the present invention.
  • a three-way valve 73 is provided in the heating water supply line L1 upstream of the water supply system of the fuel heating device 70, and a water supply flow rate adjustment valve 71 is provided in the heating water return line L2 downstream. Is provided.
  • a dump valve 72 is provided in the condensate line L3 branched from the heated water return line L2.
  • the three-way valve 73 includes an inlet through which heated water supplied from the exhaust heat recovery boiler 20 flows in, an outlet through which the heated water flows in to the fuel heating device 70, and the heated water that flows in the fuel heating device 70.
  • the three-way valve control unit 108 adjusts the valve opening degree of the outlet on the fuel heating device 70 side, the ratio of the heating water sent to the fuel heating device 70 side, the ratio of the heating water sent to the bypass line L4 side, Adjust. That is, in the third embodiment, the flow rate of the heated water flowing through the fuel heating device 70 is adjusted by the valve opening degree control on the fuel heating device 70 side, and the temperature of the fuel gas is controlled to a desired temperature.
  • a thermometer 15 is provided on the outlet side of the fuel heating device 70 in the fuel line R1.
  • a flow meter 16 is provided in the heating water supply line L1.
  • FIG. 11 is a diagram for explaining a control method of the feed water flow rate to the fuel heating device according to the third embodiment of the present invention.
  • the three-way valve control unit 108 includes a subtractor H10 and a controller H11.
  • the three-way valve control unit 108 acquires the temperature of the fuel gas on the outlet side of the fuel heating device 70 measured by the thermometer 15 from the operation data acquisition unit 101.
  • the three-way valve control unit 108 acquires the target fuel temperature from the operation data acquisition unit 101.
  • the subtractor H10 inputs the temperature of the fuel gas at the outlet side of the fuel heating device 70 and the target fuel temperature, and subtracts the temperature of the fuel gas at the outlet side of the fuel heating device 70 from the target fuel temperature.
  • the controller H11 calculates the valve opening of the three-way valve 73 on the fuel heating device 70 side so that the deviation between the target fuel temperature and the outlet side fuel gas temperature of the fuel heating device 70 approaches zero.
  • the three-way valve control unit 108 controls the opening of the three-way valve 73 on the fuel heating device 70 side so that the valve opening calculated by the controller H11 is obtained.
  • FIG. 12 is a first flowchart showing an example of a water supply control process in the third embodiment according to the present invention.
  • the operation data acquisition unit 101 acquires operation data during operation of the GTCC (step S31). Specifically, the operation data acquisition unit 101 acquires the temperature of the fuel gas and the target fuel temperature on the outlet side of the fuel heating device 70. The operation data acquisition unit 101 outputs these values to the three-way valve control unit 108.
  • the three-way valve control unit 108 calculates a deviation between the target fuel temperature and the actual temperature (step S32). Specifically, as described with reference to FIG.
  • the subtractor H ⁇ b> 10 calculates the deviation between the target fuel temperature and the value measured by the thermometer 15.
  • the three-way valve control unit 108 controls the opening degree of the three-way valve 73 on the fuel heating device 70 side (step S33). Specifically, the controller H11 calculates a valve opening that brings the deviation between the target fuel temperature and the measured value close to zero. The three-way valve control unit 108 performs control so that the opening degree of the three-way valve 73 on the fuel heating device 70 side becomes the valve opening degree calculated by the controller H11. The three-way valve control unit 108 repeats the process of step S33 by PI control. Although the example which controls the valve opening degree by the side of the fuel heating apparatus 70 of the three-way valve 73 was described in step S33, you may control the valve opening degree by the side of the bypass line L4.
  • FIG. 13 is a flowchart which shows the 2nd example of the water supply control process in 3rd embodiment which concerns on this invention.
  • the operation data acquisition unit 101 acquires operation data during operation of the GTCC (step S41). Specifically, the operation data acquisition unit 101 acquires the magnitude of the load of the gas turbine 10 and the measurement value of the flow meter 16.
  • the 1st valve opening calculation part 102 calculates the 1st valve opening according to the magnitude
  • the first valve opening calculation unit 102 outputs the first valve opening to the feed water flow rate adjustment valve control unit 105.
  • the water supply flow rate adjustment valve control unit 105 controls the water supply flow rate adjustment valve 71 so that the opening degree of the water supply flow rate adjustment valve 71 becomes the first valve opening degree (step S43).
  • the dump valve control unit 106 performs the following processing. First, the dump valve control unit 106 calculates a target flow rate by the function unit D10, and calculates a deviation between the target flow rate and the actual flow rate measured by the flow meter 16 (step S44). Next, the dump valve control unit 106 calculates the valve opening degree of the dump valve 72 so that the calculated deviation is 0, and controls the opening degree of the dump valve 72 with the calculated valve opening degree (step S45). The dump valve control unit 106 continues the processing from step S44 to step S45 by feedback control (for example, PI control).
  • feedback control for example, PI control
  • the temperature of the fuel gas at the outlet side of the fuel heating device 70 is monitored, and the exhaust heat recovery is performed so that the outlet side fuel gas temperature approaches the target fuel temperature by the valve opening degree control of the three-way valve 73.
  • the flow rate of the heating water supplied from the boiler 20 to the fuel heating device 70 is controlled. That is, if the temperature of the fuel gas at the outlet side is high, the valve opening degree of the three-way valve 73 on the fuel heating device 70 side is reduced, and the flow rate of the heated water flowing into the fuel heating device 70 is reduced.
  • the valve opening degree of the three-way valve 73 on the fuel heating device 70 side is opened, the flow rate of the heating water flowing into the fuel heating device 70 is increased, and the fuel gas is further increased. Try to heat. Thereby, the temperature of fuel gas can be made into desired temperature.
  • a three-way valve 73 is newly provided, and the control logic described with reference to FIG. The gas temperature can be controlled.
  • Control devices 100, 100A, and 100B are examples of control systems. Operation data acquisition unit 101, first valve opening calculation unit 102, second valve opening calculation unit 103, third valve opening calculation unit 104, feed water flow rate adjustment valve control unit 105, dump valve control units 106, 106A, 3 At least a part of the direction valve control unit 108 is a function provided when a processor provided in the control device 100 or the like reads out and executes a program from the storage unit 107 such as a hard disk.
  • All or part of the direction valve control unit 108 is equipped with hardware such as a microcomputer, LSI (Large Scale Integration), ASIC (Application Specific Integrated Circuit), PLD (Programmable Logic Device), FPGA (Field-Programmable Gate Array). It may be realized using.
  • storage part 107 are examples of a water supply flow volume adjustment part.
  • storage part 107 are examples of a water supply flow volume adjustment part.
  • the operation data acquisition unit 101, the first valve opening calculation unit 102, the feed water flow rate adjustment valve control unit 105, the dump valve control unit 106, the storage unit 107, and the three-way valve control unit 108 included in the control device 100B are a feed water flow rate adjustment unit. It is an example.
  • GTCC is an example of a power plant.
  • control system gas turbine, power plant, and fuel temperature control method described above, by controlling the flow rate of feed water supplied to the fuel heating device while monitoring the temperature of the fuel on the outlet side of the fuel heating device.
  • the temperature of the fuel can be controlled to a desired temperature.

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PCT/JP2018/000499 2017-01-16 2018-01-11 制御システム、ガスタービン、発電プラント及び燃料温度の制御方法 Ceased WO2018131654A1 (ja)

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US16/475,246 US11125166B2 (en) 2017-01-16 2018-01-11 Control system, gas turbine, power generation plant, and method of controlling fuel temperature
CN201880006340.1A CN110168207B (zh) 2017-01-16 2018-01-11 控制系统、燃气轮机、发电设备以及燃料温度的控制方法
KR1020197019728A KR102226983B1 (ko) 2017-01-16 2018-01-11 제어 시스템, 가스 터빈, 발전 플랜트 및 연료 온도의 제어 방법
DE112018000394.9T DE112018000394B4 (de) 2017-01-16 2018-01-11 Steuersystem, Gasturbine, Energieerzeugungsanlage und Verfahren zum Steuern einer Brennstofftemperatur

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