WO2015128958A1 - 遠心式コンプレッサ、該遠心式コンプレッサを備えるターボチャージャ及び該遠心式コンプレッサの製造方法 - Google Patents
遠心式コンプレッサ、該遠心式コンプレッサを備えるターボチャージャ及び該遠心式コンプレッサの製造方法 Download PDFInfo
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- WO2015128958A1 WO2015128958A1 PCT/JP2014/054661 JP2014054661W WO2015128958A1 WO 2015128958 A1 WO2015128958 A1 WO 2015128958A1 JP 2014054661 W JP2014054661 W JP 2014054661W WO 2015128958 A1 WO2015128958 A1 WO 2015128958A1
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- Prior art keywords
- sleeve
- impeller
- mounting hole
- diameter
- axis
- Prior art date
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Classifications
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- 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
- F04D29/266—Rotors specially for elastic fluids mounting compressor rotors on shafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/16—Other safety measures for, or other control of, 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
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/051—Axial thrust balancing
- F04D29/0513—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
-
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/40—Application in turbochargers
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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
- F05D2230/50—Building or constructing in particular ways
-
- 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
-
- 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
- F05D2240/60—Shafts
-
- 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
- F05D2260/30—Retaining components in desired mutual position
-
- 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
- F05D2260/30—Retaining components in desired mutual position
- F05D2260/37—Retaining components in desired mutual position by a press fit connection
-
- 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
- F05D2260/96—Preventing, counteracting or reducing vibration or noise
-
- 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
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the present disclosure relates to a centrifugal compressor, a turbocharger including the centrifugal compressor, and a method for manufacturing the centrifugal compressor.
- a thrust bearing for receiving a thrust force of a drive shaft (turbine shaft) is provided.
- the thrust bearing has a collar (groove portion) fitted to the drive shaft, and the collar is driven by an impeller (compressor impeller) via another collar (sleeve portion) fitted to the drive shaft. It is pushed toward the stepped portion of the drive shaft with force.
- shrink fitting When fixing the impeller to the drive shaft, shrink fitting may be used as described in Patent Document 1.
- the drive shaft In shrink fitting, the drive shaft is inserted into the mounting hole of the heated impeller, and the impeller and the drive shaft come into close contact with each other at the engaging portion (clamp surface) in the process of lowering the temperature of the impeller.
- the engaging part of a drive shaft and an impeller is located in the back side of an impeller.
- the impeller contracts in the process of lowering the temperature of the heated impeller.
- the clamp surface of the impeller first comes into close contact with the shaft portion of the drive shaft, and then the impeller further contracts around the clamp surface in the axial direction of the mounting hole.
- the impeller further contracts around the clamp surface, if the clamp surface and the sleeve portion are adjacent to each other in the axial direction of the mounting hole, the sleeve portion is not separated from the impeller.
- the clamp surface may be separated from the sleeve portion in the axial direction of the mounting hole for convenience of design.
- the impeller contracts around the clamp surface, the axial force applied from the impeller to the sleeve portion is reduced. And if axial force falls, a vibration will generate
- an object of at least one embodiment of the present invention is to provide a centrifugal force in which an axial force applied to the sleeve portion from the shrink-fitted impeller is ensured even if the sleeve portion and the clamp surface are separated in the axial direction of the mounting hole. It is providing the type compressor, the turbocharger provided with this centrifugal compressor, and the manufacturing method of this centrifugal compressor.
- a centrifugal compressor according to at least one embodiment of the present invention, A housing; A hub rotatably disposed in the housing and having a mounting hole, and an impeller having a plurality of wings provided integrally with the hub; A drive shaft having a shaft portion extending inside the mounting hole of the impeller, a step portion spaced from the impeller, and an intermediate portion located between the shaft portion and the step portion; A fastening member screwed to the tip side of the shaft portion; At least one flange fitted to the intermediate portion; A thrust member which is fixedly arranged with respect to the housing and has a through-hole which is penetrated by the drive shaft and a thrust portion which is provided around the through-hole and comes into contact with the flange portion;
- the inner peripheral surface of the mounting hole includes a clamp surface that is brought into close contact with the shaft portion by shrink fitting, and a diameter-expanded surface
- the impeller When the impeller is attached to the drive shaft by shrink fitting, after the impeller contracts and the clamp surface comes into close contact with the shaft portion, the back side of the impeller contracts toward the contraction center position.
- the direction of the sleeve-side contact portion as viewed from the contraction center position can be expressed by an arctangent of d / L.
- the sleeve inclination angle ⁇ s is equal to or greater than the inverse tangent of d / L, the diameter-expanded surface of the impeller contracts away from the sleeve-side contact portion, and the axial force applied from the impeller to the sleeve portion decreases.
- the inverse tangent of d / L is larger than the sleeve inclination angle ⁇ s.
- the diameter-enlarged surface of the impeller contracts so as to be in close contact with the sleeve-side contact portion, and the axial force applied from the impeller to the sleeve portion can be increased.
- generation of vibration and noise is suppressed during operation of the centrifugal compressor.
- the impeller has a first positioning surface that is substantially orthogonal to the axis of the mounting hole, and one of the sleeve portion and the drive shaft is substantially orthogonal to the axis of the mounting hole. And a second positioning surface capable of coming into contact with the first positioning surface during the shrink fitting.
- the sleeve tilt angle ⁇ s is 30 ° or greater. If the sleeve inclination angle ⁇ s is 30 ° or more, a sufficiently large axial force can be applied in the axial direction of the drive shaft from the impeller side contact portion to the sleeve side contact portion.
- the difference between the atan (d / L) and the sleeve inclination angle ⁇ s is 20 ° or less. If the difference between the inverse tangent of d / L and the sleeve inclination angle ⁇ s is 20 ° or less, the contact pressure between the impeller side contact portion and the sleeve side contact portion becomes excessive when the back side of the impeller contracts. It is prevented. As a result, excessive stress is prevented from acting on the impeller and the sleeve portion.
- the diameter-expanded surface is a female tapered surface having a constant inclination with respect to the axis of the mounting hole
- the diameter-reduced surface is a male tapered surface having a constant inclination with respect to the axis of the mounting hole.
- the diameter-enlarged surface is a female tapered surface having a constant inclination with respect to the axis of the mounting hole
- the diameter-reduced surface is a curved surface with a change in inclination with respect to the axis of the mounting hole.
- the diameter-expanded surface is a female tapered surface
- the diameter-reduced surface is a curved surface
- the sleeve-side contact portion is configured by a part of the curved surface.
- the diameter-enlarging surface is a curved surface that changes in inclination with respect to the axis of the mounting hole
- the reduced-diameter surface is a male tapered surface having a constant inclination with respect to the axis of the mounting hole.
- the diameter-expanded surface is a curved surface
- the diameter-reduced surface is a male tapered surface
- the impeller-side contact portion is configured by a part of the curved surface.
- a turbocharger includes any one of the centrifugal compressors described above and a turbine having a turbine blade fixed to the drive shaft. According to this configuration, in the centrifugal compressor, the axial force applied from the impeller to the sleeve portion is secured by utilizing the contraction of the impeller, so that generation of vibration and noise is suppressed when the turbocharger is operated.
- a method for manufacturing a centrifugal compressor includes: A housing, a hub rotatably disposed in the housing and having an attachment hole, and an impeller having a plurality of blades provided integrally with the hub; a shaft portion extending through the attachment hole of the impeller; and the impeller A drive shaft having a stepped portion spaced apart and an intermediate portion located between the shaft portion and the stepped portion, a fastening member screwed to the distal end side of the shaft portion, and fitted to the intermediate portion
- a thrust member that has at least one flange portion, a through hole that is fixedly disposed with respect to the housing and that is penetrated by the drive shaft, and a thrust portion that is provided around the through hole and contacts the flange portion;
- a sleeve portion that is fitted to the intermediate portion and disposed between the flange portion and the impeller, and an inner peripheral surface of the mounting hole is a clamp surface that is brought into close contact with the shaft portion by shrink fitting.
- the diameter-expanded surface and the diameter-reduced surface each have an impeller-side contact portion and a sleeve-side contact portion that contact each other, and the axis of the mounting hole in the radial direction of the mounting hole
- the length from the sleeve side contact portion to the sleeve side contact portion is d
- the length from the sleeve side contact portion to the clamp surface in the axial direction of the mounting hole is L
- the sleeve side abutment against the reduced diameter surface When the angle at which the hypothetical conical bus line that contacts the contact part and the axis of the sleeve part intersect is defined as the sleeve inclination angle ⁇ s, the relationship represented by the following formula: ⁇ s ⁇ atan (d / L) is satisfied.
- the back side of the impeller contracts toward the contraction center position.
- the direction of the sleeve-side contact portion as viewed from the contraction center position can be expressed by an arctangent of d / L.
- the inverse tangent of d / L is larger than the sleeve inclination angle ⁇ s.
- the diameter-enlarged surface of the impeller contracts so as to be in close contact with the sleeve-side contact portion, and the axial force applied from the impeller to the sleeve portion can be increased.
- generation of vibration and noise is suppressed during operation of the centrifugal compressor.
- the impeller has a first positioning surface that is substantially orthogonal to the axis of the mounting hole, and one of the sleeve portion and the drive shaft is substantially orthogonal to the axis of the drive shaft. And the second positioning surface is brought into contact with the first positioning surface in the second inserting step.
- the impeller is provided with the first positioning surface, and one of the sleeve portion and the drive shaft is provided with the second positioning surface.
- the first positioning surface and the second positioning surface are orthogonal to the axis of the mounting hole and can contact each other, and the first positioning surface and the second positioning surface are in contact with each other, so that the drive shaft with respect to the mounting hole of the impeller It is possible to prevent the insertion amount from becoming larger than the design.
- the fastening step is performed before the temperature of the impeller is lowered to the ambient temperature.
- the centrifugal compressor can be mass-produced by performing the fastening process before the temperature of the impeller is lowered to the environmental temperature.
- the centrifugal compressor in which the axial force applied to the sleeve portion from the shrink-fitted impeller is ensured
- a turbocharger including the centrifugal compressor and a method for manufacturing the centrifugal compressor are provided.
- FIG. 1 is a longitudinal sectional view schematically showing a turbocharger according to some embodiments of the present invention. It is a figure for demonstrating the fixing structure of the impeller of the compressor with respect to a drive shaft. It is a perspective view which shows an impeller and a thrust sleeve roughly.
- FIG. 4 is an enlarged view of a region IV in FIG. 2. It is a flowchart which shows roughly the procedure of the fixing method of the impeller with respect to a drive shaft included in the manufacturing method of the compressor which concerns on some embodiment.
- FIG. 5 is an enlarged view corresponding to FIG. 4 of a compressor according to some embodiments.
- FIG. 5 is an enlarged view corresponding to FIG. 4 of a compressor according to some embodiments.
- FIG. 5 is an enlarged view corresponding to FIG. 4 of a compressor according to some embodiments.
- FIG. 5 is an enlarged view corresponding to FIG. 4 of a compressor according to some embodiments.
- FIG. 5 is an enlarged view corresponding to FIG. 4 of a compressor according to some embodiments.
- FIG. 5 is an enlarged view corresponding to FIG. 4 of a compressor according to some embodiments.
- FIG. 1 is a longitudinal sectional view schematically showing a turbocharger according to some embodiments of the present invention.
- the turbocharger is applied to an internal combustion engine such as a vehicle or a ship.
- the turbocharger has a turbine 10 and a centrifugal compressor 12.
- the turbine 10 includes a turbine housing 14 and a turbine blade (turbine impeller) 16 rotatably accommodated in the turbine housing 14, and the compressor 12 is rotatably accommodated in the compressor housing 18 and the compressor housing 18.
- Impeller (compressor impeller) 20 Impeller (compressor impeller) 20.
- the turbine housing 14 and the compressor housing 18 are fixed to the bearing housing 22 by a fastening member (not shown), and the turbine rotor blade 16 of the turbine 10 and the impeller 20 of the compressor 12 are driven in a drive shaft (turbine rotor) 24 that extends in the bearing housing 22.
- a drive shaft turbine rotor
- the turbine rotor blade 16 of the turbine 10 is rotated by, for example, exhaust gas discharged from the internal combustion engine, and thereby the impeller 20 of the compressor 12 is rotated via the drive shaft 24.
- the intake air supplied to the internal combustion engine is compressed by the rotation of the impeller 20 of the compressor 12.
- the turbine housing 14 includes a cylindrical portion (shroud portion) 28 that houses the turbine rotor blade 16 and a scroll portion 30 that surrounds a portion of the cylindrical portion 28 on the bearing housing 22 side.
- the scroll portion 30 has an exhaust gas inlet (not shown) and communicates with the cylindrical portion 28 via the throat portion 32.
- the opening of the cylindrical portion 28 on the side opposite to the bearing housing 22 forms an exhaust gas outlet.
- the end wall 34 of the bearing housing 22 is fitted into the opening of the turbine housing 14 on the bearing housing 22 side.
- a cylindrical seal portion 36 is integrally and coaxially provided on the end wall 34, and the seal portion 36 forms a seal hole that penetrates the center of the end wall 34.
- An end of the drive shaft 24 on the turbine blade 16 side is disposed in the seal portion 36, and a seal ring 38 is disposed in a gap between the drive shaft 24 and the seal portion 36.
- An annular back plate 40 is disposed in an annular recess between the end wall 34 and the rear surface of the turbine rotor blade 16.
- the outer peripheral portion of the back plate 40 is sandwiched between the turbine housing 14 and the bearing housing 22, and the inner peripheral edge of the back plate 40 surrounds the seal portion 36.
- a bearing portion 44 is provided integrally with the peripheral wall 42, and a bearing hole is formed in the bearing portion 44.
- two floating bushes 46 are disposed as radial bearings, and the central portion of the drive shaft 24 is disposed in the bearing hole of the bearing portion 44 in a state of passing through the floating bush 46.
- a plate-shaped thrust member 48 orthogonal to the axis 26 is fixed to the end face of the bearing portion 44 on the compressor 12 side, and the drive shaft 24 passes through the through hole of the thrust member 48.
- a thrust collar 50 and a thrust sleeve 52 are fitted to the drive shaft 24, and the thrust member 48, the thrust collar 50, and the thrust sleeve 52 constitute a thrust bearing.
- the peripheral wall 42 of the bearing housing 22 is provided with an oil supply port 54 and an oil discharge port 56, and the bearing portion 44 and the thrust member 48 are used for supplying lubricating oil to the bearing clearances of the radial bearing and the thrust bearing.
- An oil supply path is formed.
- an oil deflector 58 is installed so as to cover the surface of the thrust member 48 on the compressor 12 side in order to prevent the lubricating oil from scattering in the direction of the compressor 12.
- a lid member 60 having a seal hole in the center is fitted into the opening of the bearing housing 22 on the compressor 12 side, and the lid member 60 is fixed to the bearing housing 22 by a fixing ring 62.
- the thrust sleeve 52 passes through the seal hole of the lid member 60, and a seal ring (not shown) is disposed in the gap between the thrust sleeve 52 and the seal hole.
- cylinder portion 64 that houses the compressor housing 18 and the impeller 20, and a scroll portion 66 that surrounds a portion of the cylinder portion 64 on the bearing housing 22 side.
- the scroll portion 66 has an air supply outlet (not shown) and communicates with the cylindrical portion 64 via the diffuser portion 68.
- the opening of the cylindrical portion 64 opposite to the bearing housing 22 forms an intake inlet.
- FIG. 2 is a view for explaining a fixing structure of the impeller 20 of the compressor 12 with respect to the drive shaft 24.
- the impeller 20 includes a hub 70 and a plurality of wings 72.
- the hub 70 has a rotationally symmetric shape about the axis 26. In the direction along the axis 26, one end side of the hub 70 is located on the intake inlet side, and the other end side of the hub 70 is located on the diffuser portion 68 side.
- the outer peripheral surface 74 of the hub 70 has a trumpet shape that expands toward the other end side, and the hub 70 has a back surface 76 that faces the lid member 60 on the other end side.
- the hub 70 is provided with mounting holes 78 that pass through the hub 70 along the axis 26, and the mounting holes 78 are open at both ends of the hub 70.
- the plurality of blades 72 are integrally attached to the outer peripheral surface 74 of the hub 70, and are arranged at a predetermined interval in the circumferential direction of the hub 70.
- the plurality of blades 72 include a full blade 72a and a splitter blade 72b that is shorter than the full blade 72a in the direction along the axis 26, and the full blade 72a and the splitter blade 72b alternate in the circumferential direction. Placed in.
- the drive shaft 24 has a shaft portion 80, a large diameter portion 82, and an intermediate portion 84 that are integrally formed with each other.
- the shaft portion 80 extends inside the mounting hole 78 of the impeller 20, and the large diameter portion 82 is separated from the impeller 20.
- the intermediate portion 84 is located between the shaft portion 80 and the large diameter portion 82.
- the intermediate portion 84 has a smaller diameter than the large diameter portion 82, and a stepped portion 86 is formed at the boundary between the intermediate portion 84 and the large diameter portion 82.
- a female screw is formed on the tip side of the shaft portion 80 located on one end side of the impeller 20, and a nut as a fastening member 88 is screwed to the female screw.
- the fastening member 88 abuts on one end side of the impeller 20 and applies an axial force toward the stepped portion 86 in a direction along the axis 26 to the impeller 20.
- At least one flange 90 is fitted to the intermediate portion 84 of the drive shaft 24.
- the thrust collar 50 and the thrust sleeve 52 fitted in series with the intermediate portion 84 each have a flange 90.
- the thrust sleeve 52 has a sleeve portion 92 fitted to the intermediate portion 84, and the sleeve portion 92 is disposed between the flange portion 90 and the impeller 20.
- the through hole of the thrust member 48 is penetrated by the intermediate portion 84, and the thrust member 48 has a thrust portion 94 that is opposed to the flange portion 90 in the direction along the axis 26 around the through hole.
- the thrust member 48 has thrust portions 94 on both sides in the direction along the axis 26.
- the inner peripheral surface of the mounting hole 78 includes a clamp surface 96 and an enlarged diameter surface 98.
- the clamp surface 96 is brought into close contact with the shaft portion 80 by shrink fitting.
- the inner diameter of a part of the region is made small in the direction along the axis 26, so that the inner peripheral surface of the region constitutes the clamp surface 96.
- the region of the mounting hole 78 that faces the region constitutes a clamp surface. To do.
- FIG. 3 is a perspective view schematically showing the impeller 20 and the thrust sleeve 52.
- FIG. 4 is an enlarged view of region IV in FIG.
- the diameter-enlarged surface 98 is located on the thrust sleeve 52 side of the clamp surface 96 in the direction along the axis 26, that is, in the axial direction of the mounting hole 78, and the clamp surface It has an inner diameter that expands away from 96.
- the enlarged diameter surface 98 comprises a female tapered surface 98a.
- the outer peripheral surface of the sleeve portion 92 of the thrust sleeve 52 is provided with a reduced diameter surface 100 whose outer diameter decreases toward the impeller 20 in the axial direction of the mounting hole 78 as it approaches the clamp surface 96.
- the reduced diameter surface 100 comprises a male tapered surface 100a.
- the enlarged diameter surface 98 and the reduced diameter surface 100 have an impeller side contact portion 102 and a sleeve side contact portion 104 that contact each other.
- the length from the axis of the mounting hole 78 in the radial direction of the mounting hole 78 to the sleeve side abutting portion 104 is d, and the length from the sleeve side abutting portion 104 in the axial direction of the mounting hole 78 to the clamp surface.
- the angle at which the virtual conical generatrix G in contact with the reduced diameter surface 100 at the sleeve side contact portion 104 and the axis 26, that is, the axis of the sleeve portion 92 intersect, is defined as the sleeve inclination angle ⁇ s.
- ⁇ s ⁇ atan (d / L) (1) The relationship indicated by is satisfied.
- atan represents an arc tangent.
- the impeller-side contact portion 102 and the sleeve-side contact portion 104 are formed by surfaces (contact surfaces).
- the sleeve-side contact portion 104 serving as a base point of the length d and the length L is used.
- the position P is set at the center of the contact surface in the radial direction and the axial direction of the mounting hole 78.
- FIG. 5 is a flowchart schematically showing a procedure of a method for fixing the impeller 20 to the drive shaft 24 in the method for manufacturing the compressor 12 described above.
- the fixing method of the impeller 20 includes a first insertion step S10, a heating step S12, a second insertion step S14, a fastening step S16, and a cooling step S18.
- the drive shaft 24 is inserted into the through hole of the thrust member 48, the flange portion 90, the sleeve portion 92, and the like. That is, the drive shaft 24 is inserted into a part to be fitted before the impeller 20 is fixed to the drive shaft 24.
- the heating step S12 the impeller 20 is heated to a predetermined temperature. Thereby, the impeller 20 is thermally expanded, and the inner diameter of the mounting hole 78 is enlarged.
- the second insertion step S14 is performed after the first insertion step S10.
- 2nd insertion process S14 the axial part 80 is inserted in the attachment hole 78 of the impeller 20 heated by heating process S12.
- the fastening step S16 is performed after the second insertion step S14.
- the fastening member 88 is screwed to the tip side of the shaft portion 80. By screwing the fastening member 88, an axial force in the direction toward the stepped portion 86 is applied to the impeller 20.
- the cooling step S18 is performed after the second insertion step S14.
- the impeller 20 is forcibly cooled or naturally cooled to the environmental temperature.
- the inner diameter of the mounting hole 78 is reduced, and the clamp surface 96 comes into close contact with the shaft portion 80. Thereby, the impeller 20 is fixed to the drive shaft 24.
- the impeller 20 contracts and the clamp surface 96 comes into close contact with the shaft portion 80, and then the rear surface 76 of the impeller 20.
- the side contracts toward the contraction center position O (see FIG. 4).
- the direction of the sleeve-side contact portion 104 (position P) viewed from the contraction center position O, that is, the azimuth angle with respect to the axis 26 (hereinafter also referred to as impeller inclination angle ⁇ i) can be expressed by an arctangent of d / L. it can.
- the sleeve inclination angle ⁇ s is the inverse tangent of d / L, that is, the impeller inclination angle ⁇ i or more
- the diameter-expanded surface 98 of the impeller 20 contracts away from the sleeve-side contact portion 104, and the impeller 20 Therefore, the axial force applied to the sleeve portion 92 is reduced. Therefore, in the compressor 12 described above, the inverse tangent of d / L, that is, the impeller inclination angle ⁇ i is set to be larger than the sleeve inclination angle ⁇ s.
- the diameter-expanded surface 98 of the impeller 20 is further contracted so as to be in close contact with the sleeve-side contact portion 104, thereby increasing the axial force applied from the impeller 20 to the sleeve portion 92. be able to.
- the enlarged diameter surface 98 is a female tapered surface 98a having a constant inclination with respect to the axis of the mounting hole 78
- the reduced diameter surface 100 is from a male tapered surface having a constant inclination with respect to the axis of the mounting hole 78.
- the taper angle of the female taper surface 98a and the male taper surface 100a that is, the sleeve inclination angle ⁇ s is set to 45 °
- the length d is set to be longer than the length L.
- the above formula (1) can be satisfied with a simple configuration. Specifically, if the change amount (shrinkage amount) ⁇ d of the length d is larger than the change amount (shrinkage amount) ⁇ L of the length L and the sleeve inclination angle ⁇ s is 45 °, the sleeve is cooled even after the impeller 20 is cooled. The impeller side contact portion 102 is not separated from the side contact portion 104.
- FIG. 6 is an enlarged view corresponding to FIG. 4 of the compressor 12 according to some embodiments.
- the impeller 20 has a first positioning surface 106 that is substantially orthogonal to the axis of the mounting hole 78, and the sleeve portion 92 is relative to the axis of the mounting hole 78.
- a second positioning surface 108 that is substantially orthogonal and capable of contacting the first positioning surface 106 during shrink fitting is provided.
- the drive shaft 24 is inserted into the mounting hole 78 of the impeller 20 in the second insertion step S14.
- the diameter-expanded surface 98 may be pushed and expanded by the diameter-reduced surface 100, and the insertion amount of the drive shaft 24 with respect to the impeller 20 may be larger than the design.
- an annular first positioning surface 106 is formed inside the mounting hole 78, and an annular second positioning surface 108 is formed at the tip of the sleeve portion 92.
- the first positioning surface 106 is continuous with the small diameter end of the diameter-expanded surface 98, and the second positioning surface 108 is continuous with the small diameter end of the diameter-reduced surface 100. According to this configuration, the first positioning surface 106 and the second positioning surface 108 can be provided with a simple configuration.
- FIG. 7 is an enlarged view corresponding to FIG. 4 of the compressor 12 according to some embodiments.
- an annular first positioning surface 110 is formed on a part of the rear surface 76 of the impeller 20, and an annular portion is formed in the flange portion protruding radially outward from the sleeve portion 92.
- a second positioning surface 112 is formed.
- the first positioning surface 110 is continuous with the large diameter end of the enlarged diameter surface 98, and the second positioning surface 112 is continuous with the large diameter end of the reduced diameter surface 100. According to this configuration, the first positioning surface 110 and the second positioning surface 112 can be provided with a simple configuration.
- FIG. 8 is an enlarged view corresponding to FIG. 4 of the compressor 12 according to some embodiments.
- an annular first positioning surface 114 is formed inside the mounting hole 78, and a second positioning surface 116 is formed on the drive shaft 24.
- the first positioning surface 114 and the second positioning surface 116 are located away from the tip of the sleeve portion 92. According to this configuration, the first positioning surface 114 and the second positioning surface 116 can be provided with a simple configuration.
- FIG. 9 is an enlarged view corresponding to FIG. 4 of the compressor 12 according to some embodiments.
- the diameter-expanded surface 98 is a female tapered surface 98 a having a constant inclination with respect to the axis of the mounting hole 78, and the diameter-reduced surface 100 is relative to the axis of the mounting hole 78.
- the diameter-expanded surface 98 is a female tapered surface 98a
- the diameter-reduced surface 100 is a curved surface 100b
- the sleeve-side contact portion 104 is formed by a part of the curved surface 100b. Composed.
- FIG. 10 is an enlarged view corresponding to FIG. 4 of the compressor 12 according to some embodiments.
- the diameter-expanded surface 98 includes a curved surface 98 b whose inclination with respect to the axis of the attachment hole 78 changes, and the diameter-reduced surface 100 is inclined with respect to the axis of the attachment hole 78. Consists of a constant male tapered surface 100a.
- the diameter-expanded surface 98 is a curved surface 98b
- the diameter-reduced surface 100 is a male tapered surface
- the impeller side contact portion 102 is configured by a part of the curved surface 98b.
- the sleeve inclination angle ⁇ s is 30 ° or greater. If the sleeve inclination angle ⁇ s is 30 ° or more, an axial force having a sufficient magnitude in the direction along the axis 26 from the impeller side contact portion 102 to the sleeve side contact portion 104, that is, in the axial direction of the drive shaft 24. Can act.
- the difference between the d / L arctangent or impeller tilt angle ⁇ i and the sleeve tilt angle ⁇ s is 20 ° or less. If the difference between the inverse tangent of d / L and the sleeve inclination angle ⁇ s is 20 ° or less, the contact pressure between the impeller side contact portion 102 and the sleeve side contact portion 104 when the back 76 side of the impeller 20 contracts. Is prevented from becoming excessive. As a result, excessive stress is prevented from acting on the impeller 20 and the sleeve portion 92. In some embodiments, the d / L arctangent or impeller tilt angle ⁇ i is less than 90 °.
- the fastening step S16 is performed before the temperature of the impeller 20 decreases to the environmental temperature.
- mass production of the compressor 12 can be performed by performing fastening process S16 before the temperature of the impeller 20 falls to environmental temperature.
- the present invention is not limited to the above-described embodiments, and includes forms obtained by changing the above-described embodiments and combinations of these forms as appropriate.
- the thrust sleeve 52 in which the sleeve portion 92 and the flange portion 90 are integrated is used, but the sleeve portion 92 and the flange portion 90 may be separate.
- the components constituting the sleeve portion 92 are not limited to the thrust sleeve 52, but are fitted to the drive shaft 24 and abut against the impeller 20 to transmit the axial force toward the step portion 86. I just need it.
- the shaft portion 80, the large diameter portion 82, and the intermediate portion 84 are integrally formed.
- the shaft portion 80 and the intermediate portion 84 are stud bolts that are separate from the large diameter portion 82. Etc. may be formed.
- the step portion 86 may be formed by a retaining ring or the like fitted to the intermediate portion 84.
- the fastening step S16 is performed before the temperature of the impeller 20 is lowered to the environmental temperature. However, after the temperature of the impeller 20 is lowered to the environmental temperature, the fastening member 88 is increased. An additional tightening step for tightening may be further provided.
- the centrifugal compressor may be a variable displacement type.
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Abstract
Description
ハウジングと、
前記ハウジング内に回転可能に配置され、取付孔を有するハブ及び該ハブと一体に設けられた複数の翼を有するインペラと、
前記インペラの取付孔の内部を延びる軸部、前記インペラから離間した段差部、及び、前記軸部と前記段差部の間に位置する中間部を有する駆動軸と、
前記軸部の先端側に螺合された締結部材と、
前記中間部に嵌合された少なくとも1つの鍔部と、
前記ハウジングに対し固定して配置され、前記駆動軸によって貫通される貫通孔及び前記貫通孔の周囲に設けられて前記鍔部と当接するスラスト部を有するスラスト部材と、
前記中間部に嵌合され、前記鍔部と前記インペラの間に配置されたスリーブ部と、を備える遠心式コンプレッサにおいて、
前記取付孔の内周面は、焼き嵌めによって前記軸部に密着させられたクランプ面と、前記取付孔の軸線方向にて前記クランプ面から離れるほど内径が拡大する拡径面とを含み、
前記スリーブ部の外周面は、前記取付孔の軸線方向にて前記クランプ面に近づくほど外径が縮小する縮径面を含み、
前記拡径面及び前記縮径面は、相互に当接するインペラ側当接部及びスリーブ側当接部をそれぞれ有し、
前記取付孔の径方向における前記取付孔の軸線から前記スリーブ側当接部までの長さをdとし、
前記取付孔の軸線方向における前記スリーブ側当接部から前記クランプ面までの長さをLとし、
前記縮径面に対し前記スリーブ側当接部にて接する仮想的な円錐の母線と前記スリーブ部の軸線とが交差する角度をスリーブ傾斜角θsとしたとき、次式:
θs<atan(d/L)
で示される関係が満たされている。
これに対し、上述した実施形態の構成では、スリーブ傾斜角θsよりもd/Lの逆正接が大きい。このため、インペラの拡径面がスリーブ側当接部に密着するように収縮し、インペラからスリーブ部に加えられる軸力を増大させることができる。この結果として、遠心式コンプレッサの作動時、振動及び騒音の発生が抑制される。
これに対し上述した実施形態の構成では、インペラの取付孔に軸部を挿入したときに、第1位置決め面が第2位置決め面に対し当接することで、インペラの取付孔に対する駆動軸の挿入量が設計よりも大きくなることを防止することができる。
スリーブ傾斜角θsが30°以上であれば、インペラ側当接部からスリーブ側当接部に対し、駆動軸の軸線方向にて十分な大きさの軸力を作用させることができる。
d/Lの逆正接とスリーブ傾斜角θsの差が20°以下であれば、インペラの背面側が収縮したときに、インペラ側当接部とスリーブ側当接部の間の接触圧が過大になることが防止される。この結果として、インペラやスリーブ部に対し過大な応力が作用することが防止される。
この構成によれば、拡径面及び縮径面が雌テーパ面及び雄テーパ面からそれぞれなるので、加工が容易である。
この構成では、拡径面が雌テーパ面からなり、縮径面が湾曲面からなり、スリーブ側当接部が湾曲面の一部によって構成される。このため、インペラ側当接部とスリーブ側当接部との間の接触面圧が局所的に高くなることが防止され、インペラが円滑に収縮することができる。この結果、インペラに局所的な応力が作用することが防止され、インペラの耐久性が向上する。
この構成では、拡径面が湾曲面からなり、縮径面が雄テーパ面からなり、インペラ側当接部が湾曲面の一部によって構成される。このため、インペラ側当接部とスリーブ側当接部との間の接触面圧が局所的に高くなることが防止され、インペラが円滑に収縮することができる。この結果、インペラに局所的な応力が作用することが防止され、インペラの耐久性が向上する。
この構成によれば、遠心式コンプレッサにおいて、インペラの収縮を利用してインペラからスリーブ部に加わる軸力が確保されるので、ターボチャージャの作動時に振動や騒音の発生が抑制される。
ハウジングと、前記ハウジング内に回転可能に配置され、取付孔を有するハブ及び該ハブと一体に設けられた複数の翼を有するインペラと、前記インペラの取付孔の内部を延びる軸部、前記インペラから離間した段差部、及び、前記軸部と前記段差部の間に位置する中間部を有する駆動軸と、前記軸部の先端側に螺合された締結部材と、前記中間部に嵌合された少なくとも1つの鍔部と、前記ハウジングに対し固定して配置され、前記駆動軸によって貫通される貫通孔及び前記貫通孔の周囲に設けられて前記鍔部と当接するスラスト部を有するスラスト部材と、前記中間部に嵌合され、前記鍔部と前記インペラの間に配置されたスリーブ部と、を備え、前記取付孔の内周面は、焼き嵌めによって前記軸部に密着させられたクランプ面と、前記取付孔の軸線方向にて前記クランプ面から離れるほど内径が拡大する拡径面とを含み、前記スリーブ部の外周面は、前記取付孔の軸線方向にて前記クランプ面に近づくほど外径が縮小する縮径面を含み、前記拡径面及び前記縮径面は、相互に当接するインペラ側当接部及びスリーブ側当接部をそれぞれ有し、前記取付孔の径方向における前記取付孔の軸線から前記スリーブ側当接部までの長さをdとし、前記取付孔の軸線方向における前記スリーブ側当接部から前記クランプ面までの長さをLとし、前記縮径面に対し前記スリーブ側当接部にて接する仮想的な円錐の母線と前記スリーブ部の軸線とが交差する角度をスリーブ傾斜角θsとしたとき、次式:θs<atan(d/L)で示される関係が満たされている、遠心式コンプレッサの製造方法であって、
前記スラスト部材の前記貫通孔、前記鍔部及び前記スリーブ部に前記駆動軸を挿入する第1挿入工程と、
前記インペラを加熱する加熱工程と、
前記第1挿入工程の後、前記加熱工程で加熱された前記インペラの取付孔に前記軸部を挿入する第2挿入工程と、
前記第2挿入工程の後、前記軸部の先端側に締結部材を螺合する締結工程と
を備える。
これに対し、上述した実施形態の構成では、スリーブ傾斜角θsよりもd/Lの逆正接が大きい。このため、インペラの拡径面がスリーブ側当接部に密着するように収縮し、インペラからスリーブ部に加えられる軸力を増大させることができる。この結果として、遠心式コンプレッサの作動時、振動及び騒音の発生が抑制される。
上述した実施形態の構成では、インペラに第1位置決め面が設けられ、スリーブ部及び駆動軸のうち一方に第2位置決め面が設けられている。第1位置決め面及び第2位置決め面は取付孔の軸線と直交し且つ相互に当接可能であり、第1位置決め面と第2位置決め面とが当接することで、インペラの取付孔に対する駆動軸の挿入量が設計よりも大きくなることを防止することができる。
この構成によれば、インペラの温度が環境温度まで低下するよりも前に締結工程を行うことで、遠心式コンプレッサを大量生産可能である。
ターボチャージャは、タービン10と、遠心式のコンプレッサ12とを有する。タービン10は、タービンハウジング14と、タービンハウジング14内に回転可能に収容されたタービン動翼(タービンインペラ)16とを有し、コンプレッサ12は、コンプレッサハウジング18と、コンプレッサハウジング18に回転可能に収容されたインペラ(コンプレッサインペラ)20とを有する。
インペラ20は、ハブ70と、複数の翼72とからなる。ハブ70は、軸線26の回りに回転対称な形状を有する。軸線26に沿う方向にて、ハブ70の一端側は吸気の入口側に位置し、ハブ70の他端側はディフューザ部68側に位置している。ハブ70の外周面74は他端側に向かって拡大するラッパ形状を有し、ハブ70は他端側に蓋部材60と対向する背面76を有する。
また、スラストスリーブ52は、中間部84に嵌合されたスリーブ部92を有し、スリーブ部92は、鍔部90とインペラ20の間に配置されている。
図2及び図3に示したように、拡径面98は、軸線26に沿う方向にて、即ち取付孔78の軸線方向にて、クランプ面96よりもスラストスリーブ52側に位置し、クランプ面96から離れるほど拡大する内径を有する。幾つかの実施形態では、拡径面98は雌テーパ面98aからなる。
拡径面98及び縮径面100は、相互に当接するインペラ側当接部102及びスリーブ側当接部104をそれぞれ有する。
θs<atan(d/L)・・・(1)
で示される関係が満たされている。式(1)中、atanは逆正接(アークタンジェント)を表す。
インペラ20の固定方法は、第1挿入工程S10、加熱工程S12、第2挿入工程S14、締結工程S16及び冷却工程S18を有する。
加熱工程S12では、インペラ20が所定の温度まで加熱される。これによりインペラ20は熱膨張し、取付孔78の内径が拡大される。
締結工程S16は第2挿入工程S14の後に行われる。締結工程S16では、軸部80の先端側に締結部材88が螺合される。締結部材88を螺合することによって、インペラ20に対し、段差部86に向かう方向の軸力が加えられる。
そこで、上述したコンプレッサ12では、スリーブ傾斜角θsよりも、d/Lの逆正接即ちインペラ傾斜角θiが大きくなるように設定される。この設定によれば、クランプ面96の密着後、インペラ20の拡径面98がスリーブ側当接部104に密着するように更に収縮し、インペラ20からスリーブ部92に加えられる軸力を増大させることができる。
幾つかの実施形態では、図6に示したように、インペラ20は、取付孔78の軸線に対し略直交する第1位置決め面106を有し、スリーブ部92は、取付孔78の軸線に対し略直交し且つ焼き嵌めの際に第1位置決め面106に対し当接可能な第2位置決め面108を有する。
これに対し上述した実施形態の構成では、インペラ20の取付孔78に軸部80を挿入したときに、第1位置決め面106が第2位置決め面108に当接することで、インペラ20の取付孔78に対する駆動軸24の挿入量が設計よりも大きくなることを防止することができる。
幾つかの実施形態では、図7に示したように、インペラ20の背面76の一部に環状の第1位置決め面110が形成され、スリーブ部92から径方向外側に張り出した鍔部に環状の第2位置決め面112が形成される。第1位置決め面110は、拡径面98の大径端に連なり、第2位置決め面112は、縮径面100の大径端に連なっている。この構成によれば、簡単な構成にて、第1位置決め面110と第2位置決め面112を設けることができる。
幾つかの実施形態では、図8に示したように、取付孔78の内部に環状の第1位置決め面114が形成され、駆動軸24に第2位置決め面116が形成されている。第1位置決め面114及び第2位置決め面116は、スリーブ部92の先端から離れた位置にある。この構成によれば、簡単な構成にて、第1位置決め面114と第2位置決め面116を設けることができる。
幾つかの実施形態では、図9に示したように、拡径面98は、取付孔78の軸線に対する傾きが一定の雌テーパ面98aからなり、縮径面100は、取付孔78の軸線に対する傾きが変化する湾曲面100bからなる
この構成では、拡径面98が雌テーパ面98aからなり、縮径面100が湾曲面100bからなり、スリーブ側当接部104が湾曲面100bの一部によって構成される。このため、インペラ側当接部102とスリーブ側当接部104との間の接触面圧が局所的に高くなることが防止され、インペラ20が円滑に収縮することができる。この結果、インペラ20に局所的な応力が作用することが防止され、インペラ20の耐久性が向上する。
幾つかの実施形態では、図10に示したように、拡径面98は、取付孔78の軸線に対する傾きが変化する湾曲面98bからなり、縮径面100は、取付孔78の軸線に対する傾きが一定の雄テーパ面100aからなる。
この構成では、拡径面98が湾曲面98bからなり、縮径面100が雄テーパ面からなり、インペラ側当接部102が湾曲面98bの一部によって構成される。このため、インペラ側当接部102とスリーブ側当接部104との間の接触面圧が局所的に高くなることが防止され、インペラ20が円滑に収縮することができる。この結果、インペラ20に局所的な応力が作用することが防止され、インペラ20の耐久性が向上する。
幾つかの実施形態では、d/Lの逆正接即ちインペラ傾斜角θiは90°未満である。
この構成によれば、インペラ20の温度が環境温度まで低下するよりも前に締結工程S16を行うことで、コンプレッサ12を大量生産することができる。
例えば、上述した幾つかの実施形態では、スリーブ部92と鍔部90が一体のスラストスリーブ52が用いられていたが、スリーブ部92と鍔部90は別体であってもよい。更に、スリーブ部92を構成する部品は、スラストスリーブ52に限定されることはなく、駆動軸24に嵌合されるとともにインペラ20に当接し、軸力を段差部86に向けて伝達するものであればよい。
上述した幾つかの実施形態では、インペラ20の温度が環境温度まで低下するよりも前に締結工程S16が行われていたが、インペラ20の温度が環境温度に低下した後に、締結部材88を増し締めする増し締め工程を更に設けてもよい。
更に、遠心式コンプレッサは可変容量タイプであってもよい。
12 コンプレッサ
14 タービンハウジング
16 タービン動翼
18 コンプレッサハウジング
20 インペラ
22 軸受ハウジング
24 駆動軸
26 軸線
28 筒部
30 スクロール部
32 スロート部
34 端壁
36 シール部
38 シールリング
40 バックプレート
42 周壁
44 軸受部
46 浮動ブッシュ
48 スラスト部材
50 スラストカラー
52 スラストスリーブ
54 給油ポート
56 排油ポート
58 オイルデフレクタ
60 蓋部材
62 固定リング
64 筒部
66 スクロール部
68 ディフューザ部
70 ハブ
72 翼
72a フルブレード
72b スプリッタブレード
74 外周面
76 背面
78 取付孔
80 軸部
82 大径部
84 中間部
86 段差部
88 締結部材
90 鍔部
92 スリーブ部
94 スラスト部
96 クランプ面
98 拡径面
98a 雌テーパ面
98b 湾曲面
100 縮径面
100a 雄テーパ面
100b 湾曲面
102 インペラ側当接部
104 スリーブ側当接部
106,110,114 第1位置決め面
108,112,116 第2位置決め面
Claims (11)
- ハウジングと、
前記ハウジング内に回転可能に配置され、取付孔を有するハブ及び該ハブと一体に設けられた複数の翼を有するインペラと、
前記インペラの取付孔の内部を延びる軸部、前記インペラから離間した段差部、及び、前記軸部と前記段差部の間に位置する中間部を有する駆動軸と、
前記軸部の先端側に螺合された締結部材と、
前記中間部に嵌合された少なくとも1つの鍔部と、
前記ハウジングに対し固定して配置され、前記駆動軸によって貫通される貫通孔及び前記貫通孔の周囲に設けられて前記鍔部と当接するスラスト部を有するスラスト部材と、
前記中間部に嵌合され、前記鍔部と前記インペラの間に配置されたスリーブ部と、
を備える遠心式コンプレッサにおいて、
前記取付孔の内周面は、焼き嵌めによって前記軸部に密着させられたクランプ面と、前記取付孔の軸線方向にて前記クランプ面から離れるほど内径が拡大する拡径面とを含み、
前記スリーブ部の外周面は、前記取付孔の軸線方向にて前記クランプ面に近づくほど外径が縮小する縮径面を含み、
前記拡径面及び前記縮径面は、相互に当接するインペラ側当接部及びスリーブ側当接部をそれぞれ有し、
前記取付孔の径方向における前記取付孔の軸線から前記スリーブ側当接部までの長さをdとし、
前記取付孔の軸線方向における前記スリーブ側当接部から前記クランプ面までの長さをLとし、
前記縮径面に対し前記スリーブ側当接部にて接する仮想的な円錐の母線と前記スリーブ部の軸線とが交差する角度をスリーブ傾斜角θsとしたとき、次式:
θs<atan(d/L)
で示される関係が満たされている
ことを特徴とする遠心式コンプレッサ。 - 前記インペラは、前記取付孔の軸線に対し略直交する第1位置決め面を有し、
前記スリーブ部及び前記駆動軸のうち一方は、前記取付孔の軸線に対し略直交し且つ前記焼き嵌めの際に前記第1位置決め面に対し当接可能な第2位置決め面を有する
ことを特徴とする請求項1に記載の遠心式コンプレッサ。 - 前記スリーブ傾斜角θsは30°以上である
ことを特徴とする請求項1又は2に記載の遠心式コンプレッサ。 - 前記atan(d/L)と前記スリーブ傾斜角θsの差は20°以下である
ことを特徴とする請求項1乃至3の何れか一項に記載の遠心式コンプレッサ。 - 前記拡径面は、前記取付孔の軸線に対する傾きが一定の雌テーパ面からなり、
前記縮径面は、前記取付孔の軸線に対する傾きが一定の雄テーパ面からなる
ことを特徴とする請求項1乃至4の何れか一項に記載の遠心式コンプレッサ。 - 前記拡径面は、前記取付孔の軸線に対する傾きが一定の雌テーパ面からなり、
前記縮径面は、前記取付孔の軸線に対する傾きが変化する湾曲面からなる
ことを特徴とする請求項1乃至4の何れか一項に記載の遠心式コンプレッサ。 - 前記拡径面は、前記取付孔の軸線に対する傾きが変化する湾曲面からなり、
前記縮径面は、前記取付孔の軸線に対する傾きが一定の雄テーパ面からなる
ことを特徴とする請求項1乃至4の何れか一項に記載の遠心式コンプレッサ。 - 請求項1乃至7の何れか一項に記載の遠心式コンプレッサと、
前記駆動軸に固定されたタービン動翼を有するタービンと
を備えることを特徴とするターボチャージャ。 - ハウジングと、前記ハウジング内に回転可能に配置され、取付孔を有するハブ及び該ハブと一体に設けられた複数の翼を有するインペラと、前記インペラの取付孔の内部を延びる軸部、前記インペラから離間した段差部、及び、前記軸部と前記段差部の間に位置する中間部を有する駆動軸と、前記軸部の先端側に螺合された締結部材と、前記中間部に嵌合された少なくとも1つの鍔部と、前記ハウジングに対し固定して配置され、前記駆動軸によって貫通される貫通孔及び前記貫通孔の周囲に設けられて前記鍔部と当接するスラスト部を有するスラスト部材と、前記中間部に嵌合され、前記鍔部と前記インペラの間に配置されたスリーブ部と、を備え、前記取付孔の内周面は、焼き嵌めによって前記軸部に密着させられたクランプ面と、前記取付孔の軸線方向にて前記クランプ面から離れるほど内径が拡大する拡径面とを含み、前記スリーブ部の外周面は、前記取付孔の軸線方向にて前記クランプ面に近づくほど外径が縮小する縮径面を含み、前記拡径面及び前記縮径面は、相互に当接するインペラ側当接部及びスリーブ側当接部をそれぞれ有し、前記取付孔の径方向における前記取付孔の軸線から前記スリーブ側当接部までの長さをdとし、前記取付孔の軸線方向における前記スリーブ側当接部から前記クランプ面までの長さをLとし、前記縮径面に対し前記スリーブ側当接部にて接する仮想的な円錐の母線と前記スリーブ部の軸線とが交差する角度をスリーブ傾斜角θsとしたとき、次式:θs<atan(d/L)で示される関係が満たされている、遠心式コンプレッサの製造方法であって、
前記スラスト部材の前記貫通孔、前記鍔部及び前記スリーブ部に前記駆動軸を挿入する第1挿入工程と、
前記インペラを加熱する加熱工程と、
前記第1挿入工程の後、前記加熱工程で加熱された前記インペラの取付孔に前記軸部を挿入する第2挿入工程と、
前記第2挿入工程の後、前記軸部の先端側に締結部材を螺合する締結工程と
を備えることを特徴とする遠心式コンプレッサの製造方法。 - 前記インペラは、前記取付孔の軸線に対し略直交する第1位置決め面を有し、
前記スリーブ部及び前記駆動軸のうち一方は、前記駆動軸の軸線に対し略直交する第2位置決め面を有し、
前記第2挿入工程において、前記第1位置決め面に対し前記第2位置決め面が当接させられる
ことを特徴とする請求項9に記載の遠心式コンプレッサの製造方法。 - 前記加熱工程の後、前記インペラの温度が環境温度まで低下する前に前記締結工程が行われることを特徴とする請求項9又は10に記載の遠心式コンプレッサの製造方法。
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