WO2017018154A1 - 給水方法、この方法を実行する給水系統、給水系統を備える蒸気発生設備 - Google Patents
給水方法、この方法を実行する給水系統、給水系統を備える蒸気発生設備 Download PDFInfo
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- WO2017018154A1 WO2017018154A1 PCT/JP2016/070116 JP2016070116W WO2017018154A1 WO 2017018154 A1 WO2017018154 A1 WO 2017018154A1 JP 2016070116 W JP2016070116 W JP 2016070116W WO 2017018154 A1 WO2017018154 A1 WO 2017018154A1
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- water
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- 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
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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
-
- 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
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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
- 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
- F01K7/34—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 of extraction or non-condensing type; Use of steam for feed-water heating
- F01K7/38—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 of extraction or non-condensing type; Use of steam for feed-water heating the engines being of turbine type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas- turbine plants for special use
- F02C6/18—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
- F02C7/12—Cooling of plants
- F02C7/14—Cooling of plants of fluids in the plant, e.g. lubricant or fuel
- F02C7/141—Cooling of plants of fluids in the plant, e.g. lubricant or fuel of working fluid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C9/00—Controlling gas-turbine plants; Controlling fuel supply in air- breathing jet-propulsion plants
- F02C9/26—Control of fuel supply
- F02C9/28—Regulating systems responsive to plant or ambient parameters, e.g. temperature, pressure, rotor speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B1/00—Methods of steam generation characterised by form of heating method
- F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
- F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22D—PREHEATING, OR ACCUMULATING PREHEATED, FEED-WATER FOR STEAM GENERATION; FEED-WATER SUPPLY FOR STEAM GENERATION; CONTROLLING WATER LEVEL FOR STEAM GENERATION; AUXILIARY DEVICES FOR PROMOTING WATER CIRCULATION WITHIN STEAM BOILERS
- F22D1/00—Feed-water heaters, i.e. economisers or like preheaters
- F22D1/02—Feed-water heaters, i.e. economisers or like preheaters with water tubes arranged in the boiler furnace, fire tubes, or flue ways
- F22D1/12—Control devices, e.g. for regulating steam temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22D—PREHEATING, OR ACCUMULATING PREHEATED, FEED-WATER FOR STEAM GENERATION; FEED-WATER SUPPLY FOR STEAM GENERATION; CONTROLLING WATER LEVEL FOR STEAM GENERATION; AUXILIARY DEVICES FOR PROMOTING WATER CIRCULATION WITHIN STEAM BOILERS
- F22D1/00—Feed-water heaters, i.e. economisers or like preheaters
- F22D1/02—Feed-water heaters, i.e. economisers or like preheaters with water tubes arranged in the boiler furnace, fire tubes, or flue ways
- F22D1/14—Safety or venting devices
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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
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- 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 water supply method, a water supply system for executing the method, and a steam generation facility including the water supply system.
- This application claims priority based on Japanese Patent Application No. 2015-146735 for which it applied to Japan on July 24, 2015, and uses the content here.
- the combined cycle plant includes a gas turbine, an exhaust heat recovery boiler that generates steam using the heat of exhaust gas from the turbine, a steam turbine that is driven by the steam from the exhaust heat recovery boiler, and an exhaust from the steam turbine. And a condenser for returning the generated steam to water.
- the water in the condenser is sent to the exhaust heat recovery boiler via the water supply line.
- the fuel of the gas turbine is preheated using water heated by an exhaust heat recovery boiler.
- the exhaust heat recovery boiler is configured to combine a water-saving unit that heats water by exchanging heat between water supplied to the exhaust heat recovery boiler and exhaust gas from the gas turbine, and water and exhaust gas heated by the economizer.
- An evaporator that heat-exchanges water into steam.
- a heating / water supply line for sending water heated by the economizer to the evaporator branches off in the middle.
- the branch line branched from the heating / water supply line is connected to a fuel preheater for heating the fuel of the gas turbine.
- the fuel preheater heats the fuel by exchanging heat between the fuel and water from the branch line.
- the fuel preheater is connected to a recovery line that returns water that has exchanged heat with the fuel. This collection line is connected to the water supply line.
- the present invention pays attention to the above-mentioned problems, and even when the amount of heat exchange between water and a medium such as fuel suddenly decreases, the flow of water flowing in the line is rapidly decreased while preventing the water from flashing. It aims at providing the water supply method which can be suppressed, the water supply system which performs this method, and the steam generation equipment provided with this water supply system.
- the water supply system as the first aspect according to the invention for solving the above problems is A first water supply line through which the first water supply flows, a second water supply line through which a second water supply having a lower pressure than the first water supply flows, a first heater for heating the first water supply, and the first heater.
- a first water supply introduction line that guides the first heated water supply that is the heated first water supply to the second water supply line, and a heat exchange between the first heated water supply and the medium that is provided in the first water supply introduction line And while cooling the first heated feed water, while the medium heat exchanger that heats the medium, in the first feed water introduction line at a position closer to the second feed water line than the medium heat exchanger,
- a cooling water injection line for injecting cooling water having a temperature lower than that of the first heating water supply.
- the cooling water is injected into the first water supply introduction line from the cooling water injection line.
- the 1st heating water supply is not discharge
- the cooling water injection line is a portion in the first water supply line through which the first unheated water supply that is the first water supply that is not heated by the first heater flows.
- the cooling water injection line injects the first unheated water supply as the cooling water into the first water supply introduction line.
- the first unheated water supply that is the first water supply that is not heated by the first heater is used as the cooling water for cooling the first water supply immediately after flowing out of the medium heat exchanger. For this reason, in the said water supply system, it is not necessary to provide the apparatus which pressurizes this cooling water separately so that cooling water can be inject
- a water supply system as a third aspect according to the invention for solving the above problems is In the water supply system of the first or second aspect, in the first water supply introduction line, at a position closer to the second water supply line than a position where the cooling water from the cooling water injection line is injected.
- the flow rate of the cooling water is adjusted based on the temperature of the water in the first water supply introduction line. For this reason, in the water supply system, the temperature of the water introduced from the first water supply introduction line to the second water supply line is managed, and the occurrence of flushing in the process of introducing this water into the second water supply line is accurately prevented. be able to.
- the water supply system as the fourth aspect according to the invention for solving the above problems is In the water supply system according to any one of the first to third aspects, in the first water supply introduction line, the second water supply line side from the position where the cooling water from the cooling water injection line is injected. And a flow rate adjusting valve that adjusts the flow rate of water flowing from the first water supply introduction line to the second water supply line.
- the flow rate of water after the water is introduced from the first water supply introduction line to the second water supply line can be managed in the second water supply line.
- a water supply system as a fifth aspect according to the invention for solving the above problems is as follows:
- the first heater causes the compressed air extracted from a compressor of a gas turbine to exchange heat with the first water supply, and the compressed air It is a heat exchanger which heats said 1st feed water while cooling.
- the first water supply line includes a first water supply main line and a first water supply branch line branched from the first water supply main line.
- a second heater that heats the first water supply that is provided in the first water supply main line and is provided downstream of the branch position with the first water supply branch line and that flows through the first water supply main line;
- the first heater is provided in the first water supply branch line and heats the first water supply flowing through the first water supply branch line.
- a water supply system as a seventh aspect according to the invention for solving the above problems is as follows:
- the first water supply introduction line is connected to the first water supply branch line, and the first heater is the first water supply introduction line in the first water supply branch line.
- the first water supply branch line is located in the first water supply main line on the downstream side of the position where the second heater is provided. It is connected.
- a water supply system as an eighth aspect according to the invention for solving the above problems is as follows: In the water supply system according to any one of the first to seventh aspects, before the medium is heated in the first medium heat exchanger that is the medium heat exchanger, the medium is heat exchanged with water, A second medium heat exchanger for cooling the water while heating the medium;
- the second medium heat exchanger is provided on the downstream side of the second water supply line from the position where the first water supply introduction line is connected, and the second water supply It is a heat exchanger for exchanging heat between water flowing through the line and the medium.
- a water supply system as a tenth aspect according to the invention for solving the above problems is as follows:
- the medium is a fuel supplied to a gas turbine, and the medium heat exchanger is a fuel preheater that heats the fuel.
- the steam generation facility as the eleventh aspect according to the invention for solving the above problems is as follows:
- the first water supply is heated by exchanging heat between the water supply system according to any one of the first to tenth aspects, exhaust gas from a gas turbine, and the first water supply that has passed through the first water supply line.
- an evaporator for converting to steam is as follows:
- the steam generation facility as the twelfth aspect according to the invention for solving the above problems is
- the first water supply is heated by exchanging heat between the water supply system according to any one of the first to fourth aspects, the exhaust gas from the gas turbine, and the first water supply that has passed through the first water supply line.
- An evaporator that converts the gas into steam, and the first heater is a economizer that heats the first feed water flowing into the evaporator by exchanging heat between the exhaust gas and the first feed water. is there.
- the steam generation facility as the thirteenth aspect according to the invention for solving the above problems is: Heat exchange is performed between the water supply system of the sixth or seventh aspect, the exhaust gas from the gas turbine and the first water supply that has passed through the first water supply line, and the first water supply is heated to steam.
- the second heater is a economizer that heats the first feed water flowing into the evaporator by exchanging heat between the exhaust gas and the first feed water.
- the water supply method as the fourteenth aspect according to the invention for solving the above problems is as follows: While the first heating step of heating the first feed water and the first heating feed water that is the first feed water heated in the first heating step and the medium are heat-exchanged to cool the first heating feed water A medium heat exchange step for heating the medium, a first feed water introduction step for introducing the first heated feed water after the medium heat exchange step into a second feed water having a pressure lower than that of the first feed water, and the medium. A cooling water injection step for injecting cooling water having a temperature lower than that of the first heating water supply into the first heating water supply after the heat exchange step and before being introduced into the second water supply water, Execute.
- the water supply method even if the flow rate of the medium that is the heat exchange target with the first heating water supply in the medium heat exchange process is reduced and the cooling amount for the first heating water supply is reduced, By injecting the cooling water into the one water supply water, it is possible to prevent the flash from being generated in the process of the first heat water supply flowing into the second water supply water. Furthermore, in the water supply method, since the first heated water supply is not discharged out of the system, it is possible to suppress a rapid decrease in water after the first heated water supply joins the second water supply.
- a water supply method as a fifteenth aspect according to the invention for solving the above problems is as follows: In the water supply method of the fourteenth aspect, in the cooling water injection step, the first unheated water supply that is the first water supply that is not heated in the first heating step is used as the cooling water.
- the first unheated water supply which is the first water supply not heated in the first heating process, is used as the cooling water for cooling the first water supply immediately after the medium heat exchange process. For this reason, in the water supply method, it is not necessary to separately provide a device for boosting the cooling water so that the cooling water can be injected into the first water supply immediately after the medium heat exchange step.
- a water supply method as a sixteenth aspect according to the invention for solving the above problems is as follows: In the water supply method of the fourteenth or the fifteenth aspect, in the cooling water injection step, the temperature of the water is determined in advance before water including the first heated water supply is introduced into the second water supply. A cooling water flow rate adjusting step of adjusting the flow rate of the cooling water so as to be within the set temperature range.
- the flow rate of the cooling water is adjusted based on the temperature of the water including the first heating water supply. For this reason, in the said water supply system method, generation
- the water supply method as the seventeenth aspect according to the invention for solving the above problems is as follows: In the water supply method according to any one of the fourteenth to the sixteenth aspects, a flow rate adjusting step of adjusting a flow rate of water including the first heated water supply introduced into the second water supply is performed.
- the flow rate of water after the first water supply is introduced into the second water supply can be managed.
- the eighteenth aspect of the water supply method according to the invention for solving the above problems is as follows: In the water supply method according to any one of the fourteenth to the seventeenth aspects, in the first heating step, the compressed air extracted from a compressor of a gas turbine and the first water supply are heat-exchanged, The first feed water is heated while cooling the compressed air.
- a water supply method as a nineteenth aspect according to the invention for solving the above problems is as follows: In the water supply method according to any one of the fourteenth to eighteenth aspects, in the medium heat exchange step, fuel supplied to a gas turbine is used as the medium, and heat exchange is performed between the first heated water supply and the fuel. The fuel is heated while cooling the first heating water supply.
- the combined cycle plant of the present embodiment includes a gas turbine facility 1 and an exhaust heat recovery facility 100 that recovers the heat of the exhaust gas EG from the gas turbine facility 1, as shown in FIG.
- the gas turbine equipment 1 includes a gas turbine 10, a fuel supply system 20 that supplies fuel F to the gas turbine 10, and a component cooling system 30 that cools high-temperature components among the components constituting the gas turbine 10.
- the gas turbine 10 includes a compressor 11 that compresses air A, a combustor 19 that generates fuel gas by burning fuel F in the air compressed by the compressor 11, and a turbine that is driven by high-temperature and high-pressure combustion gas.
- the compressor 11 includes a compressor rotor 12 that rotates about an axis Ar, and a compressor casing 13 that covers the compressor rotor 12.
- the turbine 14 includes a turbine rotor 15 that rotates about an axis Ar and a turbine casing 16 that covers the turbine rotor 15.
- the turbine rotor 15 includes a rotor shaft 15a and a plurality of moving blade rows 15b attached to the outer periphery of the rotor shaft 15a.
- a stationary blade row 17 arranged on the upstream side of each blade row 15b is fixed to the inner periphery of the turbine casing 16.
- the compressor rotor 12 and the turbine rotor 15 rotate about the same axis Ar, and are connected to each other to form a gas turbine rotor.
- a rotor of a generator G is connected to the gas turbine rotor.
- the compressor casing 13 and the turbine casing 16 are connected to each other to form a gas turbine casing.
- the fuel supply system 20 includes a fuel supply line 21 that supplies the fuel F to the combustor 19 of the gas turbine 10, and a fuel flow rate adjustment valve 22 that adjusts the flow rate of the fuel F supplied from the fuel supply line 21 to the combustor 19.
- the first fuel preheater 23 and the second fuel preheater 24 that heat the fuel F flowing through the fuel supply line 21 are provided.
- the component cooling system 30 bleeds the air compressed by the compressor 11, extracts an bleed line 31 that guides the air to the high-temperature components of the turbine 14, and an air cooler 32 that cools the air passing through the bleed line 31.
- the high-temperature component here is a component that is exposed to the combustion gas generated in the combustor 19.
- the combustor 19, the moving blade row 15 b of the turbine rotor 15, the stationary blade row 17, and the like correspond to high-temperature parts.
- the exhaust heat recovery equipment 100 includes an exhaust heat recovery boiler 110 that generates steam by the heat of the combustion gas that drives the turbine 14, that is, the exhaust gas EG exhausted from the gas turbine 10, and the exhaust gas that has passed through the exhaust heat recovery boiler 110.
- a chimney 119 that releases the gas EG to the atmosphere, steam turbines 121a, 121b, and 121c that are driven by steam generated in the exhaust heat recovery boiler 110, a condenser 123 that returns the steam that has driven the steam turbine 121a to water,
- a water supply pump 124 that returns the water in the condenser 123 to the exhaust heat recovery boiler 110.
- the exhaust heat recovery facility 100 includes a low-pressure steam turbine 121a, an intermediate-pressure steam turbine 121b, and a high-pressure steam turbine 121c as the steam turbines 121a, 121b, and 121c.
- the rotors of the steam turbines 121a, 121b, and 121c are connected to each other.
- the rotor of the generator G is connected to this rotor, for example.
- the generator G that generates power by driving the steam turbines 121a, 121b, and 121c and the generator G that generates power by driving the gas turbine 10 are separate generators. There may be.
- the exhaust heat recovery boiler 110 includes a low-pressure steam generator 111a that generates low-pressure steam LS, an intermediate-pressure steam generator 111b that generates intermediate-pressure steam IS, a high-pressure steam generator 111c that generates high-pressure steam HS, and a high-pressure steam. And a reheater 115 that heats the steam that has driven the turbine 121c.
- the low-pressure steam generator 111a, the intermediate-pressure steam generator 111b, and the high-pressure steam generator 111c are all heated by the economizers 112a, 112b, and 112c that heat water and the economizers 112a, 112b, and 112c.
- the medium pressure steam generator 111b and the high pressure steam generator 111c are water heated by the economizer 112a of the low pressure steam generator 111a, in addition to the economizers 112b and 112c, the evaporators 113b and 113c, and the superheaters 114b and 114c.
- Has pumps 116b and 116c that send the fuel to their economizers 112b and 112c.
- the economizer 112c of the high-pressure steam generator 111c is referred to as a high-pressure economizer 112c
- the evaporator 113c of the high-pressure steam generator 111c is referred to as a high-pressure evaporator 113c
- the superheater 114c of the high-pressure steam generator 111c is high-pressure. Let it be a superheater 114c.
- the economizer 112b of the intermediate pressure steam generator 111b is an intermediate pressure economizer 112b
- the evaporator 113b of the intermediate pressure steam generator 111b is an intermediate pressure evaporator 113b
- the superheater 114b of the intermediate pressure steam generator 111b is referred to as a high-pressure economizer 112c
- the evaporator 113b of the intermediate pressure steam generator 111b is an intermediate pressure evaporator 113b
- the economizer 112a of the low-pressure steam generator 111a is the low-pressure economizer 112a
- the evaporator 113a of the low-pressure steam generator 111a is the low-pressure evaporator 113a
- the superheater 114a of the low-pressure steam generator 111a is the low-pressure superheater 114a.
- the pump 116b of the intermediate pressure steam generator 111b is an intermediate pressure pump 116b
- the pump 116c of the high pressure steam generator 111c is a high pressure pump 116c.
- Reheater 115 high pressure superheater 114c, high pressure evaporator 113c, high pressure economizer 112c, medium pressure superheater 114b, medium pressure evaporator 113b, medium pressure economizer 112b, low pressure superheater 114a, low pressure evaporator 113a,
- the low-pressure economizer 112a is arranged in this order toward the downstream side of the exhaust gas EG from the turbine 14 toward the chimney 119. This order is an example, and other orders may be used.
- the condenser 123 and the low-pressure economizer 112a are connected by a water supply line 131.
- the water supply line 131 is provided with the above-described water supply pump 124.
- the low pressure superheater 114a and the steam inlet of the low pressure steam turbine 121a are connected by a low pressure steam line 132 that sends the low pressure steam LS from the low pressure superheater 114a to the low pressure steam turbine 121a.
- the steam outlet of the low-pressure steam turbine 121 a and the condenser 123 are connected to each other so that the low-pressure steam LS that drives the low-pressure steam turbine 121 a is supplied to the condenser 123.
- the high pressure superheater 114c and the steam inlet of the high pressure steam turbine 121c are connected by a high pressure steam line 138 that sends the high pressure steam HS from the high pressure superheater 114c to the high pressure steam turbine 121c.
- the steam outlet of the high pressure steam turbine 121c and the steam inlet of the reheater 115 are connected by a high pressure steam recovery line 139 that sends the high pressure steam HS from the high pressure steam turbine 121c to the reheater 115.
- the steam outlet of the reheater 115 and the steam inlet of the intermediate pressure steam turbine 121b are connected by a reheat steam line 136 that sends the high pressure steam HS superheated by the reheater 115 to the intermediate pressure steam turbine 121b as the reheat steam RHS.
- An intermediate pressure steam recovery line 137 is connected to the steam outlet of the intermediate pressure steam turbine 121b.
- the intermediate pressure steam recovery line 137 is connected to the low pressure steam line 132.
- An intermediate pressure steam line 133 is connected to the steam outlet of the intermediate pressure superheater 114b.
- This intermediate pressure steam line 133 is connected to a high pressure steam recovery line 139.
- the discharge port of the intermediate pressure pump 116b and the water inlet of the intermediate pressure economizer 112b are connected by an intermediate pressure water line 141.
- the water outlet of the medium pressure economizer 112 b and the water inlet of the intermediate pressure evaporator 114 b are connected by an intermediate pressure heating water line 142.
- the discharge port of the high pressure pump 116 c and the water inlet of the high pressure economizer 112 c are connected by a high pressure water line 143.
- the water outlet of the high pressure economizer 112c and the water inlet of the high pressure evaporator 113c are connected by a high pressure heating water line 144.
- the exhaust heat recovery equipment 100 further includes the air cooler 32, the first fuel preheater 23, and the second fuel preheater 24, the air cooler 32, the first fuel preheater 23, and the second fuel preheater 24. And various lines for sending water heated by the exhaust heat recovery boiler 110.
- the air cooler 32, the first fuel preheater 23, and the second fuel preheater 24 constitute a part of the exhaust heat recovery facility 100 and also a part of the gas turbine facility 1.
- the intermediate pressure heating water branch line 145 is connected to the intermediate pressure heating water line 142.
- the intermediate pressure heated water branch line 145 is connected to the water inlet of the first fuel preheater 23.
- the first fuel preheater 23 heat-exchanges the medium pressure heating water and the fuel F from the medium pressure heating water branch line 145 to heat the fuel F, while cooling the medium pressure heating water.
- the intermediate pressure heated water branch line 145 is provided with a flow meter 166 for detecting the flow rate of the intermediate pressure heated water flowing therethrough.
- An intermediate pressure water recovery line 146 is connected to the water outlet of the first fuel preheater 23.
- the intermediate pressure water recovery line 146 is connected to the water supply line 131.
- the intermediate pressure water recovery line 146 is provided with a recovered water flow rate adjustment valve 165.
- the recovered water flow rate adjustment valve 165 adjusts the valve opening so that the flow rate detected by the flow meter 166 provided in the intermediate pressure heating water branch line 145 becomes the target flow rate.
- the target flow rate is a flow rate determined according to, for example, the flow rate of fuel supplied to the gas turbine 10 or the output of the gas turbine.
- the high-pressure water line 143 branches into two lines along the way, one line forms a high-pressure water main line 147 connected to the high-pressure economizer 112c, and the other line forms a high-pressure water branch line 148.
- the high pressure water branch line 148 is connected to the high pressure heating water line 144.
- the high-pressure water branch line 148 is provided with an air cooler 32. The air cooler 32 heat-exchanges the high-pressure water from the high-pressure water branch line 148 and the air Ac extracted from the compressor 11 of the gas turbine 10 to heat the high-pressure water while cooling the air Ac.
- a high-pressure water introduction line 149 is connected between the connection position with the high-pressure heating water line 144 and the air cooler 32.
- the high-pressure water introduction line 149 is connected to the medium-pressure heating water branch line 145.
- the high pressure water introduction line 149 is provided with a second fuel preheater 24.
- the second fuel preheater 24 heat-exchanges the high pressure heated water from the high pressure water introduction line 149 and the fuel F heated by the first fuel preheater 23 to heat the fuel F, Cooling.
- the high-pressure heated water cooled by the second fuel preheater 24 is sent to the first fuel preheater 23 via the high-pressure water introduction line 149 and the medium-pressure heated water branch line 145 as high-pressure recovered water.
- a cooling water injection line 151 is connected to a position closer to the high-pressure pump 116c than a branch position of the high-pressure water branch line 148.
- the cooling water injection line 151 is connected to a position closer to the intermediate pressure heating water branch line 145 than the second fuel preheater 24 in the high pressure water introduction line 149.
- a cooling water flow rate adjustment valve 152 that adjusts the flow rate of high-pressure water as cooling water flowing through the cooling water injection line 151 and water from the high-pressure water introduction line 149 flow into the cooling water injection line 151.
- a check valve 153 is provided.
- thermometer 154 for detecting the temperature of the water flowing therethrough and the flow rate of the water flowing therethrough on the intermediate pressure heating water branch line 145 side from the connection position with the cooling water injection line 151.
- a recovered water flow rate adjustment valve 155 for adjusting the pressure.
- the steam generation facility includes an exhaust heat recovery boiler 110, an air cooler 32, a first fuel preheater 23, and a second fuel preheater 24. Furthermore, this steam generation facility includes various lines for mutually connecting the exhaust heat recovery boiler 110, each steam turbine 121a, 121b, 121c, the air cooler 32, the first fuel preheater 23, and the second fuel preheater 24; A valve provided in various lines and a water supply line 131 are provided.
- This steam generation facility includes a water supply system. This water supply system will be described later.
- the compressor 11 of the gas turbine 10 compresses air A in the atmosphere and supplies the compressed air A to the combustor 19. Further, the fuel F from the fuel supply line 21 is also supplied to the combustor 19. In the combustor 19, the fuel F is combusted in the compressed air A, and high-temperature and high-pressure combustion gas is generated. The combustion gas is sent to the turbine 14 and rotates the turbine rotor 15. The generator G connected to the gas turbine 10 generates electric power by the rotation of the turbine rotor 15.
- the combustion gas that has rotated the turbine rotor 15 is exhausted from the gas turbine 10 as exhaust gas EG, and is discharged from the chimney 119 to the atmosphere via the exhaust heat recovery boiler 110.
- the exhaust heat recovery facility 100 recovers heat contained in the exhaust gas EG in the process in which the exhaust gas EG from the gas turbine 10 passes through the exhaust heat recovery boiler 110.
- the water from the condenser 123 is supplied to the low pressure economizer 112 a of the exhaust heat recovery boiler 110 via the water supply line 131.
- the low pressure economizer 112a heats this water by exchanging heat with the exhaust gas EG.
- a part of the water heated by the low pressure economizer 112a is further heated by the low pressure evaporator 113a to become steam.
- This steam is further heated by the low-pressure superheater 114a and supplied as low-pressure steam LS to the low-pressure steam turbine 121a via the low-pressure steam line 132.
- the steam that has driven the low-pressure steam turbine 121 a returns to water in the condenser 123.
- This water is supplied again from the condenser 123 to the low-pressure economizer 112 a through the water supply line 131.
- the other part of the water heated by the low-pressure economizer 112a is pressurized by the intermediate-pressure pump 116b and sent to the intermediate-pressure economizer 112b through the intermediate-pressure water line 141 as intermediate-pressure water.
- the remaining water heated by the low-pressure economizer 112a is pressurized by the high-pressure pump 116c and sent to the high-pressure economizer 112c through the high-pressure water line 143 as high-pressure water.
- the high pressure economizer 112c heats the high pressure water sent from the high pressure pump 116c by exchanging heat with the exhaust gas EG.
- the high-pressure water heated by the high-pressure economizer 112c is sent to the high-pressure evaporator 113c as high-pressure heating water via the high-pressure heating water line 144.
- the high-pressure evaporator 113c exchanges heat between the high-pressure heated water and the exhaust gas EG, and turns this high-pressure heated water into steam. This steam is further heated by the high-pressure superheater 114c and supplied as high-pressure steam HS to the high-pressure steam turbine 121c via the high-pressure steam line 138.
- the medium pressure economizer 112b heats the medium pressure water sent from the medium pressure pump 116b by exchanging heat with the exhaust gas EG.
- the intermediate pressure water heated by the intermediate pressure economizer 112b is sent to the intermediate pressure evaporator 113b as intermediate pressure heated water via the intermediate pressure heated water line 142.
- the intermediate pressure evaporator 113b exchanges heat between the intermediate pressure heated water and the exhaust gas EG, and turns this intermediate pressure heated water into steam.
- This steam is further superheated by the intermediate pressure superheater 114b, and as the intermediate pressure steam IS, the most upstream side of the exhaust heat recovery boiler 110 (the gas turbine 10) via the intermediate pressure steam line 133 and the high pressure steam recovery line 139.
- Side reheater 115.
- the high-pressure steam HS driving the high-pressure steam turbine 121c and the medium-pressure steam IS from the intermediate-pressure superheater 114b are most upstream (gas turbine 10 side) in the exhaust heat recovery boiler 110 via the high-pressure steam recovery line 139.
- the reheater 115 superheats this steam by exchanging heat with the exhaust gas EG, and supplies it as reheated steam RHS to the intermediate pressure steam turbine 121b via the reheated steam line 136.
- the reheated steam RHS that has driven the intermediate pressure steam turbine 121b is supplied to the low pressure steam turbine 121a via the intermediate pressure steam recovery line 137 and the low pressure steam line 132.
- a part of the medium-pressure heated water that is medium-pressure water heated by the medium-pressure economizer 112 b is sent to the first fuel preheater 23 via the medium-pressure heated water branch line 145.
- the fuel F that has passed through the fuel supply line 21 and the medium-pressure heating water are heat-exchanged, and the fuel F is heated while the medium-pressure heating water is cooled.
- the intermediate pressure heated water cooled by the first fuel preheater 23 returns to the water supply line 131 through the intermediate pressure water recovery line 146 as intermediate pressure recovery water.
- the fuel F heated by the first fuel preheater 23 is sent to the second fuel preheater 24 through the fuel supply line 21.
- a part of the high-pressure water flowing through the high-pressure water main line 147 is sent to the air cooler 32 via the high-pressure water branch line 148.
- the air cooler 32 heat exchange is performed between the high pressure water and the air Ac extracted from the compressor 11 of the gas turbine 10, and the high pressure water is heated while the air Ac is cooled.
- the air Ac cooled by the air cooler 32 is sent to the high-temperature components of the turbine 14 through the extraction line 31.
- a part of the high-pressure water heated by the air cooler 32 is sent as high-pressure heating water to the high-pressure evaporator 113c via the high-pressure water branch line 148 and the high-pressure heating water line 144.
- the remaining part of the high-pressure heated water flowing through the high-pressure water branch line 148 is sent to the second fuel preheater 24 via the high-pressure water introduction line 149.
- the second fuel preheater 24 heat exchange is performed between the fuel F heated by the first fuel preheater 23 and the high pressure heating water, and the fuel F is heated while the high pressure heating water is cooled.
- the high pressure heated water cooled by the second fuel preheater 24 flows into the intermediate pressure heated water branch line 145 through the high pressure water introduction line 149 as high pressure recovered water.
- the high-pressure recovered water that has flowed into the intermediate-pressure heated water branch line 145 merges with the intermediate-pressure heated water that flows through the intermediate-pressure heated water branch line 145 and flows into the first fuel preheater 23.
- the fuel F heated by the second fuel preheater 24 is sent to the combustor 19 through the fuel supply line 21.
- the water supply system 50 of the present embodiment includes the high-pressure water line 143, the high-pressure heating water line 144, the medium-pressure heating water branch line 145, the high-pressure water introduction line 149, and the cooling water injection line described above. 151, valves and instruments provided in these lines, an air cooler 32, a second fuel preheater 24, and a high pressure economizer 112c.
- a line constituted by the high-pressure water line 143 and the high-pressure heating water line 144 is referred to as a first water supply line 51.
- the first water supply line 51 has a first water supply main line 51a and a first water supply branch line 51b.
- the first water supply main line 51a includes a high-pressure heating water line 144 and a high-pressure water main line 147 that constitutes a part of the high-pressure water line 143.
- the first water supply branch line 51b is composed of a high-pressure water branch line 148.
- the intermediate pressure heated water branch line 145 is referred to as a second water supply line 52.
- the high-pressure water introduction line 149 is referred to as a first water supply introduction line 53.
- the air cooler 32 be the 1st heater 32, and let the high pressure economizer 112c be the 2nd heater 112c.
- the first fuel preheater 23 is the second medium heat exchanger 23 and the second fuel preheater 24 is the first medium heat exchanger 24.
- a portion of the low-pressure heated water which is low-pressure water heated by the low-pressure economizer 112a, is boosted by the intermediate-pressure pump 116b and is supplied to the intermediate-pressure economizer 112b as intermediate-pressure water. Sent.
- This medium pressure water is heated by the medium pressure economizer 112b to become medium pressure heated water.
- the intermediate pressure heated water passes through the intermediate pressure heated water line 142 and the second water supply line 52 which is the intermediate pressure heated water branch line 145, and is supplied as the first fuel preheater 23 as the second supply water.
- the fuel F as the medium and the second feed water (medium pressure heating water) are heat-exchanged to heat the medium, while the second feed water is cooled.
- the other part of the low-pressure heating water which is low-pressure water heated by the low-pressure economizer 112a, is pressurized by the high-pressure pump 116c to become high-pressure water.
- the high-pressure water flows through the first water supply line 51 including the high-pressure water line 143 and the high-pressure heating water line 144 as the first water supply.
- the first water supply has a higher pressure than the second water supply flowing through the second water supply line 52. In other words, the pressure of the second water supply flowing through the second water supply line 52 is lower than that of the first water supply flowing through the first water supply line 51.
- the first water supply that flows through the first water supply line 51 and does not reach the first heater 32 and the second heater 112 c has a lower temperature than the second water supply that flows through the second water supply line 52.
- a part of the first water supply is sent to the second heater 112c which is the high-pressure economizer 112c via the first water supply main line 51a.
- the second heater 112c the first water supply is heated.
- the 1st water supply heated with the 2nd heater 112c is sent to the high pressure evaporator 113c through the 1st water supply main line 51a.
- Another part of the first water supply can be sent to the first heater 32 which is the air cooler 32 through the first water supply branch line 51b.
- the first water supply is heated (S1: first heating step).
- a part of the first water supply heated by the first heater 32 flows into the first water supply main line 51a through the first water supply branch line 51b.
- the first water supply heated by the first heater 32 is sent to the high-pressure evaporator 113c together with the first water supply heated by the second heater 112c.
- the other part of the first feed water heated by the first heater 32 passes through the first feed water introduction line 53 that is the high-pressure water introduction line 149 and passes through the first medium heat exchanger 24 that is the second fuel preheater 24. Sent to.
- the fuel F as the medium and the first feed water are heat-exchanged to heat the medium, while the first feed water is cooled (S2: medium heat exchange step).
- the fuel F as a medium to be heat exchanged with the first water supply in the first medium heat exchanger 24 is the fuel F heated in the second medium heat exchanger 23.
- the first water supply cooled in the medium heat exchange step (S2) is introduced into the second water supply line 52 through the first water supply introduction line 53 (S3: first water supply introduction step). This first water supply is sent to the second medium heat exchanger 23 together with the second water supply.
- the flow rate of the first water supply flowing through the first water supply introduction line 53 is detected by the flow meter 156.
- the recovered water flow rate adjustment valve 155 adjusts its valve opening so that the flow rate detected by the flow meter 156 becomes the target flow rate (S4: flow rate adjustment step).
- the target flow rate is determined according to the output of the gas turbine 10 and the flow rate of the fuel supplied to the gas turbine 10. For example, when the output of the gas turbine 10 or the flow rate of fuel supplied to the gas turbine 10 increases, the target flow rate also increases.
- the temperature of the first feed water immediately after flowing out of the first medium heat exchanger 24 is higher than the temperature of the first feed water before being heated by the first heater 32, and the second feed water flowing through the second feed water line 52.
- the temperature is close to the temperature.
- the first water supply is depressurized in the process of passing through the recovered water flow rate adjustment valve 155 provided in the first water supply introduction line 53, and becomes almost the same pressure as the pressure in the second water supply line 52.
- the cooling water injection step (S5) is also executed in parallel with the above steps.
- the temperature of the water flowing between the connection position with the cooling water injection line 151 and the first medium heat exchanger 24 in the first water supply introduction line 53 is detected by the thermometer 154.
- S6 Temperature detection step.
- the process returns to the temperature detection step (S6) (NO in S7).
- the process proceeds to the cooling water flow rate adjustment step (S8).
- the cooling water flow rate adjustment valve 152 is opened so that the temperature T1 detected by the thermometer 154 becomes the set temperature T0.
- the degree of flow is controlled, and the flow rate of the cooling water injected from the cooling water injection line 151 into the first feed water introduction line 53 is adjusted.
- This cooling water is the first unheated feed water that is the first feed water that is not heated by the first heater 32. Specifically, for example, when the temperature T1 detected by the thermometer 154 is higher than the set temperature T0, the cooling water flow rate adjustment valve 152 is opened.
- the opening degree of the cooling water flow rate adjustment valve 152 is, for example, an opening degree corresponding to a deviation between the temperature T1 detected by the thermometer 154 and the set temperature T0.
- the cooling water flow rate adjustment valve 152 is opened, and as a result, the cooling water is injected into the first water supply introduction line 53.
- the temperature on the second water supply line 52 side is lower than the cooling water injection line 151, and the temperature detected by the thermometer 154 becomes the set temperature T0.
- the cooling water and the first water supply are mixed and introduced into the second water supply line 52 through the recovered water flow rate adjustment valve 155.
- the flow rate of the water in which the cooling water and the first water supply are mixed is adjusted by the recovered water flow rate adjustment valve 155 (S4: flow rate adjustment step) and then introduced into the second water supply line 52.
- the cooling water flow rate adjustment valve 152 provided in the cooling water injection line 151 is closed as shown in FIG.
- the first water supply which is high-pressure water before being heated by the first heater 32, passes through the cooling water injection line 151, and serves as cooling water in the first water supply introduction line 53. Not injected into.
- the valve opening degree of the fuel flow control valve 22 provided in the fuel supply line 21 is suddenly completely closed or slightly opened. Changes to. In this case, the flow rate of the fuel F flowing through the fuel supply line 21 is rapidly reduced. When the flow rate of the fuel F rapidly decreases, the amount of heat exchange between the fuel F as the medium and water rapidly decreases in the first medium heat exchanger 24. As a result, the cooling amount of water flowing into the first medium heat exchanger 24 is drastically reduced, and the temperature of the first feed water immediately after flowing out of the first medium heat exchanger 24 is compared with that during steady operation of the gas turbine 10. Become higher.
- the first water supply introduced into the second water supply line 52 becomes higher than that during the steady operation of the gas turbine 10, the first water supply may be flushed in the process of flowing into the second water supply line 52. If the water is flushed in the line, there is a risk of damaging piping constituting the line and various devices provided in the line.
- the cooling water flow rate adjusting step (S8) in the cooling water injection step (S5) is executed.
- this cooling water flow rate adjustment step (S8) is executed, as shown in FIG. 3, the cooling water flow rate adjustment valve 152 is opened, and cooling water is injected from the cooling water injection line 151 into the first feed water introduction line 53, In the first water supply introduction line 53, the temperature of the water on the second water supply line 52 side is lower than the cooling water injection line 151, and the temperature T1 detected by the thermometer 154 becomes the set temperature T0.
- the first feed water introduction line 53 changes to the second feed water line 52. Flushing in the process of introducing water can be prevented.
- patent document 1 demonstrated in the column of background art. The cooling water is injected into the first water supply without discharging the first water supply to the condenser as in the technique described in 1).
- the set temperature T0 is slightly higher than the temperature of the first feed water flowing out from the first medium heat exchanger 24 during the steady operation of the gas turbine 10.
- the set temperature T0 may be, for example, a temperature slightly lower than the temperature of the first feed water flowing out from the first medium heat exchanger 24 during the steady operation of the gas turbine 10. In this case, during steady operation of the gas turbine 10, the temperature of the first water supply immediately after flowing out of the first medium heat exchanger 24 is slightly higher than the set temperature T0.
- the cooling water flow rate adjustment valve 152 is slightly opened, and the cooling water is injected from the cooling water injection line 151 into the first feed water introduction line 53, and the thermometer The temperature T1 detected at 154 becomes the set temperature T0.
- the temperature T1 detected by the thermometer 154 becomes the set temperature T0.
- the combined cycle plant of the present embodiment has a cooling water injection line 161, a cooling water flow rate adjustment valve 162, a check valve 163, and a thermometer 164 added to the combined cycle plant of the first embodiment.
- the other configuration is basically the same.
- One end of the cooling water injection line 161 is connected to the intermediate pressure water line 141, and the other end of the cooling water injection line 161 is connected to the first fuel preheater 23 and the recovered water flow rate adjustment valve 165 in the intermediate pressure water recovery line 146. Connected to a position between.
- the cooling water flow rate adjustment valve 162 and the check valve 163 are both provided in the cooling water injection line 161.
- the thermometer 164 is provided in the intermediate pressure water recovery line 146 at a position between the connection position with the cooling water injection line 161 and the recovered water flow rate adjustment valve 165.
- the combined cycle plant of the present embodiment is obtained by adding the cooling water injection line 161 and the like to the combined cycle plant of the first embodiment. Therefore, the combined cycle plant of this embodiment is also provided with the water supply system 50 (henceforth the 1st water supply system 50) which uses the air cooler 32 as the 1st heater 32 similarly to the combined cycle plant of 1st embodiment. . Furthermore, the combined cycle plant of the present embodiment includes a water supply system (hereinafter, referred to as a second water supply system 60) having the medium pressure economizer 112b as the first heater 112b.
- a water supply system hereinafter, referred to as a second water supply system 60 having the medium pressure economizer 112b as the first heater 112b.
- the second water supply system 60 of the present embodiment is provided in the medium pressure water line 141, the medium pressure heating water line 142, the medium pressure heating water branch line 145, the medium pressure water recovery line 146, the cooling water injection line 161, and these lines.
- a valve, a meter, a medium pressure economizer 112b, and a first fuel preheater 23 Provided with a valve, a meter, a medium pressure economizer 112b, and a first fuel preheater 23.
- a line constituted by the medium pressure water line 141 and the medium pressure heating water line 142 is referred to as a first water supply line 61.
- a water supply line 131 that connects the condenser 123 and the low-pressure economizer 112 a of the exhaust heat recovery boiler 110 (see FIG. 5) is referred to as a second water supply line 62.
- a line constituted by the intermediate pressure heating water branch line 145 and the intermediate pressure water recovery line 146 is referred to as a first water supply introduction line 63.
- the medium pressure economizer 112 b is the first heater 112 b and the first fuel preheater 23 is the medium heat exchanger 23.
- the water from the condenser 123 is boosted by the water supply pump 124 and passes through the second water supply line 62 which is the water supply line 131 as the second water supply.
- the exhaust heat recovery boiler 110 can be sent to the low pressure economizer 112a.
- a portion of the low-pressure heated water, which is the low-pressure water heated by the low-pressure economizer 112a, is increased in pressure by the intermediate-pressure pump 116b and sent to the intermediate-pressure economizer 112b via the intermediate-pressure water line 141 as intermediate-pressure water. .
- This medium pressure water is heated by the medium pressure economizer 112b to become medium pressure heated water. That is, as shown in FIG.
- the first feed water that is medium pressure water is sent to the medium pressure economizer 112 b that is the first heater 112 b through the first water supply line 61 that is the medium pressure water line 141. .
- This first water supply has a higher pressure than the second water supply.
- This 1st water supply is heated with this 1st heater 112b (S1: 1st heating process (refer FIG. 4)).
- a part of the first water supply heated by the first heater 112b passes through a first water supply introduction line 63 constituted by an intermediate pressure heating water branch line 145 and an intermediate pressure water recovery line 146, and then the first fuel preheater. 23 to the medium heat exchanger 23.
- the fuel F as the medium and the first feed water are heat-exchanged to heat the medium, while the first feed water is cooled (S2: medium heat exchange step).
- the first water supply is introduced into the second water supply line 62 through the first water supply introduction line 63 (S3: first water supply introduction step).
- This first feed water is sent to the low pressure economizer 112a of the exhaust heat recovery boiler via the second feed water line 62 together with the second feed water which is water from the feed pump 124.
- the flow rate of the first water supply flowing through the first water supply introduction line 63 is detected by the flow meter 166.
- the recovered water flow rate adjustment valve 165 adjusts its valve opening so that the flow rate detected by the flow meter 166 becomes the target flow rate (S4: flow rate adjustment step).
- the target flow rate is determined according to the output of the gas turbine 10 and the flow rate of the fuel supplied to the gas turbine 10.
- the temperature of the first water supply immediately after flowing out of the medium heat exchanger 23 is lower than the temperature of the first water supply immediately after being heated by the first heater 112b and is close to the temperature of the second water supply.
- the first water supply is depressurized in the process of passing through the recovered water flow rate adjustment valve 165 provided in the first water supply introduction line 63, and becomes almost the same pressure as the pressure in the second water supply line 62.
- the cooling water injection process (S5) is also performed in parallel with the above processes, similarly to the first water supply system 50.
- the temperature of the water flowing between the connection position with the cooling water injection line 161 and the medium heat exchanger 23 in the first water supply introduction line 63 is detected by the thermometer 164.
- S6 Temperature detection step.
- the cooling water injection step (S5) when the temperature T1a detected in the temperature detection step (S6) is not larger than the preset set temperature T0a, the flow returns to the temperature detection step (S6) (NO in S7).
- the process proceeds to the cooling water flow rate adjustment step (S8).
- the cooling water flow rate adjustment step (S8) in the cooling water injection step (S5) as in the first embodiment, the cooling water flow rate adjustment valve 162 is set so that the temperature detected by the thermometer 164 becomes the set temperature T0a.
- the opening degree is controlled, and the flow rate of the cooling water flowing into the first water supply introduction line 63 from the cooling water injection line 161 is adjusted.
- This cooling water is the first unheated feed water that is the first feed water that is not heated by the first heater 112b.
- the temperature of the water on the second water supply line 62 side is lower than the connection position with the cooling water injection line 161, and the temperature detected by the thermometer 164 becomes the set temperature T0a. become.
- the cooling water flow rate adjustment valve 162 provided in the cooling water injection line 161 is closed.
- the first feed water that is medium-pressure water before being heated by the first heater 112 b is not injected into the first feed water introduction line 63 via the cooling water injection line 161. .
- the flow rate of the fuel flowing through the fuel supply line 21 is rapidly reduced.
- the amount of heat exchange between the fuel F as the medium and water is drastically reduced in the medium heat exchanger 23.
- the cooling amount of water flowing into the medium heat exchanger 23 is drastically reduced, and the temperature of the first feed water immediately after flowing out of the medium heat exchanger 23 becomes higher than that during steady operation of the gas turbine 10.
- the first water supply introduced into the second water supply line 62 becomes higher than that during the steady operation of the gas turbine 10, the first water supply may be flushed in the process of flowing into the second water supply line 62.
- the cooling water flow rate adjustment step (S8) in the cooling water injection step (S5) is performed. Executed.
- the combined cycle plant of the present embodiment includes the first water supply system 50 and the second water supply system 60.
- the first water supply It is not necessary to provide the cooling water injection line 151 in the system 50.
- the 1st water supply introduction line 63 in the 2nd water supply system 60 when there is no fear of flash
- the cooling water injection line 161 may not be provided in the second water supply system 60.
- the set temperature T0a is, for example, a temperature slightly lower than the temperature of the first feed water flowing out from the medium heat exchanger 23 during the steady operation of the gas turbine 10. There may be.
- the flow rate of water is detected by the flow meters 156 and 166, and feedback control is executed so that the flow rates detected by the flow meters 156 and 166 become the target flow rate.
- the flow rate of water may not be detected by the flow meters 156 and 166.
- the target water flow rate is determined according to the operation state of the gas turbine 10 such as the load of the gas turbine 10, and the feedforward control is executed so that the actual water flow rate becomes the target water flow rate.
- the cooling water injection line 151 is connected to a position on the high-pressure pump 116c side in the first water supply main line 51a with respect to the branch position of the first water supply branch line 51b.
- the cooling water injection line 151 may be connected to a position closer to the first water supply main line 51a than the first heater 32 in the first water supply branch line 51b.
- the cooling water injection line 151 may be connected to a position between the branch position of the first water supply branch line 51b and the second heater 112c in the first water supply main line 51a.
- the cooling water injection line 151 is the first water supply that flows through the first water supply line 51, and the position where the first water supply before reaching the first heater 32 and the second heater 112c can flow into the cooling water injection line 151. As long as it is connected, it may be connected to any position.
- the first water supply introduction line 53 is connected to the intermediate pressure heated water branch line 145, and this intermediate pressure heated water branch line 145 is used as the second water supply line 52.
- the first feed water introduction line 53 is connected to a position closer to the intermediate pressure economizer 112b than the branch position of the intermediate pressure heating water branch line 145.
- a portion closer to the intermediate pressure economizer 112b than the branch position of the intermediate pressure heating water branch line 145 may be used as the second water supply line. That is, the second water supply line is not limited to the second water supply line 53 of the above-described embodiment as long as water having a pressure lower than that of the first water supply flowing through the first water supply line 51 flows.
- the first water supply before being heated by the first heater is used as cooling water for cooling the first water supply immediately after flowing out from the medium heat exchanger.
- the cooling water can cool the first feed water immediately after flowing out of the medium heat exchanger without using the first feed water before being heated by the first heater.
- other water is used.
- a separate device for boosting the other water is necessary so that water can be injected into the first water supply immediately after flowing out of the medium heat exchanger.
- the first water supply before being heated by the first heater is used as the cooling water as in each of the above embodiments, it is not necessary to separately provide a device for boosting the cooling water.
- All of the medium heat exchangers of the above embodiments exchange heat between water and the fuel F as a medium.
- the medium in the medium heat exchanger does not need to be the fuel F, and may be another medium.
- each of the above embodiments is an example in which the present invention is applied to a combined cycle plant that is a plant in which a gas turbine and a steam turbine are combined.
- the present invention may be applied to plants other than the combined cycle plant.
- the present invention may be applied to a plant that includes a gas turbine and an exhaust heat recovery boiler but does not include a steam turbine.
- the present invention may be applied to a plant that includes a boiler but does not include a gas turbine or a steam turbine. That is, the present invention may be applied to any plant that has an environment in which water that has passed through a medium heat exchanger that exchanges heat between the medium and water can be flushed.
- Gas turbine equipment 10 Gas turbine 11: Compressor 12: Compressor rotor 14: Turbine 15: Turbine rotor 15a: Rotor shaft 15b: Rotor blade row 16: Turbine casing 19: Combustor 20: Fuel supply system 21: Fuel Supply line 22: Fuel flow control valve 23: First fuel preheater (medium heat exchanger or second medium heat exchanger) 24: Second fuel preheater (medium heat exchanger or first medium heat exchanger) 30: Parts cooling system 31: Extraction line 32: Air cooler (first heater) 50: Water supply system (first water supply system) 51, 61: first water supply line 51a: first water supply main line 51b: first water supply branch line 52, 62: second water supply line 53, 63: first water supply introduction line 60: second water supply system 100: exhaust heat recovery Apparatus 110: Waste heat recovery boiler 111a: Low pressure steam generator 111b: Medium pressure steam generator 111c: High pressure steam generator 112a: Low pressure economizer 113a: Low pressure evaporator
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Abstract
Description
本願は、2015年7月24日に、日本国に出願された特願2015-146735号に基づき優先権を主張し、この内容をここに援用する。
第一給水が流れる第一給水ラインと、前記第一給水よりも圧力の低い第二給水が流れる第二給水ラインと、前記第一給水を加熱する第一加熱器と、前記第一加熱器で加熱された前記第一給水である第一加熱給水を前記第二給水ラインに導く第一給水導入ラインと、前記第一給水導入ライン中に設けられ、前記第一加熱給水と媒体とを熱交換させて、前記第一加熱給水を冷却する一方で、前記媒体を加熱する媒体熱交換器と、前記第一給水導入ライン中で前記媒体熱交換器よりも前記第二給水ライン側の位置に、前記第一加熱給水よりも温度の低い冷却水を注入する冷却水注入ラインと、を備える。
前記第一態様の前記給水系統において、前記冷却水注入ラインは、前記第一給水ライン中であって前記第一加熱器で加熱されていない前記第一給水である第一未加熱給水が流れる部分から分岐しているラインであり、前記冷却水注入ラインは、前記冷却水として前記第一未加熱給水を前記第一給水導入ラインに注入する。
前記第一又は前記第二態様の前記給水系統において、前記第一給水導入ライン中で、前記冷却水注入ラインからの前記冷却水が注入される位置よりも前記第二給水ライン側の位置での水の温度を検知する温度計と、前記温度計で検知される温度が予め定められた温度範囲内に収まるよう、前記冷却水注入ラインを流れる前記冷却水の流量を調節する冷却水流量調節弁と、を備える。
前記第一から前記第三態様のいずれかの前記給水系統において、前記第一給水導入ライン中で、前記冷却水注入ラインからの前記冷却水が注入される位置よりも前記第二給水ライン側の位置に設けられ、前記第一給水導入ラインから前記第二給水ラインに流入する水の流量を調節する流量調節弁を備える。
前記第一から前記第四態様のいずれかの前記給水系統において、前記第一加熱器は、ガスタービンの圧縮機から抽気された圧縮空気と前記第一給水とを熱交させて、前記圧縮空気を冷却する一方で前記第一給水を加熱する熱交換器である。
前記第一から前記第五態様のいずれかの前記給水系統において、前記第一給水ラインは、第一給水主ラインと、前記第一給水主ラインから分岐した第一給水分岐ラインとを有し、前記第一給水主ライン中であって前記第一給水分岐ラインとの分岐位置よりも下流側に設けられ、前記第一給水主ラインを流れる前記第一給水を加熱する第二加熱器を備え、前記第一加熱器は、前記第一給水分岐ラインに設けられ、前記第一給水分岐ラインを流れる前記第一給水を加熱する。
前記第六態様の前記給水系統において、前記第一給水分岐ラインには、前記第一給水導入ラインが接続され、前記第一加熱器は、前記第一給水分岐ライン中で前記第一給水導入ラインが接続されている位置よりも前記分岐位置側に設けられ、前記第一給水分岐ラインは、前記第一給水主ライン中であって前記第二加熱器が設けられている位置よりも下流側に接続されている。
前記第一から前記第七態様のいずれかの前記給水系統において、前記媒体熱交換器である第一媒体熱交換器で前記媒体が加熱される前に、前記媒体を水と熱交換させて、前記媒体を加熱する一方で前記水を冷却する第二媒体熱交換器を備える。
前記第八態様の前記給水系統において、前記第二媒体熱交換器は、前記第二給水ライン中で前記第一給水導入ラインが接続されている位置よりも下流側に設けられ、前記第二給水ラインを流れる水と前記媒体とを熱交換する熱交換器である。
前記第一から前記第九態様のいずれかの前記給水系統において、前記媒体はガスタービンに供給される燃料であり、前記媒体熱交換器は、前記燃料を加熱する燃料予熱器である。
前記第一から前記第十態様のいずれかの前記給水系統と、ガスタービンからの排気ガスと前記第一給水ラインを経てきた前記第一給水とを熱交換させて、前記第一給水を加熱して蒸気にする蒸発器と、を備える。
前記第一から前記第四態様のいずれかの前記給水系統と、ガスタービンからの排気ガスと前記第一給水ラインを経てきた前記第一給水とを熱交換させて、前記第一給水を加熱して蒸気にする蒸発器と、を備え、前記第一加熱器は、前記排気ガスと前記第一給水とを熱交換させて、前記蒸発器に流入する前記第一給水を加熱する節炭器である。
前記第六又は前記第七態様の前記給水系統と、ガスタービンからの排気ガスと前記第一給水ラインを経てきた前記第一給水とを熱交換させて、前記第一給水を加熱して蒸気にする蒸発器と、を備え、前記第二加熱器は、前記排気ガスと前記第一給水とを熱交換させて、前記蒸発器に流入する前記第一給水を加熱する節炭器である。
第一給水を加熱する第一加熱工程と、前記第一加熱工程で加熱された前記第一給水である第一加熱給水と媒体とを熱交換させて、前記第一加熱給水を冷却する一方で前記媒体を加熱する媒体熱交換工程と、前記第一給水よりも圧力の低い第二給水中に、前記媒体熱交換工程を経た前記第一加熱給水を導入する第一給水導入工程と、前記媒体熱交換工程を経た後であって、前記第二給水中に導入される前の前記第一加熱給水中に、前記第一加熱給水よりも温度の低い冷却水を注入する冷却水注入工程と、を実行する。
前記第十四態様の前記給水方法において、前記冷却水注入工程では、前記第一加熱工程で加熱されていない前記第一給水である第一未加熱給水を、前記冷却水として用いる。
前記第十四又は前記第十五態様の前記給水方法において、前記冷却水注入工程では、前記第一加熱給水を含む水が前記第二給水に導入される前に、前記水の温度が予め定められた温度範囲内に収まるよう、前記冷却水の流量を調節する冷却水流量調節工程を含む。
前記第十四から前記第十六態様のいずれかの前記給水方法において、前記第二給水中に導入される前記第一加熱給水を含む水の流量を調節する流量調節工程を実行する。
前記第十四から前記第十七態様のいずれかの前記給水方法において、前記第一加熱工程では、ガスタービンの圧縮機から抽気された圧縮空気と前記第一給水とを熱交させて、前記圧縮空気を冷却する一方で前記第一給水を加熱する。
前記第十四から前記第十八態様のいずれかの前記給水方法において、前記媒体熱交換工程では、前記媒体としてガスタービンに供給される燃料を用い、第一加熱給水と前記燃料とを熱交換させて、前記第一加熱給水を冷却する一方で前記燃料を加熱する。
本発明に係る給水系統を備えるコンバインドサイクルプラントの第一実施形態について、図1~図4を参照して説明する。
本発明に係る給水系統を備えるコンバインドサイクルプラントの第二実施形態について、図5及び図6を参照して説明する。
燃料の流量が急激に少なくなると、媒体熱交換器23で、媒体としての燃料Fと水との熱交換量が急激に少なくなる。この結果、媒体熱交換器23に流入する水の冷却量が急激に少なくなり、媒体熱交換器23から流出した直後の第一給水の温度がガスタービン10の定常運転時と比べて高くなる。
以上の実施形態における各給水系統50,60では、流量計156,166で水の流量を検知し、この流量計156,166で検知された流量が目的の流量になるようフィードバック制御を実行する。しかしながら、流量計156,166で水の流量を検知しなくてもよい。この場合、例えば、ガスタービン10の負荷等、ガスタービン10の運転状況に応じて、目的の水流量を定め、実際の水流量がこの目的の水流量になるようフィードフォワード制御を実行する。
10:ガスタービン
11:圧縮機
12:圧縮機ロータ
14:タービン
15:タービンロータ
15a:ロータ軸
15b:動翼列
16:タービンケーシング
19:燃焼器
20:燃料供給系統
21:燃料供給ライン
22:燃料流量調節弁
23:第一燃料予熱器(媒体熱交換器又は第二媒体熱交換器)
24:第二燃料予熱器(媒体熱交換器又は第一媒体熱交換器)
30:部品冷却系統
31:抽気ライン
32:空気冷却器(第一加熱器)
50:給水系統(第一給水系統)
51,61:第一給水ライン
51a:第一給水主ライン
51b:第一給水分岐ライン
52,62:第二給水ライン
53,63:第一給水導入ライン
60:第二給水系統
100:排熱回収装置
110:排熱回収ボイラー
111a:低圧蒸気発生部
111b:中圧蒸気発生部
111c:高圧蒸気発生部
112a:低圧節炭器
113a:低圧蒸発器
114a:低圧過熱器
112b:中圧節炭器(第一加熱器)
113b:中圧蒸発器
114b:中圧過熱器
112c:高圧節炭器(第二加熱器)
113c:高圧蒸発器
114c:高圧過熱器
116b:中圧ポンプ
116c:高圧ポンプ
119:煙突
121a:低圧蒸気タービン
121b:中圧蒸気タービン
121c:高圧蒸気タービン
123:復水器
124:給水ポンプ
131:給水ライン
132:低圧蒸気ライン
133:中圧蒸気ライン
136:再熱蒸気ライン
137:中圧蒸気回収ライン
138:高圧蒸気ライン
139:高圧蒸気回収ライン
141:中圧水ライン
142:中圧加熱水ライン
143:高圧水ライン
144:高圧加熱水ライン
145:中圧加熱水分岐ライン
146:中圧水回収ライン
147:高圧水主ライン
148:高圧水分岐ライン
149:高圧水導入ライン
151,161:冷却水注入ライン
152,162:冷却水流量調節弁
153,163:逆止弁
154,164:温度計
155,156:回収水流量調節弁
156,166:流量計
Claims (19)
- 第一給水が流れる第一給水ラインと、
前記第一給水よりも圧力の低い第二給水が流れる第二給水ラインと、
前記第一給水を加熱する第一加熱器と、
前記第一加熱器で加熱された前記第一給水である第一加熱給水を前記第二給水ラインに導く第一給水導入ラインと、
前記第一給水導入ライン中に設けられ、前記第一加熱給水と媒体とを熱交換させて、前記第一加熱給水を冷却する一方で、前記媒体を加熱する媒体熱交換器と、
前記第一給水導入ライン中で前記媒体熱交換器よりも前記第二給水ライン側の位置に、前記第一加熱給水よりも温度の低い冷却水を注入する冷却水注入ラインと、
を備える給水系統。 - 請求項1に記載の給水系統において、
前記冷却水注入ラインは、前記第一給水ライン中であって前記第一加熱器で加熱されていない前記第一給水である第一未加熱給水が流れる部分から分岐しているラインであり、
前記冷却水注入ラインは、前記冷却水として前記第一未加熱給水を前記第一給水導入ラインに注入する、
給水系統。 - 請求項1又は2に記載の給水系統において、
前記第一給水導入ライン中で、前記冷却水注入ラインからの前記冷却水が注入される位置よりも前記第二給水ライン側の位置での水の温度を検知する温度計と、
前記温度計で検知される温度が予め定められた温度範囲内に収まるよう、前記冷却水注入ラインを流れる前記冷却水の流量を調節する冷却水流量調節弁と、
を備える給水系統。 - 請求項1から3のいずれか一項に記載の給水系統において、
前記第一給水導入ライン中で、前記冷却水注入ラインからの前記冷却水が注入される位置よりも前記第二給水ライン側の位置に設けられ、前記第一給水導入ラインから前記第二給水ラインに流入する水の流量を調節する流量調節弁を備える、
給水系統。 - 請求項1から4のいずれか一項に記載の給水系統において、
前記第一加熱器は、ガスタービンの圧縮機から抽気された圧縮空気と前記第一給水とを熱交させて、前記圧縮空気を冷却する一方で前記第一給水を加熱する熱交換器である、
給水系統。 - 請求項1から5のいずれか一項に記載の給水系統において、
前記第一給水ラインは、第一給水主ラインと、前記第一給水主ラインから分岐した第一給水分岐ラインとを有し、
前記第一給水主ライン中であって前記第一給水分岐ラインとの分岐位置よりも下流側に設けられ、前記第一給水主ラインを流れる前記第一給水を加熱する第二加熱器を備え、
前記第一加熱器は、前記第一給水分岐ラインに設けられ、前記第一給水分岐ラインを流れる前記第一給水を加熱する、
給水系統。 - 請求項6に記載の給水系統において、
前記第一給水分岐ラインには、前記第一給水導入ラインが接続され、
前記第一加熱器は、前記第一給水分岐ライン中で前記第一給水導入ラインが接続されている位置よりも前記分岐位置側に設けられ、
前記第一給水分岐ラインは、前記第一給水主ライン中であって前記第二加熱器が設けられている位置よりも下流側に接続されている、
給水系統。 - 請求項1から7のいずれか一項に記載の給水系統において、
前記媒体熱交換器である第一媒体熱交換器で前記媒体が加熱される前に、前記媒体を水と熱交換させて、前記媒体を加熱する一方で前記水を冷却する第二媒体熱交換器を備える、
給水系統。 - 請求項8に記載の給水系統において、
前記第二媒体熱交換器は、前記第二給水ライン中で前記第一給水導入ラインが接続されている位置よりも下流側に設けられ、前記第二給水ラインを流れる水と前記媒体とを熱交換する熱交換器である、
給水系統。 - 請求項1から9のいずれか一項に記載の給水系統において、
前記媒体はガスタービンに供給される燃料であり、
前記媒体熱交換器は、前記燃料を加熱する燃料予熱器である、
給水系統。 - 請求項1から10のいずれか一項に記載の給水系統と、
ガスタービンからの排気ガスと前記第一給水ラインを経てきた前記第一給水とを熱交換させて、前記第一給水を加熱して蒸気にする蒸発器と、
を備える蒸気発生設備。 - 請求項1から4のいずれか一項に記載の給水系統と、
ガスタービンからの排気ガスと前記第一給水ラインを経てきた前記第一給水とを熱交換させて、前記第一給水を加熱して蒸気にする蒸発器と、
を備え、
前記第一加熱器は、前記排気ガスと前記第一給水とを熱交換させて、前記蒸発器に流入する前記第一給水を加熱する節炭器である、
蒸気発生設備。 - 請求項6又は7に記載の給水系統と、
ガスタービンからの排気ガスと前記第一給水ラインを経てきた前記第一給水とを熱交換させて、前記第一給水を加熱して蒸気にする蒸発器と、
を備え、
前記第二加熱器は、前記排気ガスと前記第一給水とを熱交換させて、前記蒸発器に流入する前記第一給水を加熱する節炭器である、
る蒸気発生設備。 - 第一給水を加熱する第一加熱工程と、
前記第一加熱工程で加熱された前記第一給水である第一加熱給水と媒体とを熱交換させて、前記第一加熱給水を冷却する一方で前記媒体を加熱する媒体熱交換工程と、
前記第一給水よりも圧力の低い第二給水中に、前記媒体熱交換工程を経た前記第一加熱給水を導入する第一給水導入工程と、
前記媒体熱交換工程を経た後であって、前記第二給水中に導入される前の前記第一加熱給水中に、前記第一加熱給水よりも温度の低い冷却水を注入する冷却水注入工程と、
を実行する給水方法。 - 請求項14に記載の給水方法において、
前記冷却水注入工程では、前記第一加熱工程で加熱されていない前記第一給水である第一未加熱給水を、前記冷却水として用いる、
給水方法。 - 請求項14又は15に記載の給水方法において、
前記冷却水注入工程では、前記第一加熱給水を含む水が前記第二給水に導入される前に、前記水の温度が予め定められた温度範囲内に収まるよう、前記冷却水の流量を調節する冷却水流量調節工程を含む、
給水方法。 - 請求項14から16のいずれか一項に記載の給水方法において、
前記第二給水中に導入される前記第一加熱給水を含む水の流量を調節する流量調節工程を実行する、
給水方法。 - 請求項14から17のいずれか一項に記載の給水方法において、
前記第一加熱工程では、ガスタービンの圧縮機から抽気された圧縮空気と前記第一給水とを熱交させて、前記圧縮空気を冷却する一方で前記第一給水を加熱する、
給水方法。 - 請求項14から18のいずれか一項に記載の給水方法において、
前記媒体熱交換工程では、前記媒体としてガスタービンに供給される燃料を用い、第一加熱給水と前記燃料とを熱交換させて、前記第一加熱給水を冷却する一方で前記燃料を加熱する、
給水方法。
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CN201680036035.8A CN107709710B (zh) | 2015-07-24 | 2016-07-07 | 供水方法、供水系统、具备供水系统的蒸汽产生设备 |
DE112016003348.6T DE112016003348B4 (de) | 2015-07-24 | 2016-07-07 | Wasserversorgungssystem, wasserversorgungsverfahren, und dampf erzeugende anlage, die mit wasserversorgungssystem bereitgestellt wird |
KR1020187000374A KR101984438B1 (ko) | 2015-07-24 | 2016-07-07 | 급수 방법, 이 방법을 실행하는 급수 계통, 급수 계통을 구비하는 증기 발생 설비 |
US15/739,898 US10352246B2 (en) | 2015-07-24 | 2016-07-07 | Water feeding method, water feeding system implementing said method, and steam generating facility provided with water feeding system |
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JP2015146735A JP6550659B2 (ja) | 2015-07-24 | 2015-07-24 | 給水方法、この方法を実行する給水系統、給水系統を備える蒸気発生設備 |
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US11719156B2 (en) * | 2021-03-30 | 2023-08-08 | Doosan Enerbility Co., Ltd. | Combined power generation system with feedwater fuel preheating arrangement |
EP4071338B1 (en) | 2021-04-08 | 2024-01-31 | General Electric Technology GmbH | Gas turbine system having serial heat exchangers |
US20230151964A1 (en) * | 2021-11-12 | 2023-05-18 | Orlando Utilities Commission | Coal-fired power generation system and air heat with recirculation path and related method |
CN114508420A (zh) * | 2021-12-29 | 2022-05-17 | 东方电气集团东方汽轮机有限公司 | 一种并联式燃气轮机压气机抽气余热利用系统 |
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DE112016003348B4 (de) | 2020-06-18 |
KR101984438B1 (ko) | 2019-05-30 |
CN107709710A (zh) | 2018-02-16 |
US20180363557A1 (en) | 2018-12-20 |
JP2017026246A (ja) | 2017-02-02 |
KR20180016494A (ko) | 2018-02-14 |
JP6550659B2 (ja) | 2019-07-31 |
DE112016003348T5 (de) | 2018-04-05 |
CN107709710B (zh) | 2019-09-24 |
US10352246B2 (en) | 2019-07-16 |
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