WO2010109954A1 - タービン翼およびガスタービン - Google Patents
タービン翼およびガスタービン Download PDFInfo
- Publication number
- WO2010109954A1 WO2010109954A1 PCT/JP2010/051571 JP2010051571W WO2010109954A1 WO 2010109954 A1 WO2010109954 A1 WO 2010109954A1 JP 2010051571 W JP2010051571 W JP 2010051571W WO 2010109954 A1 WO2010109954 A1 WO 2010109954A1
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- WO
- WIPO (PCT)
- Prior art keywords
- pin fin
- pin
- cooling
- turbine
- turbine blade
- Prior art date
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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
- F01D5/12—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
- F01D5/189—Convection cooling with an insert in the blade cavity to guide the cooling fluid, e.g. forming a separation wall the insert having a tubular cross-section, e.g. airfoil shape
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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
- F01D5/12—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
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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
- F01D9/00—Stators
- F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
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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
- F02C7/18—Cooling of plants characterised by cooling medium the medium being gaseous, e.g. air
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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
- F05D2240/00—Components
- F05D2240/10—Stators
- F05D2240/12—Fluid guiding means, e.g. vanes
- F05D2240/122—Fluid guiding means, e.g. vanes related to the trailing edge of a stator vane
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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
- F05D2240/00—Components
- F05D2240/20—Rotors
- F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
- F05D2240/304—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the trailing edge of a rotor blade
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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
- F05D2260/00—Function
- F05D2260/20—Heat transfer, e.g. cooling
- F05D2260/201—Heat transfer, e.g. cooling by impingement of a fluid
-
- 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 blade and a gas turbine, in particular, a turbine blade suitable for use in a stationary blade and a moving blade of a turbine, and a gas turbine using the turbine blade.
- Patent Document 1 discloses a technology for performing pin fin cooling by disposing an insert plate in a cavity formed inside a blade body in a turbine blade and performing impingement cooling, and providing a pin fin protruding from the inner wall of the above-described cavity. It is disclosed.
- Patent Document 2 film cooling that blows out a cooling fluid from a film hole or a shower head, or a flow path through which the cooling fluid flows inside the blade trailing edge, and pin fins that protrude from the flow path are provided to perform pin fin cooling.
- Technology is disclosed.
- the cooling fluid flowing through the region where the pin fin is provided (hereinafter referred to as the pin fin region) is increased to increase the cooling efficiency.
- Methods are generally known.
- the cooling capacity at the entrance of the pin fin region cannot be increased, and the cooling efficiency of the entire pin fin region is reduced.
- the inlet portion of the pin fin region has a problem that the cooling capacity of the inlet portion is insufficient because the flow rate of the cooling fluid cannot be increased despite the large heat load received from the combustion gas.
- the present invention has been made to solve the above-described problem, and is a turbine capable of improving the cooling performance on the trailing edge side of the turbine blade by improving the flow velocity of the cooling fluid on the inlet side of the pin fin region.
- An object is to provide a blade and a gas turbine.
- the turbine blade according to the present invention includes an airfoil portion, a supply passage that extends in the span direction inside the airfoil portion, a cooling fluid flows, and the blade from the supply passage along a center line of the airfoil portion.
- a pair of pin fin channels that extend toward the trailing edge of the shape portion and open to the outside of the airfoil portion at the trailing edge, and the pin fin channel in a region on the supply channel side of the pin fin channel
- a plurality of intermittent pin fins that protrude from the opposing inner walls and that form a gap extending in the span direction therebetween, a pin fin that connects the pair of opposing inner walls in the rear edge side region of the pin fin channel, and the gap
- an insertion portion that reduces the flow area of the cooling fluid in a region on the supply flow path side of the pin fin flow path.
- the cooling fluid on the supply flow channel side of the pin fin passage flows compared to the case where the insertion portion is not disposed.
- the channel cross-sectional area is reduced, and the flow rate of the cooling fluid in the region on the supply channel side is increased.
- the cross-sectional area of the insertion portion decreases as it goes from the supply flow path to the trailing edge.
- the cross-sectional area of the pin fin channel itself decreases as it goes from the supply channel toward the rear edge
- the cross-sectional area of the insertion unit also decreases, so cooling in the region where the insertion unit is arranged A change in the flow path cross-sectional area of the fluid is suppressed.
- the tip of the intermittent pin fin is in contact with the insertion portion.
- the cooling fluid flowing between the inner wall of the pin fin channel and the insertion portion flows between the intermittent pin fins. Therefore, the tip fin and the insertion portion are separated from each other, and the cooling performance by the pin fins is improved as compared with the case where a part of the cooling fluid flows between the intermittent pin fin and the insertion portion.
- the gas turbine of the present invention is provided with the turbine blade of the present invention.
- the cooling performance of the turbine blade can be improved and the deterioration of productivity can be suppressed.
- the insertion portion is disposed in the gap formed between the intermittent pin fins, thereby cooling the pin fin passage on the supply passage side as compared with the case where the insertion portion is not disposed.
- the cross-sectional area of the flow path through which the fluid flows decreases, and the flow speed of the cooling fluid in the region on the supply flow path side increases.
- the cooling capacity in the region on the supply flow path side is improved, and the cooling capacity related to the pin fin flow path, and hence the cooling performance of the turbine blades can be improved.
- FIG. 3 is a cross-sectional view illustrating a schematic configuration of the stationary blade of FIG. 2. It is a schematic diagram explaining the structure in the vicinity of the pin fin channel of FIG. It is a schematic diagram explaining another structure in the vicinity of the pin fin channel of FIG.
- FIG. 4 is a cross-sectional view for explaining another schematic configuration of the stationary blade of FIG. 3. It is the elements on larger scale explaining the structure of the edge part in the rear part insert of FIG.
- a gas turbine according to an embodiment of the present invention will be described with reference to FIGS.
- the turbine blade of the present invention will be described as applied to the first-stage stationary blade and the second-stage stationary blade in the turbine section 4 of the gas turbine 1.
- FIG. 1 is a schematic diagram illustrating the configuration of a gas turbine according to the present embodiment. As shown in FIG. 1, the gas turbine 1 is provided with a compression unit 2, a combustion unit 3, a turbine unit 4, and a rotating shaft 5.
- a compression unit 2 As shown in FIG. 1, the gas turbine 1 is provided with a compression unit 2, a combustion unit 3, a turbine unit 4, and a rotating shaft 5.
- the compression unit 2 sucks and compresses air, and supplies the compressed air to the combustion unit 3.
- a rotational driving force is transmitted from the turbine unit 4 to the compression unit 2 via the rotary shaft 5, and the compression unit 2 sucks and compresses air by being driven to rotate.
- a compression part 2 a well-known thing can be used and it does not specifically limit.
- the combustion unit 3 mixes fuel supplied from the outside and supplied compressed air, burns the air-fuel mixture to generate a high-temperature gas, and generates the generated high-temperature gas to the turbine unit 4. To supply.
- a combustion part 3 a well-known thing can be used and it does not specifically limit.
- the turbine unit 4 extracts a rotational driving force from the supplied high-temperature gas and rotationally drives the rotary shaft 5.
- a stationary blade (turbine blade) 10 attached to a casing (not shown) of the gas turbine 1 and a moving blade attached to the rotating shaft 5 and rotating together with the rotating shaft 5 are equally spaced in the circumferential direction. Are arranged side by side.
- the stationary blades 10 and the moving blades are alternately arranged in the order of the stationary blades 10 and the moving blades in the downstream direction of the high-temperature gas flow from the combustion unit 3 side.
- a pair of the stationary blade 10 and the moving blade is referred to as a stage, and is counted as a first stage and a second stage from the combustion unit 3 side.
- the rotating shaft 5 transmits a rotational driving force from the turbine unit 4 to the compression unit 2.
- the rotary shaft 5 is provided with a compression unit 2 and a turbine unit 4.
- a rotating shaft 5 a well-known thing can be used and it does not specifically limit.
- the stationary blade 10 provided in the first stage and the second stage which is a feature of the present invention, that is, the first stage stationary blade and the second stage stationary blade will be described.
- FIG. 2 is a perspective view illustrating a schematic configuration of the stationary blade of FIG.
- FIG. 3 is a cross-sectional view illustrating a schematic configuration of the stationary blade of FIG.
- the stationary blade 10 is provided with an airfoil portion 11, a front insert 12, and a rear insert 13.
- the airfoil portion 11 is formed in a wing shape in cross section and extends in the span direction (vertical direction in FIG. 2).
- the airfoil 11 includes a front cavity 14 which is a cavity formed in the span direction on the leading edge LE side, and a rear cavity (a supply flow) which is a cavity formed in the span direction on the trailing edge TE side. Path) 15 and a film cooling hole 16 communicating with the front cavity 14 are provided.
- a cavity extending in the span direction is formed inside the airfoil part 11, and a partition wall 17 that divides the cavity into a front cavity 14 and a rear cavity 15 is provided in the cavity.
- the front cavity 14 and the rear cavity 15 are cavities through which the cooling fluid supplied from the outside to the stationary blade 10 flows, and a structure related to impingement cooling that cools the airfoil portion 11 together with the front cavity 14 and the rear cavity 15. It constitutes.
- An example of the cooling fluid is compressed air extracted from the compression unit 2 or the like.
- the front insert 12 is disposed at a predetermined distance from the inner wall of the front cavity 14.
- the rear insert 13 is disposed in the rear cavity 15 at a predetermined distance from the inner wall of the rear cavity 15.
- the film cooling hole 16 is a through hole that connects the front cavity 14 and the outside of the airfoil part 11, and is formed on the suction surface SS that is a convexly protruding curved surface in the airfoil part 11. These are through holes provided side by side in the span direction. Furthermore, the film cooling hole 16 is formed as an oblique hole inclined from the front edge LE toward the rear edge TE toward the outside from the front cavity 14.
- the rear cavity 15 is a cavity extending from the rear cavity 15 along the center line CL of the airfoil portion 11 toward the rear edge TE, and is an area where the intermittent pin fins 19 and the pin fins 20 are provided.
- a pin fin channel 18 is provided.
- the pin fin channel 18 is a channel through which the cooling fluid after being used for impingement cooling in the rear cavity 15 flows, and constitutes a structure related to pin fin cooling that cools the vicinity of the trailing edge TE in the airfoil portion 11. is there.
- the pin fin channel 18 is a channel that extends from the rear cavity 15 to the rear edge TE of the airfoil 11 and opens to the outside at the rear edge TE.
- intermittent pin fins 19 and pin fins 20 are provided in the pin fin channel 18.
- the intermittent pin fin 19 is a region on the rear cavity 15 side in the pin fin channel 18, and is a plurality of substantially cylindrical members formed to protrude from a pair of inner walls constituting the pin fin channel 18.
- the protruding amount of the intermittent pin fin 19 from the inner wall is set such that a gap is formed between the intermittent pin fin 19 so that the end 22 of the rear insert 13 is inserted.
- the pin fin 20 is a region on the trailing edge TE side in the pin fin channel 18 and is a plurality of substantially cylindrical members that connect a pair of inner walls constituting the pin fin channel 18.
- a known shape or the like can be used as the shape and arrangement method of the pin fins 20 and are not particularly limited.
- the front insert 12 and the front cavity 14 constitute a structure related to impingement cooling for cooling the front edge LE side of the airfoil 11.
- the front insert 12 is a substantially cylindrical member having a cross-sectional shape similar to that of the front cavity 14. Further, the front insert 12 is formed with a plurality of ejection holes 21 through which the cooling fluid flowing through the interior is ejected toward the inner wall of the front cavity 14.
- the rear insert 13 similarly to the front insert 12, constitutes a structure related to impingement cooling that cools the rear edge side of the airfoil 11.
- the rear insert 13 is a substantially cylindrical member having a cross-sectional shape substantially similar to the cross-sectional shape of the rear cavity 15. Further, the rear insert 13 is formed with a plurality of ejection holes 21 through which the cooling fluid flowing through the rear insert 13 is ejected toward the inner wall of the rear cavity 15.
- FIG. 4 is a schematic diagram illustrating a configuration in the vicinity of the pin fin channel of FIG.
- the end portion (insertion portion) 22 on the rear edge TE side of the rear insert 13 is disposed in a gap formed between the intermittent pin fins 19, and at least the front end and the rear portion of the intermittent pin fins 19.
- the end portion 22 of the insert 13 is in contact.
- the end 22 is disposed so as to fill the gap between the intermittent pin fins 19, the end 22 is formed to have a predetermined length.
- the length of the end 22 is the longest and is about half of the total length of the pin fin channel 18.
- the rear insert 13 is formed by forming a single plate member into a cylindrical shape, and a portion where both ends of the plate member are in contact with each other is an end portion 22.
- the above-mentioned contacted part is longer than the end 22 and extends not only to the gap between the intermittent pin fins 19 but also to the region of the rear cavity 15.
- the above-mentioned contact portion, in particular, the end 22 portion is formed to have the same thickness from the rear cavity 15 toward the rear edge TE.
- the cooling fluid flowing between the inner wall of the pin fin channel 18 and the end 22 flows between the intermittent pin fins 19. Therefore, the tip fin end 19 and the end portion 22 are separated from each other, and the cooling performance of the pin fin cooling is improved as compared with the case where a part of the cooling fluid flows between the intermittent pin fin 19 and the end portion 22.
- the end 22 of the rear insert 13 may be formed so that its cross-sectional area becomes narrower toward the rear edge TE, and is not particularly limited.
- the cross-sectional area of the pin fin channel 18 itself may be formed such that the cross-sectional area of the end portion 22 decreases as the cross-sectional area decreases from the rear insert 13 toward the rear edge TE.
- FIG. 5 is a schematic diagram illustrating another configuration in the vicinity of the pin fin channel of FIG. 3.
- the end portion 22 on the rear edge TE side of the rear insert 13 gradually approaches the plate member of the rear insert 13 from the rear cavity 15 toward the intermittent pin fins 19. 22, the plate member may be in close contact with each other, and as shown in FIG. 5, the plate member of the rear insert 13 that has been separated in the rear cavity 15 approaches smoothly between the intermittent pin fins 19.
- the plate member may be in close contact with the end portion (insertion portion) 22 ⁇ / b> A, and is not particularly limited.
- the ejection hole 21 in the rear insert 13 is formed in a region where the intermittent pin fins 19 in the rear cavity 15 are not provided, in other words, in a portion that is not the end 22 in the rear cavity 15. In other words, the ejection hole 21 is not formed in the end 22 facing the intermittent pin fin 19 in the rear insert 13.
- a cooling fluid for cooling the stationary blade 10 is supplied from the outside of the stationary blade 10 to the front cavity 14 and the rear cavity 15.
- the compressed air extracted from the compression unit 2 is used as a cooling fluid
- the extracted compressed air flows from the hub (root) side of the stationary blade 10 to the inside of the front insert 12 in the front cavity 14. And it is supplied to the inside of the rear insert 13 in the rear cavity 15.
- the cooling fluid supplied to the inside of the front insert 12 and the rear insert 13 flows in the span direction and is ejected toward the inner walls of the front cavity 14 and the rear cavity 15 through the ejection holes 21.
- the cooling fluid ejected from the ejection holes 21 collides with the inner walls of the front cavity 14 and the rear cavity 15, and cools the collided inner wall and the surrounding airfoil part 11 (impinge cooling).
- the cooling fluid that has undergone impingement cooling in the front cavity 14 flows through the space between the front cavity 14 and the front insert 12 and flows into the film cooling holes 16.
- the cooling fluid that has flowed into the film cooling hole 16 flows out from the negative pressure surface SS of the airfoil portion 11 to the outside, that is, into the high-temperature gas flowing through the turbine portion 4, and forms a film on the downstream side of the film cooling hole 16 in the negative pressure surface SS. Cover.
- the cooling fluid covers the airfoil portion 11 in a film shape, thereby reducing the inflow of heat from the high-temperature gas flowing through the turbine portion 4 to the airfoil portion 11 (film cooling).
- the cooling fluid that has undergone impingement cooling in the rear cavity 15 flows through the space between the rear cavity 15 and the rear insert 13 and flows into the pin fin channel 18.
- the cooling fluid that has flowed into the pin fin channel 18 flows between the intermittent pin fins 19, then flows between the pin fins 20, and cools the trailing edge TE in the airfoil portion 11 and its surroundings (pin fin cooling).
- the cooling fluid after performing pin fin cooling flows out from the opening on the trailing edge TE side in the pin fin channel 18 to the outside, that is, into the high-temperature combustion gas flowing through the turbine unit 4.
- the edge part 22 compared with the case where the edge part 22 is not arrange
- the cross-sectional area of the flow path through which the fluid flows decreases, and the flow rate of the cooling fluid in the region on the rear cavity 15 side increases. Therefore, the cooling capacity in the region on the rear cavity 15 side is improved, and the cooling capacity of the pin fin channel 18 and thus the cooling performance of the turbine blade can be improved.
- FIG. 6 is a cross-sectional view for explaining another schematic configuration of the stationary blade of FIG.
- FIG. 7 is a partially enlarged view for explaining the structure of the end portion of the rear insert in FIG. 6.
- the edge part of the plate member which comprises the rear part insert 13 and the edge part 22 may be aligned as shown in FIG. 3, or as shown in FIG. 6 and FIG.
- the end of the plate member may be displaced, and the end 22B may be formed only from one plate member, and is not particularly limited.
- the plate thickness of one plate member extending toward the trailing edge TE side is larger than the plate thickness of the other portion. It is thick. And the part where the said plate
- the turbine blade of the present invention is applied to the first stage and second stage stationary blades 10 of the turbine unit 4.
- the turbine blade of the present invention is applied to the first stage and second stage stationary blades 10 of the turbine unit 4.
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Abstract
Description
つまり、タービン翼は鋳造により形成される場合が多く、かかる場合に上述の流路は中子により形成される。上述のように流路の断面積を狭くするためには、中子の断面積を狭くする必要があり、中子の厚みを薄くすると、中子の強度が低下する。すると、中子の破損などによる鋳造不良が発生しやすくなり、タービン翼の製造性が悪化するという問題があった。
特に、ピンフィン領域の入口部は、燃焼ガスから受ける熱負荷が大きいにも拘わらず、冷却流体の流速は速くできないため、入口部の冷却能力が不足する問題があった。
本発明のタービン翼は、翼形部と、該翼形部の内部をスパン方向に延び、冷却流体が流れる供給流路と、前記供給流路から前記翼形部の中心線に沿って前記翼形部の後縁に向かって延び、前記後縁において前記翼形部の外部に開口するピンフィン流路と、該ピンフィン流路の前記供給流路側の領域における、前記ピンフィン流路を構成する一対の対向する内壁から突出するとともに、間に前記スパン方向に延びる隙間を形成する複数の間欠ピンフィンと、前記ピンフィン流路の前記後縁側の領域における前記一対の対向する内壁を繋ぐピンフィンと、前記隙間に配置され、前記ピンフィン流路の前記供給流路側の領域における前記冷却流体の流路面積を減じる挿入部と、が設けられている。
ガスタービン1には、図1に示すように、圧縮部2と、燃焼部3と、タービン部4と、回転軸5と、が設けられている。
なお、圧縮部2としては、公知のものを用いることができ、特に限定するものではない。
なお、燃焼部3としては、公知のものを用いることができ、特に限定するものではない。
タービン部4には、ガスタービン1のケーシング(図示せず)に取り付けられる静翼(タービン翼)10と、回転軸5に取り付けられ回転軸5とともに回転する動翼と、が周方向に等間隔に並んで配置されている。
なお、回転軸5としては、公知のものを用いることができ、特に限定するものではない。
静翼10には、図2および図3に示すように、翼形部11と、前部インサート12と、後部インサート13と、が設けられている。
翼形部11には、前縁LE側にスパン方向に延びて形成された空洞である前部キャビティ14と、後縁TE側にスパン方向に延びて形成された空洞である後部キャビティ(供給流路)15と、前部キャビティ14と連通するフィルム冷却孔16と、が設けられている。言い換えると、翼形部11の内部には、スパン方向に延びる空洞が形成され、当該空洞を前部キャビティ14と後部キャビティ15とに区切る隔壁17が、当該空洞に設けられている。
冷却流体としては、圧縮部2などから抽気された圧縮空気を例示することができる。
さらに、フィルム冷却孔16は、前部キャビティ14から外部に向かって、前縁LEから後縁TE側に傾斜する斜め孔として形成されている。
ピンフィン流路18は、後部キャビティ15におけるインピンジ冷却に用いられた後の冷却流体が流れる流路であって、翼形部11における後縁TE近傍を冷却するピンフィン冷却に係る構造を構成するものである。ピンフィン流路18は、後部キャビティ15から翼形部11の後縁TEまで延びる流路であり、後縁TEにおいて外部に開口するものである。
後部インサート13における後縁TE側の端部(挿入部)22は、図4に示すように、間欠ピンフィン19の間に形成された隙間に配置され、少なくとも一部の間欠ピンフィン19の先端と後部インサート13の端部22とは接触している。言い換えると、後部インサート13と対向して配置された間欠ピンフィン19の先端と、後部インサート13とが接触していることが望ましい。
なお、端部22の長さは最長でピンフィン流路18の全長の半分程度とされている。
このようにすることで、ピンフィン流路18の後部キャビティ15側の領域において、冷却流体が流れる流路断面積の変化が抑制される。
なお、後部インサート13における後縁TE側の端部22は、図4に示すように、後部キャビティ15から間欠ピンフィン19の間に向かって、後部インサート13の板部材が徐々に接近し、端部22において板部材が密着した構成であってもよいし、図5に示すように、後部キャビティ15において離れていた後部インサート13の板部材が、間欠ピンフィン19の間に入るところで、滑らかに接近して間欠ピンフィン19の隙間において、言い換えれば、端部(挿入部)22Aにおいて当該板部材が密着した構成であってもよく、特に限定するものではない。
静翼10を冷却する冷却流体は、静翼10の外部から前部キャビティ14および後部キャビティ15に供給される。例えば、圧縮部2から抽気された圧縮空気を冷却流体として利用する場合には、抽気された圧縮空気は、静翼10のハブ(根元)側から前部キャビティ14における前部インサート12の内部、および、後部キャビティ15における後部インサート13の内部に供給される。
噴出孔21から噴出した冷却流体は、前部キャビティ14および後部キャビティ15の内壁と衝突し、当該衝突した内壁、および、その周囲の翼形部11を冷却する(インピンジ冷却)。
このように、冷却流体が翼形部11を膜状に覆うことにより、タービン部4を流れる高温ガスから翼形部11への熱の流入を減少させることができる(フィルム冷却)。
ピンフィン冷却を行った後の冷却流体は、ピンフィン流路18における後縁TE側の開口から外部、つまりタービン部4を流れる高温燃焼ガス中に流出する。
なお、上述の実施形態のように、後部インサート13および端部22を構成する板部材の端部が、図3に示すように揃っていてもよいし、図6および図7に示すように、板部材の端部がズレ、一方の板部材のみから端部22Bが形成されていてもよく、特に限定するものではない。
このように構成することにより、ピンフィン領域の入口部における冷却流体が流れる流路断面積をほぼ一定にできる。
例えば、上記の実施の形態においては、本発明のタービン翼をタービン部4の第1段、第2段の静翼10に適用して説明したが、静翼10に限られることなく、動翼に用いてもよく、特に限定するものではない。
10 静翼(タービン翼)
11 翼形部
15 後部キャビティ(供給流路)
18 ピンフィン流路
19 間欠ピンフィン
20 ピンフィン
22,22A,22B 端部(挿入部)
CL 中心線
TE 後縁
Claims (4)
- 翼形部と、
該翼形部の内部をスパン方向に延び、冷却流体が流れる供給流路と、
前記供給流路から前記翼形部の中心線に沿って前記翼形部の後縁に向かって延び、前記後縁において前記翼形部の外部に開口するピンフィン流路と、
該ピンフィン流路の前記供給流路側の領域における、前記ピンフィン流路を構成する一対の対向する内壁から突出するとともに、間に前記スパン方向に延びる隙間を形成する複数の間欠ピンフィンと、
前記ピンフィン流路の前記後縁側の領域における前記一対の対向する内壁を繋ぐピンフィンと、
前記隙間に配置され、前記ピンフィン流路の前記供給流路側の領域における前記冷却流体の流路面積を減じる挿入部と、
が設けられているタービン翼。 - 前記挿入部の断面積が、前記供給流路から前記後縁に向かうに伴い減少する請求項1記載のタービン翼。
- 前記間欠ピンフィンの先端と、前記挿入部とが接触する請求項1または2に記載のタービン翼。
- 請求項1から3のいずれかに記載のタービン翼が設けられているガスタービン
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