WO2017110894A1 - 蒸気タービン - Google Patents
蒸気タービン Download PDFInfo
- Publication number
- WO2017110894A1 WO2017110894A1 PCT/JP2016/088148 JP2016088148W WO2017110894A1 WO 2017110894 A1 WO2017110894 A1 WO 2017110894A1 JP 2016088148 W JP2016088148 W JP 2016088148W WO 2017110894 A1 WO2017110894 A1 WO 2017110894A1
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- WIPO (PCT)
- Prior art keywords
- steam
- pressure
- rotor
- steam turbine
- turbine
- Prior art date
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- 238000001816 cooling Methods 0.000 claims description 364
- 238000004891 communication Methods 0.000 claims description 166
- 230000002093 peripheral effect Effects 0.000 claims description 56
- 238000010438 heat treatment Methods 0.000 claims description 7
- 230000007423 decrease Effects 0.000 abstract description 8
- 238000010586 diagram Methods 0.000 description 38
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 38
- 239000007789 gas Substances 0.000 description 31
- 230000000149 penetrating effect Effects 0.000 description 15
- 229920006395 saturated elastomer Polymers 0.000 description 12
- 239000012530 fluid Substances 0.000 description 7
- 230000000694 effects Effects 0.000 description 6
- 239000000567 combustion gas Substances 0.000 description 4
- 239000000446 fuel Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000011084 recovery Methods 0.000 description 3
- 239000000470 constituent Substances 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 230000001681 protective effect Effects 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 238000010248 power generation Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/08—Heating, heat-insulating or cooling means
- F01D5/081—Cooling fluid being directed on the side of the rotor disc or at the roots of the blades
- F01D5/082—Cooling fluid being directed on the side of the rotor disc or at the roots of the blades on the side of the rotor disc
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/08—Heating, heat-insulating or cooling means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
- F01D11/04—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type using sealing fluid, e.g. steam
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/08—Cooling; Heating; Heat-insulation
- F01D25/12—Cooling
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D9/00—Stators
- F01D9/06—Fluid supply conduits to nozzles or the like
- F01D9/065—Fluid supply or removal conduits traversing the working fluid flow, e.g. for lubrication-, cooling-, or sealing fluids
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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
- F01K13/00—General layout or general methods of operation of complete plants
- F01K13/006—Auxiliaries or details not otherwise provided for
-
- 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
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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
- F02C7/16—Cooling of plants characterised by cooling medium
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/30—Application in turbines
- F05D2220/31—Application in turbines in steam turbines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2260/00—Function
- F05D2260/20—Heat transfer, e.g. cooling
- F05D2260/232—Heat transfer, e.g. cooling characterized by the cooling medium
- F05D2260/2322—Heat transfer, e.g. cooling characterized by the cooling medium steam
Definitions
- the present invention relates to a steam turbine applied to a combined cycle plant.
- a steam turbine described in Patent Document 1 is configured such that a rotor having a plurality of early stages and a part of the rotor are surrounded, and a leakage region exists between the rotor, and one part thereof.
- a stator portion having a cooling steam channel for flowing cooling steam from to the leakage area, and an axially offset around the rotor, receiving cooling steam from the leakage area and supplying the cooling steam to at least a portion of the early stage And at least one cooling vapor delivery channel.
- Patent Document 1 includes a gas turbine and a boiler (heat recovery steam generator) that is coupled to the output of the gas turbine and uses the gas turbine exhaust gas to heat steam / water to a high temperature. And a combined cycle power plant that supplies hot steam generated in a boiler to a steam turbine.
- the steam turbine described in Patent Document 2 has an inner casing, and a rotor that is rotatable about an axis is disposed in the inner casing.
- a multi-stage arrangement of a guide vane fixed to the inner casing and a rotor blade fixed to the rotor is provided inside, hot steam from the inlet is released under work output.
- the thermal load of the rotor and the inner casing is at least in the steam passage, in parallel with the rotor surface and / or in the vicinity thereof. Parallel to and in the vicinity of the inner surface of the casing, a plate-like shape that protects the underlying surfaces of this rotor or inner casing from the direct action of hot steam flowing through the steam passage It is described that a protective shield is provided.
- a method and apparatus for cooling a steam turbine power generation facility described in Patent Document 3 includes a superheater that superheats steam in a boiler, and supplies steam extracted from the superheater to the steam turbine as cooling steam. It is described to do.
- JP 2011-085135 A Japanese Patent No. 5008735 International Publication No. 2010/097983 Pamphlet
- the steam turbine described in Patent Document 1 includes a steam source that supplies high-pressure and low-temperature steam to the casing steam channel, and there is no specific description of this steam source.
- a steam source that supplies high-pressure and low-temperature steam to the casing steam channel, and there is no specific description of this steam source.
- a steam passage in which a moving blade provided in the rotor and a stationary blade provided in the passenger compartment are disposed is formed between the rotor and the casing, and the steam turbine communicates with the steam passage.
- a nozzle part stationary blade is provided in the opening of the nozzle part for supplying superheated steam. Therefore, since the nozzle vane is exposed to steam heated to about 550 ° C. to 600 ° C., it is desired to improve durability.
- Patent Document 3 since the cooling steam is supplied to the outlet side of the nozzle part stationary blade, it does not cool the nozzle part stationary blade and does not contribute to the improvement of durability.
- the present invention solves the above-described problems, and provides a steam turbine that does not require a separate power source and that can prevent a decrease in cycle efficiency in a combined cycle plant and can improve the durability of the nozzle vane.
- the purpose is to provide.
- a steam turbine includes a gas turbine, a boiler that uses exhaust gas discharged from the gas turbine as a heating source, and high-pressure steam that is driven by high-pressure steam generated in the boiler.
- a turbine a low-pressure steam turbine driven by low-pressure steam generated in the boiler and steam that has passed through the high-pressure steam turbine, a condenser that condenses steam that has passed through the low-pressure steam turbine, and the condenser from the condenser And a condensate pump for supplying condensate to the boiler, wherein the boiler is generated by a high-pressure evaporator that generates steam from the condensate from the condenser and the high-pressure evaporator.
- a high pressure primary superheater that superheats the steam that has been heated, and a high pressure secondary superheater that further superheats the steam that has been superheated by the high pressure primary superheater.
- the steam superheated by the heater is supplied to the drive of the high-pressure steam turbine, from the outlet of the high-pressure evaporator through the high-pressure primary superheater to the inside of the high-pressure secondary superheater, and inside the high-pressure steam turbine,
- a cooling steam supply unit including a connection line that communicates with each other is provided.
- the cooling steam supply unit including the connection line that communicates the outlet from the high-pressure evaporator through the high-pressure primary superheater to the inside of the high-pressure secondary superheater and the inside of the high-pressure steam turbine is provided.
- cooling steam having a pressure higher than that of the superheated steam supplied to the high-pressure steam turbine and lower in temperature can be supplied to the inside of the high-pressure steam turbine.
- the generated steam in the combined cycle plant is used and cooling is not performed using the fluid inside the high-pressure steam turbine, the operating efficiency of the high-pressure steam turbine can be prevented from being lowered, and as a result, the cycle efficiency can be prevented from being lowered.
- connection line is formed between the outlet of the high pressure primary superheater and the inlet of the high pressure secondary superheater, and inside the high pressure steam turbine. It is characterized by communicating.
- the high-pressure steam turbine in the first or second invention, includes a rotor extending along an axis of rotation of the own turbine, a casing for housing the rotor, A steam passage provided between the rotor and the passenger compartment along the extending direction of the rotor, and provided to communicate with the steam passage through the passenger compartment from the outside of the passenger compartment.
- cooling steam having a pressure higher than that of the superheated steam supplied to the high-pressure steam turbine and having a low temperature can be suitably supplied to the inside of the high-pressure steam turbine.
- the high-pressure steam supply section is formed in an annular shape surrounding the outer periphery of the rotor, and the steam passage is between the outer surface of the rotor and the outer peripheral surface of the rotor.
- a high-pressure steam nozzle chamber that is attached to the vehicle compartment with a gap communicating with the inner space and is formed in an annular shape in the interior thereof, and extends from the high-pressure steam nozzle chamber toward the rotor in the steam passage.
- the cooling steam having a pressure higher than that of the superheated steam supplied to the high-pressure steam turbine and a low temperature is discharged into the gap between the high-pressure steam supply unit and the outer peripheral surface of the rotor via the communication channel.
- the rotor can be cooled.
- the superheated steam is discharged into the gap between the high pressure steam supply unit and the outer peripheral surface of the rotor via the communication channel, and the cooling steam is at a pressure higher than that of the superheated steam supplied to the high pressure steam turbine.
- the communication flow path includes a cooling steam nozzle provided at an opening communicating with the gap.
- the flow speed of the cooling steam discharged from the communication flow path into the gap by the cooling steam nozzle is increased.
- the temperature of the cooling steam can be lowered and the cooling efficiency can be improved.
- the cooling steam nozzle is provided with its tip directed in the rotation direction of the rotor.
- the cooling steam is discharged from the communication flow path into the gap along the rotation direction of the rotor by the cooling steam nozzle.
- friction loss caused by the difference between the rotational speed of the rotor and the speed of the cooling steam can be reduced.
- the high pressure steam turbine includes a nozzle portion stationary blade in the opening of the high pressure steam nozzle chamber in the high pressure steam nozzle portion. And a moving blade is attached to the outer periphery of the rotor adjacent to the nozzle portion stationary blade, and the cooling steam supply portion is a base end portion of the moving blade on the nozzle portion stationary blade side, the nozzle portion It includes a projection provided on at least one of the tip of the stationary blade on the moving blade side.
- the high-pressure steam supply section is formed in an annular shape surrounding the outer periphery of the rotor, and the steam passage is between the outer surface of the rotor and the outer peripheral surface of the rotor.
- a high-pressure steam nozzle chamber that is attached to the vehicle compartment with a gap communicating with the inner space and is formed in an annular shape in the interior thereof, and extends from the high-pressure steam nozzle chamber toward the rotor in the steam passage.
- a high-pressure steam nozzle part to which the steam superheated by the high-pressure secondary superheater is supplied to the high-pressure steam nozzle chamber, and the high-pressure steam nozzle part includes the high-pressure steam nozzle part.
- a nozzle part vane is attached to the opening, and the communication flow path is provided to penetrate the nozzle part vane and communicate with the gap.
- the cooling steam having a pressure higher than that of the superheated steam supplied to the high-pressure steam turbine and a low temperature is discharged into the gap between the high-pressure steam supply unit and the outer peripheral surface of the rotor via the communication channel.
- the rotor can be cooled.
- the superheated steam is discharged into the gap between the high pressure steam supply unit and the outer peripheral surface of the rotor via the communication channel, and the cooling steam is at a pressure higher than that of the superheated steam supplied to the high pressure steam turbine. Prevents leakage from the steam passage through the gap.
- the communication flow path is provided through the nozzle part stationary blade, the nozzle part stationary blade can be cooled, and the durability of the nozzle part stationary blade can be improved against the high temperature of the high-pressure steam turbine. it can.
- the communication flow path includes a cooling hole that penetrates the nozzle part stationary blade and opens to the steam passage.
- the cooling steam is discharged into the steam passage through the cooling hole penetrating the nozzle portion stationary blade.
- the nozzle part stationary blade can be cooled, and the durability of the nozzle part stationary blade can be improved against further increase in the temperature of the high-pressure steam turbine.
- the communication flow path includes a cooling steam nozzle provided in an opening communicating with the gap.
- the flow speed of the cooling steam discharged from the communication flow path into the gap by the cooling steam nozzle is increased.
- the temperature of the cooling steam can be lowered and the cooling efficiency can be improved.
- the cooling steam nozzle is provided with its tip directed in the rotational direction of the rotor.
- the cooling steam is discharged from the communication flow path into the gap along the rotation direction of the rotor by the cooling steam nozzle.
- friction loss caused by the difference between the rotational speed of the rotor and the speed of the cooling steam can be reduced.
- the high-pressure steam turbine has a gap communicating with the steam passage between the casing that forms the steam passage and an outer peripheral surface of the rotor. And having a steam passage vane attached thereto, and the communication channel is provided to penetrate the steam passage vane and communicate with the gap.
- the cooling steam having a pressure higher than that of the superheated steam supplied to the high-pressure steam turbine and a low temperature is discharged to the gap between the steam passage vane and the outer peripheral surface of the rotor through the communication channel.
- the rotor can be cooled.
- the communication flow path is provided through the steam passage vane, the steam passage vane can be cooled, and the durability of the steam passage vane can be improved against high temperatures of the high-pressure steam turbine. it can.
- the communication flow path includes a cooling hole that passes through the steam passage vane and opens into the steam passage.
- the cooling steam is discharged into the steam passage through the cooling hole penetrating the steam passage stationary blade.
- the nozzle part stationary blade can be cooled, and the durability of the steam passage stationary blade can be improved against further increase in the temperature of the high-pressure steam turbine.
- the communication flow path includes a cooling steam nozzle provided at an opening communicating with the gap.
- the flow speed of the cooling steam discharged from the communication flow path into the gap by the cooling steam nozzle is increased.
- the temperature of the cooling steam can be lowered and the cooling efficiency can be improved.
- the cooling steam nozzle is provided with its tip directed in the rotation direction of the rotor.
- the cooling steam is discharged from the communication flow path into the gap along the rotation direction of the rotor by the cooling steam nozzle.
- friction loss caused by the difference between the rotational speed of the rotor and the speed of the cooling steam can be reduced.
- the high pressure steam turbine has a rotor blade attached to the outer periphery of the rotor adjacent to the stationary blade
- the cooling steam supply unit includes a base end portion on the stationary blade side of the moving blade adjacent to the stationary blade through which the communication channel passes, a distal end portion on the moving blade side of the stationary blade through which the communication channel passes, Including a protrusion provided on at least one of the above.
- a steam turbine is a gas turbine, a boiler that uses exhaust gas discharged from the gas turbine as a heating source, and high-pressure steam that is driven by high-pressure steam generated in the boiler.
- the turbine, the intermediate pressure steam turbine driven by the intermediate pressure steam generated in the boiler, the low pressure steam generated by the boiler and the low pressure steam turbine driven by the steam via the intermediate pressure steam turbine, and the low pressure steam turbine A combined cycle plant comprising: a condenser that condenses steam; and a condensate pump that supplies the condensate from the condenser to the boiler, wherein the boiler includes the condenser from the condenser An intermediate pressure evaporator that generates steam from the condensate, an intermediate pressure superheater that superheats the steam generated by the intermediate pressure evaporator, and a steam that is superheated by the intermediate pressure superheater A primary reheater that reheats and a secondary reheater that reheats the steam superheated by the primary reheater, and the steam that is superheated by the secondary reheater is the medium pressure steam Supplied to the drive of the turbine and communicates from the outlet of the intermediate pressure evaporator to the inside of the secondary reheater through the
- connection line that communicates from the outlet of the intermediate pressure evaporator to the inside of the secondary reheater through the intermediate pressure superheater and the primary reheater, and the inside of the intermediate pressure steam turbine.
- the operation efficiency of the intermediate pressure steam turbine can be prevented from being lowered, and as a result, the cycle efficiency can be prevented from being lowered.
- connection line extends from the outlet of the intermediate pressure superheater to the inlet of the primary reheater, and inside the intermediate pressure steam turbine. It is characterized by communicating.
- the temperature of the superheated steam supplied to the intermediate pressure steam turbine is kept constant. Since the amount of steam obtained from the intermediate pressure evaporator can be increased, the amount of superheated steam supplied to the intermediate pressure steam turbine can be increased. As a result, the operation efficiency of the intermediate pressure steam turbine can be improved, and the cycle efficiency can be improved.
- connection line is formed between the outlet of the primary reheater and the inlet of the secondary reheater, and inside the intermediate pressure steam turbine. And communicating with each other.
- the temperature of the superheated steam supplied to the intermediate pressure steam turbine is kept constant.
- the amount of steam obtained from the intermediate pressure evaporator can be increased, the amount of superheated steam supplied to the intermediate pressure steam turbine can be increased. As a result, the operation efficiency of the intermediate pressure steam turbine can be improved, and the cycle efficiency can be improved.
- the intermediate-pressure steam turbine stores a rotor extending along an axis of rotation of the medium turbine and the rotor.
- an intermediate pressure steam supply unit that is supplied with steam superheated by the secondary reheater, and the cooling steam supply unit is connected to the connection line and is the intermediate pressure steam supply unit
- it includes a communication flow path that penetrates the vehicle compartment from the outside of the vehicle compartment and communicates with the steam passage.
- cooling steam having a pressure higher than that of the superheated steam supplied to the intermediate pressure steam turbine and a low temperature can be suitably supplied to the inside of the intermediate pressure steam turbine.
- the intermediate pressure steam supply section is formed in an annular shape surrounding the outer periphery of the rotor, and the steam is disposed between the outer surface of the rotor and the outer peripheral surface of the rotor.
- An intermediate pressure steam nozzle chamber that is attached to the passenger compartment with a gap communicating with a passage and is formed in an annular shape therein, and extends from the intermediate pressure steam nozzle chamber toward the extending direction of the rotor.
- An intermediate pressure steam nozzle section having an opening communicating with a steam passage, to which steam heated by the secondary reheater is supplied to the intermediate pressure steam nozzle chamber, and the communication flow path includes the intermediate pressure
- the steam nozzle portion is provided in communication with the gap on the side opposite to the opening of the intermediate pressure steam nozzle chamber.
- the cooling steam having a pressure higher than that of the superheated steam supplied to the intermediate pressure steam turbine and a low temperature is discharged into the gap between the intermediate pressure steam supply unit and the outer peripheral surface of the rotor via the communication channel. Therefore, the rotor can be cooled.
- the superheated steam that is higher in pressure than the superheated steam supplied to the intermediate pressure steam turbine and the low-temperature cooling steam is discharged into the gap between the intermediate pressure steam supply unit and the outer peripheral surface of the rotor via the communication channel. Prevents steam from leaking out of the steam passage through the gap. As a result, since the loss of superheated steam is prevented, the operating efficiency of the intermediate pressure steam turbine can be improved, and the cycle efficiency can be improved.
- the communication flow path includes a cooling steam nozzle provided in an opening communicating with the gap.
- the flow speed of the cooling steam discharged from the communication flow path into the gap by the cooling steam nozzle is increased.
- the temperature of the cooling steam can be lowered and the cooling efficiency can be improved.
- the cooling steam nozzle is provided with its tip directed in the rotation direction of the rotor.
- the cooling steam is discharged from the communication flow path into the gap along the rotation direction of the rotor by the cooling steam nozzle.
- friction loss caused by the difference between the rotational speed of the rotor and the speed of the cooling steam can be reduced.
- the intermediate pressure steam turbine has a nozzle portion in the opening of the intermediate pressure steam nozzle chamber in the intermediate pressure steam nozzle portion.
- a stationary blade is attached, and a moving blade is attached to the outer periphery of the rotor adjacent to the nozzle portion stationary blade, and the cooling steam supply unit is a base end portion of the moving blade on the nozzle portion stationary blade side, It includes a protrusion provided on at least one of the tip of the nozzle part stationary blade on the moving blade side.
- the intermediate pressure steam supply section is formed in an annular shape surrounding the outer periphery of the rotor, and the steam is provided between the outer surface of the rotor and the outer peripheral surface of the rotor.
- An intermediate pressure steam nozzle chamber that is attached to the passenger compartment with a gap communicating with a passage and is formed in an annular shape therein, and extends from the intermediate pressure steam nozzle chamber toward the extending direction of the rotor.
- a nozzle part stationary blade is attached to the opening of the intermediate pressure steam nozzle chamber, and the communication channel is provided so as to penetrate the nozzle part stationary blade and communicate with the gap.
- the cooling steam having a pressure higher than that of the superheated steam supplied to the intermediate pressure steam turbine and a low temperature is discharged into the gap between the intermediate pressure steam supply unit and the outer peripheral surface of the rotor via the communication channel. Therefore, the rotor can be cooled.
- the superheated steam that is higher in pressure than the superheated steam supplied to the intermediate pressure steam turbine and the low-temperature cooling steam is discharged into the gap between the intermediate pressure steam supply unit and the outer peripheral surface of the rotor via the communication channel. Prevents steam from leaking out of the steam passage through the gap.
- the communication flow path is provided through the nozzle portion stationary blade, the nozzle portion stationary blade can be cooled, and the durability of the nozzle portion stationary blade can be improved against the high temperature of the intermediate pressure steam turbine. Can do.
- the communication flow path includes a cooling hole that penetrates the nozzle part stationary blade and opens into the steam passage.
- the cooling steam is discharged into the steam passage through the cooling hole penetrating the nozzle portion stationary blade.
- the nozzle part stationary blade can be cooled, and the durability of the nozzle part stationary blade can be improved against further increase in the temperature of the intermediate pressure steam turbine.
- the communication flow path includes a cooling steam nozzle provided in an opening communicating with the gap.
- the flow speed of the cooling steam discharged from the communication flow path into the gap by the cooling steam nozzle is increased.
- the temperature of the cooling steam can be lowered and the cooling efficiency can be improved.
- the cooling steam nozzle is provided with its tip directed in the rotational direction of the rotor.
- the cooling steam is discharged from the communication flow path into the gap along the rotation direction of the rotor by the cooling steam nozzle.
- friction loss caused by the difference between the rotational speed of the rotor and the speed of the cooling steam can be reduced.
- the intermediate-pressure steam turbine is a gap communicating with the steam passage between the casing forming the steam passage and an outer peripheral surface of the rotor.
- a steam passage vane is attached, and the communication channel is provided to penetrate the steam passage vane and communicate with the gap.
- the cooling steam having a pressure higher than that of the superheated steam supplied to the intermediate-pressure steam turbine and a low temperature is discharged to the gap between the steam passage vane and the outer peripheral surface of the rotor via the communication channel. Therefore, the rotor can be cooled. Moreover, since the communication flow path is provided through the steam passage vane, the steam passage vane can be cooled, and the durability of the steam passage vane can be improved against the high temperature of the intermediate pressure steam turbine. Can do.
- the communication flow path includes a cooling hole that penetrates the steam passage vane and opens to the steam passage.
- the cooling steam is discharged into the steam passage through the cooling hole penetrating the steam passage stationary blade.
- the nozzle part stationary blade can be cooled, and the durability of the steam passage stationary blade can be improved against further increase in the temperature of the intermediate pressure steam turbine.
- the communication flow path includes a cooling steam nozzle provided in an opening communicating with the gap.
- the flow speed of the cooling steam discharged from the communication flow path into the gap by the cooling steam nozzle is increased.
- the temperature of the cooling steam can be lowered and the cooling efficiency can be improved.
- the cooling steam nozzle is provided with its tip directed in the rotation direction of the rotor.
- the cooling steam is discharged from the communication flow path into the gap along the rotation direction of the rotor by the cooling steam nozzle.
- friction loss caused by the difference between the rotational speed of the rotor and the speed of the cooling steam can be reduced.
- the intermediate pressure steam turbine has a rotor blade attached to the outer periphery of the rotor adjacent to the stationary blade.
- the cooling steam supply section includes a base end portion on the stationary blade side of the moving blade adjacent to the stationary blade through which the communication channel passes, and a distal end portion on the moving blade side of the stationary blade through which the communication channel passes. And a protrusion provided on at least one of the above.
- a separate power source is not required, and the cycle efficiency in the combined cycle plant can be prevented from being lowered, and the durability of the nozzle part stationary blade can be improved.
- FIG. 1 is a schematic configuration diagram illustrating an example of a combined cycle plant according to Embodiment 1 of the present invention.
- FIG. 2 is a schematic configuration diagram illustrating another example of the combined cycle plant according to Embodiment 1 of the present invention.
- FIG. 3 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the first embodiment of the present invention.
- FIG. 4 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the first embodiment of the present invention.
- FIG. 5 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the first embodiment of the present invention.
- FIG. 6 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the first embodiment of the present invention.
- FIG. 1 is a schematic configuration diagram illustrating an example of a combined cycle plant according to Embodiment 1 of the present invention.
- FIG. 2 is a schematic configuration diagram illustrating another example of the combined cycle plant according to Embodiment 1 of the present
- FIG. 7 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the first embodiment of the present invention.
- FIG. 8 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the first embodiment of the present invention.
- FIG. 9 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the first embodiment of the present invention.
- FIG. 10 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the first embodiment of the present invention.
- FIG. 11 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the first embodiment of the present invention.
- FIG. 12 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the first embodiment of the present invention.
- FIG. 13 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the first embodiment of the present invention.
- FIG. 14 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the first embodiment of the present invention.
- FIG. 15 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the first embodiment of the present invention.
- FIG. 16 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the first embodiment of the present invention.
- FIG. 17 is a schematic configuration diagram illustrating an example of a combined cycle plant according to Embodiment 2 of the present invention.
- FIG. 18 is a schematic configuration diagram illustrating another example of the combined cycle plant according to Embodiment 2 of the present invention.
- FIG. 19 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the second embodiment of the present invention.
- FIG. 20 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the second embodiment of the present invention.
- FIG. 21 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the second embodiment of the present invention.
- FIG. 22 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the second embodiment of the present invention.
- FIG. 23 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the second embodiment of the present invention.
- FIG. 24 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the second embodiment of the present invention.
- FIG. 20 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the second embodiment of the present invention.
- FIG. 21 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the second embodiment of the present invention.
- FIG. 25 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the second embodiment of the present invention.
- FIG. 26 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the second embodiment of the present invention.
- FIG. 27 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the second embodiment of the present invention.
- FIG. 28 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the second embodiment of the present invention.
- FIG. 29 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the second embodiment of the present invention.
- FIG. 30 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the second embodiment of the present invention.
- FIG. 31 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the second embodiment of the present invention.
- FIG. 32 is a schematic configuration diagram illustrating an example of a cooling steam supply unit according to the second embodiment of the present invention.
- Embodiment 1 Embodiment 1 according to the present invention will be described below in detail with reference to the drawings.
- the present invention is not limited to the first embodiment.
- constituent elements in the first embodiment include those that can be easily replaced by those skilled in the art or those that are substantially the same.
- FIG. 1 is a schematic configuration diagram illustrating an example of a combined cycle plant according to the first embodiment.
- a combined cycle plant 100 shown in FIG. 1 includes a gas turbine 110, a high-pressure steam turbine 120, an intermediate-pressure steam turbine 130, and a low-pressure steam turbine 140. These gas turbine 110, high-pressure steam turbine 120, intermediate-pressure steam turbine 130, and low-pressure The steam turbine 140 is disposed coaxially with the generator 150.
- the gas turbine 110 includes a compressor 111, a combustor 112, and a turbine 113.
- the compressor inlet air 114 is pressurized and supplied to the combustor 112.
- the combustor 112 high-temperature combustion gas is generated by the supplied air and fuel 115 and supplied to the turbine 113.
- the combustion gas passing through the turbine 113 is discharged as exhaust gas after the turbine 113 is driven to rotate.
- the combined cycle plant 100 includes a boiler (exhaust heat recovery boiler) 1 that generates superheated steam from water using the exhaust gas discharged from the turbine 113 in the gas turbine 110 as a heating source.
- the superheated steam generated by the boiler 1 drives the high-pressure steam turbine 120, the intermediate-pressure steam turbine 130, and the low-pressure steam turbine 140.
- Electric power is generated by the generator 150 by driving the gas turbine 110, the high pressure steam turbine 120, the intermediate pressure steam turbine 130, and the low pressure steam turbine 140.
- the steam used in the low-pressure steam turbine 140 is converted into condensate by a condenser 160 connected to the low-pressure steam turbine 140 and sent to the boiler 1 as water for generating superheated steam.
- the boiler 1 is connected to a flue 113a provided on the exhaust side of the turbine 113 in the gas turbine 110.
- the boiler 1 includes a low-pressure economizer 10, a low-pressure drum 11, a low-pressure evaporator 12, a medium-pressure economizer 13, a high-pressure primary economizer 14, an intermediate-pressure drum 15, and an intermediate-pressure evaporator from the downstream side of the exhaust gas flow.
- the boiler 1 includes a low-pressure system that generates low-pressure superheated steam for driving the low-pressure steam turbine 140, a medium-pressure system that generates medium-pressure superheated steam for driving the intermediate-pressure steam turbine 130, and high-pressure steam. And a high-pressure system that generates high-pressure superheated steam for driving the turbine 120.
- the low pressure system includes a low pressure economizer 10, a low pressure drum 11, a low pressure evaporator 12, a low pressure superheater 17, and a condensate pump 26.
- the intermediate pressure system includes an intermediate pressure economizer 13, an intermediate pressure drum 15, an intermediate pressure evaporator 16, an intermediate pressure superheater 19, a primary reheater 23, a secondary reheater 24, and an intermediate pressure feed water pump 27.
- the high-pressure system includes a high-pressure primary economizer 14, a high-pressure secondary economizer 18, a high-pressure drum 20, a high-pressure evaporator 21, a high-pressure primary superheater 22, a high-pressure secondary superheater 25, and a high-pressure feed water pump 28.
- the low pressure economizer 10 is connected to the condenser 160 through the connection line 30.
- a condensate pump 26 is provided in the connection line 30.
- the low-pressure economizer 10 is connected to the low-pressure drum 11 through a low-pressure branch line 31a among the connection lines 31 branched into three.
- the low pressure drum 11 is connected to the low pressure evaporator 12.
- the low-pressure drum 11 is connected to the low-pressure superheater 17 through a connection line 32.
- the low pressure superheater 17 is connected to the inlet side of the low pressure steam turbine 140 through the connection line 33.
- the outlet side of the low-pressure steam turbine 140 is connected to the condenser 160 through the connection line 34.
- the water (condensate) of the condenser 160 flows into the low-pressure economizer 10 through the connection line 30 and is heated by the condensate pump 26 and is heated through the low-pressure branch line 31 a of the connection line 31. It flows into the drum 11.
- the water supplied to the low-pressure drum 11 is evaporated by the low-pressure evaporator 12 to become saturated steam, returned to the low-pressure drum 11, and sent to the low-pressure superheater 17 through the connection line 32.
- the saturated steam is superheated in the low-pressure superheater 17, and this superheated steam is supplied to the low-pressure steam turbine 140 through the connection line 33.
- the steam discharged by driving the low-pressure steam turbine 140 is guided to the condenser 160 through the connection line 34 to become water (condensate), and is supplied to the low-pressure economizer 10 through the connection line 30 by the condensate pump 26. Sent out.
- the medium pressure economizer 13 is connected to the low pressure economizer 10 by an intermediate pressure branch line 31b among the connection lines 31 that branch into three.
- An intermediate pressure feed water pump 27 is provided in the intermediate pressure branch line 31b.
- the intermediate pressure economizer 13 is connected to the intermediate pressure drum 15 through a connection line 35.
- the connection line 35 is provided with a flow rate adjusting valve 36 on the way.
- the intermediate pressure drum 15 is connected to the intermediate pressure evaporator 16. Further, the intermediate pressure drum 15 is connected to the intermediate pressure superheater 19 through a connection line 37.
- the intermediate pressure superheater 19 is connected to the inlet side of the primary reheater 23 by a connection line 38.
- the primary reheater 23 is connected to the outlet side of the high-pressure steam turbine 120 through the connection line 40. Further, the primary reheater 23 is connected to the secondary reheater 24 by a connection line 41. The secondary reheater 24 is connected to the inlet side of the intermediate pressure steam turbine 130 through the connection line 42. The outlet side of the intermediate pressure steam turbine 130 is connected to the inlet side of the low pressure steam turbine 140 through a connection line 39.
- the water heated by the low pressure economizer 10 is further heated by flowing into the intermediate pressure economizer 13 via the intermediate pressure branch line 31b of the connection line 31 by the intermediate pressure feed water pump 27. It flows into the intermediate pressure drum 15 via the line 35.
- the water supplied to the intermediate pressure drum 15 is evaporated by the intermediate pressure evaporator 16 to become saturated vapor, returned to the intermediate pressure drum 15, and sent to the intermediate pressure superheater 19 through the connection line 37.
- the saturated steam is superheated in the intermediate pressure superheater 19, and this superheated steam is supplied to the primary reheater 23 via the connection line 38.
- the steam discharged by driving the high-pressure steam turbine 120 is sent to the primary reheater 23 through the connection line 40.
- the steam is superheated in the primary reheater 23, and this superheated steam is sent to the secondary reheater 24 through the connection line 41.
- the steam is further superheated in the secondary reheater 24, and this superheated steam is supplied to the intermediate pressure steam turbine 130 via the connection line 42.
- the steam discharged by driving the intermediate pressure steam turbine 130 is supplied to the low pressure steam turbine 140 through the connection line 39.
- the primary reheater 23 and the secondary reheater 24 superheat steam, they have the same function as the superheater and are included in the superheater in the first embodiment. That is, the primary reheater 23 is also referred to as a first superheater, and the secondary reheater 24 is also referred to as a second superheater.
- the high-pressure primary economizer 14 is connected to the low-pressure economizer 10 by a high-pressure branch line 31c among the connection lines 31 that branch into three.
- a high-pressure feed water pump 28 is provided in the high-pressure branch line 31c.
- the high-pressure primary economizer 14 is connected to the high-pressure secondary economizer 18 through a connection line 43.
- the high pressure secondary economizer 18 is connected to the high pressure drum 20 via a connection line 44.
- the connection line 44 is provided with a flow rate adjustment valve 45 in the middle.
- the high pressure drum 20 is connected to a high pressure evaporator 21.
- the high-pressure drum 20 is connected to the high-pressure primary superheater 22 through a connection line 46.
- the high-pressure primary superheater 22 is connected to the high-pressure secondary superheater 25 by a connection line 47.
- the high pressure secondary superheater 25 is connected to the inlet side of the high pressure steam turbine 120 by a connection line 48.
- the outlet side of the high-pressure steam turbine 120 is connected to the intermediate pressure primary reheater 23 through the connection line 40 as described above.
- the water heated in the low-pressure economizer 10 is further heated by flowing into the high-pressure primary economizer 14 via the high-pressure branch line 31 c of the connection line 31 by the high-pressure feed water pump 28. Then, it flows into the high-pressure secondary economizer 18 and is further heated and flows into the high-pressure drum 20 through the connection line 44.
- the water supplied to the high-pressure drum 20 is evaporated by the high-pressure evaporator 21 to become saturated steam, returned to the high-pressure drum 20, and sent to the high-pressure primary superheater 22 through the connection line 46.
- the saturated steam is superheated in the high-pressure primary superheater 22, and this superheated steam is sent to the high-pressure secondary superheater 25 through the connection line 47.
- the superheated steam is further superheated in the high pressure secondary superheater 25, and this superheated steam is supplied to the high pressure steam turbine 120 via the connection line 48.
- FIG. 2 is a schematic configuration diagram showing another example of the combined cycle plant according to the first embodiment.
- the combined cycle plant 200 shown in FIG. 2 includes the above-described medium pressure steam turbine 130, medium pressure system in the boiler 1 (medium pressure economizer 13, medium pressure drum 15, medium pressure evaporator 16, medium pressure superheater 19, primary pressure
- the reheater 23, the secondary reheater 24, the intermediate pressure feed water pump 27), the respective lines 31b, 35, 37, 38, 40, 41, 42 and the flow rate adjusting valve 36 related thereto are not provided. Therefore, about the combined cycle plant 200 and the boiler 1 shown in FIG. 2, the same code
- the outlet side of the high-pressure steam turbine 120 is connected to the inlet side of the low-pressure steam turbine 140 through the connection line 49, and the steam discharged by driving the high-pressure steam turbine 120 passes through the connection line 49. Supplied to the low pressure steam turbine 140.
- the steam turbine of the first embodiment includes a cooling steam supply unit (first cooling steam supply unit) 51 that cools the inside of the high-pressure steam turbine 120.
- the cooling steam supply unit 51 is provided between the outlet of the high pressure evaporator 21 and the high pressure secondary superheater 25 through the high pressure primary superheater 22 and the inside of the high pressure steam turbine 120.
- a connection line 51A connects the connection line 46 that connects the high-pressure drum 20 and the high-pressure primary superheater 22, the inside of the high-pressure primary superheater 22, and the high-pressure primary superheater 22 and the high-pressure secondary superheater 25.
- At least a part of the connection line 47 and the inside of the high-pressure secondary superheater 25 and the inside of the high-pressure steam turbine 120 communicate with each other.
- the superheated steam supplied to the high-pressure steam turbine 120 passes through the connection line 48 from the high-pressure secondary superheater 25, but the pressure decreases in the process of passing through the connection line 48. Therefore, the steam from the outlet of the high-pressure evaporator 21 to the inside of the high-pressure secondary superheater 25 through the high-pressure primary superheater 22 has a higher pressure and a lower temperature (superheated) than the superheated steam supplied to the high-pressure steam turbine 120.
- the temperature of steam is lower than about 550 ° C. to 600 ° C.). Therefore, it is possible to supply cooling steam having a higher pressure and lower temperature than the superheated steam supplied to the high-pressure steam turbine 120 into the high-pressure steam turbine 120.
- the passage from the outlet of the high-pressure evaporator 21 through the high-pressure primary superheater 22 to the inside of the high-pressure secondary superheater 25 and the inside of the high-pressure steam turbine 120 are communicated.
- the cooling steam supply unit 51 including the connecting line 51A the high-pressure steam turbine can supply cooling steam having a pressure higher than that of the superheated steam supplied to the high-pressure steam turbine 120 in the combined cycle plants 100 and 200. 120 can be supplied inside. As a result, it is possible to cool a high-temperature part such as a rotor inside the high-pressure steam turbine 120 without requiring another power source.
- the generated steam in the combined cycle plants 100 and 200 is used and the fluid inside the high-pressure steam turbine 120 is not cooled, the operating efficiency of the high-pressure steam turbine 120 is prevented from being lowered, and as a result, the cycle efficiency is prevented from being lowered. be able to.
- connection line 51 ⁇ / b> A includes a connection line 47 between the outlet of the high-pressure primary superheater 22 and the inlet of the high-pressure secondary superheater 25; It is preferable to communicate with the inside of the high-pressure steam turbine 120.
- the cooling steam is supplied to the inside of the high-pressure steam turbine 120 from the connection line 47 between the outlet of the high-pressure primary superheater 22 and the inlet of the high-pressure secondary superheater 25, the steam supplied to the high-pressure secondary superheater 25 is reduced. Therefore, the superheating efficiency in the high pressure secondary superheater 25 is improved, and the temperature of the superheated steam supplied to the high pressure steam turbine 120 is increased. As a result, the operating efficiency of the high-pressure steam turbine 120 can be improved, and the cycle efficiency can be improved.
- the superheated steam supplied to the high-pressure steam turbine 120 is supplied.
- the temperature is constant, the amount of steam obtained from the high-pressure evaporator 21 can be increased, so that the amount of superheated steam supplied to the high-pressure steam turbine 120 can be increased.
- the operating efficiency of the high-pressure steam turbine 120 can be improved, and the cycle efficiency can be improved.
- 3 to 16 are schematic configuration diagrams showing an example of the cooling steam supply unit according to the first embodiment.
- the high-pressure steam turbine 120 includes a rotor 121, a vehicle compartment 122, a steam passage 123, and a high-pressure steam supply unit 124.
- the rotor 121 is provided so as to extend along the axis S of rotation thereof.
- the vehicle compartment 122 houses the rotor 121 and supports the rotor 121 so as to be rotatable around the axis S.
- the steam passage 123 is an annular space provided between the rotor 121 and the vehicle compartment 122 along the extending direction of the rotor 121.
- the high-pressure steam supply unit 124 is provided to communicate with the steam passage 123 through the vehicle compartment 122 from the outside of the vehicle compartment 122, and the steam heated by the high-pressure secondary superheater 25 is connected to the connection line 48. By being supplied, the steam is supplied to the steam passage 123.
- the high-pressure steam supply part 124 includes a high-pressure steam nozzle part 124A.
- the high-pressure steam nozzle portion 124 ⁇ / b> A is attached to the vehicle interior 122 with a gap 125 ⁇ / b> A that is formed in an annular shape surrounding the outer periphery of the rotor 121 and communicates with the steam passage 123 between the outer surface and the outer peripheral surface of the rotor 121.
- the high-pressure steam nozzle portion 124A includes a high-pressure steam nozzle chamber 124Aa formed in an annular shape therein, and an opening 124Ab that leads from the high-pressure steam nozzle chamber 124Aa to the steam passage 123 in the extending direction of the rotor 121. Have.
- the high-pressure steam nozzle portion 124A is connected to the connection line 48, the steam superheated by the high-pressure secondary superheater 25 is supplied to the high-pressure steam nozzle chamber 124Aa, and is discharged from the opening 124Ab to the steam passage 123.
- a plurality of nozzle unit vanes 126A are attached to the opening 124Ab of the high-pressure steam nozzle chamber 124Aa in the high-pressure steam nozzle unit 124A along an annular shape.
- the rotor 121 side is the leading end and the vehicle compartment 122 side is the base end.
- a plurality of steam passage vanes 126B are attached to the passenger compartment 122 along an annular shape.
- the steam passage vane 126 ⁇ / b> B is provided in a plurality of stages along the extending direction of the rotor 121.
- the steam passage vane 126 ⁇ / b> B has a tip end portion on the rotor 121 side and an annular member 126 ⁇ / b> Ba attached thereto.
- the steam passage stationary blade 126 ⁇ / b> B has a gap 125 ⁇ / b> B between the annular member 126 ⁇ / b> Ba and the outer peripheral surface of the rotor 121.
- the side is the base end.
- a plurality of moving blades 127 are attached to the outer periphery of the rotor 121 along the annular shape adjacent to the stationary blades 126A and 126B.
- the moving blades 127 are provided in a plurality of stages along the extending direction of the rotor 121.
- the rotor blade 127 has a base end on the side attached to the rotor 121 and an annular member 127 a attached to the rotor 121, and a side facing the vehicle compartment 122 becomes a tip.
- the steam heated by the high-pressure secondary superheater 25 is supplied to the high-pressure steam nozzle chamber 124Aa, discharged from the opening 124Ab to the steam passage 123, and rotated by the stationary blades 126A and 126B and the moving blade 127. 121 rotates.
- the cooling steam supply unit 51 is connected to the connection line 51A and the high-pressure steam supply unit 124 is connected.
- a communication channel 51B that penetrates the vehicle compartment 122 from the outside of the vehicle compartment 122 to the steam passage 123 and communicates therewith is included.
- the communication flow path 51B passes through the vehicle compartment 122 on the side opposite to the opening 124Ab of the high-pressure steam nozzle chamber 124Aa in the high-pressure steam nozzle section 124A and communicates with the gap 125A.
- An opening is provided toward the outer peripheral surface of 121.
- a plurality of communication channels 51B may be provided along the circumferential direction (rotation direction of the rotor 121) of the high-pressure steam nozzle portion 124A, or may be provided as a single unit. When there are a plurality of communication channels 51B, the connection line 51A is branched into a plurality and connected to each communication channel 51B.
- the cooling steam C supplied via the connection line 51A is a gap 125A between the high-pressure steam supply part 124 and the outer peripheral surface of the rotor 121 via the communication channel 51B, and the rotor 121. Is discharged toward the outer peripheral surface of the gas, flows along the extending direction of the rotor 121 through the gap 125A, reaches the steam passage 123, and between the nozzle unit stationary blade 126A and the moving blade 127, a high-pressure steam supply unit. The superheated steam G supplied to the steam passage 123 through 124 is joined.
- the cooling steam C having a pressure higher than that of the superheated steam G supplied to the high-pressure steam turbine 120 and a low temperature is connected to the high-pressure steam supply unit 124 via the communication channel 51B. Since the ink is discharged into a gap 125A with the outer peripheral surface of the rotor 121, the rotor 121 can be cooled. Moreover, according to the cooling steam supply unit 51 shown in FIG. 3, the high-pressure and low-temperature cooling steam C higher than the superheated steam G supplied to the high-pressure steam turbine 120 passes through the communication channel 51B.
- the superheated steam G is prevented from leaking from the steam passage 123 through the gap 125A by being discharged into the gap 125A between the rotor 121 and the outer peripheral surface of the rotor 121.
- the operating efficiency of the high-pressure steam turbine 120 can be improved, and the cycle efficiency can be improved.
- the communication flow path 51B shown in FIG. 3 preferably includes a cooling steam nozzle 51C provided at an opening communicating with the gap 125A.
- the cooling steam nozzle 51 ⁇ / b> C narrows the opening communicating with the gap 125 ⁇ / b> A in the communication flow path 51 ⁇ / b> B, thereby increasing the flow velocity of the cooling steam C discharged from the communication flow path 51 ⁇ / b> B to the gap 125 ⁇ / b> A. .
- the temperature of the cooling steam C can be lowered and the cooling efficiency can be improved.
- the cooling steam nozzle 51 ⁇ / b> C is preferably provided with the tip 51 ⁇ / b> Ca facing the rotation direction R of the rotor 121.
- the cooling steam C is discharged from the communication flow path 51B to the gap 125A along the rotation direction R of the rotor 121.
- friction loss caused by the difference between the rotational speed of the rotor 121 and the speed of the cooling steam C can be reduced.
- the cooling steam nozzle 51C is not limited to a configuration that is a plate member that is a separate member from the communication channel 51B, and the opening of the communication channel 51B may be narrowed. .
- the gap 125A through which the communication flow path 51B shown in FIG. 3 passes is the part that reaches the steam passage 123, and the nozzle part static air of the moving blade 127 adjacent to the nozzle part stationary blade 126A. It is preferable to include a protrusion 51Ea provided on the annular member 127a at the base end portion on the blade 126A side. Further, in the cooling steam supply unit 51 shown in FIG. 6, a gap 125A through which the communication flow path 51B shown in FIG. 3 passes is a part reaching the steam passage 123, which is the tip of the nozzle part stationary blade 126A and the moving blade 127. It is preferable to include a protruding portion 51Eb provided on a part of the high-pressure steam nozzle portion 124A facing the annular member 127a at the base end portion.
- the protrusions 51Ea and 51Eb are preferably provided continuously along the circumferential direction of the high-pressure steam turbine 120 (rotation direction of the rotor 121).
- the protrusions 51Ea and 51Eb are located between the opening 124Ab of the high-pressure steam nozzle chamber 124Aa in the high-pressure steam nozzle portion 124A provided with the nozzle portion stationary blade 126A and the annular member 127a at the base end portion of the moving blade 127.
- a vortex is generated in the cooling steam C toward the steam passage 123.
- protrusion part 51Ea, 51Eb it is preferable to provide both protrusion part 51Ea and 51Eb.
- both the protrusions 51Ea and 51Eb it is preferable that the protrusion 51Ea is provided at a position near the rotor 121 and the protrusion 51Eb is provided at a position far from the rotor 121.
- a vortex is first generated by the protrusion 51Ea with respect to the cooling steam C discharged from the communication flow path 51B penetrating the nozzle vane 126A toward the outer peripheral surface of the rotor 121, and then the vortex is generated by the protrusion 51Eb.
- the protrusion 51Eb causes it to occur.
- the protruding portions 51Ea and 51Eb may be provided together with the cooling steam nozzle 51C.
- the communication flow path 51B passes through the casing 122, the opening 124Ab of the high pressure steam nozzle chamber 124Aa in the high pressure steam nozzle part 124A, and the nozzle part stationary blade 126A, and communicates with the gap 125A.
- the opening is provided toward the outer peripheral surface of the rotor 121.
- a plurality of communication channels 51B may be provided along the circumferential direction (rotation direction of the rotor 121) of the high-pressure steam nozzle portion 124A, or may be provided as a single unit. When there are a plurality of communication channels 51B, the connection line 51A is branched into a plurality and connected to each communication channel 51B.
- the cooling steam C supplied via the connection line 51A is a gap 125A between the high-pressure steam supply part 124 and the outer peripheral surface of the rotor 121 via the communication channel 51B, and the rotor 121. Is discharged toward the outer peripheral surface of the gas, flows along the extending direction of the rotor 121 through the gap 125A, reaches the steam passage 123, and enters the steam passage 123 between the nozzle portion stationary blade 126A and the moving blade 127. It joins with the superheated steam G to be supplied.
- the cooling steam C having a pressure higher than that of the superheated steam G supplied to the high-pressure steam turbine 120 and a low temperature is connected to the high-pressure steam supply unit 124 via the communication channel 51B. Since the ink is discharged into a gap 125A with the outer peripheral surface of the rotor 121, the rotor 121 can be cooled. Moreover, according to the cooling steam supply unit 51 shown in FIG. 7, the high-pressure and low-temperature cooling steam C higher than the superheated steam G supplied to the high-pressure steam turbine 120 passes through the communication channel 51B.
- the superheated steam G is prevented from leaking from the steam passage 123 through the gap 125A by being discharged into the gap 125A between the rotor 121 and the outer peripheral surface of the rotor 121.
- the cooling steam supply unit 51 shown in FIG. 7 since the communication flow path 51B is provided through the nozzle part stationary blade 126A, the nozzle part stationary blade 126A can be cooled, and the high-pressure steam turbine 120 The durability of the nozzle vane 126A can be improved against high temperatures.
- the communication flow path 51B shown in FIG. 7 includes a cooling hole 51D that passes through the nozzle part vane 126A and opens to the steam passage 123.
- the cooling steam C is discharged into the steam passage 123 through the cooling hole 51D penetrating the nozzle portion stationary blade 126A.
- the nozzle part vane 126 ⁇ / b> A can be cooled, and the durability of the nozzle part vane 126 ⁇ / b> A can be improved against a further increase in the temperature of the high-pressure steam turbine 120.
- the communication flow path 51B shown in FIG. 7 preferably includes a cooling steam nozzle 51C provided in an opening communicating with the gap 125A.
- the cooling steam nozzle 51C narrows the opening that communicates with the gap 125A in the communication channel 51B, thereby increasing the flow rate of the cooling steam C that is discharged from the communication channel 51B to the gap 125A. .
- the temperature of the cooling steam C can be lowered and the cooling efficiency can be improved.
- the cooling steam nozzle 51 ⁇ / b> C is preferably provided with the tip 51 ⁇ / b> Ca facing the rotation direction R of the rotor 121.
- the cooling steam C is discharged from the communication flow path 51B to the gap 125A along the rotation direction R of the rotor 121.
- friction loss caused by the difference between the rotational speed of the rotor 121 and the speed of the cooling steam C can be reduced.
- cooling steam nozzle 51C is not limited to a configuration that is a plate member that is a separate member from the communication flow path 51B as shown in FIGS. 9 and 10, and the opening of the communication flow path 51B itself may be narrowed. . Further, the cooling steam nozzle 51C may be provided together with the cooling hole 51D.
- the cooling steam supply part 51 shown in FIG. 11 it is provided in the annular member 127a at the base end part on the nozzle part stationary blade 126A side of the moving blade 127 adjacent to the nozzle part stationary blade 126A through which the communication flow path 51B shown in FIG. It is preferable that the protrusion 51Ea to be included is included. Further, in the cooling steam supply section 51 shown in FIG. 11, the high-pressure steam facing the annular member 127 a at the distal end portion of the nozzle section stationary blade 126 ⁇ / b> A through which the communication flow path 51 ⁇ / b> B shown in FIG. It is preferable that the projection part 51Eb provided in a part of nozzle part 124A is included.
- the protrusions 51Ea and 51Eb are preferably provided continuously along the circumferential direction of the high-pressure steam turbine 120 (rotation direction of the rotor 121).
- the protrusions 51Ea and 51Eb are located between the opening 124Ab of the high-pressure steam nozzle chamber 124Aa in the high-pressure steam nozzle portion 124A provided with the nozzle portion stationary blade 126A and the annular member 127a at the base end portion of the moving blade 127.
- a vortex is generated in the cooling steam C toward the steam passage 123.
- protrusion part 51Ea, 51Eb it is preferable to provide both protrusion part 51Ea and 51Eb.
- both the protrusions 51Ea and 51Eb it is preferable that the protrusion 51Ea is provided at a position near the rotor 121 and the protrusion 51Eb is provided at a position far from the rotor 121.
- a vortex is first generated by the protrusion 51Ea with respect to the cooling steam C discharged from the communication flow path 51B penetrating the nozzle vane 126A toward the outer peripheral surface of the rotor 121, and then the vortex is generated by the protrusion 51Eb.
- the protrusion 51Eb causes it to occur.
- the protrusions 51Ea and 51Eb may be provided together with the cooling steam nozzle 51C and the cooling hole 51D.
- the communication flow path 51B passes through the casing 122, the steam passage vane 126B, and the annular member 126Ba at the tip of the steam passage vane 126B, and communicates with the gap 125B to the rotor.
- An opening is provided toward the outer peripheral surface of 121.
- a plurality of communication channels 51B may be provided along the circumferential direction (rotation direction of the rotor 121) of the high-pressure steam nozzle portion 124A, or may be provided as a single unit. When there are a plurality of communication channels 51B, the connection line 51A is branched into a plurality and connected to each communication channel 51B.
- the cooling steam C supplied through the connection line 51A is passed through the communication passage 51B in the gap 125B between the annular member 126Ba of the steam passage vane 126B and the outer peripheral surface of the rotor 121. And is discharged toward the outer peripheral surface of the rotor 121, flows along the extending direction of the rotor 121 through the gap 125B, reaches the steam passage 123, and between the steam passage stationary blade 126B and the moving blade 127.
- the superheated steam G supplied to the steam passage 123 merges.
- the cooling steam C having a pressure higher than that of the superheated steam G supplied to the high-pressure steam turbine 120 and a low temperature is supplied to the steam passage vane 126B via the communication channel 51B. Since it discharges to gap 125B between annular member 126Ba and the outer peripheral surface of rotor 121, rotor 121 can be cooled.
- the cooling steam supply unit 51 shown in FIG. 12 since the communication flow path 51B is provided through the steam passage vane 126B, the steam passage vane 126B can be cooled, and the high-pressure steam turbine 120 The durability of the steam passage vane 126B can be improved against high temperatures.
- the communication flow path 51B shown in FIG. 12 includes a cooling hole 51D that penetrates the steam passage vane 126B and opens to the steam passage 123.
- the cooling steam C is discharged to the steam passage 123 through the cooling hole 51D penetrating the steam passage vane 126B.
- the nozzle part vane 126A can be cooled, and the durability of the steam passage vane 126B can be improved against further increase in the temperature of the high-pressure steam turbine 120.
- the communication flow path 51B shown in FIG. 12 preferably includes a cooling steam nozzle 51C provided in an opening communicating with the gap 125B.
- the cooling steam nozzle 51C narrows the opening communicating with the gap 125B in the communication flow path 51B, thereby increasing the flow rate of the cooling steam C discharged from the communication flow path 51B to the gap 125B. .
- the temperature of the cooling steam C can be lowered and the cooling efficiency can be improved.
- the cooling steam nozzle 51 ⁇ / b> C is preferably provided with the tip 51 ⁇ / b> Ca facing the rotation direction R of the rotor 121. Accordingly, the cooling steam C is discharged from the communication flow path 51B into the gap 125B along the rotation direction R of the rotor 121. As a result, friction loss caused by the difference between the rotational speed of the rotor 121 and the speed of the cooling steam C can be reduced.
- the cooling steam nozzle 51C is not limited to a configuration that is a plate member that is a separate member from the communication flow path 51B, and the opening of the communication flow path 51B itself may be narrowed. . Further, the cooling steam nozzle 51C may be provided together with the cooling hole 51D.
- cooling steam supply part 51 In the cooling steam supply part 51 shown in FIG. 16, it is provided in the annular member 127a of the base end part on the steam passage stationary blade 126B side of the moving blade 127 adjacent to the steam passage stationary blade 126B through which the communication flow path 51B shown in FIG. It is preferable that the protrusion 51Ea to be included is included. Further, in the cooling steam supply unit 51 shown in FIG. 16, an annular member that is the tip of the steam passage vane 126B through which the communication flow path 51B shown in FIG. It is preferable to include a protrusion 51Eb provided at 126Ba.
- the protrusions 51Ea and 51Eb are preferably provided continuously along the circumferential direction of the high-pressure steam turbine 120 (rotation direction of the rotor 121).
- protrusion part 51Ea, 51Eb it is preferable to provide both protrusion part 51Ea and 51Eb.
- both the protrusions 51Ea and 51Eb it is preferable that the protrusion 51Ea is provided at a position near the rotor 121 and the protrusion 51Eb is provided at a position far from the rotor 121.
- the protrusions 51Ea and 51Eb may be provided together with the cooling steam nozzle 51C and the cooling hole 51D.
- the protrusions 51Ea and 51Eb shown in FIG. 15 are downstream of the flow of the superheated steam G between the annular member 126Ba at the distal end of the steam passage vane 126B and the annular member 127a at the proximal end of the moving blade 127. Although it is provided on the side, it may be provided on the upstream side of the flow of the superheated steam G.
- Embodiment 2 Embodiment 2 according to the present invention will be described below in detail with reference to the drawings.
- the present invention is not limited to the second embodiment.
- constituent elements in the second embodiment include those that can be easily replaced by those skilled in the art, or those that are substantially the same.
- FIG. 17 is a schematic configuration diagram illustrating an example of a combined cycle plant according to the second embodiment.
- FIG. 18 is a schematic configuration diagram illustrating another example of the combined cycle plant according to the second embodiment.
- a combined cycle plant 100 shown in FIGS. 17 and 18 includes a gas turbine 110, a high-pressure steam turbine 120, an intermediate-pressure steam turbine 130, and a low-pressure steam turbine 140. These gas turbine 110, high-pressure steam turbine 120, and intermediate-pressure steam turbine. 130, the low-pressure steam turbine 140 is disposed coaxially with the generator 150.
- the gas turbine 110 includes a compressor 111, a combustor 112, and a turbine 113.
- the compressor inlet air 114 is pressurized and supplied to the combustor 112.
- the combustor 112 high-temperature combustion gas is generated by the supplied air and fuel 115 and supplied to the turbine 113.
- the combustion gas passing through the turbine 113 is discharged as exhaust gas after the turbine 113 is driven to rotate.
- the combined cycle plant 100 includes a boiler (exhaust heat recovery boiler) 1 that generates superheated steam from water using the exhaust gas discharged from the turbine 113 in the gas turbine 110 as a heating source.
- the superheated steam generated by the boiler 1 drives the high-pressure steam turbine 120, the intermediate-pressure steam turbine 130, and the low-pressure steam turbine 140.
- Electric power is generated by the generator 150 by driving the gas turbine 110, the high pressure steam turbine 120, the intermediate pressure steam turbine 130, and the low pressure steam turbine 140.
- the steam used in the low-pressure steam turbine 140 is converted into condensate by a condenser 160 connected to the low-pressure steam turbine 140 and sent to the boiler 1 as water for generating superheated steam.
- the boiler 1 is connected to a flue 113a provided on the exhaust side of the turbine 113 in the gas turbine 110.
- the boiler 1 includes a low-pressure economizer 10, a low-pressure drum 11, a low-pressure evaporator 12, a medium-pressure economizer 13, a high-pressure primary economizer 14, an intermediate-pressure drum 15, and an intermediate-pressure evaporator from the downstream side of the exhaust gas flow.
- the boiler 1 includes a low-pressure system that generates low-pressure superheated steam for driving the low-pressure steam turbine 140, a medium-pressure system that generates medium-pressure superheated steam for driving the intermediate-pressure steam turbine 130, and high-pressure steam. And a high-pressure system that generates high-pressure superheated steam for driving the turbine 120.
- the low pressure system includes a low pressure economizer 10, a low pressure drum 11, a low pressure evaporator 12, a low pressure superheater 17, and a condensate pump 26.
- the intermediate pressure system includes an intermediate pressure economizer 13, an intermediate pressure drum 15, an intermediate pressure evaporator 16, an intermediate pressure superheater 19, a primary reheater 23, a secondary reheater 24, and an intermediate pressure feed water pump 27.
- the high-pressure system includes a high-pressure primary economizer 14, a high-pressure secondary economizer 18, a high-pressure drum 20, a high-pressure evaporator 21, a high-pressure primary superheater 22, a high-pressure secondary superheater 25, and a high-pressure feed water pump 28.
- the low pressure economizer 10 is connected to the condenser 160 through the connection line 30.
- a condensate pump 26 is provided in the connection line 30.
- the low-pressure economizer 10 is connected to the low-pressure drum 11 through a low-pressure branch line 31a among the connection lines 31 branched into three.
- the low pressure drum 11 is connected to the low pressure evaporator 12.
- the low-pressure drum 11 is connected to the low-pressure superheater 17 through a connection line 32.
- the low pressure superheater 17 is connected to the inlet side of the low pressure steam turbine 140 through the connection line 33.
- the outlet side of the low-pressure steam turbine 140 is connected to the condenser 160 through the connection line 34.
- the water (condensate) of the condenser 160 flows into the low-pressure economizer 10 through the connection line 30 and is heated by the condensate pump 26 and is heated through the low-pressure branch line 31 a of the connection line 31. It flows into the drum 11.
- the water supplied to the low-pressure drum 11 is evaporated by the low-pressure evaporator 12 to become saturated steam, returned to the low-pressure drum 11, and sent to the low-pressure superheater 17 through the connection line 32.
- the saturated steam is superheated in the low-pressure superheater 17, and this superheated steam is supplied to the low-pressure steam turbine 140 through the connection line 33.
- the steam discharged by driving the low-pressure steam turbine 140 is guided to the condenser 160 through the connection line 34 to become water (condensate), and is supplied to the low-pressure economizer 10 through the connection line 30 by the condensate pump 26. Sent out.
- the medium pressure economizer 13 is connected to the low pressure economizer 10 by an intermediate pressure branch line 31b among the connection lines 31 that branch into three.
- An intermediate pressure feed water pump 27 is provided in the intermediate pressure branch line 31b.
- the intermediate pressure economizer 13 is connected to the intermediate pressure drum 15 through a connection line 35.
- the connection line 35 is provided with a flow rate adjusting valve 36 on the way.
- the intermediate pressure drum 15 is connected to the intermediate pressure evaporator 16. Further, the intermediate pressure drum 15 is connected to the intermediate pressure superheater 19 through a connection line 37.
- the intermediate pressure superheater 19 is connected to the inlet side of the primary reheater 23 by a connection line 38.
- the primary reheater 23 is connected to the outlet side of the high-pressure steam turbine 120 through the connection line 40. Further, the primary reheater 23 is connected to the secondary reheater 24 by a connection line 41. The secondary reheater 24 is connected to the inlet side of the intermediate pressure steam turbine 130 through the connection line 42. The outlet side of the intermediate pressure steam turbine 130 is connected to the inlet side of the low pressure steam turbine 140 through a connection line 39.
- the water heated by the low pressure economizer 10 is further heated by flowing into the intermediate pressure economizer 13 via the intermediate pressure branch line 31b of the connection line 31 by the intermediate pressure feed water pump 27. It flows into the intermediate pressure drum 15 via the line 35.
- the water supplied to the intermediate pressure drum 15 is evaporated by the intermediate pressure evaporator 16 to become saturated vapor, returned to the intermediate pressure drum 15, and sent to the intermediate pressure superheater 19 through the connection line 37.
- the saturated steam is superheated in the intermediate pressure superheater 19, and this superheated steam is supplied to the primary reheater 23 via the connection line 38.
- the steam discharged by driving the high-pressure steam turbine 120 is sent to the primary reheater 23 through the connection line 40.
- the steam is superheated in the primary reheater 23, and this superheated steam is sent to the secondary reheater 24 through the connection line 41.
- the steam is further superheated in the secondary reheater 24, and this superheated steam is supplied to the intermediate pressure steam turbine 130 via the connection line 42.
- the steam discharged by driving the intermediate pressure steam turbine 130 is supplied to the low pressure steam turbine 140 through the connection line 39.
- the primary reheater 23 and the secondary reheater 24 superheat steam, they have the same function as the superheater and are included in the superheater in the second embodiment. That is, the primary reheater 23 is also referred to as a first superheater, and the secondary reheater 24 is also referred to as a second superheater.
- the high-pressure primary economizer 14 is connected to the low-pressure economizer 10 by a high-pressure branch line 31c among the connection lines 31 that branch into three.
- a high-pressure feed water pump 28 is provided in the high-pressure branch line 31c.
- the high-pressure primary economizer 14 is connected to the high-pressure secondary economizer 18 through a connection line 43.
- the high pressure secondary economizer 18 is connected to the high pressure drum 20 via a connection line 44.
- the connection line 44 is provided with a flow rate adjustment valve 45 in the middle.
- the high pressure drum 20 is connected to a high pressure evaporator 21.
- the high-pressure drum 20 is connected to the high-pressure primary superheater 22 through a connection line 46.
- the high-pressure primary superheater 22 is connected to the high-pressure secondary superheater 25 by a connection line 47.
- the high pressure secondary superheater 25 is connected to the inlet side of the high pressure steam turbine 120 by a connection line 48.
- the outlet side of the high-pressure steam turbine 120 is connected to the intermediate pressure primary reheater 23 through the connection line 40 as described above.
- the water heated in the low-pressure economizer 10 is further heated by flowing into the high-pressure primary economizer 14 via the high-pressure branch line 31 c of the connection line 31 by the high-pressure feed water pump 28. Then, it flows into the high-pressure secondary economizer 18 and is further heated and flows into the high-pressure drum 20 through the connection line 44.
- the water supplied to the high-pressure drum 20 is evaporated by the high-pressure evaporator 21 to become saturated steam, returned to the high-pressure drum 20, and sent to the high-pressure primary superheater 22 through the connection line 46.
- the saturated steam is superheated in the high-pressure primary superheater 22, and this superheated steam is sent to the high-pressure secondary superheater 25 through the connection line 47.
- the superheated steam is further superheated in the high pressure secondary superheater 25, and this superheated steam is supplied to the high pressure steam turbine 120 via the connection line 48.
- the steam turbine of the second embodiment includes a cooling steam supply unit (second cooling steam supply unit) 51 that cools the inside of the intermediate pressure steam turbine 130.
- the cooling steam supply unit 51 extends from the outlet of the intermediate pressure evaporator 16 to the inside of the secondary reheater 24 through the intermediate pressure superheater 19 and the primary reheater 23.
- a connection line 51 ⁇ / b> A that communicates with the inside of the intermediate pressure steam turbine 130.
- the connection line 51A connects the connection line 37 that connects the intermediate-pressure drum 15 and the intermediate-pressure superheater 19, the inside of the intermediate-pressure superheater 19, and the intermediate-pressure superheater 19 and the primary reheater 23.
- connection line 38 (and a part of the connection line 40), the interior of the primary reheater 23, the connection line 41 connecting the primary reheater 23 and the secondary reheater 24, the interior of the secondary reheater 24, Is communicated with the inside of the intermediate pressure steam turbine 130.
- the superheated steam supplied to the intermediate pressure steam turbine 130 passes through the connection line 42 from the secondary reheater 24, but the pressure decreases in the process of passing through the connection line 42. Therefore, the steam from the outlet of the intermediate pressure evaporator 16 to the inside of the secondary reheater 24 through the intermediate pressure superheater 19 and the primary reheater 23 is more than the superheated steam supplied to the intermediate pressure steam turbine 130.
- are high pressure and low temperature temperature lower than about 550 ° C. to 600 ° C. of superheated steam). Therefore, it is possible to supply cooling steam having a higher pressure and lower temperature than the superheated steam supplied to the intermediate pressure steam turbine 130 into the intermediate pressure steam turbine 130.
- the intermediate pressure from the outlet of the intermediate pressure evaporator 16 to the inside of the secondary reheater 24 through the intermediate pressure superheater 19 and the primary reheater 23, and the intermediate pressure.
- the cooling steam supply unit 51 including the connection line 51 ⁇ / b> A communicating with the inside of the steam turbine 130
- the combined cycle plant 100 has a higher pressure and lower temperature than the superheated steam supplied to the intermediate pressure steam turbine 130. Cooling steam can be supplied to the interior of the intermediate pressure steam turbine 130. As a result, it is possible to cool a high temperature part such as a rotor inside the intermediate pressure steam turbine 130 without requiring another power source.
- the generated steam in the combined cycle plant 100 is used and the fluid inside the intermediate pressure steam turbine 130 is not cooled, the operation efficiency of the intermediate pressure steam turbine 130 is prevented from being lowered, and as a result, the cycle efficiency is prevented from being lowered. be able to.
- connection line 51 ⁇ / b> A is connected to the connection line 38 (and the connection line 40) between the outlet of the intermediate pressure superheater 19 and the inlet of the primary reheater 23. It is preferable to communicate a part) with the inside of the intermediate pressure steam turbine 130.
- the primary reheat is performed. Since the steam supplied to the regenerator 23 and the secondary reheater 24 is reduced, the superheat efficiency in the primary reheater 23 and the secondary reheater 24 is improved, and the temperature of the superheated steam supplied to the intermediate pressure steam turbine 130 is increased. To do. As a result, the operation efficiency of the intermediate pressure steam turbine 130 can be improved, and the cycle efficiency can be improved.
- connection line 38 (and a part of the connection line 40) between the outlet of the intermediate pressure superheater 19 and the inlet of the primary reheater 23
- the amount of steam obtained from the intermediate pressure evaporator 16 can be increased, so that the amount of superheated steam supplied to the intermediate pressure steam turbine 130 can be increased.
- the operation efficiency of the intermediate pressure steam turbine 130 can be improved, and the cycle efficiency can be improved.
- connection line 51 ⁇ / b> A includes the connection line 41 between the outlet of the primary reheater 23 and the inlet of the secondary reheater 24, and the intermediate pressure steam. It is preferable to communicate with the inside of the turbine 130.
- the cooling steam is supplied to the inside of the intermediate pressure steam turbine 130 from the connection line 41 between the outlet of the primary reheater 23 and the inlet of the secondary reheater 24, the superheat supplied to the intermediate pressure steam turbine 130.
- the temperature of the steam is constant, the amount of steam obtained from the intermediate pressure evaporator 16 can be increased, so that the amount of superheated steam supplied to the intermediate pressure steam turbine 130 can be increased.
- the operation efficiency of the intermediate pressure steam turbine 130 can be improved, and the cycle efficiency can be improved.
- 19 to 32 are schematic configuration diagrams illustrating an example of a cooling steam supply unit according to the second embodiment.
- the intermediate pressure steam turbine 130 includes a rotor 131, a passenger compartment 132, a steam passage 133, and an intermediate pressure steam supply unit 134.
- the rotor 131 is provided so as to extend along the axis S of rotation thereof.
- the casing 132 houses the rotor 131 and supports the rotor 131 so as to be rotatable around the axis S.
- the steam passage 133 is an annular space provided between the rotor 131 and the vehicle compartment 132 along the extending direction of the rotor 131.
- the intermediate-pressure steam supply unit 134 is provided to communicate with the steam passage 133 from the outside of the passenger compartment 132 through the passenger compartment 132, and is connected to the connection line 42 to be superheated by the secondary reheater 24. Is supplied to the steam passage 133.
- the intermediate pressure steam supply part 134 includes an intermediate pressure steam nozzle part 134A.
- the intermediate-pressure steam nozzle portion 134A is attached to the passenger compartment 132 with a gap 135A that is formed in an annular shape surrounding the outer periphery of the rotor 131 and communicates with the steam passage 133 between the outer surface and the outer peripheral surface of the rotor 131. ing.
- the intermediate pressure steam nozzle portion 134A has an intermediate pressure steam nozzle chamber 134Aa formed in an annular shape inside thereof, and an opening that leads from the intermediate pressure steam nozzle chamber 134Aa to the steam passage 133 in the extending direction of the rotor 131. 134 Ab.
- the intermediate pressure steam nozzle part 134A is connected to the connection line 42, the steam superheated by the secondary reheater 24 is supplied to the intermediate pressure steam nozzle chamber 134Aa, and is discharged from the opening 134Ab to the steam passage 133.
- a plurality of nozzle part stationary blades 136A are attached along an annular shape to the opening 134Ab of the intermediate pressure steam nozzle chamber 134Aa in the intermediate pressure steam nozzle part 134A.
- the rotor 131 side is a tip portion and the vehicle compartment 132 side is a base end portion.
- a plurality of steam passage vanes 136B are attached to the passenger compartment 132 along an annular shape.
- the steam passage vane 136 ⁇ / b> B is provided in a plurality of stages along the extending direction of the rotor 131.
- the steam passage vane 136B has a tip portion on the rotor 131 side and an annular member 136Ba attached thereto, and has a gap 135B between the annular member 136Ba and the outer peripheral surface of the rotor 131, and is attached to the vehicle interior 132.
- the side is the base end.
- a plurality of moving blades 137 are attached to the outer periphery of the rotor 131 along the annular shape adjacent to the stationary blades 136A and 136B.
- the moving blades 137 are provided in a plurality of stages along the extending direction of the rotor 131.
- the moving blade 137 has a base end portion on the side attached to the rotor 131 and an annular member 137a attached to the rotor 131, and a side facing the passenger compartment 132 becomes a tip portion.
- the steam superheated by the secondary reheater 24 is supplied to the intermediate pressure steam nozzle chamber 134Aa and discharged from the opening 134Ab to the steam passage 133, and the stationary blades 136A and 136B and the moving blade 137 are discharged. As a result, the rotor 131 rotates.
- the cooling steam supply unit 51 is connected to the connection line 51A to supply the medium-pressure steam.
- a communication channel 51 ⁇ / b> B that penetrates the vehicle compartment 132 from the outside of the vehicle compartment 132 to the steam passage 133 and communicates therewith is included.
- the communication flow path 51B penetrates the vehicle compartment 132 on the opposite side of the opening 134Ab of the intermediate pressure steam nozzle chamber 134Aa in the intermediate pressure steam nozzle part 134A and communicates with the gap 135A. And open toward the outer peripheral surface of the rotor 131.
- a plurality of communication flow paths 51B may be provided along the circumferential direction of the intermediate pressure steam nozzle portion 134A (the rotation direction of the rotor 131), or may be provided as a single unit.
- the connection line 51A is branched into a plurality and connected to each communication channel 51B.
- the cooling steam C supplied via the connection line 51A is a gap 135A between the intermediate-pressure steam supply part 134 and the outer peripheral surface of the rotor 131 via the communication flow path 51B. It is discharged toward the outer peripheral surface of 131, flows along the extending direction of the rotor 131 through the gap 135A, reaches the steam passage 133, and is medium-pressure steam between the nozzle portion stationary blade 136A and the moving blade 137. The superheated steam G supplied to the steam passage 133 through the supply unit 134 is joined.
- the cooling steam C having a pressure higher than that of the superheated steam G supplied to the intermediate pressure steam turbine 130 and a low temperature is supplied to the intermediate pressure steam supply unit via the communication channel 51B. Since the air is discharged into a gap 135A between the outer surface of the rotor 134 and the rotor 131, the rotor 131 can be cooled. Moreover, according to the cooling steam supply unit 51 shown in FIG. 19, the cooling steam C having a pressure higher than that of the superheated steam G supplied to the intermediate pressure steam turbine 130 is supplied via the communication channel 51B.
- the communication flow path 51B shown in FIG. 19 preferably includes a cooling steam nozzle 51C provided at an opening communicating with the gap 135A.
- the cooling steam nozzle 51C narrows the opening communicating with the gap 135A in the communication flow path 51B, thereby increasing the flow velocity of the cooling steam C discharged from the communication flow path 51B to the gap 135A. .
- the temperature of the cooling steam C can be lowered and the cooling efficiency can be improved.
- the cooling steam nozzle 51 ⁇ / b> C is provided with the tip 51 ⁇ / b> Ca facing the rotation direction R of the rotor 131.
- the cooling steam C is discharged from the communication flow path 51B into the gap 135A along the rotation direction R of the rotor 131.
- friction loss caused by the difference between the rotational speed of the rotor 131 and the speed of the cooling steam C can be reduced.
- the cooling steam nozzle 51C is not limited to a configuration that is a plate member that is a separate member from the communication channel 51B, and the opening of the communication channel 51B may be narrowed. .
- a gap 135A through which the communication flow path 51B shown in FIG. 19 passes is a part that reaches the steam passage 133, and the nozzle part static air of the moving blade 137 adjacent to the nozzle part stationary blade 136A. It is preferable to include a protrusion 51Ea provided on the annular member 137a at the base end on the blade 136A side. Further, in the cooling steam supply unit 51 shown in FIG. 22, a gap 135A through which the communication flow path 51B shown in FIG. 19 passes is a part reaching the steam passage 133, and is a tip part of the nozzle part stationary blade 136 ⁇ / b> A and the moving blade 137. It is preferable to include a protrusion 51Eb provided on a part of the intermediate-pressure steam nozzle portion 134A that faces the annular member 137a at the base end of the first end.
- the protrusions 51Ea and 51Eb are preferably provided continuously along the circumferential direction of the intermediate pressure steam turbine 130 (rotation direction of the rotor 131).
- the protrusions 51Ea and 51Eb are located between the opening 134Ab of the intermediate pressure steam nozzle chamber 134Aa in the intermediate pressure steam nozzle portion 134A provided with the nozzle portion stationary blade 136A and the annular member 137a at the base end portion of the moving blade 137.
- Vortices are generated in the cooling steam C toward the steam passage 133.
- protrusion part 51Ea, 51Eb it is preferable to provide both protrusion part 51Ea and 51Eb.
- both the protrusions 51Ea and 51Eb it is preferable to provide the protrusion 51Ea at a position close to the rotor 131 and to provide the protrusion 51Eb at a position far from the rotor 131.
- the protruding portions 51Ea and 51Eb may be provided together with the cooling steam nozzle 51C.
- the communication flow path 51B passes through the casing 132, the opening 134Ab of the intermediate pressure steam nozzle chamber 134Aa in the intermediate pressure steam nozzle part 134A, and the nozzle part stationary blade 136A, and the gap 135A. Is provided to open toward the outer peripheral surface of the rotor 131.
- a plurality of communication flow paths 51B may be provided along the circumferential direction of the intermediate pressure steam nozzle portion 134A (the rotation direction of the rotor 131), or may be provided as a single unit.
- the connection line 51A is branched into a plurality and connected to each communication channel 51B.
- the cooling steam C supplied via the connection line 51A is a gap 135A between the intermediate-pressure steam supply part 134 and the outer peripheral surface of the rotor 131 via the communication flow path 51B. It is discharged toward the outer peripheral surface of 131, flows along the extending direction of the rotor 131 through the gap 135A, reaches the steam passage 133, and the steam passage 133 between the nozzle portion stationary blade 136A and the moving blade 137. And the superheated steam G supplied to.
- the cooling steam C having a pressure higher than that of the superheated steam G supplied to the intermediate pressure steam turbine 130 and a low temperature is supplied to the intermediate pressure steam supply unit via the communication channel 51B. Since the air is discharged into a gap 135A between the outer surface of the rotor 134 and the rotor 131, the rotor 131 can be cooled. Moreover, according to the cooling steam supply unit 51 shown in FIG. 23, the cooling steam C having a higher pressure and lower temperature than the superheated steam G supplied to the intermediate pressure steam turbine 130 is supplied through the communication channel 51B.
- the cooling steam supply section 51 shown in FIG. 23 the communication flow path 51B is provided through the nozzle section stationary blade 136A, so that the nozzle section stationary blade 136A can be cooled, and the intermediate pressure steam turbine 130 can be cooled.
- the durability of the nozzle vane 136A can be improved with respect to higher temperatures.
- the communication flow path 51B shown in FIG. 23 includes a cooling hole 51D that passes through the nozzle part vane 136A and opens to the steam passage 133.
- the cooling steam C is discharged to the steam passage 133 through the cooling hole 51D penetrating the nozzle portion stationary blade 136A.
- the nozzle part stationary blade 136A can be cooled, and the durability of the nozzle part stationary blade 136A can be improved against further increase in the temperature of the intermediate pressure steam turbine 130.
- the communication flow path 51B shown in FIG. 23 preferably includes a cooling steam nozzle 51C provided in an opening communicating with the gap 135A.
- the cooling steam nozzle 51C narrows the opening communicating with the gap 135A in the communication flow path 51B, thereby increasing the flow rate of the cooling steam C discharged from the communication flow path 51B to the gap 135A. .
- the temperature of the cooling steam C can be lowered and the cooling efficiency can be improved.
- the cooling steam nozzle 51C is preferably provided with the tip 51Ca facing the rotation direction R of the rotor 131.
- the cooling steam C is discharged from the communication flow path 51B into the gap 135A along the rotation direction R of the rotor 131.
- friction loss caused by the difference between the rotational speed of the rotor 131 and the speed of the cooling steam C can be reduced.
- the cooling steam nozzle 51C is not limited to the configuration that is a plate member separate from the communication flow path 51B, and may be formed by constricting the opening itself of the communication flow path 51B. . Further, the cooling steam nozzle 51C may be provided together with the cooling hole 51D.
- the cooling steam supply part 51 shown in FIG. 27 it is provided in the annular member 137a at the base end part on the nozzle part stationary blade 136A side of the moving blade 137 adjacent to the nozzle part stationary blade 136A through which the communication flow path 51B shown in FIG. It is preferable that the protrusion 51Ea to be included is included. Further, in the cooling steam supply unit 51 shown in FIG. 27, the intermediate pressure facing the annular member 137a at the tip end portion of the nozzle portion stationary blade 136A through which the communication flow path 51B shown in FIG. It is preferable to include a protrusion 51Eb provided in a part of the steam nozzle part 134A.
- the protrusions 51Ea and 51Eb are preferably provided continuously along the circumferential direction of the intermediate pressure steam turbine 130 (rotation direction of the rotor 131).
- the protrusions 51Ea and 51Eb are located between the opening 134Ab of the intermediate pressure steam nozzle chamber 134Aa in the intermediate pressure steam nozzle portion 134A provided with the nozzle portion stationary blade 136A and the annular member 137a at the base end portion of the moving blade 137.
- Vortices are generated in the cooling steam C toward the steam passage 133.
- protrusion part 51Ea, 51Eb it is preferable to provide both protrusion part 51Ea and 51Eb.
- both the protrusions 51Ea and 51Eb it is preferable to provide the protrusion 51Ea at a position close to the rotor 131 and to provide the protrusion 51Eb at a position far from the rotor 131.
- the protrusions 51Ea and 51Eb may be provided together with the cooling steam nozzle 51C and the cooling hole 51D.
- the communication flow path 51B passes through the casing 132, the steam passage stationary blade 136B, and the annular member 136Ba at the tip of the steam passage stationary blade 136B, and communicates with the gap 135B to the rotor.
- An opening is provided toward the outer peripheral surface of 131.
- a plurality of communication flow paths 51B may be provided along the circumferential direction of the intermediate pressure steam nozzle portion 134A (the rotation direction of the rotor 131), or may be provided as a single unit.
- the connection line 51A is branched into a plurality and connected to each communication channel 51B.
- the cooling steam C supplied via the connection line 51A is formed in a gap 135B between the annular member 136Ba of the steam passage vane 136B and the outer peripheral surface of the rotor 131 via the communication flow path 51B. And is discharged toward the outer peripheral surface of the rotor 131, flows along the extending direction of the rotor 131 through the gap 135B, reaches the steam passage 133, and between the steam passage stationary blade 136B and the moving blade 137.
- the superheated steam G supplied to the steam passage 133 joins.
- the cooling steam C having a pressure higher than that of the superheated steam G supplied to the intermediate pressure steam turbine 130 and a low temperature is supplied to the steam passage vane 136B via the communication channel 51B. Since the discharge is made in the gap 135B between the annular member 136Ba and the outer peripheral surface of the rotor 131, the rotor 131 can be cooled.
- the communication flow path 51B is provided through the steam passage stationary blade 136B, so that the steam passage stationary blade 136B can be cooled, and the intermediate pressure steam turbine 130 can be cooled. The durability of the steam passage vane 136B can be improved with respect to higher temperatures.
- the communication flow path 51B shown in FIG. 28 includes a cooling hole 51D that passes through the steam passage vane 136B and opens to the steam passage 133.
- the cooling steam C is discharged to the steam passage 133 through the cooling hole 51D penetrating the steam passage vane 136B.
- the nozzle part stationary blade 136A can be cooled, and the durability of the steam passage stationary blade 136B can be improved against further increase in the temperature of the intermediate pressure steam turbine 130.
- the communication flow path 51B shown in FIG. 28 preferably includes a cooling steam nozzle 51C provided in an opening communicating with the gap 135B.
- the cooling steam nozzle 51C narrows the opening communicating with the gap 135B in the communication flow path 51B, thereby increasing the flow velocity of the cooling steam C discharged from the communication flow path 51B to the gap 135B. .
- the temperature of the cooling steam C can be lowered and the cooling efficiency can be improved.
- the cooling steam nozzle 51 ⁇ / b> C is provided with the tip 51 ⁇ / b> Ca facing the rotation direction R of the rotor 131. Accordingly, the cooling steam C is discharged from the communication flow path 51B into the gap 135B along the rotation direction R of the rotor 131. As a result, friction loss caused by the difference between the rotational speed of the rotor 131 and the speed of the cooling steam C can be reduced.
- cooling steam nozzle 51C is not limited to a configuration that is a plate member that is a separate member from the communication flow path 51B as shown in FIGS. 30 and 31, and may be formed by constricting the opening itself of the communication flow path 51B. . Further, the cooling steam nozzle 51C may be provided together with the cooling hole 51D.
- the cooling steam supply part 51 shown in FIG. 32 it is provided in the annular member 137a at the base end part on the steam passage stationary blade 136B side of the moving blade 137 adjacent to the steam passage stationary blade 136B through which the communication flow path 51B shown in FIG. It is preferable that the protrusion 51Ea to be included is included. Further, in the cooling steam supply unit 51 shown in FIG. 32, an annular member that is the tip of the steam passage stationary blade 136B through which the communication channel 51B shown in FIG. 28 passes and is opposed to the annular member 137a at the base end of the moving blade 137. It is preferable to include a protrusion 51Eb provided on 136Ba.
- the protrusions 51Ea and 51Eb are preferably provided continuously along the circumferential direction of the intermediate pressure steam turbine 130 (rotation direction of the rotor 131).
- protrusion part 51Ea, 51Eb it is preferable to provide both protrusion part 51Ea and 51Eb.
- both the protrusions 51Ea and 51Eb it is preferable to provide the protrusion 51Ea at a position close to the rotor 131 and to provide the protrusion 51Eb at a position far from the rotor 131.
- a vortex is first generated by the protrusion 51Ea with respect to the cooling steam C discharged toward the outer peripheral surface of the rotor 131 from the communication passage 51B penetrating the steam passage vane 136B, and then the vortex is generated by the protrusion 51Eb.
- the protrusion 51Eb causes it to occur.
- the protrusions 51Ea and 51Eb may be provided together with the cooling steam nozzle 51C and the cooling hole 51D.
- the protrusions 51Ea and 51Eb shown in FIG. 32 are downstream of the flow of the superheated steam G between the annular member 136Ba at the distal end of the steam passage stationary blade 136B and the annular member 137a at the proximal end of the moving blade 137. Although it is provided on the side, it may be provided on the upstream side of the flow of the superheated steam G.
- the intermediate pressure steam turbine 130 shown in FIGS. 28 to 32 includes a configuration integrated with the high pressure steam turbine 120.
- steam having a pressure higher than that of the superheated steam G and having a low temperature is supplied to the gap 135A to drive the high-pressure steam turbine 120.
- the rotor 131 is cooled in the gap 135A, and the superheated steam G is prevented from leaking from the gap 135A.
- the cooling steam C is discharged into the gap 135B from the communication flow path 51B penetrating the steam passage vane 136B toward the outer peripheral surface of the rotor 131, and the rotor 131 is cooled around the gap 135B.
- the above-described second embodiment may be configured together with the above-described first embodiment.
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Abstract
Description
以下に、本発明に係る実施形態1を図面に基づいて詳細に説明する。なお、この実施形態1によりこの発明が限定されるものではない。また、下記実施形態1における構成要素には、当業者が置換可能かつ容易なもの、あるいは実質的に同一のものが含まれる。
以下に、本発明に係る実施形態2を図面に基づいて詳細に説明する。なお、この実施形態2によりこの発明が限定されるものではない。また、下記実施形態2における構成要素には、当業者が置換可能かつ容易なもの、あるいは実質的に同一のものが含まれる。
10 低圧節炭器
11 低圧ドラム
12 低圧蒸発器
13 中圧節炭器
14 高圧一次節炭器
15 中圧ドラム
16 中圧蒸発器
17 低圧過熱器
18 高圧二次節炭器
19 中圧過熱器
20 高圧ドラム
21 高圧蒸発器
22 高圧一次過熱器
23 一次再熱器
24 二次再熱器
25 高圧二次過熱器
26 復水ポンプ
27 中圧給水ポンプ
28 高圧給水ポンプ
30 接続ライン
31 接続ライン
31a 低圧分岐ライン
31b 中圧分岐ライン
31c 高圧分岐ライン
32 接続ライン
33 接続ライン
34 接続ライン
35 接続ライン
36 流量調整弁
37 接続ライン
38 接続ライン
39 接続ライン
40 接続ライン
41 接続ライン
42 接続ライン
43 接続ライン
44 接続ライン
45 流量調整弁
46 接続ライン
47 接続ライン
48 接続ライン
49 接続ライン
51 冷却蒸気供給部
51A 接続ライン
51B 連通流路
51C 冷却蒸気ノズル
51Ca 先端
51D 冷却孔
51Ea 突起部
51Eb 突起部
100,200 コンバインドサイクルプラント
110 ガスタービン
111 圧縮機
112 燃焼器
113 タービン
113a 煙道
114 圧縮機入口空気
115 燃料
120 高圧蒸気タービン
121 ロータ
122 車室
123 蒸気通路
124 高圧蒸気供給部
124A 高圧蒸気ノズル部
124Aa 高圧蒸気ノズル室
124Ab 開口
125A 隙間
125B 隙間
126A ノズル部静翼
126B 蒸気通路静翼
126Ba 環状部材
127 動翼
127a 環状部材
130 中圧蒸気タービン
131 ロータ
132 車室
133 蒸気通路
134 中圧蒸気供給部
134A 中圧蒸気ノズル部
134Aa 中圧蒸気ノズル室
134Ab 開口
135A 隙間
135B 隙間
136A ノズル部静翼
136B 蒸気通路静翼
136Ba 環状部材
137 動翼
137a 環状部材
140 低圧蒸気タービン
150 発電機
160 復水器
C 冷却蒸気
G 過熱蒸気
R 回転方向
S 軸心
Claims (14)
- ガスタービンと、
前記ガスタービンから排出される排ガスを加熱源とするボイラと、
自身の回転の軸心に沿って延在するロータと、前記ロータを格納する車室と、前記ロータの延在方向に沿って前記ロータと前記車室との間に設けられた蒸気通路と、前記車室の外部から前記車室を貫通して前記蒸気通路に至り連通して設けられ過熱された蒸気が供給される高圧蒸気供給部と、を含み、前記ボイラで発生した高圧蒸気により駆動する高圧蒸気タービンと、
前記ボイラで発生した低圧蒸気および前記高圧蒸気タービンを経た蒸気により駆動する低圧蒸気タービンと、
前記低圧蒸気タービンを経た蒸気を復水にする復水器と、
前記復水器からの前記復水を前記ボイラに供給する復水ポンプと、
前記高圧蒸気供給部とは別に前記車室の外部から前記車室を貫通して前記蒸気通路に至り連通する連通流路を含み、前記高圧蒸気タービンの内部に連通する第一冷却蒸気供給部と、
を備えるコンバインドサイクルプラントに係り、
前記高圧蒸気供給部は、
前記ロータの外周を囲む環状に形成されてその外面と前記ロータの外周面との間に前記蒸気通路に連通する隙間を有して前記車室に取り付けられ、その内部に環状に沿って形成された高圧蒸気ノズル室と、前記高圧蒸気ノズル室から前記ロータの延在方向に向いて前記蒸気通路に連通する開口とを有し、前記高圧蒸気ノズル室に過熱された蒸気が供給される高圧蒸気ノズル部を含み、
前記高圧蒸気ノズル部は、前記高圧蒸気ノズル室の前記開口にノズル部静翼が取り付けられており、
前記連通流路は、
前記ノズル部静翼を貫通して前記隙間に連通して設けられることを特徴とする蒸気タービン。 - 前記ボイラは、
前記復水器からの前記復水から蒸気を発生する高圧蒸発器と、前記高圧蒸発器で発生した蒸気を過熱する高圧一次過熱器と、前記高圧一次過熱器で過熱された蒸気をさらに過熱する高圧二次過熱器と、を含み、前記高圧二次過熱器で過熱された蒸気が前記高圧蒸気タービンの駆動に供給され、
前記第一冷却蒸気供給部は、
前記高圧蒸発器の出口から前記高圧一次過熱器を経て前記高圧二次過熱器内までの間と、前記高圧蒸気タービンの内部とを連通する接続ラインを含むことを特徴とする請求項1に記載の蒸気タービン。 - 前記接続ラインは、前記高圧一次過熱器の出口から前記高圧二次過熱器の入口までの間と、前記高圧蒸気タービンの内部とを連通することを特徴とする請求項2に記載の蒸気タービン。
- 前記コンバインドサイクルプラントは、
自身の回転の軸心に沿って延在するロータと、前記ロータを格納する車室と、前記ロータの延在方向に沿って前記ロータと前記車室との間に設けられた蒸気通路と、前記車室の外部から前記車室を貫通して前記蒸気通路に至り連通して設けられ過熱された蒸気が供給される中圧蒸気供給部と、を含み、前記ボイラで発生した中圧蒸気により駆動する中圧蒸気タービンと、
前記中圧蒸気供給部とは別に前記車室の外部から前記車室を貫通して前記蒸気通路に至り連通する連通流路を含み、前記中圧蒸気供給部の内部に連通する第二冷却蒸気供給部と、
を備え、
前記中圧蒸気供給部は、
前記ロータの外周を囲む環状に形成されてその外面と前記ロータの外周面との間に前記蒸気通路に連通する隙間を有して前記車室に取り付けられ、その内部に環状に沿って形成された中圧蒸気ノズル室と、前記中圧蒸気ノズル室から前記ロータの延在方向に向いて前記蒸気通路に連通する開口とを有し、前記中圧蒸気ノズル室に過熱された蒸気が供給される中圧蒸気ノズル部を含み、
前記中圧蒸気ノズル部は、前記中圧蒸気ノズル室の前記開口にノズル部静翼が取り付けられており、
前記連通流路は、
前記ノズル部静翼を貫通して前記隙間に連通して設けられることを特徴とする請求項1~3のいずれか1つに記載の蒸気タービン。 - 前記ボイラは、
前記復水器からの前記復水から蒸気を発生する中圧蒸発器と、前記中圧蒸発器で発生した蒸気を過熱する中圧過熱器と、前記中圧過熱器で過熱された蒸気を再過熱する一次再熱器と、前記一次再熱器で過熱された蒸気をさらに再過熱する二次再熱器と、を含み、前記二次再熱器で過熱された蒸気が前記中圧蒸気タービンの駆動に供給され、
前記第二冷却蒸気供給部は、
前記中圧蒸発器の出口から前記中圧過熱器および前記一次再熱器を経て前記二次再熱器内までの間と、前記中圧蒸気タービンの内部とを連通する接続ラインを含むことを特徴とする請求項4に記載の蒸気タービン。 - 前記接続ラインは、前記中圧過熱器の出口から前記一次再熱器の入口までの間と、前記中圧蒸気タービンの内部とを連通することを特徴とする請求項5に記載の蒸気タービン。
- 前記接続ラインは、前記一次再熱器の出口から前記二次再熱器の入口までの間と、前記中圧蒸気タービンの内部とを連通することを特徴とする請求項5に記載の蒸気タービン。
- 前記蒸気通路をなす前記車室に、前記ロータの外周面との間に前記蒸気通路に連通する隙間を有して蒸気通路静翼が取り付けられており、
前記連通流路は、
前記蒸気通路静翼を貫通して前記隙間に連通して設けられることを特徴とする請求項1~7のいずれか1つに記載の蒸気タービン。 - 前記ロータの外周に前記静翼に隣接して動翼が取り付けられており、
前記第一冷却蒸気供給部は、
前記連通流路が貫通する前記静翼に隣接する前記動翼の前記静翼側の基端部、前記連通流路が貫通する前記静翼の前記動翼側の先端部、の少なくとも一方に設けられる突起部を含むことを特徴とする請求項1~8のいずれか1つに記載の蒸気タービン。 - 前記連通流路は、前記静翼を貫通して前記蒸気通路に開口する冷却孔を含むことを特徴とする請求項1~9のいずれか1つに記載の蒸気タービン。
- 前記連通流路は、前記隙間に連通する開口に設けられる冷却蒸気ノズルを含むことを特徴とする請求項1~10のいずれか1つに記載の蒸気タービン。
- 前記冷却蒸気ノズルは、前記ロータの回転方向に先端を向けて設けられることを特徴とする請求項11に記載の蒸気タービン。
- ガスタービンと、
前記ガスタービンから排出される排ガスを加熱源とするボイラと、
前記ボイラで発生した高圧蒸気により駆動する高圧蒸気タービンと、
前記ボイラで発生した低圧蒸気および前記高圧蒸気タービンを経た蒸気により駆動する低圧蒸気タービンと、
前記低圧蒸気タービンを経た蒸気を復水にする復水器と、
前記復水器からの前記復水を前記ボイラに供給する復水ポンプと、
を備えるコンバインドサイクルプラントに係り、
前記ボイラは、前記復水器からの前記復水から蒸気を発生する高圧蒸発器と、前記高圧蒸発器で発生した蒸気を過熱する高圧一次過熱器と、前記高圧一次過熱器で過熱された蒸気をさらに過熱する高圧二次過熱器と、を含み、前記高圧二次過熱器で過熱された蒸気が前記高圧蒸気タービンの駆動に供給され、
前記高圧蒸発器の出口から前記高圧一次過熱器を経て前記高圧二次過熱器内までの間と、前記高圧蒸気タービンの内部とを連通する接続ラインを含む冷却蒸気供給部を備えることを特徴とする蒸気タービン。 - ガスタービンと、
前記ガスタービンから排出される排ガスを加熱源とするボイラと、
前記ボイラで発生した高圧蒸気により駆動する高圧蒸気タービンと、
前記ボイラで発生した中圧蒸気により駆動する中圧蒸気タービンと、
前記ボイラで発生した低圧蒸気および前記中圧蒸気タービンを経た蒸気により駆動する低圧蒸気タービンと、
前記低圧蒸気タービンを経た蒸気を復水にする復水器と、
前記復水器からの前記復水を前記ボイラに供給する復水ポンプと、
を備えるコンバインドサイクルプラントに係り、
前記ボイラは、前記復水器からの前記復水から蒸気を発生する中圧蒸発器と、前記中圧蒸発器で発生した蒸気を過熱する中圧過熱器と、前記中圧過熱器で過熱された蒸気を再過熱する一次再熱器と、前記一次再熱器で過熱された蒸気をさらに再過熱する二次再熱器と、を含み、前記二次再熱器で過熱された蒸気が前記中圧蒸気タービンの駆動に供給され、
前記中圧蒸発器の出口から前記中圧過熱器および前記一次再熱器を経て前記二次再熱器内までの間と、前記中圧蒸気タービンの内部とを連通する接続ラインを含む冷却蒸気供給部を備えることを特徴とする蒸気タービン。
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JPS58167802A (ja) * | 1982-03-16 | 1983-10-04 | シーメンス・アクチエンゲゼルシヤフト | 軸流蒸気タ−ビン |
JPH06200704A (ja) * | 1992-12-28 | 1994-07-19 | Mitsubishi Heavy Ind Ltd | 蒸気タービンノズル室 |
JPH11132006A (ja) * | 1997-10-29 | 1999-05-18 | Hitachi Ltd | ガスタービン設備 |
JP2002147205A (ja) * | 2000-11-13 | 2002-05-22 | Mitsubishi Heavy Ind Ltd | コンバインドサイクルガスタービン |
JP2004239262A (ja) * | 2003-02-05 | 2004-08-26 | Siemens Ag | 蒸気タービンロータと蒸気タービンおよび蒸気タービンロータの能動的冷却方法と能動的冷却の使用方法 |
WO2010097983A1 (ja) * | 2009-02-25 | 2010-09-02 | 三菱重工業株式会社 | 蒸気タービン発電設備の冷却方法及び装置 |
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US10876408B2 (en) | 2020-12-29 |
US20180371917A1 (en) | 2018-12-27 |
KR102040423B1 (ko) | 2019-11-04 |
CN108431369A (zh) | 2018-08-21 |
CN108431369B (zh) | 2020-08-14 |
DE112016006048T5 (de) | 2018-09-20 |
KR20180084116A (ko) | 2018-07-24 |
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