WO2009107312A1 - ガスタービン及びディスク並びにディスクの径方向通路形成方法 - Google Patents
ガスタービン及びディスク並びにディスクの径方向通路形成方法 Download PDFInfo
- Publication number
- WO2009107312A1 WO2009107312A1 PCT/JP2008/073483 JP2008073483W WO2009107312A1 WO 2009107312 A1 WO2009107312 A1 WO 2009107312A1 JP 2008073483 W JP2008073483 W JP 2008073483W WO 2009107312 A1 WO2009107312 A1 WO 2009107312A1
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- WO
- WIPO (PCT)
- Prior art keywords
- disk
- radial passage
- rotation axis
- gas turbine
- turbine
- 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
- F01D5/02—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/08—Heating, heat-insulating or cooling means
- F01D5/085—Heating, heat-insulating or cooling means cooling fluid circulating inside the rotor
- F01D5/087—Heating, heat-insulating or cooling means cooling fluid circulating inside the rotor in the radial passages of the rotor disc
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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
- F05D2230/00—Manufacture
- F05D2230/10—Manufacture by removing material
-
- 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
- F05D2250/14—Two-dimensional elliptical
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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
- F05D2250/00—Geometry
- F05D2250/30—Arrangement of components
- F05D2250/31—Arrangement of components according to the direction of their main axis or their axis of rotation
- F05D2250/314—Arrangement of components according to the direction of their main axis or their axis of rotation the axes being inclined in relation to each other
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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
- F05D2260/94—Functionality given by mechanical stress related aspects such as low cycle fatigue [LCF] of high cycle fatigue [HCF]
- F05D2260/941—Functionality given by mechanical stress related aspects such as low cycle fatigue [LCF] of high cycle fatigue [HCF] particularly aimed at mechanical or thermal stress reduction
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49229—Prime mover or fluid pump making
Definitions
- the present invention relates to a gas turbine, a disk, and a radial passage forming method for the disk, and more particularly, to a gas turbine, a disk, and a disk radial path forming method for cooling a moving blade with air.
- the gas turbine as a device for extracting energy from combustion gas obtained by burning fuel.
- the gas turbine injects fuel into compressed air, rotates the turbine using the energy of combustion gas generated by burning the fuel, and outputs rotational energy from the rotor.
- the moving blade cooling medium supplied from the outside of the turbine structure passes through the hollow shaft disposed in the center hole of the disk in a state before cooling, and is provided in the radial direction provided in the spacer.
- a gas turbine equipped with a turbine cooling system for cooling a moving blade by being guided to the outer peripheral side of a disk through a hole.
- the radial hole formed in the radial direction of the disk which is a rotating body, is loaded in the circumferential direction by inertial force when the disk rotates. At this time, depending on the shape of the radial hole, stress may concentrate on a specific portion.
- the present invention has been made in view of the above, and an object of the present invention is to reduce the uneven stress distribution generated in the radial passage formed in the radial direction of the disk.
- the gas turbine according to the present invention includes a combustion blade that is received by the moving blade by connecting a moving blade that receives combustion gas obtained by burning fuel to a side peripheral portion.
- a disk that rotates with the gas energy transmitted around the rotation axis, and a curved surface that is centered on the rotation axis, and a virtual curved surface that has the same distance from all points on the curved surface to the rotation axis In a cross-section, a hole is formed including a portion having a shape in which the circumferential length of the disk is larger than the length in a direction parallel to the rotation axis, and the disk is formed on the disk from the rotation axis side. And a radial passage formed toward the outer side.
- the radial passage When the disk rotates about the rotation axis, the radial passage is loaded with a force in the circumferential direction of the disk.
- the section of the radial passage in the virtual curved surface is longer in the circumferential direction of the disk than in the direction parallel to the rotation axis. It is formed into a large ellipse. Therefore, in the gas turbine, the stress generated in the portion passing through the centroid of the cross section and orthogonal to the force is reduced. Thereby, in the gas turbine, the uneven stress distribution generated in the radial passage is reduced.
- the radial passage has a portion not included in a virtual plane including the rotation axis.
- the gas turbine according to the present invention is an ellipse in which the section of the radial passage in the virtual curved surface is naturally greater in the circumferential length of the disk than in the direction parallel to the rotation axis. It has a part that becomes a shape. Therefore, in the gas turbine, the stress generated in the portion passing through the centroid of the cross section and orthogonal to the force is reduced. Thereby, in the gas turbine, the uneven stress distribution generated in the radial passage is reduced.
- the passage through which the cooling air flows becomes longer because the radial passage is formed to be inclined with respect to the reference virtual plane. Therefore, in the gas turbine, heat exchange between the cooling air and the object to be cooled is promoted. Thereby, the cooling performance of the gas turbine is improved.
- the radial passage has one opening end opened in a space formed inside the side peripheral portion of the disk, and the other opening end is the side peripheral portion of the disk. And an angle of not less than 10 degrees and not more than 45 degrees with respect to a reference virtual plane including the one opening end and the rotation axis when projected from a direction of the rotation axis onto a plane orthogonal to the rotation axis. It is desirable to have
- the stress generated in the portion that passes through the centroid of the cross section and is orthogonal to the force is reduced more favorably.
- the bias of the stress distribution generated in the radial passage is more favorably reduced.
- the disk rotates in a predetermined rotation direction
- the radial passage is a region opposite to the rotation direction with the reference virtual plane as a boundary at the one opening end portion. It is desirable to lean on
- the collision between the cooling air guided to the radial passage and the wall surface of one opening end is alleviated, and the cooling air flows into the radial passage. That is, in the gas turbine, the cooling air easily flows into the radial passage. Therefore, in the gas turbine, the flow rate of the cooling air supplied to the radial passage is increased. Thereby, as for the said gas turbine, heat exchange with the said cooling air and cooling object is accelerated
- the disk according to the present invention is a curved surface having a rotation axis as an axis, and the distance from all points on the curved surface to the rotation axis is all equal.
- the radial passage When the disc according to the present invention is rotated about the rotation axis, the radial passage is loaded with a force in the circumferential direction of the disc.
- the disk has an elliptical shape in which the cross section of the radial path of the radial passage is larger in the circumferential direction than the length in the direction parallel to the rotation axis. It is formed. Therefore, the stress generated in the disk passing through the centroid of the cross section and orthogonal to the force is reduced. As a result, the disc has a reduced stress distribution bias generated in the radial passage.
- a method of forming a radial passage for a disc according to the present invention is such that a drill blade is parallel to a virtual plane including a disc-shaped disc rotation axis and predetermined from the virtual plane.
- a first procedure for attaching the disc to a drilling machine installed at a distance and a second procedure for forming a first radial passage as a hole in the disc by moving the drill blade parallel to the virtual plane.
- a fifth procedure in which the third procedure and the fourth procedure are repeated until a desired number of the radial passages are formed in the disk.
- the radial passage forming method of the disk according to the present invention can easily process the radial passage using a conventional machine tool.
- an elliptical cross section of the radial passage in the virtual curved surface is longer in the circumferential direction of the disk than in the direction parallel to the rotation axis. It is formed in a shape. Therefore, in the gas turbine, the stress generated in the portion passing through the centroid of the cross section and orthogonal to the force is reduced. Thereby, in the gas turbine, the uneven stress distribution generated in the radial passage is reduced.
- the collision between the cooling air guided to the radial passage and the wall surface of one opening end is alleviated, and the cooling air flows into the radial passage. That is, in the gas turbine, the cooling air easily flows into the radial passage. Therefore, in the gas turbine, the flow rate of the cooling air supplied to the radial passage is increased. Thereby, the gas turbine has improved cooling performance by the cooling air.
- the passage through which the cooling air flows becomes longer because the radial passage is formed to be inclined with respect to the reference virtual plane. Therefore, in the gas turbine, heat exchange between the cooling air and the object to be cooled is promoted. Thereby, the cooling performance of the gas turbine is improved.
- the present invention can reduce the uneven stress distribution generated in the radial passage formed in the radial direction of the disk.
- FIG. 1 is a schematic diagram illustrating a configuration of a gas turbine according to the present embodiment.
- FIG. 2 is a cross-sectional view schematically showing an enlarged turbine portion of the gas turbine according to the present embodiment.
- FIG. 3 is a projection view in which the radial passage formed in the disk according to the present embodiment is projected from the direction of the rotation axis onto a plane orthogonal to the rotation axis.
- FIG. 4 is a projection view in which a radial passage formed in a conventional disk is projected from a rotation axis direction onto a plane orthogonal to the rotation axis.
- FIG. 5 is a schematic diagram showing a side peripheral portion of a conventional disk developed on a plane.
- FIG. 6 is a schematic diagram showing a side circumferential portion of the disk according to the present embodiment developed in a plane.
- FIG. 7 is a projection view in which the vicinity of the inner opening end of the radial passage formed in the conventional disk is projected from the direction of the rotation axis onto a plane orthogonal to the rotation axis.
- FIG. 8 is a projection view in which the vicinity of the inner opening end of the radial passage formed in the disk according to the present embodiment is projected from the rotation axis direction onto a plane orthogonal to the rotation axis.
- FIG. 9 is a diagram for explaining the amount by which the drill blade is displaced from the virtual plane when processing the radial passage according to the present embodiment.
- FIG. 1 is a schematic diagram showing a configuration of a gas turbine according to the present embodiment.
- the gas turbine 1 according to the present embodiment is installed on the floor GND.
- the gas turbine 1 includes a compression unit 120, a combustion unit 130, a turbine unit 110, and an exhaust unit 140 in order from the upstream side to the downstream side of the fluid flow.
- Compressor 120 pressurizes air and sends the pressurized air to combustion unit 130.
- the combustor 130 supplies fuel to the pressurized air.
- the combustion part 130 injects a fuel into the compressed air, and burns the said fuel.
- the turbine unit 110 converts the energy of the combustion gas sent out from the combustion unit 130 into rotational energy.
- the exhaust unit 140 discharges the combustion gas to the atmosphere.
- the compression unit 120 includes an air suction port 121, a compressor housing 122, a compressor side stationary blade 123, and a compressor side moving blade 124.
- the air inlet 121 takes air from the atmosphere into the compressor housing 122.
- the plurality of compressor side stationary blades 123 and the plurality of compressor side moving blades 124 are alternately provided in the compressor casing 122.
- the turbine section 110 includes a turbine section casing 111, a turbine side stationary blade 112, and a turbine side moving blade 113.
- the plurality of turbine side stationary blades 112 and the plurality of turbine side moving blades 113 are alternately arranged in the turbine part casing 111 along the direction of the flow of the combustion gas.
- the exhaust unit 140 includes an exhaust diffuser 141 that is continuous with the turbine unit 110.
- the exhaust diffuser 141 converts the dynamic pressure of the exhaust gas that has passed through the turbine unit 110 into a static pressure.
- the gas turbine 1 has a rotor 150 as a rotating body.
- the rotor 150 is provided so as to penetrate through the center of the compression unit 120, the combustion unit 130, the turbine unit 110, and the exhaust unit 140.
- the rotor 150 is rotatably supported at the end on the compression unit 120 side by a bearing 151 and is rotatably supported at the end on the exhaust unit 140 side by a bearing 152.
- a plurality of disks 114 are fixed to the rotor 150.
- a compressor-side moving blade 124 and a turbine-side moving blade 113 are connected to the disk 114.
- a generator input shaft of the generator is connected to the end of the rotor 150 on the compression unit 120 side.
- the gas turbine 1 takes in air from the air inlet 121 of the compression unit 120.
- the taken-in air is compressed by the plurality of compressor side stationary blades 123 and the compressor side moving blades 124. Thereby, the air becomes compressed air having a higher temperature and a higher pressure than the atmosphere.
- the combustion unit 130 supplies predetermined fuel to the compressed air and burns the fuel.
- the plurality of turbine-side stationary blades 112 and the plurality of turbine-side moving blades 113 constituting the turbine unit 110 convert the energy of the combustion gas generated in the combustion unit 130 into rotational energy.
- the turbine-side moving blade 113 transmits the rotational energy to the rotor 150. As a result, the rotor 150 rotates.
- the gas turbine 1 drives a generator (not shown) connected to the rotor 150.
- the exhaust gas after passing through the turbine section 110 is released into the atmosphere after the dynamic pressure is converted to a static pressure by the exhaust diffuser 141 of the exhaust section 140.
- FIG. 2 is a cross-sectional view schematically showing an enlarged turbine portion of the gas turbine according to the present embodiment.
- the rotor 150 includes a disk 114 and a turbine side moving blade 113.
- the disk 114 rotates about the rotation axis RL shown in FIGS.
- a plurality of turbine side rotor blades 113 are connected along the circumferential direction to a radially outer side peripheral portion of a disk 114 formed in a disk shape.
- the turbine-side moving blade 113 also rotates with the disk 114 about the rotation axis RL.
- combustion gas having a higher temperature and pressure than the atmosphere generated in the combustion unit 130 is supplied to the turbine unit 110.
- heat is received from the combustion gas, and the temperatures of the turbine side rotor blade 113 and the disk 114 rise. Therefore, the gas turbine 1 supplies cooling air having a temperature lower than that of the turbine side rotor blade 113 and the disk 114 to the turbine side rotor blade 113 and the disk 114 to cool the turbine side rotor blade 113 and the disk 114.
- the disk 114 and the turbine rotor blade 113 are provided in a plurality of stages along the flow of the combustion gas.
- the disks 114 are a first disk 114a and a second disk 114b from the upstream side of the flow of the combustion gas among the plurality of disks 114 provided.
- the turbine side moving blade 113 is made into the 1st turbine side moving blade 113a and the 2nd turbine side moving blade 113b from the upstream of the flow of a combustion gas among the turbine side moving blades 113 provided with two or more.
- the first turbine side rotor blade 113a is connected to the first disk 114a
- the second turbine side rotor blade 113b is connected to the second disk 114b.
- the turbine unit 110 includes a first supply passage 11, a first space 12, a radial passage 13, a second space 14, a cooling passage 15, a second supply passage 16, and a third space 17. Composed.
- the first supply passage 11 is a passage through which cooling air flows. The cooling air is supplied from the compression unit 120 shown in FIG. 1 to the first supply passage 11 shown in FIG. 2 through a passage (not shown) and a cooler that cools the air guided from the compression unit 120.
- the first space 12 is formed in the rotor 150.
- a plurality of radial passages 13 are formed in the first disk 114a from the inside of the first disk 114a formed in a disk shape toward the radially outer side of the first disk 114a.
- the second space 14 is formed between the first disk 114a and the first turbine blades 113a.
- a plurality of cooling passages 15 are formed in the first turbine-side moving blade 113a.
- the first supply passage 11 is supplied with cooling air from one opening end, and the other end opens to the first space 12. Thereby, the cooling air is supplied to the first space 12 through the first supply passage 11.
- one opening end 13 a opens into the first space 12, and the other opening end 13 b opens into the second space 14.
- the cooling air in the first space 12 is supplied to the second space 14 via the radial passage 13.
- the cooling air exchanges heat with the first disk 114 a having a temperature higher than that of the cooling air while passing through the inside of the radial passage 13.
- the cooling air cools the first disk 114 a while passing through the radial passage 13.
- the cooling passage 15 has one end opened to the second space 14 and the other end opened to the turbine compartment 111.
- the cooling air in the second space 14 is discharged to the turbine casing 111 through the cooling passage 15.
- the cooling air exchanges heat with the first turbine blades 113a having a temperature higher than that of the cooling air while passing through the inside of the cooling passage 15.
- the cooling air cools the first turbine blades 113 a while passing through the cooling passage 15.
- the second supply passage 16 is formed in the first disk 114a in the direction of the rotation axis RL.
- the third space 17 is formed between the first disk 114a and the second disk 114b.
- One end of the second supply passage 16 opens into the first space 12, and the other end opens into the third space 17. Accordingly, the cooling air that has not been supplied to the radial passage 13 among the cooling air in the first space 12 is guided to the third space 17 via the second supply passage 16.
- the cooling air in the third space 17 includes passages, spaces, and cooling passages formed in the second disk 114b and the second turbine side rotor blade 113b in substantially the same manner as the first disk 114a and the first turbine side rotor blade 113a.
- the radial passage 13 is formed in parallel with a plane orthogonal to the rotation axis RL.
- the radial passage 13 may be formed to be inclined with respect to a plane orthogonal to the rotation axis RL.
- FIG. 3 is a projection view in which the radial passage formed in the disk according to the present embodiment is projected from the direction of the rotation axis onto a plane orthogonal to the rotation axis.
- the gas turbine 1 is characterized by a radial passage 13 formed in the disk 114.
- the virtual plane V01 is an arbitrary plane including the rotation axis RL.
- a plurality of radial passages 13 are provided from the radially inner side of the disk 114 toward the radially outer side.
- the radial passage 13 intersects the virtual plane V01 passing through the rotation axis RL or is parallel to the virtual plane V01, it is not completely included in the virtual plane V01. That is, in the radial passage 13, an imaginary line obtained by extending the radial passage 13 inward in the radial direction of the disk 114 does not intersect the rotation axis RL.
- a virtual surface including one open end 13a of the radial passage 13 and the rotation axis RL is defined as a reference virtual plane V02.
- the gas turbine 1 is formed such that an angle ⁇ formed by the reference virtual plane V02 and the radial passage 13 is, for example, 30 degrees.
- the angle ⁇ formed by the reference virtual plane V02 and the radial passage 13 is set to be equal to 30 degrees, but this embodiment is not limited to this.
- the plurality of radial passages 13 provided in the disk 114 may be set such that the angle ⁇ formed by the reference virtual plane V02 and the radial passage 13 is different.
- the fitting part 18 shown in FIG. 3 is a part in which the edge part of the turbine side moving blade 113 is fitted.
- the fitting portion 18 is fitted to a fitting portion formed at an end portion of the turbine-side moving blade 113 to support the turbine-side moving blade 113 on the side peripheral portion of the disk 114.
- the radial passage 13 is formed from the outer side in the radial direction of the disk 114 toward the inner side in the radial direction of the disk 114 by, for example, a drill, avoiding a space between the plurality of fitting portions 18 formed on the side periphery of the disk 114. . Thereby, the other opening end 13b opens between the plurality of fitting portions 18 provided.
- FIG. 4 is a projection view in which the radial passage formed in the conventional disk is projected from the direction of the rotation axis onto a plane orthogonal to the rotation axis.
- FIG. 5 is a schematic diagram showing a side peripheral portion of a conventional disk developed on a plane.
- the conventional gas turbine 2 includes a disk 214 and a radial passage 23 formed in the disk 214.
- the other opening end 23 b of the radial passage 23 opens in the side periphery of the disk 214.
- the other open end 23b of the radial passage 23 has a substantially perfect circle shape as shown in FIG.
- a force F is applied to the disk 214 in the circumferential direction by inertial force on the other opening end 23b.
- stress is generated at the other opening end 23b.
- the stress of the part P that passes through the centroid of the other opening end 23b and is orthogonal to the force F among the substantially circular edges of the other opening end 23b is maximized. That is, in the gas turbine 2, stress concentrates on the part P.
- FIG. 6 is a schematic diagram showing a side peripheral portion of the disk according to the present embodiment expanded in a plane.
- the disk 114 has a longer elliptical shape in the circumferential direction. That is, the other opening end 13b is longer in the circumferential length w of the disk 114 than in the length h in the direction parallel to the rotation axis RL.
- the radial passage 13 is loaded with a force F in the circumferential direction of the disk 114 when the disk 114 rotates about the rotation axis RL shown in FIG. At this time, if the disk 114 shown in FIG. 3 and the disk 214 shown in FIG. 4 rotate under the same conditions, the force F acting on the other opening end 13b is equal to the force F acting on the other opening end 23b. However, if the shape of the opening is different, the magnitude of the stress generated in the specific part P is different even if the same force F is applied to the opening.
- the stress generated in is smaller. That is, in the gas turbine 1, the stress generated in the part P of the other opening end 13b is reduced, and the bias of the stress distribution generated in the other opening end 13b is reduced.
- the circumferential length w of the disk 114 is the rotation axis RL. Unlike the case where the length is greater than the length h in the direction parallel to the stress, the stress generated at the site P increases.
- the shape of the other opening end 13b is in a direction parallel to the rotation axis RL.
- the length h increases. That is, when the radial passage 13 is formed to be inclined with respect to the plane orthogonal to the rotation axis RL, the stress generated in the portion P increases.
- the gas turbine 1 is formed in an elliptical shape at one opening end 13a of the radial passage 13 shown in FIG. 3 similarly to the other opening end 13b.
- the gas turbine 1 similarly to the other opening end 13b, in the one opening end 13a, the gas turbine 1 reduces the stress generated in the portion P of the one opening end 13a.
- the uneven stress distribution generated at the one open end 13a is reduced.
- a virtual curved surface having a rotational axis RL as an axis and having the same predetermined distance ⁇ from all points on the curved surface to the rotational axis RL is defined as a virtual curved surface V03. That is, the virtual curved surface V03 is a side surface of a cylinder whose axis is the rotation axis RL and whose radius between the bottom surface and the top surface is a predetermined distance ⁇ .
- the predetermined distance ⁇ is a distance that is not less than the distance from the rotation axis RL to the one opening end 13a and not more than the distance from the rotation axis RL to the other opening end 13b.
- the radial passage 13 has a cross-sectional shape on the virtual curved surface V03, like the one opening end 13a and the other opening end 13b, in the circumferential direction of the disk 114 rather than the length h in the direction parallel to the rotation axis RL.
- the length w becomes larger.
- the uneven stress distribution generated in the cross section is reduced. That is, the gas turbine 1 is not limited to the one open end 13a and the other open end 13b, and the stress distribution bias generated in the radial passage 13 is reduced.
- FIG. 7 is a projection view in which the vicinity of the inner opening end of the radial passage formed in the conventional disk is projected from the direction of the rotation axis onto a plane orthogonal to the rotation axis.
- FIG. 8 is a projection view in which the vicinity of the inner opening end of the radial passage formed in the disk according to the present embodiment is projected from the rotation axis direction onto a plane orthogonal to the rotation axis.
- the cooling air is guided from the first space 12 shown in FIG. 2 to the radial passage 13 through one open end 13a.
- the disk 114 rotates in a predetermined rotation direction as indicated by an arrow RD in FIG.
- the cooling air flows into the one open end 13 a as indicated by the arrow FL in FIG. 8.
- the gas turbine 2 has an angle ⁇ of 0 degree. Therefore, as shown by the arrow FL in FIG. 7, the cooling air hardly collides with the wall surface of the one open end 23 a and hardly flows into the radial passage 23.
- the radial passage 13 forms an angle ⁇ with the reference virtual plane V02. That is, the radial passage 13 is formed to be inclined from the reference virtual plane V02. Further, the radial passage 13 is formed to be inclined in a region opposite to the rotation direction of the disk 114 indicated by the arrow RD in FIGS. 3 and 8 with the reference virtual plane V02 as a boundary.
- the cooling air flows into the radial passage 13 with the collision with the wall surface of the one open end 13a alleviated. That is, the cooling air is more likely to flow in the radial passage 13 than in the radial passage 23.
- the one opening end 13a is formed so that the shape of the one opening end 13a is elliptical, so that the circumferential length w of the disk 114 is as shown in FIGS. 7 is larger than the circumferential length w of the disk 214 of one open end 23a shown in FIG. Therefore, as shown by the arrow FL in FIG. 8, the cooling air is more likely to flow into the one opening end 13a than to the one opening end 23a.
- the gas turbine 1 the flow rate of the cooling air supplied to the radial passage 13 is increased. Accordingly, the gas turbine 1 also increases the flow rate of the cooling air supplied to the cooling passage 15 shown in FIG. Therefore, in the gas turbine 1, heat exchange between the cooling air and the turbine side moving blade 113 and the disk 114 is promoted. That is, in the gas turbine 1, the disk 114 and the turbine rotor blade 113 are further cooled.
- the radial passage 13 is formed to be inclined with respect to the reference virtual plane V02, so that the passage through which the cooling air flows is longer than the radial passage 23 shown in FIG. Therefore, in the gas turbine 1 including the radial passage 13, the contact area between the cooling air and the turbine-side moving blade 113 is increased. Thereby, in the gas turbine 1, heat exchange between the cooling air and the turbine rotor blade 113 is further promoted. That is, in the gas turbine 1, the turbine side moving blade 113 is further cooled.
- the angle ⁇ is set to 30 degrees, for example, but the present embodiment is not limited to this.
- the angle ⁇ is set to 10 degrees or more and 45 degrees or less, the uneven stress distribution generated in the radial passage 13 is reduced. Moreover, the gas turbine 1 has improved cooling performance by cooling air.
- the radial passage 13 is formed from the radially outer side of the disk 114 toward the radially inner side of the disk 114 by, for example, a drill.
- a drill for example, a drill.
- the drill blade D is shifted to a position away from the virtual plane V01 by a predetermined distance ⁇ , and is moved parallel to the virtual plane V01 when the radial passage 13 is processed.
- FIG. 9 is a diagram for explaining the amount by which the drill blade is displaced from the virtual plane when the radial passage according to the present embodiment is processed.
- the predetermined distance ⁇ is obtained by the distance r from the rotation axis RL to the one opening end 13a and the angle ⁇ .
- the predetermined distance ⁇ is a product of the distance r and sin ⁇ .
- the worker who processes the radial passage 13 first attaches the disk-shaped disk 114 to the drilling machine. At this time, the drill blade D is installed parallel to the virtual plane V01 and shifted by a predetermined distance ⁇ from the virtual plane V01. An operator processes the first radial passage 13 under these conditions.
- the worker rotates the disk 114 by a predetermined angle about the rotation axis RL.
- the predetermined angle is obtained from the number of radial passages 13 provided in the disk 114. For example, when a predetermined number ⁇ is formed in the disk 114, the disk 114 is rotated by an angle obtained by dividing 360 by the predetermined number ⁇ . In this state, the worker processes the second radial passage 13. Thereafter, the worker repeats the procedure of rotating the disc by a predetermined angle and the processing procedure until a desired number of radial passages 13 are formed in the disc 114.
- the gas turbine 1 can easily process the radial passage 13 using a conventional machine tool. Thereby, the gas turbine 1 provided with the radial passage 13 reduces the bias of the stress distribution generated in the radial passage 13 as described above. Further, in the gas turbine 1 provided with the radial passage 13, the disk 114 and the turbine rotor blade 113 are more suitably cooled as described above.
- path 13 is formed in linear form, for example, this embodiment is not limited to this.
- the radial passage 13 may be formed in a shape in which a plurality of straight lines are combined, that is, bent.
- the portion having the angle ⁇ is preferably formed in the vicinity of one opening end 13a or the other opening end 13b of the radial passage 13.
- the other opening end 13b is farthest from the rotation axis RL in the radial passage 13 formed in the disk 114. Therefore, the portion near the other opening end 13 b is loaded with the largest force F in the radial passage 13. Therefore, when the portion having the angle ⁇ is formed in the vicinity of the other opening end 13 b of the radial passage 13, the gas turbine 1 is generated in the portion where the largest force F is loaded in the radial passage 13. The uneven stress distribution is reduced.
- the angle ⁇ may be set to 0 degree as shown in FIG. 4.
- the radial passage 13 has an elliptical cross section at the virtual curved surface V ⁇ b> 03.
- the radial passage 13 is processed by electric discharge machining.
- the cross section of the radial passage 13 at the virtual curved surface V03 is longer than the length h in the direction parallel to the rotation axis RL, as shown in FIG.
- the disk 114 is formed in an elliptical shape having a larger circumferential length w.
- the “elliptical shape” in the present embodiment is not necessarily limited to an accurate ellipse. That is, the shape of the cross section of the radial passage 13 at the virtual curved surface V03 is not limited to a curve formed of a set of points such that the sum of the distances from two specific points on the plane is constant.
- the cross-sectional shape of the radial passage 13 at the virtual curved surface V03 may be a substantially elliptical shape having no corners.
- the gas turbine, the disk, and the disk radial passage forming method according to the present embodiment are useful for a gas turbine in which a radial passage through which cooling air flows in the radial direction of the disk is formed.
- the present invention is suitable for a gas turbine that reduces the uneven stress distribution generated in the radial passage.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Abstract
Description
11 第1供給通路
12 第1空間
13、23 径方向通路
13a、23a 一方の開口端
13b、23b 他方の開口端
14 第2空間
15 冷却通路
16 第2供給通路
17 第3空間
18 嵌合部
110 タービン部
111 タービン部車室
112 タービン側静翼
113 タービン側動翼
114、214 ディスク
120 圧縮部
121 空気吸入口
122 圧縮機筐体
123 圧縮機側静翼
124 圧縮機側動翼
130 燃焼部
140 排気部
141 排気ディフューザ
150 ロータ
151、152 軸受
D ドリル刃
GND 床
RL 回転軸
V01 仮想平面
V02 基準仮想平面
V03 仮想曲面
Claims (6)
- 側周部に燃料が燃焼した燃焼ガスを受ける動翼が連結されることで前記動翼が受けた前記燃焼ガスのエネルギーが伝えられて回転軸を中心に回転するディスクと、
前記回転軸を軸心とする曲面であって前記曲面上の全ての点から前記回転軸までの距離が全て等しい仮想曲面での断面において、前記回転軸と平行な方向の長さよりも前記ディスクの周方向の長さのほうが大きい形状となる部分を含んで形成される孔であって、前記ディスクに前記回転軸側から前記ディスクの外側へ向かって形成される径方向通路と、
を備えることを特徴とするガスタービン。 - 前記径方向通路は前記回転軸を含む仮想平面に含まれない部分を備えることを特徴とする請求項1に記載のガスタービン。
- 前記径方向通路は、一方の開口端が前記ディスクの前記側周部よりも内側に形成される空間に開口し、他方の開口端が前記ディスクの前記側周部に開口すると共に、前記回転軸と直交する面に前記回転軸方向から投影されたときに、前記一方の開口端と前記回転軸とを含む基準仮想平面に対して10度以上45度以下の角度を有することを特徴とする請求項2に記載のガスタービン。
- 前記ディスクは所定の回転方向に向かって回転し、前記径方向通路は、前記一方の開口端部分において前記基準仮想平面を境に前記回転方向とは反対側の領域に傾いていることを特徴とする請求項3に記載のガスタービン。
- 回転軸を軸心とする曲面であって前記曲面上の全ての点から前記回転軸までの距離が全て等しい仮想曲面での断面において、前記回転軸と平行な方向の長さよりも前記ディスクの周方向の長さのほうが大きい形状となる部分を含んで形成される孔であって、前記ディスクに前記回転軸側から前記ディスクの外側へ向かって形成される径方向通路と、
を備えることを特徴とするディスク。 - ドリル刃が円盤状のディスクの回転軸を含む仮想平面と平行かつ、前記仮想平面から所定距離ずらされて設置されるボール盤に前記ディスクを取り付ける第1手順と、
前記ドリル刃を前記仮想平面と平行に移動させて前記ディスクに孔である1個目の径方向通路を形成する第2手順と、
前記ディスクを前記回転軸を軸に所定角度回転させる第3手順と、
前記ドリル刃を前記仮想平面と平行に移動させて前記ディスクに孔である2個目の径方向通路を形成する第4手順と、
前記第3手順と前記第4手順とを前記ディスクに所望の個数前記径方向通路が形成されるまで反復する第5手順と、
を備えることを特徴とするディスクの径方向通路形成方法。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US12/865,641 US20100326039A1 (en) | 2008-02-28 | 2008-12-24 | Gas turbine, disk, and method for forming radial passage of disk |
EP08872916.5A EP2246525B1 (en) | 2008-02-28 | 2008-12-24 | Gas turbine comprising a turbine disk and method for forming a radial passage of the turbine disk |
KR1020107017728A KR101318476B1 (ko) | 2008-02-28 | 2008-12-24 | 가스 터빈 및 디스크 그리고 디스크의 직경 방향 통로 형성 방법 |
CN2008801270316A CN101952555A (zh) | 2008-02-28 | 2008-12-24 | 燃气轮机及轮盘以及轮盘的径方向通路形成方法 |
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JP2008-048249 | 2008-02-28 | ||
JP2008048249A JP4981709B2 (ja) | 2008-02-28 | 2008-02-28 | ガスタービン及びディスク並びにディスクの径方向通路形成方法 |
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WO2009107312A1 true WO2009107312A1 (ja) | 2009-09-03 |
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PCT/JP2008/073483 WO2009107312A1 (ja) | 2008-02-28 | 2008-12-24 | ガスタービン及びディスク並びにディスクの径方向通路形成方法 |
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US (1) | US20100326039A1 (ja) |
EP (1) | EP2246525B1 (ja) |
JP (1) | JP4981709B2 (ja) |
KR (1) | KR101318476B1 (ja) |
CN (1) | CN101952555A (ja) |
WO (1) | WO2009107312A1 (ja) |
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US10113432B2 (en) * | 2014-03-19 | 2018-10-30 | Ansaldo Energia Switzerland AG | Rotor shaft with cooling bore inlets |
CN104454025B (zh) * | 2014-11-12 | 2015-11-18 | 中国科学院工程热物理研究所 | 一种用于高温旋转轮盘的冷却结构 |
KR101675269B1 (ko) | 2015-10-02 | 2016-11-11 | 두산중공업 주식회사 | 가스터빈 디스크 |
PL415045A1 (pl) * | 2015-12-03 | 2017-06-05 | General Electric Company | Tarcze turbiny i sposoby ich wytwarzania |
US10024170B1 (en) * | 2016-06-23 | 2018-07-17 | Florida Turbine Technologies, Inc. | Integrally bladed rotor with bore entry cooling holes |
WO2019066750A2 (en) * | 2017-05-23 | 2019-04-04 | Uyanik Talat | TURBINE COOLING FOR GAS TURBINE ENGINES |
CN108374692B (zh) * | 2018-01-25 | 2020-09-01 | 南方科技大学 | 一种涡轮轮盘及涡轮发动机 |
US10794190B1 (en) * | 2018-07-30 | 2020-10-06 | Florida Turbine Technologies, Inc. | Cast integrally bladed rotor with bore entry cooling |
JP7328794B2 (ja) | 2019-05-24 | 2023-08-17 | 三菱重工業株式会社 | ロータディスク、ロータ軸、タービンロータ、及びガスタービン |
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KR20100102211A (ko) | 2010-09-20 |
JP2009203926A (ja) | 2009-09-10 |
CN101952555A (zh) | 2011-01-19 |
EP2246525B1 (en) | 2017-08-09 |
EP2246525A4 (en) | 2013-05-01 |
KR101318476B1 (ko) | 2013-10-18 |
EP2246525A1 (en) | 2010-11-03 |
US20100326039A1 (en) | 2010-12-30 |
JP4981709B2 (ja) | 2012-07-25 |
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