WO2016002602A1 - タービン静翼、タービン、及び、タービン静翼の改造方法 - Google Patents
タービン静翼、タービン、及び、タービン静翼の改造方法 Download PDFInfo
- Publication number
- WO2016002602A1 WO2016002602A1 PCT/JP2015/068228 JP2015068228W WO2016002602A1 WO 2016002602 A1 WO2016002602 A1 WO 2016002602A1 JP 2015068228 W JP2015068228 W JP 2015068228W WO 2016002602 A1 WO2016002602 A1 WO 2016002602A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- turbine
- passage
- shroud
- cooling
- inner shroud
- Prior art date
Links
Images
Classifications
-
- 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
- F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
-
- 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
- F01D5/12—Blades
- F01D5/14—Form or construction
- F01D5/18—Hollow blades, i.e. blades with cooling or heating channels or cavities; Heating, heat-insulating or cooling means on blades
- F01D5/187—Convection 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
- 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
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/001—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between stator blade and rotor
-
- 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
- F01D5/12—Blades
- F01D5/14—Form or construction
- F01D5/18—Hollow blades, i.e. blades with cooling or heating channels or cavities; Heating, heat-insulating or cooling means on blades
- F01D5/187—Convection cooling
- F01D5/188—Convection cooling with an insert in the blade cavity to guide the cooling fluid, e.g. forming a separation wall
-
- 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
- F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
- F01D9/04—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector
-
- 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
- F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
- F01D9/04—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector
- F01D9/041—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector using blades
-
- 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
-
- 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
-
- 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
- F02C7/18—Cooling of plants characterised by cooling medium the medium being gaseous, e.g. air
-
- 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
- F05D2240/00—Components
- F05D2240/80—Platforms for stationary or moving blades
- F05D2240/81—Cooled platforms
-
- 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
- F05D2250/00—Geometry
- F05D2250/10—Two-dimensional
- F05D2250/18—Two-dimensional patterned
- F05D2250/185—Two-dimensional patterned serpentine-like
-
- 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
-
- 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
- F05D2260/221—Improvement of heat transfer
- F05D2260/2214—Improvement of heat transfer by increasing the heat transfer surface
- F05D2260/22141—Improvement of heat transfer by increasing the heat transfer surface using fins or ribs
Definitions
- the present invention relates to a turbine vane, a turbine provided with the same, and a method of remodeling the turbine vane.
- Priority is claimed on Japanese Patent Application No. 2014-134442, filed Jun. 30, 2014, the content of which is incorporated herein by reference.
- a conventional turbine includes, for example, as in Patent Document 1, a turbine vane including a radially extending vane main body of the turbine and a plate-like outer shroud and an inner shroud provided at both ends in the extension direction of the wing body. It is provided.
- a serpentine flow path meandering in the radial direction of the turbine is provided inside the wing body. The blade body is cooled by the flow of the cooling medium (cooling air) through the serpentine flow path.
- the cooling medium after passing through the serpentine flow path is guided to a space radially inward of the turbine than the inner shroud, and then the inner shroud of the turbine stator vane axially adjacent to the turbine is It flows out to the combustion gas passage from the gap with the platform of the turbine blade. This prevents the combustion gas passing through the combustion gas passage from entering the space radially inward of the turbine than the inner shroud.
- a serpentine flow path is formed, and a plurality of cooling air holes are provided on the trailing edge side of the inner shroud.
- the turbine vane of Patent Document 2 uses part of the cooling air for cooling the trailing edge of the inner shroud.
- FIGS. 13 An example of the cooling structure on the trailing edge side of the inner shroud in a conventional turbine vane is shown in FIGS.
- the cooling air supplied from the outer shroud (not shown) of the turbine vane 3 ⁇ / b> A enters the serpentine flow path 30 and cools the wing body 21. Thereafter, the cooling air flows into the most downstream main flow passage 31B of the serpentine flow passages 30 which is located closest to the trailing edge 21B of the wing main body 21.
- the cooling air flowing through the most downstream main flow passage 31B convectively cools the trailing edge portion of the wing body 21 when discharged from the trailing edge 21B of the wing body 21 into the combustion gas.
- a cavity CB is disposed radially inward of the inner shroud 22 and cooling air is supplied from the outer shroud to the cavity CB.
- one end that is the first end communicates with the cavity CB, and the other end that is the second end is the turbine axial direction downstream end of the inner shroud 22.
- a cooling passage 70 is formed in the opening.
- the cooling passage 70 is formed along the flow direction of the combustion gas.
- a plurality of cooling passages 70 are arranged in the circumferential direction of the inner shroud 22.
- a plurality of cooling passages 70 mainly cool the trailing edge of the inner shroud 22.
- the serpentine flow passage 30 is connected to the end flow passage 31 C formed in the inner shroud 22 at the downstream end of the most downstream main flow passage 31 B located most downstream of the serpentine flow passage 30.
- an outflow passage 29 is provided that communicates the end flow passage 31C and the disk cavity CD located on the downstream side of the cavity CB in the turbine axial direction.
- the opening where the end flow passage 31C opens to the upstream end surface 26a of the rib 26 of the inner shroud 22 is closed by a lid 26b or the like.
- the cooling passages at the trailing edge of the inner shroud may not be arranged uniformly in the circumferential direction of the inner shroud. That is, when the inner shroud is viewed from the circumferential direction (cross section XI-XI shown in FIG. 15), one end of the cooling passage communicates with the cavity, and the other end of the cooling passage is the downstream end surface of the inner shroud and opens into the combustion gas. doing.
- end flow paths exist around the junction between the blade body and the inner shroud at the downstream end of the most downstream main flow path.
- the cooling passages can not be arranged at uniform intervals in the circumferential direction. As a result, in the rear edge portion of the inner shroud, cooling in the circumferential direction of the inner shroud becomes uneven, and there is a possibility that temperature distribution occurs in the circumferential direction and oxidation reduction occurs in the high temperature portion.
- the present invention is provided with a turbine vane that can effectively utilize the cooling medium that has passed through the serpentine flow path by suppressing the thickness reduction of the high temperature part that occurs with the uneven cooling of the trailing edge of the inner shroud.
- a turbine and a method of remodeling a turbine vane are provided.
- a turbine vane includes a blade body extending in the radial direction of the turbine, and a plate-like member provided at the radially inner end of the blade body.
- the cooling medium flows through the serpentine flow path to cool the wing body, and then flows through the cooling passage. This makes it possible to uniformly cool the trailing edge side portion (trailing edge portion) of one shroud and to suppress oxidation reduction of the high temperature portion of the shroud.
- the cooling medium after passing through the serpentine flow path is reused, and the cooling medium can be used effectively.
- the one shroud is located on the opposite side of the first main surface of the one shroud on which the wing body is disposed.
- the cavity may be provided on the second main surface, and the axial downstream end face of the cavity may be disposed on the upstream side in the axial direction from the most downstream main flow path of the serpentine flow path.
- the cooling passage is formed along the flow direction of the combustion gas, and the circumferential direction of the one shroud is the cooling path.
- the most downstream main flow path of the serpentine flow path may be provided within the range of the position where it is joined to the one shroud.
- the cooling passage is formed along the flow direction of the combustion gas, and the one shroud In the circumferential direction, at least an area where the end flow path of the serpentine flow path is disposed may be provided.
- the cooling passage extends in the circumferential direction of the turbine between one end and the other end.
- a widening cavity may be provided.
- cooling passages are arranged spaced apart from each other in the circumferential direction of the turbine, and the axial direction of the turbine from the widening cavity portion And a plurality of branch passages extending to the rear edge of the one shroud.
- the area on the trailing edge side of one shroud cooled by the cooling medium flowing through the cooling passage can be expanded in the circumferential direction of the turbine. That is, the cooling medium after passing through the serpentine flow path can be used more effectively.
- the one shroud has one end disposed with the wing main body of the one shroud.
- a second opening is provided in a cavity provided in a second main surface opposite to the first main surface, and the other end is opened in a trailing edge of the one shroud to pass the cooling medium in the cavity
- the cooling passage may be provided, and the second cooling passage may be spaced apart in the circumferential direction of the turbine from the first cooling passage which is the cooling passage.
- a region of the trailing edge of one of the shrouds located near the trailing edge of the wing body can be cooled by the cooling medium passing through the first cooling passage as described above.
- a region of the trailing edge of one of the shrouds, which is offset from the vicinity of the trailing edge of the blade body to the circumferential direction of the turbine, can be cooled by the cooling medium passing through the second cooling passage. That is, it is possible to efficiently cool the entire trailing edge of one shroud.
- a turbine according to an eighth aspect of the present invention is fixed to a rotor, a turbine casing surrounding the periphery of the rotor, a turbine bucket fixed to the outer periphery of the rotor, and an inner periphery of the turbine casing, A turbine blade and the turbine vane according to any one of the first to seventh aspects alternately arranged in the axial direction of the rotor.
- a method of modifying a turbine vane comprising: a radially extending blade main body of the turbine; a plate-like inner shroud provided at a radially inner end of the blade main body; A plate-like outer shroud provided at a radially outer end of the wing body, the wing body being formed in a radially meandering manner in the inner side thereof, and including a serpentine flow path through which a cooling medium flows
- a method of remodeling a stator blade wherein one end of the inner shroud and the outer shroud opens to the downstream end of the serpentine flow path, and the other end opens to the trailing edge of the one shroud.
- the temperature distribution in the circumferential direction of the trailing edge of one shroud is made uniform, and the oxidation reduction of the high temperature part of one shroud is suppressed.
- the cooling medium after passing through the serpentine flow path is reused, and the cooling medium can be used effectively. As a result, the amount of cooling air is reduced, and the thermal efficiency of the gas turbine is improved.
- FIG. 4 is a cross-sectional view of the turbine vane according to the first embodiment of the present invention cut along the blade centerline Q, and is a cross-sectional view taken along line II-II in FIG. 3;
- FIG. 3 is a cross-sectional view taken along line III-III in FIG.
- FIG. 4 is a cross-sectional view taken along line IV-IV in FIG. It is a figure which shows the positional relationship of the cooling passage of the trailing edge part of the inner shroud of the conventional turbine vane, and the end flow path of serpentine flow paths.
- It is sectional drawing which shows an example of the turbine stator blade before remodeling.
- FIG. 6 is a cross-sectional view of a turbine vane according to a second embodiment of the present invention cut along the circumferential direction of the turbine. It is sectional drawing which cut
- FIG. 12 is a cross-sectional view taken along the line V-V in FIG. FIG.
- FIG. 7 is a partial plan view showing a cooling passage on a trailing edge side of an inner shroud of a conventional turbine vane.
- FIG. 14 is a cross-sectional view taken along line XX in FIG.
- FIG. 14 is a cross-sectional view taken along line XI-XI in FIG.
- the gas turbine GT supplies fuel to the compressor C generating the compressed air c and the compressed air c supplied from the compressor C to generate the combustion gas g.
- a plurality of combustors B and a turbine T for obtaining rotational power by the combustion gas g supplied from the combustors B are provided.
- the rotor R C of the compressor C and the rotor R T of the turbine T are connected at their shaft ends and extend on the turbine shaft P.
- the turbine T includes a rotor RT , a turbine casing 1 surrounding the rotor RT , a turbine blade 2, and a turbine vane 3.
- the rotor RT is constituted by a plurality of rotor disks arranged in the axial direction of the turbine.
- the turbine moving blade 2 is fixed to the outer periphery of the rotor RT .
- a plurality of turbine blades 2 are arranged at intervals in the circumferential direction of the turbine.
- the turbine moving blade 2 constitutes an annular moving blade row.
- An annular moving blade row is arranged in the turbine axial direction.
- the turbine moving blade 2 is configured by arranging the blade main body 11, the platform 12, and the blade root portion 13 in the above order from the outer side to the inner side in the radial direction of the turbine.
- the wing body 11 extends radially outward from the outer periphery of the rotor RT .
- the platform 12 is provided at a radially inner end (a base end of the blade body 11) of the blade body 11 located on the rotor RT side (inside in the radial direction of the turbine).
- the platform 12 extends in the axial direction of the turbine and in the circumferential direction of the turbine with respect to the proximal end of the wing body 11.
- the blade root portion 13 is formed to be continuous with the platform 12 in the radial direction of the turbine. Blade root portion 13, that fits into the blade root groove formed on the outer periphery of the rotor R T, bound the rotor R T.
- the turbine stationary blade 3 is fixed to the inner periphery of the turbine casing 1.
- a plurality of turbine stator blades 3 are arranged at intervals in the circumferential direction of the turbine.
- the turbine stator blades 3 constitute an annular stator blade row.
- An annular stator vane row is arranged in the turbine axial direction.
- the stationary blade row and the moving blade row described above are alternately arranged in the turbine axial direction. Thereby, the turbine moving blades 2 and the turbine stationary blades 3 are alternately arranged in the turbine axial direction.
- the turbine stationary blade 3 is provided with a blade body 21 extending in the radial direction of the turbine and a plate provided on the radially inner end of the blade body 21 (tip of the blade body 21) , And a plate-like outer shroud 23 provided at the radially outer end of the wing body 21 (the base end of the wing body 21).
- the tip end portion of the wing body 21 is joined to a first major surface 22 a of the inner shroud 22 facing the outer shroud 23.
- the base end of the wing body 21 is joined to the first major surface 23 a of the outer shroud 23 facing the inner shroud 22.
- the outer shroud 23 extends in the axial direction of the turbine and in the circumferential direction of the turbine with respect to the proximal end of the blade body 21.
- the outer shroud 23 is fixed to the inner periphery of the turbine casing 1.
- the compressed air that functions as cooling air (cooling medium) by the outer shroud 23 and the turbine casing 1 on the side of the first main surface 23 a of the outer shroud 23 and the second main surface 23 b located on the opposite side in the radial direction An outer cavity CA to which c is supplied is formed.
- the inner shroud 22 extends in the axial direction of the turbine and in the circumferential direction of the turbine with respect to the tip of the blade body 21.
- the inner shroud 22 is disposed between the platforms 12 of the two turbine blades 2 arranged in the axial direction of the turbine.
- the region between the inner shrouds 22 and platforms 12 alternately arranged in the turbine axial direction and the inner periphery of the outer shrouds 23 facing the radially outer side of the inner shrouds 22 and platforms 12 is It is a combustion gas passage GP through which the combustion gas g flows.
- one side left side in FIGS.
- the end of the inner shroud 22 located upstream of the combustion gas passage GP with respect to the front edge 21A of the wing body 21 is the upstream end surface (front edge) 22C of the inner shroud 22 and the trailing edge of the wing body 21
- the end of the inner shroud 22 located downstream of the combustion gas passage GP with respect to 21B is referred to as a downstream end surface (rear edge) 22D of the inner shroud 22.
- the inner cavity CB protrudes radially inward from the inner shroud 22 and the second main surface 22b of the inner shroud 22 and is spaced apart from each other in the axial direction of the turbine, and the inner rib CB and the inner rib 26; It is a space surrounded by the seal ring 27 fixed to the protruding direction leading end of the upstream rib 25 and the downstream rib 26 so as to face the second major surface 22 b of the shroud 22.
- the upstream end surface of the inner cavity CB in the turbine axial direction corresponds to the downstream end surface 25 a of the upstream rib 25.
- the downstream end surface of the inner cavity CB in the turbine axial direction corresponds to the upstream end surface 26 a of the downstream rib 26.
- a disk cavity CC and a disk cavity CD are formed on both sides in the turbine axial direction of the inner cavity CB.
- the disk cavity CC and the disk cavity CD are formed by the blade root 13 of the turbine moving blade 2 and the above-described rotor disk opposed to each other in the axial direction of the turbine, the upstream rib 25 provided on the turbine vane 3, and the downstream rib 26 And the seal ring 27.
- Each disk cavity CC and disk cavity CD are in communication with the combustion gas passage GP from the gap between the inner shroud 22 and the platform 12.
- the first disc cavity CC located upstream of the combustion gas passage GP than the inner cavity CB is in communication with the inner cavity CB through the flow hole 28 formed in the seal ring 27.
- a portion of the compressed air c is discharged to the first disk cavity CC and the second disk cavity CD, and is discharged to the combustion gas passage GP as purge air. This prevents the backflow of the combustion gas g to the first disk cavity CC and the second disk cavity CD.
- the wing main body 21 is internally formed with a serpentine flow path 30 through which compressed air c, which functions as cooling air (cooling medium), is formed to meander in the radial direction of the turbine.
- the serpentine flow passage 30 is a plurality of (five in the illustrated example) main flow passages 31 formed by folded flow passages extending in the radial direction of the turbine, and a plurality (four in the illustrated example) connecting the adjacent main flow passages 31.
- the most upstream main flow passage 31A which is disposed closest to the front edge 21A of the wing main body 21 among the plurality of main flow passages 31, is formed through the inflow passage 33 formed through the outer shroud 23 in the thickness direction. It communicates with the outer cavity CA.
- the most downstream main flow passage 31B disposed closest to the trailing edge 21B of the wing main body 21 among the plurality of main flow passages 31 is radially inward in the inner shroud 22 from the joining position of the wing main body 21 and the inner shroud 22 It is connected to the extending end channel 31C.
- the end flow passage 31 ⁇ / b> C communicates with the outside of the turbine vane 3 via a first cooling passage 40 described later formed in the inner shroud 22.
- the outflow passage 29 which connects the terminal flow passage 31C and the second disk cavity CD is formed in the inner shroud 22 shown in FIG. 2, the outflow passage 29 is closed by a plug or the like.
- the compressed air c functioning as the cooling air (cooling medium) flows from the outer cavity CA into the most upstream main flow path 31A through the inflow passage 33 of the outer shroud 23. Thereafter, the compressed air c passes through the serpentine flow passage 30 and flows from the most downstream main flow passage 31 B into the first cooling passage 40 via the end flow passage 31 C of the inner shroud 22. That is, in the present embodiment, the radially outer end portion of the most upstream main flow channel 31A is the upstream end of the serpentine flow channel 30. In the present embodiment, the end flow passage 31 ⁇ / b> C radially inward of the most downstream main flow passage 31 ⁇ / b> B is the downstream end of the serpentine flow passage 30.
- a plurality of cooling holes 34 penetrating from the flow passage wall surface of the most downstream main flow passage 31B to the rear edge end 21B of the blade main body 21 are formed in the blade main body 21.
- the plurality of cooling holes 34 are arranged at intervals in the radial direction of the turbine. As a result, part of the compressed air c flowing through the most downstream main flow passage 31B flows into the cooling holes 34, convectively cools the rear edge of the blade main body 21, and flows out from the rear edge 21B into the combustion gas passage GP.
- the inner shroud (one shroud) 22 has a first cooling passage 40 having one end open to the end flow passage 31 C on the downstream end side of the serpentine flow passage 30 and the other end open to the downstream end surface 22 D of the inner shroud 22.
- the serpentine flow passage 30 is in communication with the combustion gas passage GP (outside of the inner shroud 22) by the first cooling passage 40.
- the first cooling passage 40 of the present embodiment is formed to extend from the end flow passage 31C at the downstream end of the serpentine flow passage 30 of the wing main body 21 to the downstream end surface 22D of the inner shroud 22.
- the first cooling passage 40 of the present embodiment is formed along the flow direction of the combustion gas g.
- the compressed air c flowing out from the downstream end of the serpentine flow passage 30 flows into the first cooling passage 40, convectively cools the rear edge portion of the inner shroud 22, and flows out from the downstream end surface 22D.
- the compressed air c flows out from the downstream end face 22D of the inner shroud 22 to the gap between the platform 12 facing the downstream end face 22D of the inner shroud 22.
- the inner shroud 22 of the turbine vane 3 opens at one end into the inner cavity CB provided on the second main surface 22b side of the inner shroud 22 and the other end
- a second cooling passage 50 opens to the downstream end surface 22D of the inner shroud 22.
- the second cooling passage 50 is a passage for flowing the compressed air c in the inner cavity CB to cool the trailing edge of the inner shroud 22.
- the second cooling passages 50 are arranged at intervals in the circumferential direction of the turbine with respect to the first cooling passages 40 described above.
- a part of the second cooling passage 50 is also formed on the downstream rib 26 located downstream of the combustion gas passage GP among the upstream rib 25 and the downstream rib 26 described above.
- one end of the second cooling passage 50 is open to the upstream end surface 26 a of the downstream rib 26 that defines the inner cavity CB.
- a plurality of second cooling passages 50 are arranged at intervals in the circumferential direction of the turbine.
- the second cooling passages 50 are disposed on both sides of the first cooling passage 40 in the circumferential direction of the turbine.
- the second cooling passage 50 linearly extends parallel to the first cooling passage 40, but is not limited thereto.
- the turbine vane 3 of this embodiment includes a supply tube 60 that supplies compressed air c that functions as cooling air (cooling medium) from the outer cavity CA to the inner cavity CB.
- the supply tube 60 is provided through the outer shroud 23, the wing body 21 and the inner shroud 22.
- the supply tubes 60 are provided one by one so as to pass through the two main channels 31 arranged closer to the trailing edge 21B of the wing main body 21 than the uppermost stream main channel 31A. There is no limitation to this.
- the range in which the first cooling passage 40 can be disposed will be described.
- the cooling passage 70 for cooling the trailing edge of the inner shroud 22 interferes with the end flow passage 31C of the serpentine flow passage 30 so that the cooling passage 70 is cooled. Can not be placed. As a result, there is a region where a non-uniform temperature distribution occurs at the trailing edge of the inner shroud 22.
- the range of the end flow passage 31C formed in the inner shroud 22 of the conventional turbine vane 3A will be described below.
- the end flow passage 31C formed inside the inner shroud 22 is connected on the upstream side to the downstream end of the most downstream main flow passage 31B of the serpentine flow passage 30.
- the end flow path 31 ⁇ / b> C has a downstream side connected to an opening formed in the upstream end surface 26 a of the downstream rib 26. That is, the upstream end of the terminal flow passage 31C is indicated by a flow passage cross section K1L1M1 formed at a position where the blade main body 21 is joined to the first main surface 22a of the inner shroud 22 and has a substantially triangular flow passage cross section.
- a point closer to the rear end 21B of the inner walls forming the most downstream main flow path 31B of the serpentine flow path 30 is taken as a point K1, and the turbine rotation is most among the front inner wall forming the most downstream main flow path 31B.
- a point located on the front side of the direction is a point L1, and a point located on the rear side in the rotation direction is a point M1.
- the end flow path 31C is connected to the opening L2L3K2M2 while forming an inclined flow path toward the opening L2L3K2M2 formed in the upstream end face 26a of the downstream side rib 26. Is formed. That is, the shape of the flow passage cross section of the end flow passage 31C viewed from the radial direction on the first main surface 22a is a triangular flow passage cross section surrounded by the points K1L1M1.
- the shape of the cross section of the end channel 31C when the opening L2L3K2M2 formed in the upstream end surface 26a of the downstream rib 26 is viewed from the axial direction has the upper side (radially outer side) indicated by the side L2M2
- the lower side (radially inner side) has a rectangular shape indicated by the side K2L3. That is, in the flow path section K1L1M1 formed on the first main surface 22a, the side K1L1 forms the bottom surface of the terminal flow path 31C while the flow path is directed radially inward and inclined toward the upstream side in the axial direction And connect to the side K2L3.
- the side L1M1 forms a ceiling surface of the terminal flow path 31C while being inclined toward the axially upstream side while the flow path is directed radially inward, and is connected to the side L2M2. That is, the end flow passage 31C is displayed by a flow passage surrounded by the ceiling surface L1M1M2L2, the bottom surface K1L1L3K2, the front side L1L2L3 in the rotation direction, and the rear side K1M1M2K2 in the rotation direction. As described above, the opening L2L3K2M2 is closed by the lid 26b.
- the first cooling passage 40 it is possible to cool a region where it is difficult to provide the above-mentioned cooling passage 70 (second cooling passage 50). That is, as shown in FIG. 3, the first cooling passage 40 opens to the combustion gas passage GP at the downstream end surface 22D of the inner shroud 22 so that the upstream side thereof is connected to the terminal passage 31C. Arranged as. Therefore, the problem of interference mentioned above does not occur. As shown in FIGS. 2, 3 and 5, when the inner shroud 22 is viewed in the radial direction, the first cooling passage 40 is located in a region where the end flow passage 31C is disposed in the circumferential direction of the inner shroud 22. It can be provided.
- the area occupied by the most downstream main channel 31B of the serpentine channel 30 at the position where the blade main body 21 joins with the first main surface 22a of the inner shroud 22 is the inner It can be said that the provision of the above-mentioned first cooling passage 40 is the most effective area as a measure against the oxidation loss which occurs at the trailing edge of the shroud 22.
- Cooling air discharged from the end of the serpentine flow passage 30 flows through the first cooling passage 40. That is, the cooling air passing through the first cooling passage 40 is different from the cooling air flowing through the second cooling passage 50 (cooling passage 70). Therefore, it is possible to cool the vicinity of the end flow passage 31C of the inner shroud 22 which can not be cooled by the second cooling passage 50 (the cooling passage 70) and the downstream region of the end flow passage 31C in the turbine axial direction. Thereby, the trailing edge of the inner shroud 22 can be cooled uniformly. That is, the temperature distribution in the circumferential direction of the rear edge portion of the inner shroud 22 can be made uniform, and oxidation reduction of the high temperature portion of the inner shroud 22 can be suppressed.
- the cooling air after cooling the blade main body 21 in the serpentine flow path 30 is used to cool the above-described region, so that the cooling air can be effectively used by using the cooling air.
- first cooling passage 40 Although only one first cooling passage 40 is present in FIG. 3, a plurality of first cooling passages 40 may be present, for example. It is desirable that the bore diameter (cross section of the flow passage) of the first cooling passage 40 be larger than that of the second cooling passage 50. This is because it is desirable that the temperature of the cooling air discharged from the serpentine flow passage 30 be higher than the cooling air flowing through the second cooling passage 50, and more cooling air flow to increase the cooling efficiency.
- the first cooling passage 40 is not limited to being provided as illustrated in FIG. 3 when the inner shroud 22 is viewed in the radial direction, and at least the end flow passage 31C is disposed in the circumferential direction of the inner shroud 22. It may be provided to include an area. That is, for example, in the circumferential direction of the inner shroud 22, the first cooling passage 40 may be provided so as to protrude in the circumferential direction of the turbine from the region where the end flow passage 31C is disposed.
- the first cooling passage 40 is not limited to being provided as illustrated in FIG. 3 when the inner shroud 22 is viewed in the radial direction, and at least the wing body 21 and the inner shroud 22 in the circumferential direction of the inner shroud 22.
- the first cooling passage 40 may be provided, for example, in the circumferential direction of the inner shroud 22 so as to protrude in the circumferential direction of the turbine from the occupation range of the above-described most downstream main flow passage 31B.
- the turbine stationary blade 3 in the gas turbine GT configured as described above can be obtained by modifying the conventional turbine stationary blade 3A not provided with the first cooling passage 40, as shown in FIG.
- an outflow passage 29 is formed which communicates the end flow passage 31C at the downstream end of the serpentine flow passage 30 and the space inside the inner shroud 22 in the radial direction.
- the outflow passage 29 communicates the downstream end of the serpentine passage 30 with the second disk cavity CD located downstream of the combustion gas passage GP than the inner cavity CB.
- the outflow passage 29 is formed in the downstream rib 26, but may be formed in the inner shroud 22, for example.
- the compressed air c flowing out from the downstream end of the serpentine flow passage 30 is discharged to the second disk cavity CD through the outflow passage 29, and the downstream end face of the inner shroud 22 and the inner shroud 22 It flows out to the combustion gas passage GP from the gap between the platform 12 facing the 22D.
- the compressed air c discharged to the second disk cavity CD through the outflow passage 29 is used as a purge gas together with the compressed air c (see FIG. 2) leaked from the above-described disk seal 62, and the combustion gas passage GP is The passing combustion gas g is prevented from intruding into the second disk cavity CD from between the inner shroud 22 and the platform 12.
- one end of the inner shroud 22 is a serpentine passage 30 as shown in FIG.
- a passage forming a first cooling passage 40 which opens at the downstream end end flow path 31C and at the other end opens at the downstream end face 22D of the inner shroud 22 and connects the serpentine flow path 30 to the outside of the inner shroud 22 Step S1 may be performed.
- the conventional turbine stationary blade 3A having the outflow passage 29 illustrated in FIG. 6 is modified, as shown in FIG. 7, the outflow passage 29 is removed after the passage forming step S1 or before the passage forming step S1.
- a passage sealing step S2 for sealing may be performed. In the passage sealing step S2, for example, the outflow passage 29 may be closed by a plug or the like.
- the compressed air c flows from the outer cavity CA into the serpentine flow passage 30 through the inflow passage 33 and flows from the upstream end to the downstream end of the serpentine flow passage 30 to cool the blade body 21.
- a portion of the compressed air flowing through the most downstream main flow path 31B of the serpentine flow path 30 is discharged to the cooling holes 34, and flows out from the rear end 21B of the blade main body 21 to the combustion gas passage GP.
- the compressed air c cools the portion on the trailing edge 21 B side of the wing body 21.
- the compressed air c flowing out of the end flow passage 31 C of the serpentine flow passage 30 flows into the first cooling passage 40 and flows out from the downstream end surface 22 D of the inner shroud 22 between the inner shroud 22 and the platform 12.
- the downstream end surface 22D side portion (rear edge portion) of the inner shroud 22, particularly the rear edge portion of the inner shroud 22 is the most downstream of the serpentine flow path 30 which is not sufficiently cooled by the conventional turbine vane.
- the region from the position to the downstream end surface 22D is cooled, including the position where the main flow passage 31B and the first main surface 22a of the inner shroud 22 are joined.
- the compressed air c flows out from the first cooling passage 40 into the gap between the inner shroud 22 and the platform 12 so that the combustion gas passing through the combustion gas passage GP together with the compressed air c leaking from the disk seal 62 described above. g is prevented from intruding into the second disk cavity CD from the gap between the inner shroud 22 and the platform 12.
- the compressed air c in the outer cavity CA flows into the inner cavity CB through the supply tube 60.
- the compressed air c flowing into the inner cavity CB mainly flows into the first disk cavity CC through the flow holes 28 of the seal ring 27. Thereafter, the compressed air c flows out from between the inner shroud 22 and the platform 12 opposed to the upstream end surface 22C of the inner shroud 22 into the combustion gas passage GP. This prevents the combustion gas g passing through the combustion gas passage GP from intruding into the first disk cavity CC from the gap between the inner shroud 22 and the platform 12.
- a region which is shifted in the circumferential direction of the turbine from the rear edge of the inner shroud 22, particularly the rear edge of the inner shroud 22 from the vicinity of the rear edge 21B of the blade body 21 (the vicinity of the first cooling passage 40) is cooled Ru.
- the compressed air c flows out from the second cooling passage 50 between the inner shroud 22 and the platform 12 so that the combustion gas g passing through the combustion gas passage GP is from the space between the inner shroud 22 and the platform 12 to the second disk cavity CD.
- the compressed air c flows in the serpentine flow passage 30 to cool the blade main body 21, and then flows in the first cooling passage 40. It becomes possible to cool the rear edge portion of the inner shroud 22, particularly the region from the position where the most downstream main flow passage 31B and the first major surface 22a of the inner shroud 22 are joined to the downstream end surface 22D. That is, by effectively utilizing the compressed air c after passing through the serpentine flow path 30, the cooling air can be used repeatedly, leading to a reduction in the amount of cooling air. As a result, the thermal efficiency of the gas turbine GT is improved.
- the region near the trailing edge 21 B of the blade body 21 in the trailing edge of the inner shroud 22 is cooled by the compressed air c flowing through the first cooling passage 40.
- a region shifted in the circumferential direction of the turbine from the vicinity of the rear edge 21 B of the blade main body 21 (the vicinity of the first cooling passage 40) is compressed air c flowing through the second cooling passage 50. It can be cooled. Therefore, the entire trailing edge of the inner shroud 22 can be cooled efficiently. That is, the rear edge portion of the inner shroud 22 can be uniformly cooled to suppress oxidation reduction of the high temperature portion of the inner shroud 22.
- the turbine vane 3 of the present embodiment a portion of the trailing edge of the inner shroud 22 is cooled by the compressed air c (cooling air) after passing through the serpentine flow passage 30. Therefore, the amount of compressed air c passing through the second cooling passage 50 can be reduced as compared to the case where the entire trailing edge of the inner shroud 22 is cooled by the compressed air c flowing through the second cooling passage 50. That is, the amount of compressed air c required to cool the rear edge of the inner shroud 22 can be reduced. Thus, the efficiency of the turbine T can be improved.
- the turbine vane 3 of this embodiment includes a wing body 21 and an inner shroud 22 similar to those of the first embodiment.
- the wing body 21 is provided with the serpentine flow passage 30 similar to that of the first embodiment.
- the inner shroud 22 includes a first cooling passage 40 having one end open to the downstream end of the serpentine flow passage 30 and the other end open to the downstream end surface 22D of the inner shroud 22 as in the first embodiment.
- the first cooling passage 40 of the present embodiment includes a widened cavity portion 41 extending in the circumferential direction of the turbine between one end and the other end.
- the first cooling passage 40 includes a plurality of branch passages 42 extending from the widening cavity portion 41 in the axial direction of the turbine and opening to the downstream end surface 22D of the inner shroud 22.
- the plurality of branch passages 42 are arranged at intervals in the circumferential direction of the turbine.
- the dimension of each branch passage 42 in the circumferential direction of the turbine is set sufficiently smaller than that of the widening cavity portion 41.
- the axial dimension of the widening cavity portion 41 in the turbine axial direction may be shorter than the branch passage 42 as in the illustrated example, but may be set longer than the branch passage 42, for example.
- the compressed air c flowing out from the downstream end of the serpentine flow passage 30 flows into the widening cavity portion 41 of the first cooling passage 40, and further flows into the respective branch passages 42 from the widening cavity portion 41. It flows out from the side end face 22D.
- the same effects as those of the first embodiment can be obtained.
- the area of the trailing edge of the inner shroud 22 cooled by the compressed air c flowing through the first cooling passage 40 can be expanded in the circumferential direction of the turbine. That is, the compressed air c after passing through the serpentine flow path 30 can be used more effectively.
- the amount of compressed air c passing through the second cooling passage 50 can be further reduced, and the efficiency of the turbine T can be further improved.
- one end that is the upstream end of the upstream passage is connected to the end flow passage 31C, and the other end is the downstream of the inner shroud 22
- the second embodiment is opened to the side end face 22D, and a wide cavity portion is provided in the middle between one end and the other end.
- the upstream passages 40A and the upstream passages 40B branch from the end flow passage 31C. That is, in the present modification, the plurality of upstream passages 40A and 40B are branched from the end flow passage 31C.
- the upstream passage 40A and the upstream passage 40B are connected to the widening cavity portion 41A and the widening cavity portion 41B.
- a plurality of branch passages 42A and branch passages 42B are branched from the widening cavity portion 41A and the widening cavity portion 41B.
- the branch passage 42A and the branch passage 42B open at the downstream end surface 22D of the inner shroud 22 into the combustion gas passage GP.
- the other configuration and the modification method to this modification are the same as in the first embodiment and the second embodiment.
- the same effects as the first embodiment and the second embodiment can be obtained.
- the area of the trailing edge of the inner shroud 22 cooled by the compressed air c flowing through the first cooling passage 40 can be further expanded as compared with the second embodiment. . That is, the compressed air c after passing through the serpentine flow path 30 can be used more effectively.
- Second Modification of Second Embodiment a second modified example of the second embodiment will be described with reference to FIG. 10, focusing on the differences between the second embodiment and the first modified example of the second embodiment.
- symbol is attached
- the first cooling passage 40 has one end, which is the upstream end of the upstream passage, connected to the end flow passage 31C, and the other end is the inner shroud 22.
- the second embodiment is the same as the second embodiment and the first modification of the second embodiment in that the downstream end surface 22D is opened and the wide cavity portion is provided between the one end and the other end. It is common to the first modified example of the second embodiment in that a plurality of first cooling passages 40 provided with a widened cavity portion are provided.
- the inner cavity CB disposed radially inward of the inner shroud 22 is axially moved upstream, The position of the rib 26 was moved axially upstream. That is, the difference is that the axial length of the inner cavity CB is reduced as a structure in which the downstream rib 26 is disposed upstream of the axial position intermediate position or axial position of the inner shroud 22.
- the range in which the inner shroud 22 is cooled by the compressed air c (cooling air) discharged from the downstream end of the serpentine flow passage 30 can be expanded.
- the region where the first cooling passage 40 is disposed is expanded, and the region where the second cooling passage 50 is disposed is reduced, and compressed air c (cooling air) discharged from the downstream end of the serpentine passage 30
- the area that can be effectively used is expanded. That is, the first cooling passage 40 connected to the end flow passage 31C is branched into the plurality of upstream passages 40A, 40B, and 40C.
- Each upstream passage 40A, 40B, and 40C is provided with widening cavity portions 43A, 43B, and 43C.
- Branch passages 44A, 44B, and 44C are disposed downstream of the widening cavity portions 43A, 43B, and 43C, respectively.
- the upstream passage 40A is mainly intended to cool the rear edge of the inner shroud 22 as in the second embodiment.
- the upstream passage 40B and the upstream passage 40C arrange the widening cavity portion 43B and the widening cavity portion 43C at the downstream side position as close as possible to the downstream side rib 26 in the axial direction. That is, the widening cavity portion 43B is disposed on the negative pressure surface 24a (the convexly formed wing surface in a radial cross section of the wing body) in the circumferential direction of the inner shroud 22.
- the widening cavity portion 43C is disposed on the positive pressure surface 24b (in a radial cross-sectional view of the wing main body, a wing surface formed in a concave shape) in the circumferential direction of the inner shroud 22.
- a plurality of branch passages 44B and a branch passage 44C which are extended in the axial direction downstream side from the widening cavity portion 43B and the widening cavity portion 43C are respectively disposed.
- the branch passage 44 ⁇ / b> B and the branch passage 44 ⁇ / b> C communicate with the combustion gas passage GP at the downstream end surface 22 ⁇ / b> D of the inner shroud 22.
- the upstream passage 40B and the upstream passage 40C are branched from the end flow passage 31C, and are temporarily flowed along the negative pressure surface 21a and the positive pressure surface 21b of the wing main body 21 toward the upstream direction in the inner shroud 22. It is formed as.
- the upstream passage 40B and the upstream passage 40C are connected to the widening cavity portions 43B and 43C.
- one end does not have the widening cavity portion and the end flow passage 31C.
- the first cooling passage 40 may be combined with the first cooling passage 40, the other end of which is open to the downstream end surface 22D of the inner shroud 22.
- the second cooling passages 50 are axially disposed along both circumferential end portions (the forward and rear end portions in the rotational direction) of the inner shroud 22. One end of the second cooling passage 50 opens to the inner cavity CB, and the other end opens to the downstream end surface 22D of the inner shroud 22.
- the second cooling passages 50 are limited to the case where they are disposed along the axial direction at both circumferential end portions of the inner shroud 22, but the second cooling passages 50 may not be provided.
- the other configuration and the modification method to this modification are the same as in the first embodiment and the second embodiment and the first modification of the second embodiment.
- the same effects as the first embodiment and the second embodiment can be obtained.
- the region of the trailing edge of the inner shroud 22 cooled by the compressed air c flowing through the first cooling passage 40 is further added
- the area to which the second cooling passage 50 is disposed is further reduced. That is, the amount of compressed air discharged from the inner cavity CB into the combustion gas g via the second cooling passage 50 is reduced, and the amount of compressed air after passing through the serpentine passage 30 is increased, so that the cooling air Can be used more effectively.
- the widened cavity portion 43B and the widened portion disposed on the negative pressure surface 24a side and the positive pressure surface 24b side of the inner shroud 22 are supplied from a source different from that of the widening cavity 43A. That is, the supply source of the compressed air c supplied to the widening cavity portion 43A is the compressed air c flowing into the end flow passage 31C after the blade body 21 is cooled in the process of passing through the serpentine flow passage 30.
- the source of the compressed air c supplied to the widening cavity portion 43B and the widening cavity portion 43C is the compressed air c taken out from the return flow passage 32 on the upstream side of the serpentine flow passage 30 from the most downstream main flow passage 31B. is there.
- the other configuration is basically the same as that of the second modification.
- the upstream passage 40B is connected to the widening cavity portion 43B which constitutes a part of the first cooling passage 40 disposed on the negative pressure surface 24a side.
- the upstream passage 40B is connected to an opening 32P (FIG. 12) formed in the return passage 32 formed on the inner shroud 22 side on the upstream side of the serpentine passage 30 with respect to the most downstream main passage 31B.
- An upstream passage 40C is connected to the widening cavity portion 43C that constitutes a part of the first cooling passage 40 disposed on the positive pressure surface 24b side.
- the upstream passage 40C is, similarly to the upstream passage 40B, an opening (not shown) formed in the return passage 32 formed on the inner shroud 22 side upstream of the serpentine passage 30 with respect to the most downstream main passage 31B.
- the return flow passage 32 which constitutes a part of the serpentine flow passage 30 (FIG. 12 shows the inner shroud of the upstream flow passage of the serpentine flow passage 30 adjacent to the most downstream main flow passage 31B.
- a recess 32A that is further recessed radially inward from the bottom of the return flow channel 32 is formed.
- An opening 32P to which the upstream passage 40B is connected is formed on the side wall on the negative pressure surface 24a side of the recess 32A.
- an opening (not shown) is formed in the side wall on the pressure surface 24b side of the recess 32A, and the upstream passage 40C is connected.
- the same effects as the first embodiment and the second embodiment can be obtained.
- compressed air c having a lower temperature is supplied to the widening cavity portion 43B and the widening cavity portion 43C as compared to the second variation of the second embodiment, so that the inner shroud Even when the temperature distribution on the negative pressure surface 24a side and the positive pressure surface 24b side of the 22 and the trailing edge portion is expanded, the cooling of the inner shroud 22 becomes possible over a wide range with lower temperature cooling air, and the oxidation reduction of the inner shroud 22 is suppressed. can do.
- the temperature reduction in the circumferential direction of the rear edge portion of the inner shroud 22 can be reduced, and the oxidation reduction can be suppressed. Since the inner shroud 22 is convectively cooled using the compressed air c after passing through the serpentine flow path 30 to cool the blade body 21, the cooling air is used up and the thermal efficiency of the gas turbine is improved.
- the first cooling passage 40 has a plurality of branch passages 42, but may have only one, for example.
- the second cooling passage 50 is formed in both the inner shroud 22 and the downstream rib 26, but may be formed only in the inner shroud 22, for example.
- the passage sealing process is performed to modify the conventional turbine vane 3A
- the passage sealing process may not be performed, for example.
- a portion of the compressed air c flowing out from the downstream end of the serpentine flow passage 30 flows into the first cooling passage 40 as in the turbine vane 3 of the above embodiment.
- a portion of the compressed air c flowing in flows out from the downstream end surface 22D of the inner shroud 22 between the inner shroud 22 and the platform 12.
- the remaining portion of the compressed air c flowing out from the downstream end of the serpentine flow passage 30 flows into the second disk cavity CD through the outflow passage 29 as in the case of the turbine vane 3A before the remodeling.
- the remaining portion of the compressed air c flowing in flows out from between the inner shroud 22 and the platform 12 opposed to the downstream end face 22D of the inner shroud 22 into the combustion gas passage GP. This makes it possible to more preferably prevent the combustion gas g passing through the combustion gas passage GP from intruding into the second disk cavity CD.
- the downstream end of the serpentine flow passage 30 is located on the inner shroud 22 side, but may be located on the outer shroud 23 side, for example.
- the outer shroud 23 opens at the downstream end of the serpentine flow passage 30 at one end and the trailing edge of the outer shroud 23 at the other end, similarly to the first cooling passage 40 of the inner shroud 22 in the above embodiment, for example.
- the first cooling passage may be open to the In this configuration, the trailing edge portion of the outer shroud 23 can be cooled by the compressed air c flowing out of the serpentine flow passage 30 as in the above embodiment.
- the outer shroud 23 When the outer shroud 23 includes the first cooling passage, the outer shroud 23 opens at one end into the outer cavity (cavity) CA and the other end, similarly to the second cooling passage 50 of the inner shroud 22 in the above embodiment, for example. May have a second cooling passage that opens at the trailing edge of the outer shroud 23.
- the temperature distribution in the circumferential direction of the trailing edge of one of the shrouds is made uniform, and oxidation reduction of the high temperature part of one of the shrouds is suppressed.
- the cooling medium after passing through the serpentine flow path is used repeatedly, and the cooling medium can be used effectively. As a result, the amount of cooling air is reduced, and the thermal efficiency of the gas turbine is improved.
- Turbine R T rotor 1 Turbine casing 2 Turbine rotor blade 3 Turbine stator blade 21 Blade body 21B Trailing edge 22 Inner shroud (one shroud) 22a first main surface 22b second main surface 22D downstream end surface (rear edge) 23 outer shroud 23a first major surface 23b second major surface 30 serpentine channel 31B most downstream main channel 31C end channel 40 first cooling channel 40A, 40B, 40C upstream channel 41A, 41B, 43A, 43B, 43C widening Cavity portion 42, 42A, 42B, 44A, 44B, 44C Branch passage 50 second cooling passage CB Inner cavity (cavity) c Compressed air (coolant)
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Abstract
Description
本願は、2014年6月30日に出願された特願2014-134442号について優先権を主張し、その内容をここに援用する。
すなわち、一方のシュラウドの後縁部全体を効率よく冷却することが可能となる。
以下、図1~6を参照して本発明の第一実施形態について説明する。
図1に示すように、本実施形態に係るガスタービンGTは、圧縮空気cを生成する圧縮機Cと、圧縮機Cから供給される圧縮空気cに燃料を供給して燃焼ガスgを生成する複数の燃焼器Bと、燃焼器Bから供給される燃焼ガスgにより回転動力を得るタービンTと、を備える。ガスタービンGTにおいては、圧縮機CのロータRCとタービンTのロータRTとが、それぞれの軸端で連結されてタービン軸P上に延びている。
以下の説明では、タービンTのロータRTの延在方向をタービン軸方向、ロータRTの円周方向をタービン周方向、ロータRTの半径方向をタービン径方向と呼ぶ。
タービン動翼2は、翼本体11とプラットフォーム12と翼根部13とを、タービン径方向の外側から内側に上記の順に配列して構成されている。翼本体11は、ロータRTの外周からタービン径方向外側に向けて延びている。プラットフォーム12は、ロータRT側(タービン径方向の内側)に位置する翼本体11の径方向内側の端部(翼本体11の基端部)に設けられている。プラットフォーム12は、翼本体11の基端部に対してタービン軸方向及びタービン周方向に延びている。翼根部13は、プラットフォーム12に対してタービン径方向の内側に連ねて形成されている。翼根部13は、ロータRTの外周に形成された翼根溝に嵌合することで、ロータRTに拘束される。
翼本体21の先端部は、外側シュラウド23に対向する内側シュラウド22の第一主面22aに接合されている。翼本体21の基端部は、内側シュラウド22に対向する外側シュラウド23の第一主面23aに接合されている。
ここで、タービン軸方向に交互に配列される内側シュラウド22及びプラットフォーム12と、これら内側シュラウド22及びプラットフォーム12の径方向外側に対向する外側シュラウド23の内周との間の領域は、タービンTにおいて燃焼ガスgが流れる燃焼ガス通路GPとなっている。以下の説明では、タービンTに対して圧縮機Cや燃焼器Bが配されるタービン軸方向の第一端部側である一方側(図1~3において左側)を燃焼ガス通路GPの上流側、タービン軸方向の一方側の反対側となるタービン軸方向の第二端部側である他方側(図1~3において右側)を燃焼ガス通路GPの下流側と呼ぶ。
内側キャビティCBよりも燃焼ガス通路GPの上流側に位置する第一ディスクキャビティCCは、シールリング27に形成された流通孔28を介して内側キャビティCBに連通している。これにより、内側キャビティCB内の圧縮空気cの一部が、内側キャビティCBから第一ディスクキャビティCCに排出される。排出された圧縮空気cの一部は、内側シュラウド22と内側シュラウド22の上流側端面22Cに対向するプラットフォーム12との間から燃焼ガス通路GPに流出する。シールリング27の径方向内側には、ロータディスクからタービン軸方向に延在するリム61が設けられている。リム61とシールリング27の間にはディスクシール62が設けられている。第一ディスクキャビティCC側からディスクシール62を介して下流側の第二ディスクキャビティCDに漏れ出した圧縮空気cは、同様に、下流側の燃焼ガス通路GPに排出される。圧縮空気cの一部が、第一ディスクキャビティCC及び第二ディスクキャビティCDに排出され、パージ空気として燃焼ガス通路GPに排出される。これにより、燃焼ガスgが第一ディスクキャビティCC及び第二ディスクキャビティCDに逆流することを防止している。
サーペンタイン流路30は、タービン径方向に延びる折り返し流路で形成された複数(図示例では五つ)のメイン流路31と、隣り合うメイン流路31同士を接続する複数(図示例では四つ)のリターン流路32と、を備える。
これにより、サーペンタイン流路30の下流端から流出した圧縮空気cは、第一冷却通路40に流れ込み、内側シュラウド22の後縁部を対流冷却して、下流側端面22Dから外部に流出する。具体的に、圧縮空気cは内側シュラウド22の下流側端面22Dから内側シュラウド22の下流側端面22Dに対向するプラットフォーム12との間の隙間に流出する。
これにより、内側キャビティCB内の圧縮空気cの一部が第二冷却通路50に流れ込み、内側シュラウド22の後縁部を対流冷却して、下流側端面22Dから外部に流出する。
前述のように、従来のサーペンタイン流路を有するタービン静翼3Aでは、内側シュラウド22の後縁部を冷却する冷却通路70とサーペンタイン流路30の末端流路31Cとが干渉して、冷却通路70の配置ができない。その結果、内側シュラウド22の後縁部に不均一な温度分布が生ずる領域が存在する。
前述のように、内側シュラウド22の内部に形成される末端流路31Cは、サーペンタイン流路30の最下流メイン流路31Bの下流端に上流側が接続する。末端流路31Cは、下流側が下流側リブ26の上流側端面26aに形成された開口部に接続する。すなわち、末端流路31Cの上流端は、翼本体21が内側シュラウド22の第一主面22aに接合する位置に形成される流路断面K1L1M1で示され、略三角形状の流路断面を有する。ここで、サーペンタイン流路30の最下流メイン流路31Bを形成する内壁のうち最も後縁端21Bに近い点を点K1とし、最下流メイン流路31Bを形成する前縁側内壁のうち最もタービン回転方向の前方側に位置する点を点L1とし、回転方向の後方側に位置する点を点M1としている。
前述のように、末端流路31Cが形成された範囲では、キャビティCBから内側シュラウド22のタービン軸方向下流端まで延びる従来の冷却通路70が末端流路31Cと干渉してしまうため、冷却通路70を配置することが出来ない。そのため、従来のタービン静翼3Aでは、図5の右側のグラフに示すように、内側シュラウド22の後縁部の周方向の温度分布を描いた場合、冷却通路70が配列されていない領域(冷却通路70が末端流路31Cと干渉する領域)では温度が高く、その他の領域では温度が低い放物線状の温度分布となる。その結果、従来のタービン静翼3Aでは、内側シュラウド22に高温部の酸化減肉が発生する可能性がある。
第一冷却通路40は、図2、図3及び図5に示すように、内側シュラウド22を径方向から見た場合、内側シュラウド22の周方向において、末端流路31Cが配置される領域内に設けることができる。別の見方をすれば、内側シュラウド22の周方向において、翼本体21が内側シュラウド22の第一主面22aと接合する位置でサーペンタイン流路30の最下流メイン流路31Bが占める範囲が、内側シュラウド22の後縁部に生ずる酸化減肉に対する対策として、前述の第一冷却通路40を設けることが最も有効な領域と言える。
サーペンタイン流路30で翼本体21を冷却した後の冷却空気を用いて上記した領域を冷却するので、冷却空気の使い廻しによる冷却空気の有効利用ができる。
第一冷却通路40は、内側シュラウド22を径方向から見た場合に、図3に例示するように設けられることに限らず、内側シュラウド22の周方向において、少なくとも翼本体21と内側シュラウド22の第一主面22aとの接合位置におけるサーペンタイン流路30の最下流メイン流路31Bの占有範囲を含むように設けられればよい。すなわち、第一冷却通路40は、例えば内側シュラウド22の周方向において、上記した最下流メイン流路31Bの占有範囲からタービン周方向に張り出すように設けられてもよい。
従来のタービン静翼3Aには、サーペンタイン流路30の下流端の末端流路31Cと、内側シュラウド22の径方向内側の空間とを連通する流出通路29が形成されている。図6において、流出通路29は、サーペンタイン流路30の下流端と、内側キャビティCBよりも燃焼ガス通路GPの下流側に位置する第二ディスクキャビティCDとを連通している。図6においては、流出通路29が、下流側リブ26に形成されているが、例えば内側シュラウド22に形成されてもよい。
図6に例示した流出通路29を有する従来のタービン静翼3Aを改造する場合には、図7に示すように通路形成工程S1の後、あるいは、通路形成工程S1の前に、流出通路29を封止する通路封止工程S2を実行すればよい。通路封止工程S2では、例えば流出通路29をプラグ等によって閉塞すればよい。
圧縮空気cは、外側キャビティCAから流入通路33を介してサーペンタイン流路30に流入し、サーペンタイン流路30の上流端から下流端に向けて流れることで、翼本体21を冷却する。サーペンタイン流路30の最下流メイン流路31Bを流れる圧縮空気の一部が冷却孔34に排出され、翼本体21の後縁端21Bから燃焼ガス通路GPに流出する。その結果、圧縮空気cは、翼本体21の後縁端21B側の部分を冷却する。
これにより、内側シュラウド22の下流側端面22D側の部分(後縁部)、特に内側シュラウド22の後縁部のうち、従来のタービン静翼では冷却が十分でなかったサーペンタイン流路30の最下流メイン流路31Bと内側シュラウド22の第一主面22aとが接合する位置を含んで、その位置から下流側端面22Dまでの領域が冷却される。圧縮空気cが第一冷却通路40から内側シュラウド22とプラットフォーム12との間の隙間に流出することで、前述のディスクシール62から漏れ出した圧縮空気cと共に、燃焼ガス通路GPを通過する燃焼ガスgが内側シュラウド22とプラットフォーム12の間の隙間から第二ディスクキャビティCDに侵入することを防いでいる。
次に、本発明の第二実施形態について、図8を参照して、第一実施形態との相違点を中心に説明する。なお、第一実施形態と共通する構成については、同一符号を付し、その説明を省略する。
これにより、サーペンタイン流路30の下流端から流出した圧縮空気cは、第一冷却通路40の拡幅キャビティ部41に流れ込み、さらに、拡幅キャビティ部41から各分岐通路42に流れ込んで内側シュラウド22の下流側端面22Dから外部に流出する。
本実施形態のタービン静翼3によれば、第一冷却通路40を流れる圧縮空気cによって冷却される内側シュラウド22の後縁部の領域をタービン周方向に拡大することができる。すなわち、サーペンタイン流路30を通過した後の圧縮空気cをさらに有効に活用することができる。
第一実施形態の場合と比較して、第二冷却通路50を通る圧縮空気cの量をさらに減らすことが可能となり、タービンTの効率をさらに向上させることができる。
次に、第二実施形態の第一変形例について、図9を参照しつつ、第二実施形態との相違点を中心に説明する。なお、第一実施形態及び第二実施形態と共通する構成については、同一符号を付し、その説明を省略する。
本変形例のタービン静翼によれば、第二実施形態と比較して、第一冷却通路40を流れる圧縮空気cによって冷却される内側シュラウド22の後縁部の領域を更に拡大することができる。すなわち、サーペンタイン流路30を通過した後の圧縮空気cを一層有効に活用することができる。
次に、第二実施形態の第二変形例について、図10を参照しつつ、第二実施形態及び第二実施形態の第一変形例との相違点を中心に説明する。なお、第一実施形態、第二実施形態、及び第二実施形態の第一変形例と共通する構成については、同一符号を付し、その説明を省略する。
本変形例のタービン静翼によれば、第二実施形態の第一変形例と比較して、第一冷却通路40を流れる圧縮空気cによって冷却される内側シュラウド22の後縁部の領域を更に拡大させ、第二冷却通路50を配置する領域を一層減少させている。すなわち、内側キャビティCBから第二冷却通路50を介して燃焼ガスg中に排出される圧縮空気量を低減し、サーペンタイン流路30を通過した後の圧縮空気量を増加させているので、冷却空気を一層有効に活用することができる。
次に、第二実施形態の第三変形例について、図11及び図12を参照しつつ、第二実施形態の第二変形例との相違点を中心に説明する。なお、第一実施形態、第二実施形態、第二実施形態の第一変形例、及び第二実施形態の第二変形例と共通する構成については、同一符号を付し、その説明を省略する。
なお、凹部32Aを備えたリターン流路32は、最下流メイン流路31Bに隣接するサーペンタイン流路30のリターン流路32に限定する必要はなく、最上流メイン流路31Aの内側シュラウド22側のリターン流路32でもよい。末端流路31Cの下流端は、内側キャビティCBに開口するように形成され、開口端が蓋26bで閉塞されているのは、他の実施形態及び変形例と同様である。
本変形例のタービン静翼によれば、第二実施形態の第二変形例と比較して、温度の低い圧縮空気cが拡幅キャビティ部43B及び拡幅キャビティ部43Cに供給される、そのため、内側シュラウド22の負圧面24a側及び正圧面24b側並びに後縁部の温度分布が拡大した場合でも、より低温の冷却空気で広範囲にわたり内側シュラウド22の冷却が可能となり、内側シュラウド22の酸化減肉を抑制することができる。
例えば、上記第二実施形態では、第一冷却通路40が分岐通路42を複数備えるが、例えば一つだけ備えてもよい。
RT ロータ
1 タービンケーシング
2 タービン動翼
3 タービン静翼
21 翼本体
21B 後縁端
22 内側シュラウド(一方のシュラウド)
22a 第一主面
22b 第二主面
22D 下流側端面(後縁)
23 外側シュラウド
23a 第一主面
23b 第二主面
30 サーペンタイン流路
31B 最下流メイン流路
31C 末端流路
40 第一冷却通路
40A、40B、40C 上流通路
41A、41B、43A、43B、43C 拡幅キャビティ部
42、42A、42B、44A、44B、44C 分岐通路
50 第二冷却通路
CB 内側キャビティ(キャビティ)
c 圧縮空気(冷却媒体)
Claims (9)
- タービンの径方向に延在する翼本体と、該翼本体の径方向内側の端部に設けられる板状の内側シュラウドと、前記翼本体の径方向外側の端部に設けられる板状の外側シュラウドと、を備え、
前記翼本体は、その内部において径方向に蛇行して形成され、冷却媒体が流れるサーペンタイン流路を備え、
前記内側シュラウド及び前記外側シュラウドのうち一方のシュラウドは、一端が前記サーペンタイン流路の下流端側に開口すると共に、他端が前記一方のシュラウドの後縁に開口し、前記サーペンタイン流路を前記一方のシュラウドの外部に連通させる冷却通路を備えるタービン静翼。 - 前記一方のシュラウドは、前記一方のシュラウドのうち前記翼本体が配される第一主面と反対側に位置する第二主面に設けられたキャビティを備え、前記キャビティの軸方向の下流側端面は、前記サーペンタイン流路の最下流メイン流路より軸方向の上流側に配置されている請求項1に記載のタービン静翼。
- 前記冷却通路は、燃焼ガスの流れ方向に沿って形成され、前記一方のシュラウドの周方向において、前記サーペンタイン流路の最下流メイン流路が前記一方のシュラウドと接合する位置の範囲内に設けられている請求項1又は請求項2に記載のタービン静翼。
- 前記冷却通路は、燃焼ガスの流れ方向に沿って形成され、前記一方のシュラウドの周方向において、少なくとも前記サーペンタイン流路の下流端である末端流路が配置された領域を含んで設けられている請求項1から請求項3のいずれか一項に記載のタービン静翼。
- 前記冷却通路が、その一端と他端との間において前記タービンの周方向に延びる拡幅キャビティ部を備える請求項1から請求項4のいずれか一項に記載のタービン静翼。
- 前記冷却通路が、前記タービンの周方向に互いに間隔をあけて配列され、前記拡幅キャビティ部から前記タービンの軸方向に延びて前記一方のシュラウドの後縁に開口する複数の分岐通路を備える請求項5に記載のタービン静翼。
- 前記一方のシュラウドは、一端が前記一方のシュラウドのうち前記翼本体が配される第一主面と反対側に位置する第二主面に設けられたキャビティに開口すると共に、他端が前記一方のシュラウドの後縁に開口して、前記キャビティ内の冷却媒体を通過させる第二冷却通路を備え、
該第二冷却通路が、前記冷却通路である第一冷却通路と前記タービンの周方向に間隔をあけて配される請求項1から請求項6のいずれか一項に記載のタービン静翼。 - ロータと、
前記ロータの周囲を囲むタービンケーシングと、
前記ロータの外周に固定されるタービン動翼と、
前記タービンケーシングの内周に固定され、前記タービン動翼と前記ロータの軸方向に交互に配列される請求項1から請求項7のいずれか一項に記載のタービン静翼と、を備えるタービン。 - タービンの径方向に延在する翼本体と、該翼本体の径方向内側の端部に設けられる板状の内側シュラウドと、前記翼本体の径方向外側の端部に設けられる板状の外側シュラウドと、を備え、前記翼本体が、その内部において径方向に蛇行して形成され、冷却媒体が流れるサーペンタイン流路を備えるタービン静翼の改造方法であって、
前記内側シュラウド及び前記外側シュラウドのうち一方のシュラウドに、一端が前記サーペンタイン流路の下流端側に開口すると共に、他端が前記一方のシュラウドの後縁に開口して、前記サーペンタイン流路を前記一方のシュラウドの外部に連通させる冷却通路を形成する通路形成工程を実行するタービン静翼の改造方法。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201580030987.4A CN106460534B (zh) | 2014-06-30 | 2015-06-24 | 涡轮静叶、涡轮、以及涡轮静叶的改造方法 |
JP2016531300A JP6344869B2 (ja) | 2014-06-30 | 2015-06-24 | タービン静翼、タービン、及び、タービン静翼の改造方法 |
DE112015003047.6T DE112015003047B4 (de) | 2014-06-30 | 2015-06-24 | Turbinenleitschaufel, turbine und verfahren zum modifizieren einer turbinenleitschaufel |
US15/315,471 US10544685B2 (en) | 2014-06-30 | 2015-06-24 | Turbine vane, turbine, and turbine vane modification method |
KR1020167034656A KR101852290B1 (ko) | 2014-06-30 | 2015-06-24 | 터빈 정익, 터빈, 및 터빈 정익의 개조 방법 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2014134442 | 2014-06-30 | ||
JP2014-134442 | 2014-06-30 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2016002602A1 true WO2016002602A1 (ja) | 2016-01-07 |
Family
ID=55019144
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2015/068228 WO2016002602A1 (ja) | 2014-06-30 | 2015-06-24 | タービン静翼、タービン、及び、タービン静翼の改造方法 |
Country Status (6)
Country | Link |
---|---|
US (1) | US10544685B2 (ja) |
JP (1) | JP6344869B2 (ja) |
KR (1) | KR101852290B1 (ja) |
CN (1) | CN106460534B (ja) |
DE (1) | DE112015003047B4 (ja) |
WO (1) | WO2016002602A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2020186708A (ja) * | 2019-05-17 | 2020-11-19 | 三菱パワー株式会社 | タービン静翼、ガスタービン及びタービン静翼の製造方法 |
CN112112688A (zh) * | 2019-06-21 | 2020-12-22 | 斗山重工业建设有限公司 | 透平静叶片、包含它的透平及燃气轮机 |
Families Citing this family (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10060269B2 (en) | 2015-12-21 | 2018-08-28 | General Electric Company | Cooling circuits for a multi-wall blade |
US10208607B2 (en) | 2016-08-18 | 2019-02-19 | General Electric Company | Cooling circuit for a multi-wall blade |
US10227877B2 (en) | 2016-08-18 | 2019-03-12 | General Electric Company | Cooling circuit for a multi-wall blade |
US10208608B2 (en) | 2016-08-18 | 2019-02-19 | General Electric Company | Cooling circuit for a multi-wall blade |
US10267162B2 (en) * | 2016-08-18 | 2019-04-23 | General Electric Company | Platform core feed for a multi-wall blade |
US10221696B2 (en) | 2016-08-18 | 2019-03-05 | General Electric Company | Cooling circuit for a multi-wall blade |
JP6684842B2 (ja) * | 2018-03-29 | 2020-04-22 | 三菱重工業株式会社 | タービン動翼及び回転機械 |
JP7129277B2 (ja) * | 2018-08-24 | 2022-09-01 | 三菱重工業株式会社 | 翼およびガスタービン |
JP6508499B1 (ja) * | 2018-10-18 | 2019-05-08 | 三菱日立パワーシステムズ株式会社 | ガスタービン静翼、これを備えているガスタービン、及びガスタービン静翼の製造方法 |
EP3663522B1 (en) * | 2018-12-07 | 2021-11-24 | ANSALDO ENERGIA S.p.A. | Stator assembly for a gas turbine and gas turbine comprising said stator assembly |
EP3816405B1 (en) * | 2019-11-04 | 2023-05-03 | ANSALDO ENERGIA S.p.A. | Stator assembly for a gas turbine and gas turbine comprising said stator assembly |
JP7284737B2 (ja) * | 2020-08-06 | 2023-05-31 | 三菱重工業株式会社 | ガスタービン静翼 |
JP2022061204A (ja) * | 2020-10-06 | 2022-04-18 | 三菱重工業株式会社 | ガスタービン静翼 |
JP7460510B2 (ja) | 2020-12-09 | 2024-04-02 | 三菱重工航空エンジン株式会社 | 静翼セグメント |
CN113623014B (zh) * | 2021-07-22 | 2023-04-14 | 西安交通大学 | 一种燃气轮机透平叶片-轮盘联合冷却结构 |
CN113586251B (zh) * | 2021-07-22 | 2023-03-14 | 西安交通大学 | 一种燃气轮机冷却气流逐级利用的部件冷却-轮缘密封结构 |
KR20240055099A (ko) * | 2021-11-29 | 2024-04-26 | 미츠비시 파워 가부시키가이샤 | 터빈 정익 |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5609466A (en) * | 1994-11-10 | 1997-03-11 | Westinghouse Electric Corporation | Gas turbine vane with a cooled inner shroud |
JPH10252410A (ja) * | 1997-03-11 | 1998-09-22 | Mitsubishi Heavy Ind Ltd | ガスタービンの翼冷却空気供給システム |
JPH10252411A (ja) * | 1997-03-11 | 1998-09-22 | Mitsubishi Heavy Ind Ltd | ガスタービン冷却静翼 |
JP2005146858A (ja) * | 2003-11-11 | 2005-06-09 | Mitsubishi Heavy Ind Ltd | ガスタービン |
US8702375B1 (en) * | 2011-05-19 | 2014-04-22 | Florida Turbine Technologies, Inc. | Turbine stator vane |
JP2015059486A (ja) * | 2013-09-18 | 2015-03-30 | 株式会社東芝 | タービン静翼 |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4962640A (en) | 1989-02-06 | 1990-10-16 | Westinghouse Electric Corp. | Apparatus and method for cooling a gas turbine vane |
JP3495554B2 (ja) | 1997-04-24 | 2004-02-09 | 三菱重工業株式会社 | ガスタービン静翼の冷却シュラウド |
JP3495579B2 (ja) | 1997-10-28 | 2004-02-09 | 三菱重工業株式会社 | ガスタービン静翼 |
US6761529B2 (en) * | 2002-07-25 | 2004-07-13 | Mitshubishi Heavy Industries, Ltd. | Cooling structure of stationary blade, and gas turbine |
US8011881B1 (en) * | 2008-01-21 | 2011-09-06 | Florida Turbine Technologies, Inc. | Turbine vane with serpentine cooling |
US8096772B2 (en) * | 2009-03-20 | 2012-01-17 | Siemens Energy, Inc. | Turbine vane for a gas turbine engine having serpentine cooling channels within the inner endwall |
-
2015
- 2015-06-24 WO PCT/JP2015/068228 patent/WO2016002602A1/ja active Application Filing
- 2015-06-24 US US15/315,471 patent/US10544685B2/en active Active
- 2015-06-24 DE DE112015003047.6T patent/DE112015003047B4/de active Active
- 2015-06-24 JP JP2016531300A patent/JP6344869B2/ja active Active
- 2015-06-24 KR KR1020167034656A patent/KR101852290B1/ko active IP Right Grant
- 2015-06-24 CN CN201580030987.4A patent/CN106460534B/zh active Active
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5609466A (en) * | 1994-11-10 | 1997-03-11 | Westinghouse Electric Corporation | Gas turbine vane with a cooled inner shroud |
JPH10252410A (ja) * | 1997-03-11 | 1998-09-22 | Mitsubishi Heavy Ind Ltd | ガスタービンの翼冷却空気供給システム |
JPH10252411A (ja) * | 1997-03-11 | 1998-09-22 | Mitsubishi Heavy Ind Ltd | ガスタービン冷却静翼 |
JP2005146858A (ja) * | 2003-11-11 | 2005-06-09 | Mitsubishi Heavy Ind Ltd | ガスタービン |
US8702375B1 (en) * | 2011-05-19 | 2014-04-22 | Florida Turbine Technologies, Inc. | Turbine stator vane |
JP2015059486A (ja) * | 2013-09-18 | 2015-03-30 | 株式会社東芝 | タービン静翼 |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2020186708A (ja) * | 2019-05-17 | 2020-11-19 | 三菱パワー株式会社 | タービン静翼、ガスタービン及びタービン静翼の製造方法 |
WO2020235245A1 (ja) * | 2019-05-17 | 2020-11-26 | 三菱日立パワーシステムズ株式会社 | タービン静翼、ガスタービン及びタービン静翼の製造方法 |
JP7242421B2 (ja) | 2019-05-17 | 2023-03-20 | 三菱重工業株式会社 | タービン静翼、ガスタービン及びタービン静翼の製造方法 |
CN112112688A (zh) * | 2019-06-21 | 2020-12-22 | 斗山重工业建设有限公司 | 透平静叶片、包含它的透平及燃气轮机 |
CN112112688B (zh) * | 2019-06-21 | 2023-02-17 | 斗山重工业建设有限公司 | 透平静叶片、包含它的透平及燃气轮机 |
Also Published As
Publication number | Publication date |
---|---|
JPWO2016002602A1 (ja) | 2017-04-27 |
US10544685B2 (en) | 2020-01-28 |
KR101852290B1 (ko) | 2018-06-11 |
DE112015003047B4 (de) | 2021-08-26 |
KR20170003989A (ko) | 2017-01-10 |
DE112015003047T5 (de) | 2017-03-16 |
CN106460534B (zh) | 2018-05-18 |
US20170198594A1 (en) | 2017-07-13 |
JP6344869B2 (ja) | 2018-06-20 |
CN106460534A (zh) | 2017-02-22 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2016002602A1 (ja) | タービン静翼、タービン、及び、タービン静翼の改造方法 | |
US10612397B2 (en) | Insert assembly, airfoil, gas turbine, and airfoil manufacturing method | |
US9080458B2 (en) | Blade outer air seal with multi impingement plate assembly | |
US9644485B2 (en) | Gas turbine blade with cooling passages | |
JP4559751B2 (ja) | ガスタービンエンジンのタービンノズルの二又状インピンジメントバッフル | |
US8277177B2 (en) | Fluidic rim seal system for turbine engines | |
TWI632289B (zh) | 葉片、及具備該葉片的燃氣渦輪機 | |
JP6063250B2 (ja) | ガスタービンステータアセンブリ | |
JP2005180418A (ja) | ガスタービンエンジンを組立てるための方法及び装置 | |
TWI641753B (zh) | 定子葉片、及具備其之燃氣輪機 | |
JP5965633B2 (ja) | タービンロータブレードのプラットフォーム領域を冷却するための装置及び方法 | |
JP2012102726A (ja) | タービンロータブレードのプラットフォーム領域を冷却するための装置、システム、及び方法 | |
JP6110665B2 (ja) | タービン集成体及び集成体の温度を制御するための方法 | |
JP2015092076A (ja) | タービンアセンブリに冷却を提供するための方法およびシステム | |
JP2011085136A (ja) | ターボ機械ロータ冷却 | |
JP2012132438A (ja) | タービンロータブレードのプラットフォーム領域を冷却するための装置及び方法 | |
WO2017033920A1 (ja) | タービン動翼、及び、ガスタービン | |
JP6512573B2 (ja) | シール部材 | |
US9909426B2 (en) | Blade for a turbomachine | |
US20130028704A1 (en) | Blade outer air seal with passage joined cavities | |
WO2018110009A1 (ja) | 分割環及びガスタービン | |
JP2020097907A (ja) | ガスタービンの静翼及びガスタービン | |
US11542825B2 (en) | Gas turbine ring assembly comprising ring segments having integrated interconnecting seal |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 15814031 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2016531300 Country of ref document: JP Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 15315471 Country of ref document: US |
|
ENP | Entry into the national phase |
Ref document number: 20167034656 Country of ref document: KR Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 112015003047 Country of ref document: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 15814031 Country of ref document: EP Kind code of ref document: A1 |