EP3211241B1 - Impulseur, et machine tournante - Google Patents

Impulseur, et machine tournante Download PDF

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Publication number
EP3211241B1
EP3211241B1 EP15865836.9A EP15865836A EP3211241B1 EP 3211241 B1 EP3211241 B1 EP 3211241B1 EP 15865836 A EP15865836 A EP 15865836A EP 3211241 B1 EP3211241 B1 EP 3211241B1
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EP
European Patent Office
Prior art keywords
impeller
reinforcing ring
impeller body
back surface
axis
Prior art date
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Application number
EP15865836.9A
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German (de)
English (en)
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EP3211241A1 (fr
EP3211241A4 (fr
Inventor
Yasunori Watanabe
Ryoji Okabe
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Publication of EP3211241A1 publication Critical patent/EP3211241A1/fr
Publication of EP3211241A4 publication Critical patent/EP3211241A4/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/02—Selection of particular materials
    • F04D29/023—Selection of particular materials especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • 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
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/60—Properties or characteristics given to material by treatment or manufacturing
    • F05D2300/603—Composites; e.g. fibre-reinforced

Definitions

  • the invention relates to an impeller provided in a rotary machine, and a rotary machine including an impeller.
  • Turbochargers are rotary machines that can enhance effects of fuel efficiency improvement and CO 2 reduction by sending compressed air into an engine to combust fuel compared to natural intake engines.
  • a turbine In the turbochargers, a turbine is rotationally driven with exhaust gas of an engine, thereby rotating an impeller of a centrifugal compressor. The air compressed by the rotation of the impeller is raised in pressure by being reduced in speed by a diffuser, and is supplied to the engine through a scroll flow passage.
  • methods for driving the turbochargers not only methods of being driven with exhaust gas but also, for example, methods using electric motors, methods using prime movers, and the like are known.
  • an impeller using a complex material (hereinafter referred to as a resin) of synthetic resins, such as carbon fiber reinforced plastic, is known as described in, for example, PTL 1.
  • a resin impeller has low rigidity compared to a metallic impeller, and if the resin impeller rotates, the amount of deformation thereof becomes large under the influence of a centrifugal force. For this reason, a boss hole into which a rotating shaft is fitted may be increased in diameter, and rotation balance may be impaired.
  • the impeller is formed of the resin in a case where the metallic ring is used, the materials of the impeller and the ring are different from each other. Therefore, the metallic ring has a larger coefficient of linear expansion than the impeller made of the resin. As a result, there are possibilities that, depending on operation conditions, a stress generated in the impeller cannot be distributed to the ring and the deformation of the impeller cannot be suppressed. Additionally, since the density of the metal is high compared to the resin, the diameter of the ring itself may be increased due to the influence of a centrifugal force, deformation of the impeller cannot be suppressed, and it is difficult to guarantee the reliability of the impeller.
  • a refrigerant or coolant compressor of the radial type with an impeller having a plurality of vane elements that can be used for compressing water vapor as a refrigerant or coolant under vacuum conditions.
  • the impeller includes vane elements, disk elements, vane support elements and a hub.
  • the vane elements are individually connected to the hub by the support elements.
  • the support elements maybe either ring-shaped elements connecting a rear surface of the disk elements to the hub, or may be pin-shaped insert members connecting the root of each vane element to the hub.
  • the components of the impeller are made of a polymer composite material reinforced preferably with carbon fibers.
  • reference document US 2008/0286113 A1 relates to a high speed type impeller, including: a body having a shaft coupling hole into which a rotation shaft of a motor is coupled, the outer circumference of the body being widened from the top to bottom end in the insertion direction of the rotation shaft to form a bent surface; a plurality of blades installed on the bent surface of the body to be bent at a predetermined angle to the rotation shaft direction; and a reinforcing ring installed on a back surface of the impeller body.
  • the invention provides an impeller and a rotary machine that can guarantee reliability even if resin materials are used.
  • an impeller according to claim 1 is provided.
  • the reinforcing ring is formed of the resin and the reinforcing fibers, the material of the impeller body and the material of the reinforcing ring become substantially the same. For this reason, a difference between the coefficients of linear expansion of the impeller body and the reinforcing ring becomes small. As a result, the constraint force of the impeller body can be inhibited from decreasing due to an increase in the diameter of the reinforcing ring caused by thermal expansion. Moreover, since the density of the resin is low, the constraint force of the impeller body can be inhibited from decreasing by the diameter of the reinforcing ring being increased due to a centrifugal force.
  • the reinforcing ring includes reinforcing fibers, rigidity can be improved, the constraint force of the impeller body can be inhibited from decreasing due to a diameter increase caused by the centrifugal force of the reinforcing ring itself. Therefore, a centrifugal force that acts on the impeller body can be distributed to the reinforcing ring, the stress of the impeller body caused by the centrifugal force can be reduced, and it is possible to suppress deformation of the entire impeller.
  • the step section in the above first aspect may be formed at a position of 2/3 of a diameter dimension between the rotation center axis and an outer peripheral end of the impeller body from the rotation center axis.
  • the reinforcing ring is provided at the position of 2/3 of the radial dimension of the impeller body from the central axis of the impeller body.
  • the step section in the above first aspect may be formed such that the center of the reinforcing ring in a radial direction is located at a position that is larger than 0.1 times a diameter dimension between the rotation center axis and an outer peripheral end of the impeller body from the rotation center axis and is smaller than the diameter dimension.
  • the step section is formed at such a position, the stress of the impeller body caused by a centrifugal force can be reduced more effectively, and deformation of the entire impeller can be suppressed.
  • the impeller body in the above first aspect may be provided with a boss part that protrudes from the back surface and has the rotating shaft fitted thereto, and the step section may be formed at the boss part.
  • the reinforcing ring is provided at the boss part provided in the impeller body. Accordingly, a stress caused by a centrifugal force at the boss part can be reduced, and deformation of the entire impeller can be suppressed.
  • a width dimension of the reinforcing ring in a radial direction and a blade thickness dimension of the blades in the circumferential direction in the first to fourth aspects may be the same, and a thickness dimension of the reinforcing ring in a direction of the rotation center axis may be larger than the width dimension of the reinforcing ring in the radial direction.
  • the reinforcing ring is formed with such a dimension, the stress of the impeller body caused by a centrifugal force can be reduced more effectively, and deformation of the entire impeller can be suppressed.
  • the reinforcing ring in the first to fifth aspects may be disposed such that the reinforcing fibers extend in the circumferential direction of the impeller body.
  • the impeller may further include a second reinforcing ring that is disposed in the circumferential direction of the impeller body inside the impeller body in the first to seventh aspects and forms an annular shape.
  • the rigidity of the impeller body can be further improved. Additionally, since the second reinforcing ring is disposed inside the impeller body, slip-out from the impeller body can be suppressed even if a material having a different coefficient of linear expansion from the impeller body is used. Therefore, a centrifugal force that acts on the impeller body can be distributed to the second reinforcing ring, a stress generated in the impeller body due to the centrifugal force can be further reduced, and deformation of the entire impeller can be suppressed.
  • a rotary machine includes the impeller in the above first to eighth aspects; and a rotating shaft that is attached to the impeller and rotates together with the impeller.
  • the constraint force of the impeller body can be inhibited from decreasing. Therefore, a centrifugal force that acts on the impeller body can be distributed to the reinforcing ring, and a stress generated in the impeller body due to the centrifugal force can be reduced.
  • the reinforcing ring is provided.
  • resin materials are used, it is possible to guarantee reliability.
  • turbocharger 1 rotary machine
  • the turbocharger 1 includes a rotating shaft 2, a turbine 3 and a compressor 4 that rotate together with the rotating shaft 2, and a housing coupling part 5 that couples the turbine 3 and the compressor 4 and supports the rotating shaft 2.
  • a turbine 3 is rotated with exhaust gas G from an engine (not illustrated), and air AR compressed by the compressor 4 is supplied to the engine with the rotation.
  • the rotating shaft 2 extends in a direction of an axis O.
  • the rotating shaft 2 rotates about the axis O.
  • the turbine 3 is disposed on one side (the right side of Fig. 1 ) in the direction of the axis O.
  • the turbine 3 includes a turbine impeller 14 that has the rotating shaft 2 attached thereto and has a turbine blade 15, and a turbine housing 11 that covers the turbine impeller 14 from an outer peripheral side.
  • the rotating shaft 2 is fitted into the turbine impeller 14.
  • the turbine impeller 14 is rotatable around the axis O together with the rotating shaft 2.
  • the turbine housing 11 covers the turbine impeller 14.
  • the turbine impeller 14 and the rotating shaft 2 are rotated by the exhaust gas G being introduced into the turbine impeller 14 from the scroll passage 12.
  • a discharge port 13 opening to one side of the axis O is formed in the turbine housing 11.
  • the exhaust gas G that has passed through the turbine blade 15 flows toward one side of the axis O, and is discharged from the discharge port 13 to the outside of the turbine housing 11.
  • the compressor 4 is disposed on the other side (the left side of Fig. 1 ) in the direction of the axis O.
  • the compressor 4 includes a compressor impeller 24 that has the rotating shaft 2 attached thereto and has a compressor blade 25, and a compressor housing 21 that covers the compressor impeller 24 from the outer peripheral side.
  • the rotating shaft 2 is fitted into the compressor impeller 24.
  • the compressor impeller 24 is rotatable around the axis O together with the rotating shaft 2.
  • the compressor housing 21 covers the compressor impeller 24.
  • a suction port 23 opening to the other side of the axis O is formed in the compressor housing 21.
  • the air AR is introduced from the outside of the compressor housing 21 through the suction port 23 into the compressor impeller 24. Then, by a rotative force from the turbine impeller 14 being transmitted to the compressor impeller 24 via the rotating shaft 2, the compressor impeller 24 rotates around the axis O and the air AR is compressed.
  • the air AR compressed by the compressor impeller 24 is introduced to the compressor passage 22, and is discharged to the outside of the compressor housing 21.
  • the housing coupling part 5 is disposed between the compressor housing 21 and the turbine housing 11 to couple these housings.
  • the housing coupling part 5 covers the rotating shaft 2 from the outer peripheral side.
  • the housing coupling part 5 is provided with a bearing 6.
  • the rotating shaft 2 is supported by the bearing 6 so as to become rotatable relative to the housing coupling part 5.
  • the compressor impeller 24 includes a plurality of the compressor blades 25, an impeller body 31 that supports the compressor blades 25 on a hub surface 31a formed on a front surface side, and a reinforcing ring 41 fitted to a back surface 32 of the impeller body 31.
  • the plurality of compressor blades 25 are provided apart from each other in a circumferential direction of the rotating shaft 2 and the impeller body 31.
  • a flow passage FC through which the air AR flows is formed between the compressor blades 25 that are adjacent to each other in the circumferential direction.
  • the compressor blades 25 are formed of a resin in the present embodiment.
  • resins used for the compressor blades 25 for example, polyether sulfone (PES), polyether imide (PEI), polyether ether ketone (PEEK), polyether ketone (PEK), polyether ketone ketone (PEKK), poly ketone sulfide (PKS), polyaryl ether ketone (PAEK), aromatic polyamide (PA), polyamide imide (PAI), polyimide (PI), and the like are exemplified.
  • compressor blades 25 are not limited to the case where the compressor blades are a resin, and may be made of a metal or the like.
  • the impeller body 31 forms a disk-like shape and supports the compressor blades 25 on the front surface side, that is, the compressor blades 25 on the other side in the direction of the axis O so as to protrude from the hub surface 31a.
  • the impeller body 31 is made of the same resin as that of the above-described compressor blades 25.
  • a step section 36 having a fitting surface 37 that faces the outer peripheral side (radial outer side) is formed on the back surface 32 of the impeller body 31, that is, a surface on one side in the direction of the axis O.
  • a boss hole section 31b having the rotating shaft 2 inserted therethrough and fitted thereinto is formed in a region on a radial inner side in the impeller body 31.
  • the step section 36 is formed so as to be recessed annularly about the axis O from the back surface 32 of the impeller body 31 toward the other side in the direction of the axis O, and splits the back surface 32 into a first back surface 32A located on the radial outer side and a second back surface 32B located on the radial inner side.
  • the first back surface 32A and the second back surface 32B are formed in a radial direction.
  • the fitting surface 37 is disposed between the first back surface 32A and the second back surface 32B, and the step section 36 is formed on the back surface 32 by connecting the first back surface 32A and the second back surface 32B.
  • the second back surface 32B is inclined so as to face one side in the direction of the axis O while being curved in a concave shape to the other side in the direction of the axis O as it becomes closer to the radial inner side, and is continuous with the boss hole section 31b after being bent so as to run in the radial direction from a halfway position.
  • the fitting surface 37 in this step section 36 is formed at a position of 2/3 of a diameter dimension R between the axis O and an outer peripheral end (an end part on the outermost side in the radial direction) of the impeller body 31 from the axis O that becomes a rotation center axis of the impeller body 31.
  • the reinforcing ring 41 forms an annular shape, and is fitted to the step section 36 of the impeller body 31 from the outer peripheral side. That is, fitting to the step section 36 is made as an inner peripheral surface thereof contacts the fitting surface 37 in the step section 36.
  • the reinforcing ring 41 is formed in a shape and a size such that, in a state where the reinforcing ring 41 is fitted, the center of the reinforcing ring 41 coincides with the axis O and the reinforcing ring 41 is smoothly continuous with the second back surface 32B of the impeller body 31.
  • the shape of a cross-section including the axis O forms a rectangular shape, the thickness dimension in the direction of the axis O coincides with the length dimension of the fitting surface 37, and the width dimension in the radial direction is larger than the thickness dimension in the direction of the axis O.
  • the reinforcing ring 41 is formed of the same resin as that of the compressor blades 25 and the impeller body 31 and further reinforcing fibers. That is, the reinforcing ring 41 is formed of a complex material (carbon fiber reinforced plastic) consisting of resin and carbon fibers, in the present embodiment.
  • the reinforcing fibers in the reinforcing ring 41 are not limited to the carbon fibers, and may be glass fibers, Whisker, and the like.
  • the reinforcing ring 41 may be provided so as to be fitted into the impeller body 31 by insert molding, or may be provided by recoating the fitting surface 37 in the step section 36 with a fiber reinforcing resin.
  • the reinforcing ring 41 of the compressor impeller 24 is formed of the complex material including the resin, the material of the reinforcing ring 41 and the material of the impeller body 31 become substantially the same. For this reason, a difference between the coefficients of linear expansion of the impeller body 31 and the reinforcing ring 41 becomes small. As a result, the constraint force of the impeller body 31 can be inhibited from decreasing due to an increase in the diameter of the reinforcing ring 41 caused by thermal expansion.
  • the density of the resin is low compared to the metal or the like. For this reason, the constraint force of the impeller body 31 can be inhibited from decreasing by the diameter of the reinforcing ring 41 being increased due to a centrifugal force.
  • the reinforcing ring 41 includes the carbon fibers as the reinforcing resin, the rigidity thereof can be improved. For this reason, the constraint force of the impeller body 31 can be inhibited from decreasing due to a diameter increase caused by the centrifugal force of the reinforcing ring 41 itself.
  • the step section 36 of the impeller body 31 is formed at the position of 2/3 of the diameter dimension R between the axis O and the outer peripheral end of the impeller body 31 from the axis O that becomes the rotation center axis of the impeller body 31.
  • the reinforcing ring 41 is provided at the position of 2/3 of the diameter dimension R of the impeller body 31 from the rotation center axis of the impeller body 31.
  • an end part position on the other side of the axis O that becomes a side into which the air AR flows is set as 0, and an end part position on one side of the axis O that becomes a side from which the air AR flows is set as 1.0.
  • the formation range of the compressor blades 25 is about 0.3 to 0.8.
  • a thickness dimension b of the reinforcing ring 41 in the direction of the axis O is 0.03 times the thickness of the impeller body 31 in the direction of the axis O and a width dimension a of the reinforcing ring 41 in the radial direction is 0.03 times the external diameter dimension of the impeller body 31.
  • the fitting surface 37 in this step section 36 is not limited to a case where the fitting surface is formed at the position of 2/3 of the diameter dimension R of the impeller body 31 from the rotation center axis (axis O) of the impeller body 31.
  • the fitting surface has only to be formed a position closer to the axis O than the position of 2/3 of the radial dimension.
  • the step section 36 maybe formed so as to be larger than 0.1 times the diameter dimension R between the rotation center axis of the impeller body 31 and the outer peripheral end of the impeller body 31 from the rotation center axis (axis O) of the impeller body 31 and such that the center of the reinforcing ring 41 in the radial direction is located at a position smaller than the diameter dimension R. That is, in a case where a distance between the center of the reinforcing ring 41 in the radial direction and the axis O is defined as h, the reinforcing ring 41 maybe provided so as to satisfy 0.1R ⁇ h ⁇ 1.0R.
  • the turbocharger 50 of the present embodiment is different from the first embodiment in the shape of a compressor impeller 51.
  • the compressor impeller 51 is provided with a boss part 53 that protrudes from a back surface of an impeller body 52 to one side in the direction of the axis O.
  • the impeller body 52 forms substantially the same shape substantially as the impeller body 31 of the first embodiment, and is made of the above-described resin.
  • a back surface 54 of the impeller body 52 extends in the radial direction, and is curved smoothly toward one side in the direction of the axis O as it becomes closer to the radial inner side.
  • the boss part 53 is formed integrally with the impeller body 52 at a position on the radial inner side in the impeller body 52, and forms an annular shape about the axis O.
  • a boss hole section 53a that is continuous with the boss hole section 31b is formed at the boss part 53.
  • the rotating shaft 2 is fitted to the boss hole section 53a.
  • the boss part 53 has a fitting surface 57 that faces the radial outer side.
  • the fitting surface 57 is smoothly continuous with the curved back surface 54 of the impeller body 52. Accordingly, the fitting surface 57 is formed in a rounded shape that is smoothly curved toward one side in the direction of the axis O so as to run in the direction of the axis O as it becomes closer to the radial inner side.
  • a reinforcing ring 61 is fitted to the boss part 53. That is, in the present embodiment, a step section 56 having the fitting surface 57 is formed at the boss part 53, and the reinforcing ring 61 is fitted to the step section 56.
  • the shape of a cross-section including the axis O does not form a rectangular shape, and the shape of this cross-section is such that the inner peripheral surface 65 that faces the radial inner side becomes a curved surface that forms a convex shape toward the axis O.
  • the shape of this curved surface corresponds to the curved shape of the fitting surface 57.
  • an outer peripheral surface 66 that extends substantially parallel to the axis O continuously with the inner peripheral surface 65, which becomes the above curved surface, and faces the radial outer side
  • an axial surface 67 that connects the inner peripheral surface 65 and the outer peripheral surface 66 together, is orthogonal to the axis O, and faces one side in the direction of the axis O are formed in the reinforcing ring 61.
  • the material of the reinforcing ring 61 and the material of the impeller body 52 become substantially the same. For this reason, a difference between the coefficients of linear expansion of the impeller body 52 and the reinforcing ring 61 becomes small. As a result, the constraint force of the impeller body 52 can be inhibited from decreasing due to an increase in the diameter of the reinforcing ring 61 caused by thermal expansion. Additionally, since the density of the resin is low compared to the metal or the like, the constraint force of the impeller body 52 can be inhibited from decreasing by the diameter of the reinforcing ring 61 being increased due to a centrifugal force.
  • the reinforcing ring 61 includes the carbon fibers as the reinforcing resin, the constraint force of the impeller body 52 can be inhibited from decreasing by a diameter increase caused by the centrifugal force of the reinforcing ring 61 itself, and even if the resin is used for the impeller body 52, it is possible to sufficiently suppress deformation.
  • the thickness dimension of the reinforcing ring 61 in the direction of the axis O is 0.15 times the thickness of the impeller body 31 in the direction of the axis O and the width dimension of the reinforcing ring 61 in the radial direction is 0.05 times the external diameter of the impeller body 31.
  • the other analysis conditions are the same as those illustrated in Fig. 3 in the first embodiment.
  • the compressor impeller 24 (or the compressor impeller 51 of the second embodiment) of the first embodiment further includes a second reinforcing ring 71.
  • An annular groove part 75 of the rotating shaft 2 that is recessed to the radial outer side and runs in the circumferential direction is formed in an inner peripheral surface of the boss hole section 31b.
  • annular groove part 75 an inside groove part 75a that opens to the inner peripheral surface of the boss hole section 31b, extends to the radial outer side, and forms a rectangular shape as the shape of a cross-section including the axis O, and an outside groove part 75b that communicates with the inside groove part 75a, extends to the radial outer side, and forms a rectangular shape, which protrudes to both sides of the axis O from the inside groove part 75a, as the shape of a cross-section including the axis O are formed.
  • the annular groove part 75 has a T-shaped cross-section.
  • the second reinforcing ring 71 is disposed inside the annular groove part 75 of the impeller body 31.
  • the second reinforcing ring 71 has a base part 72 that has a rectangular cross-section corresponding to the inside groove part 75a and forms an annular shape in the circumferential direction of the impeller body 31, and an engaging part 63 that extends to both sides in the direction of the axis O from the base part 72, on the radial outer side closer to the inside of the impeller body 31 than the base part 72 continuously with the base part 72.
  • the second reinforcing ring 71 is disposed without a gap inside the annular groove part 75.
  • the base part 72 is exposed to the inner peripheral surface of the boss hole section 31b and is flush with the inner peripheral surface.
  • the second reinforcing ring 71 forms an annular shape about the axis O and has a T-shaped cross-section, in a state where the second reinforcing ring is disposed inside the impeller body 31.
  • the second reinforcing ring 71 is formed of a complex material including a thermosetting resin and reinforcing fibers.
  • a thermosetting resin similar to the reinforcing ring 41, carbon fibers, glass fibers, Whisker, and the like can be used.
  • thermosetting resin phenol resins, epoxy resins, melamine resins, silicon resins, and the like can be used.
  • the second reinforcing ring 71 may be formed of metallic materials, such as aluminum, instead of the complex material.
  • the second reinforcing ring 71 is provided to be fitted into the impeller body 31, for example by insert molding.
  • the rigidity of the impeller body 31 can be improved by disposing the second reinforcing ring 71 inside the impeller body 31 made of the resin in the compressor impeller 24. Additionally, since the second reinforcing ring 71 is disposed inside the impeller body 31, slip-out from the impeller body 31 can be suppressed even if a material having a different coefficient of linear expansion from the impeller body 31 is used. Therefore, a centrifugal force that acts on the impeller body 31 can be distributed to the second reinforcing ring 71, a stress generated in the impeller body 31 due to the centrifugal force can be reduced, and it is possible to suppress deformation of the entire compressor impeller 24.
  • the second reinforcing ring 71 has the base part 72, and an engaging part 73 continuous with the base part 72, when a tensile force acts on the impeller body 31 to the radial outer side due to the centrifugal force in a case where the impeller body 31 has rotated, the engaging part 73 is caught inside the impeller body 31, so that the centrifugal force that acts on the impeller body 31 can be firmly distributed to the second reinforcing ring 71. Therefore, it is possible to further reduce the stress generated in the impeller body 31, and deformation of the impeller body 31 can be suppressed.
  • the second reinforcing ring 71 is formed of the complex material including the thermosetting resin and the reinforcing fibers, and thereby the coefficient of linear expansion of the complex material is small compared to metals, slackening of the second reinforcing ring 71 with respect to the impeller body 31 due to thermal expansion does not easily occur. Therefore, a centrifugal force that acts on the impeller body 31 can be effectively distributed to the second reinforcing ring 71, and it is possible to further reduce a stress generated in the impeller body 31.
  • the rigidity of the second reinforcing ring 71 itself becomes high. Therefore, deformation does not easily occur when a centrifugal force has acts, and slackening of the second reinforcing ring 71 with respect to the impeller body 31 does not easily occur. Therefore, a centrifugal force that acts on the impeller body 31 can be effectively distributed to the second reinforcing ring 71, and a stress generated in the impeller body 31 can be further reduced.
  • the second reinforcing ring 71A may have a christmas tree-shaped cross-section.
  • the second reinforcing ring 71A has a curved engaging surface 80 that is an outer surface that is curved so as to protrude toward the impeller body 31.
  • the concentration of a stress generated in the impeller body 31 can be suppressed at a position where the second reinforcing ring 71A and the impeller body 31 contact each other. For this reason, further suppression of deformation or damage of the impeller body 31 is possible by the curved engaging surface 80.
  • the shapes of the second reinforcing rings 71 and 71A are not limited.
  • the second reinforcing rings 71 and 71A may be disposed at a position in the direction of the axis O where a stress generated in the impeller body 31 reaches a maximum.
  • the second reinforcing rings 71 and 71A are not exposed to the inner peripheral surface of the boss hole section 31b, and may be completely embedded inside the impeller body 31.
  • sectional shapes of the reinforcing rings 41 and 61 is not limited are not limited to the cases of the above-described embodiments.
  • a circular cross-sectional shape and the like may be adopted.
  • the thickness dimension (the thickness dimension in the circumferential direction) of the compressor blades 25 may be the same as the width dimension a (refer to Fig. 2 ) of the reinforcing ring 41 (61) in the radial direction.
  • the thickness dimension b (refer to Fig. 2 ) of the reinforcing ring 41 (61) in the direction of the axis O may be larger than the width dimension a in the radial direction.
  • the reinforcing fibers may be disposed so as to extend in the circumferential direction of the rotating shaft 2.
  • compressor blades 25 and the impeller body 31 (52) may include the same reinforcing fibers as the reinforcing ring 41 (61) in addition to the resin.
  • turbocharger As the above-described embodiments, as the rotary machine, the turbocharger has been described as an example. However, the invention may be used for other centrifugal compressors and the like.
  • the reinforcing ring is provided.
  • resin materials are used, it is possible to guarantee reliability.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Supercharger (AREA)

Claims (8)

  1. Une roue à aubes comprenant :
    un corps de roue à aubes (31) qui est formé d'une résine, présente une forme semblable à un disque, et tourne autour d'un axe central de rotation (O) en même temps qu'un arbre tournant (2) ;
    une pluralité d'aubes (25) disposées sur une surface avant du corps de roue à aubes ; et
    une bague de renfort (41) qui est formée sur une surface arrière (32) du corps de roue à aubes (31) et est formée d'une résine et de fibres de renfort, et qui présente une forme annulaire dans une direction circonférentielle du corps de roue à aubes (31),
    caractérisée en ce que la bague de renfort (41) est ajustée pour venir en contact avec une surface d'ajustement (37) d'une section étagée (36) à partir du côté périphérique externe, la section étagée (36) ayant la surface d'ajustement (37) tournée vers un côté périphérique externe,
    la section étagée (36) sépare la surface arrière (32) en une première surface arrière (32A) située d'un côté radialement externe et en une seconde surface arrière (32B) située d'un côté radialement interne, et
    la surface d'ajustement (37) est disposée entre la première surface arrière (32A) et la seconde surface arrière (32B), et
    la seconde surface arrière (32B) est inclinée de manière à rapprocher un côté de l'axe central de rotation (O) opposé à un orifice d'aspiration (23) lorsque la seconde surface arrière (32B) est plus proche du côté interne radial, tout en étant courbée avec une forme concave tournée vers l'autre côté.
  2. La roue à aubes selon la revendication 1,
    dans laquelle la section étagée (36) est formée en une position située aux 2/3 d'une dimension diamétrale entre l'axe central de rotation (O) et une extrémité périphérique externe du corps de roue à aubes (31) par rapport à l'axe central de rotation (O).
  3. La roue à aubes selon la revendication 1,
    dans laquelle la section étagée (36) est formée de telle manière que le centre de la bague de renfort (41) dans une direction radiale est situé en une position qui soit plus grande que 0,1 fois une dimension diamétrale entre l'axe central de rotation (O) et une extrémité périphérique externe du corps de roue à aubes (31) par rapport à l'axe central de rotation (O), et soit inférieure à la dimension diamétrale.
  4. La roue à aubes selon la revendication 1,
    dans laquelle le corps de roue à aubes (31) est pourvu d'une partie proéminente (53) qui fait saillie depuis la surface arrière (32) et à laquelle est ajusté l'arbre tournant (2), et
    dans laquelle la section étagée (36) est formée au niveau de la partie proéminente (53).
  5. La roue à aubes selon l'une des revendications 1 à 4,
    dans laquelle une dimension en largeur de la bague de renfort (41) dans une direction radiale et une dimension d'épaisseur d'aube des aubes (25) dans la direction circonférentielle sont les mêmes, et une dimension en épaisseur de la bague de renfort (41) dans une direction de l'axe central de rotation (O) est supérieure à la dimension en largeur de la bague de renfort (41) dans la direction radiale.
  6. La roue à aubes selon l'une des revendications 1 à 5,
    dans laquelle la bague de renfort (41) est disposée de telle manière que les fibres de renfort s'étendent dans la direction circonférentielle du corps de roue à aubes (31).
  7. La roue à aubes selon l'une des revendications 1 à 6, comprenant en outre :
    une seconde bague de renfort (71, 71A), qui est disposée dans la direction circonférentielle du corps de roue à aubes (31) à l'intérieur du corps de roue à aubes (31) et qui présente une forme annulaire.
  8. Une machine tournante (1) comprenant :
    la roue à aubes selon l'une des revendications 1 à 7 ; et
    un arbre tournant (2) qui est solidaire de la roue à aubes et qui tourne en même temps que la roue à aubes.
EP15865836.9A 2014-12-03 2015-10-09 Impulseur, et machine tournante Active EP3211241B1 (fr)

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JP2014245157A JP6288516B2 (ja) 2014-12-03 2014-12-03 インペラ、及び回転機械
PCT/JP2015/078778 WO2016088451A1 (fr) 2014-12-03 2015-10-09 Impulseur, et machine tournante

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JP6919220B2 (ja) * 2017-02-22 2021-08-18 株式会社Ihi 遠心圧縮機
DE112019006752T5 (de) * 2019-03-14 2021-11-04 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Kompressorradvorrichtung und lader
DE102019006665A1 (de) * 2019-09-23 2021-03-25 KSB SE & Co. KGaA Einschaufelrad

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CN107002705A (zh) 2017-08-01
JP2016108986A (ja) 2016-06-20
EP3211241A1 (fr) 2017-08-30
EP3211241A4 (fr) 2017-11-22
CN107002705B (zh) 2019-03-08
US20170328372A1 (en) 2017-11-16
WO2016088451A1 (fr) 2016-06-09
JP6288516B2 (ja) 2018-03-07

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