WO2015128978A1 - 浮動ブッシュ軸受装置、及び、該軸受装置を備えるターボチャージャ - Google Patents
浮動ブッシュ軸受装置、及び、該軸受装置を備えるターボチャージャ Download PDFInfo
- Publication number
- WO2015128978A1 WO2015128978A1 PCT/JP2014/054802 JP2014054802W WO2015128978A1 WO 2015128978 A1 WO2015128978 A1 WO 2015128978A1 JP 2014054802 W JP2014054802 W JP 2014054802W WO 2015128978 A1 WO2015128978 A1 WO 2015128978A1
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- WIPO (PCT)
- Prior art keywords
- floating bush
- peripheral surface
- circumferential groove
- regions
- hole
- Prior art date
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/1045—Details of supply of the liquid to the bearing
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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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
- F01D25/166—Sliding contact bearing
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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
- F02B33/00—Engines characterised by provision of pumps for charging or scavenging
- F02B33/32—Engines with pumps other than of reciprocating-piston type
- F02B33/34—Engines with pumps other than of reciprocating-piston type with rotary pumps
- F02B33/40—Engines with pumps other than of reciprocating-piston type with rotary pumps of non-positive-displacement type
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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
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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
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/14—Lubrication of pumps; Safety measures therefor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
- F16C17/18—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with floating brasses or brushing, rotatable at a reduced speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/1075—Wedges, e.g. ramps or lobes, for generating pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/1085—Channels or passages to recirculate the liquid in the bearing
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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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2240/00—Components
- F05D2240/50—Bearings
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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
- F05D2260/98—Lubrication
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/23—Gas turbine engines
- F16C2360/24—Turbochargers
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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
- 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 floating bush bearing device and a turbocharger including the bearing device.
- a turbocharger for an automobile includes a turbine and a compressor, and turbine blades of the turbine and an impeller of the compressor are connected via a rotor shaft.
- the rotor shaft is rotatably supported by a radial bearing that supports a radial load.
- the radial bearing described in Patent Document 1 is a floating bush bearing, and the floating bush bearing has a floating bush fitted to the rotor shaft with a gap.
- the floating bush is disposed in the bearing hole, and an oil passage (oil supply hole) is opened on the inner peripheral surface of the bearing hole.
- the floating bush has a plurality of communication holes for lubricating oil that pass through the floating bush diagonally in the radial direction, and the lubricating oil supplied into the bearing hole through the oil supply hole passes through the communication hole for lubricating oil in the floating bush. Flows into the inside.
- the central region of the outer peripheral surface of the floating bush where the lubricating oil communication hole opens is formed as a concave surface, and by this concave surface, a circumferential groove having a constant width over the entire circumference is formed in the outer peripheral surface of the floating bush. Is formed.
- an object of at least one embodiment of the present invention is to provide a floating bush that suppresses vibration by providing a pressing force against the floating bush by lubricating oil while providing a circumferential groove on the entire outer periphery of the floating bush.
- a bearing device and a turbocharger including the bearing device are provided.
- a floating bush bearing device includes: A casing having a bearing hole; A rotating shaft rotatably disposed in the bearing hole; A floating bush disposed rotatably in the bearing hole and surrounding the rotation shaft; An oil supply hole for lubricating oil that opens to the inner peripheral surface of the bearing hole; A plurality of communication holes formed in the floating bush, each extending between an inner peripheral surface and an outer peripheral surface of the floating bush, and arranged at intervals in a circumferential direction of the floating bush; It is formed on the outer peripheral surface of the floating bush or the inner peripheral surface of the bearing hole and passes through the openings of the plurality of communication holes or faces the openings of the plurality of communication holes, A circumferential groove extending over the entire circumference of the inner peripheral surface of the bearing hole, The circumferential groove has a different cross-sectional area depending on the circumferential position.
- the cross-sectional area of the circumferential groove differs depending on the circumferential position, and the cross-sectional area is relatively small at one or more portions. Since the cross-sectional area of the one or more portions is relatively small, the flow of the lubricating oil in the circumferential groove is suppressed, and the pressure drop of the lubricating oil in the vicinity of the opening of the oil supply hole is suppressed. As a result, the floating bush can be pressed in one direction by the lubricating oil supplied from the oil supply hole. On the other hand, according to this configuration, there is a portion where the cross-sectional area is relatively narrow, while there is a portion where the cross-sectional area is relatively large.
- the lubricating oil is temporarily stored in the portion where the cross-sectional area is large, so that a sufficient amount of lubricating oil is supplied to the inside of the floating bush through the communication hole even if there is a portion where the cross-sectional area is small. be able to.
- the circumferential groove is formed on an outer peripheral surface of the floating bush;
- the circumferential groove includes a plurality of first regions that overlap positions and openings of the plurality of communication holes in a circumferential direction of the floating bush, and a plurality of second regions that respectively extend between the plurality of first regions.
- Have A cross-sectional area of each of the plurality of first regions is larger than a cross-sectional area of each of the plurality of second regions.
- the circumferential groove is formed on an inner peripheral surface of the bearing hole,
- the circumferential groove includes a plurality of first regions provided corresponding to the intervals between the plurality of communication holes in a circumferential direction of the bearing hole, and a plurality of second regions extending between the plurality of first regions, respectively.
- a cross-sectional area of each of the plurality of first regions is larger than a cross-sectional area of each of the plurality of second regions.
- the width of each of the plurality of first regions is greater than the width of each of the plurality of second regions. According to this configuration, by making the width of the first region larger than the width of the second region, the cross-sectional area of the first region can be easily made larger than the cross-sectional area of the second region.
- the width of each of the plurality of first regions is in the range of 0.9 to 1.3 times the width of each of the plurality of communication holes, At least one of the plurality of first regions includes a portion where the circumferential groove has a maximum width, The width of each of the plurality of second regions is in the range of 0.2 to 0.4 times the maximum width of the circumferential groove.
- the width of the first region is in the range of 0.9 to 1.3 times the width of each communication hole, a sufficient amount of lubricating oil can be stored in the first region.
- the width of the second region is 0.2 to 0.4 times the maximum width of the circumferential groove, the flow of the lubricating oil in the circumferential direction can be reliably regulated in the second region. .
- the plurality of first regions are each formed by a plurality of recesses
- the opening shape of each of the plurality of recesses is any one of a circle, an ellipse, and a rectangle. According to this configuration, since the opening shape of the first region is a circle, an ellipse, or a rectangle, the first region can be easily formed.
- the cross-sectional area of one portion of the circumferential groove is substantially equal to the cross-sectional area of the other portion 180 ° opposite the one portion. According to this structure, it is prevented that the weight balance of the floating bush is lost due to the formation of the circumferential groove whose width changes according to the circumferential position, and the occurrence of vibration due to the formation of the circumferential groove is prevented. be able to.
- the depth of each of the plurality of first regions is deeper than the depth of each of the plurality of second regions. According to this configuration, by making the depth of the first region larger than the depth of the second region, the cross-sectional area of the first region can be easily made larger than the cross-sectional area of the second region. Further, according to this configuration, the depth of the first region is relatively deeper than that of the second region, thereby inducing a flow of the lubricating oil toward the communication hole, and more effectively supplying the lubricating oil to the floating bush. Can be fed inside.
- the circumferential groove width is substantially constant;
- the maximum depth of the circumferential groove is not more than 50 times the radial clearance between the outer peripheral surface of the floating bush and the inner peripheral surface of the bearing hole,
- the minimum depth of the circumferential groove is in the range of 2 to 3 times the radial gap.
- the maximum depth of the circumferential groove is set to 50 times or less of the radial gap, and the minimum depth of the circumferential groove is set to a range of 2 to 3 times the radial gap.
- the cross-sectional area of the downstream region connected to the downstream side of the communication hole in the rotation direction of the floating bush is closer to the communication hole in the circumferential direction of the floating bush. It is expanding.
- the cross-sectional area of the downstream region increases as it approaches the communication hole, and when the lubricating oil is supplied from the oil supply hole when the floating bush is stopped, the lubricating oil is communicated from the downstream region to the communication hole.
- a rotational force is applied to the floating bush by the lubricating oil. Therefore, if the lubricating oil is supplied at the start of rotation of the rotating shaft, the rotation start of the floating bush can be assisted by the rotational force from the lubricating oil.
- the bottom surface of the downstream region connected to the communication hole is formed by an inclined surface inclined with respect to the outer peripheral surface,
- the inclined surface is inclined so that the depth of the circumferential groove becomes deeper toward the communication hole in the circumferential direction of the floating bush. According to this configuration, the cross-sectional area of the downstream region can be easily enlarged toward the communication hole by forming the bottom surface of the downstream region connected to the communication hole with the inclined surface.
- the inner peripheral surface of the floating bush has a Rouleau polygonal shape in a cross section orthogonal to the axis of the floating bush.
- the vibration stability can be increased compared to the case where the inner peripheral surface of the floating bush has a perfect circular shape in cross section, Bearing loss can be reduced.
- the inner peripheral surface of the floating bush has a Roule polygonal shape in cross section
- the inner peripheral surface of the floating bush and the rotating shaft are larger than when the inner peripheral surface of the floating bush has a perfect circular shape in cross section. The gap between the outer peripheral surface of the first and second outer surfaces increases.
- a turbocharger includes: Any one of the above floating bush bearing devices; A centrifugal compressor having an impeller; A turbine having turbine blades, The turbine blade and the impeller are connected via the rotating shaft.
- a floating bush bearing device in which a circumferential groove is provided on the outer peripheral surface of the floating bush over the entire circumference, and a pressing force against the floating bush by the lubricating oil is ensured to suppress vibration.
- a turbocharger including the bearing device.
- FIG. 1 is a longitudinal sectional view schematically showing a turbocharger according to some embodiments of the present invention.
- FIG. 2 is an enlarged schematic view of a thrust bearing device and a radial bearing device in FIG. 1.
- FIG. 3 is a sectional view taken along line III-III in FIG. 2.
- FIG. 4 is a perspective view schematically showing a floating bush in FIG. 3. It is a figure which shows schematically the cross section of the floating bush of FIG. It is a figure which expands and shows the outer peripheral surface of the floating bush of FIG. 4 schematically. It is a figure which shows schematically the cross section of the floating bush which concerns on some embodiment. It is a figure which expands and shows an outer peripheral surface of the floating bush of Drawing 7 roughly.
- FIG. 10 is a diagram schematically showing the outer peripheral surface of the floating bush of FIG. 9 in a developed state. It is a figure which expands and shows roughly the peripheral surface of the floating bush concerning some embodiments. It is a figure which shows roughly the cross section of the floating bush which concerns on some embodiment with a drive shaft. It is a figure which expand
- 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 a bearing housing (casing) 22 by a fastening member (not shown), and the turbine blade 16 of the turbine 10 and the impeller 20 of the compressor 12 are driven through a drive shaft (turbine).
- the rotors 24 are connected to each other. Therefore, the turbine rotor blade 16, the impeller 20, and the drive shaft 24 are disposed on the same axis line 26.
- 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 45 is formed in the bearing portion 44.
- a bearing hole 45 is formed in the bearing portion 44.
- two floating bushes 46 are arranged in the bearing hole 45 of the bearing portion 44, and the central portion of the drive shaft 24 passes through the floating bush 46, and the inside of the bearing hole 45 of the bearing portion 44 is inside. Placed in.
- 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 device.
- 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.
- 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 plurality of blades 72 are arranged on the outer peripheral surface 74 of the hub 70 at intervals in the circumferential direction.
- the drive shaft 24 penetrates the hub 70, and a female screw is formed on the distal end side of the drive shaft 24 located on one end side of the hub 70, and a nut as a fastening member 78 is screwed to the female screw.
- the fastening member 78 abuts on one end side of the hub 70 and applies an axial force toward the turbine 10 in the direction along the axis 26 to the impeller 20.
- FIG. 2 is an enlarged schematic view of the thrust bearing device and the radial bearing device in FIG.
- the drive shaft 24 has a large-diameter portion 80 disposed in the bearing hole 45 and a small-diameter portion 82 extending between the bearing hole 45 and the impeller 20, and a step at the boundary between the large-diameter portion 80 and the small-diameter portion 82.
- a portion 84 is formed.
- At least one flange 86 is fitted to the small diameter portion 82 of the drive shaft 24.
- the thrust collar 50 and the thrust sleeve 52 fitted in series with the small diameter portion 82 each have a flange 86 (86a, 86b).
- the thrust collar 50 and the thrust sleeve 52 each have a sleeve portion 88 (88a, 88b) integrally formed with the flange portion 86 (86a, 86b), and the sleeve portion 88 (88a, 88b) has a small diameter portion 82. Is fitted.
- the sleeve portion 88a is positioned between the flange portion 86a and the flange portion 86b, and the sleeve portion 88b is disposed between the flange portion 86b and the impeller 20.
- the thrust collar 50 and the thrust sleeve 52 are sandwiched between the back surface 76 of the impeller 20 and the stepped portion 84 by the axial force of the fastening member 78, and are configured to rotate together with the drive shaft 24.
- the through hole 90 of the thrust member 48 is penetrated by the small diameter portion 82, and a sleeve portion 88 a is disposed between the inner peripheral surface of the through hole 90 and the outer peripheral surface of the small diameter portion 82.
- the thrust member 48 has a thrust portion 92 that slidably contacts with the flange portions 86 a and 86 b in the direction along the axis 26 around the through hole 90.
- the thrust member 48 has thrust portions 92 (92a, 92b) on both sides in the direction along the axis 26.
- the thrust member 48 is provided with an oil supply hole 94 that forms an oil supply passage, and an outlet of the oil supply hole 94 opens to the inner peripheral surface of the through hole 90.
- the lubricating oil that has flowed out from the outlet of the oil supply hole 94 passes through the gap between the outer peripheral surface of the sleeve portion 88a and the inner peripheral surface of the through hole 90, and between the thrust portion 92 (92a, 92b) and the flange portion 86 (86a, 86b). It is comprised so that it may be supplied to.
- the floating bush 46 on the compressor 12 side is sandwiched between the collar portion 86 a of the thrust collar 50 and the annular partition ring 96.
- a bearing chamber 98 for the floating bush 46 is defined in the bearing hole 45 between the flange portion 86 a and the partition ring 96.
- a bearing chamber for the floating bush 46 on the turbine 10 side is also defined in the bearing hole 45.
- FIG. 3 is a sectional view taken along line III-III in FIG.
- the floating bush 46 and the large-diameter portion (rotating shaft) 80 of the drive shaft 24 are coaxially disposed in the bearing chamber 98, that is, in the bearing hole 45, so that the floating bush 46 is large.
- the diameter portion 80 is surrounded.
- An oil supply hole 102 forming an oil supply passage is opened in the inner peripheral surface 100 of the bearing hole 45, and lubricating oil is supplied into the bearing chamber 98 along the radial direction of the floating bush 46 through the oil supply hole 102. .
- only one oil supply hole 102 opens on the inner peripheral surface 100 of the bearing hole 45 in the upper part of the bearing hole 45, and is directed downward in the vertical direction. Lubricating oil is supplied.
- the inner peripheral surface 100 is formed with a concave portion 104 extending in an arc shape along the inner peripheral surface 100, and an oil supply hole 102 is formed on the bottom surface of the concave portion 104. It is open. In other words, the opening of the oil supply hole 102 is expanded in the circumferential direction of the inner peripheral surface 100 due to the presence of the recess 104.
- FIG. 4 is a perspective view schematically showing the floating bush 46.
- FIG. 5 is a view schematically showing a cross section of the floating bush 46.
- FIG. 6 is a diagram schematically showing the outer peripheral surface of the floating bush 46 in a developed state.
- the floating bush 46 includes a main body portion 106, a plurality of communication holes 108, and a circumferential groove 110.
- the main body 106 has a cylindrical shape and has an inner peripheral surface 112 and an outer peripheral surface 114.
- the inner peripheral surface 112 and the outer peripheral surface 114 have a perfect circular shape in cross section. That is, the radial thickness of the main body 106 is constant in the circumferential direction.
- the plurality of communication holes 108 respectively extend between the inner peripheral surface 112 and the outer peripheral surface 114 of the main body 106 and are arranged at intervals in the circumferential direction of the main body 106. In some embodiments, the plurality of communication holes 108 extend in the radial direction of the main body portion 106, but may be along the radial direction, and may extend while being inclined with respect to the radial direction.
- the circumferential groove 110 extends over the entire circumference in the circumferential direction of the outer peripheral surface 114, and passes through the openings of the plurality of communication holes 108.
- the circumferential groove 110 has a different cross-sectional area according to the circumferential position of the main body portion 106. That is, the cross-sectional area of the circumferential groove 110 in a cross section orthogonal to the circumferential direction of the main body portion 106 differs depending on the circumferential position of the main body portion 106.
- the cross-sectional area of the circumferential groove 110 differs depending on the circumferential position, and the cross-sectional area is relatively small at one or more portions. Since the cross-sectional area of the one or more portions is relatively small, the flow of the lubricating oil in the circumferential groove 110 is suppressed.
- a plurality of thick arrows P in FIG. 3 schematically represent the distribution of the static pressure of the lubricating oil, and by suppressing the flow of the lubricating oil in the circumferential groove 110, the vicinity of the opening of the oil supply hole 102 The pressure drop of the lubricating oil at is suppressed.
- the white arrow F in FIG. 3 the floating bush 46 and the drive shaft 24 are pressed in one direction toward the opposite side of the oil supply hole 102 by the lubricating oil supplied from the oil supply hole 102. A force is generated, and unstable vibration of the drive shaft 24 can be prevented.
- static pressure distribution can be generated more effectively by opening the recess 104 and enlarging the opening of the oil supply hole 102.
- the circumferential groove 110 has a plurality of first regions 110a that overlap with the openings of the plurality of communication holes 108 in the circumferential direction of the floating bush 46, respectively. And a plurality of second regions 110b extending between the plurality of first regions 110a. And each cross-sectional area of several 1st area
- the cross-sectional area of the first region 110a whose position overlaps with the opening of the communication hole 108 is made larger than the cross-sectional area of the second region 110b extending between the first regions 110a.
- a relatively large amount of lubricating oil can be stored. That is, a sufficient amount of lubricating oil can be stored in the vicinity of the communication hole 108. As a result, a sufficient amount of lubricating oil can be effectively supplied into the floating bush 46 through the communication hole 108.
- the width Wa of each of the plurality of first regions 110a in the axial direction of the floating bush 46 is larger than the width Wb of each of the plurality of second regions 110b. According to this configuration, by making the width of the first region 110a larger than the width of the second region 110b, the cross-sectional area of the first region 110a can be easily made larger than the cross-sectional area of the second region 110b. .
- the width Wa of each of the plurality of first regions 110 a is in the range of 0.9 times to 1.3 times the width Wc of each of the plurality of communication holes 108.
- at least one of the plurality of first regions 110a includes a portion where the width of the circumferential groove 110 is the maximum width Wmax in the axial direction of the floating bush 46, and in the axial direction of the floating bush 46,
- the width Wb of each of the plurality of second regions 110b is in the range of 0.2 to 0.4 times the maximum width Wmax of the circumferential groove 110.
- the width Wa of the first region 110a is in the range of 0.9 to 1.3 times the width Wc of each communication hole 108, the first region 110a is sufficient for the first region 110a in the vicinity of the communication hole 108.
- a large amount of lubricating oil can be stored.
- a sufficient amount of lubricating oil can be effectively supplied into the floating bush 46 through the communication hole 108.
- the width Wb of the second region 110b is not less than 0.2 times and not more than 0.4 times the maximum width Wmax of the circumferential groove 110, the flow of lubricating oil in the circumferential direction is reliably ensured in the second region 110b. Can be regulated.
- the width Wa of the first region 110a is about 1.1 times the width Wc of each of the communication holes 108, and the width Wb of the second region 110b is about the maximum width Wmax of the circumferential groove 110. 1/3. According to this configuration, since the width Wa of the first region 110a is approximately 1.1 times the width Wc of each communication hole 108, a sufficient amount of lubricating oil can be stored in the first region 110a. On the other hand, since the width Wb of the second region 110b is about 1/3 of the maximum width of the circumferential groove 110, the flow of the lubricating oil in the circumferential direction can be reliably restricted in the second region 110b.
- the plurality of first regions 110 a are formed by the plurality of recesses 116 formed in the outer peripheral surface 114, respectively, and the plurality of recesses 116 in the outer peripheral surface 114 are formed.
- Each of the openings has a circular shape.
- the opening shape of each of the plurality of recesses 116 may be elliptical or rectangular.
- the opening shape of the first region 110a is circular, elliptical, or rectangular, the first region 110a can be easily formed.
- the plurality of recesses 116 can be formed by, for example, shot blasting, laser, or stamping (pressing a steel ball).
- the cross-sectional area of the circumferential groove 110 in one region in the circumferential direction of the floating bush 46 is different from that of the other region by 180 ° on the other side. It is approximately equal to the cross-sectional area of the circumferential groove 110 in the region.
- only the circumferential groove 110 is formed on the outer peripheral surface 114 of the main body portion 106, and no axial groove extending from the circumferential groove 110 to the axial end surface of the main body portion 106 is formed.
- FIG. 7 is a diagram schematically illustrating a cross section of a floating bush 120 according to some embodiments.
- FIG. 8 is a diagram schematically showing the outer peripheral surface 114 of the floating bush 120 in a developed state.
- a circumferential groove 122 is formed on the outer circumferential surface 114 of the main body portion 106 of the floating bush 120 instead of the circumferential groove 110.
- the circumferential groove 122 extends over the entire circumference of the outer peripheral surface 114 through the openings of the plurality of communication holes 108.
- the depth of the circumferential groove 122 in the radial direction of the floating bush 120 varies depending on the circumferential position.
- the circumferential groove 122 includes a plurality of first regions 122a that overlap with the openings and positions of the plurality of communication holes 108 in the circumferential direction of the floating bush 122, and a plurality that extends between the plurality of first regions 122a.
- the depth Da of each of the plurality of first regions 122a is deeper than the depth Db of each of the plurality of second regions 122b.
- the depth Da of the first region 122a is easily made larger than the cross-sectional area of the second region 122b. can do.
- the depth Da of the first region 122a is relatively deeper than the depth Db of the second region 122b, so that the communication is performed as indicated by the thick arrow u in FIG. The flow of the lubricating oil toward the hole 108 is induced, and the lubricating oil can be supplied to the inside of the floating bush 120 more effectively.
- the width Wg of the circumferential groove 122 in the axial direction of the floating bush 120 is substantially constant, and the maximum depth Dmax of the circumferential groove 122 in the radial direction of the floating bush 120 is the floating bush 120. Is less than 50 times the radial gap G between the outer peripheral surface 114 and the inner peripheral surface 100 of the bearing hole 45, and the minimum depth Dmin of the circumferential groove 122 in the radial direction of the floating bush 120 is the radial clearance. It is in the range of 2 to 3 times G.
- the communication hole 108 is set by setting the maximum depth Dmax to 50 times or less of the radial gap G and setting the minimum depth Dmin to a range of 2 to 3 times the radial gap G.
- the lubricating oil can be supplied to the inside of the floating bush 120 more effectively.
- the depth of the circumferential groove 122 in the radial direction of the floating bush 120 changes continuously or in a wave shape depending on the circumferential position of the floating bush 120. According to this configuration, the lubricating oil smoothly flows into the communication hole 108, and the lubricating oil can be supplied to the inside of the floating bush 120 more effectively.
- FIG. 9 is a diagram schematically illustrating a cross section of a floating bush 130 according to some embodiments.
- FIG. 10 is a diagram schematically showing the outer peripheral surface 114 of the floating bush 130 in a developed state.
- a circumferential groove 132 is formed on the outer circumferential surface 114 of the main body portion 106 of the floating bush 130 instead of the circumferential groove 110.
- the circumferential groove 132 extends over the entire circumference of the outer peripheral surface 114 through the openings of the plurality of communication holes 108.
- the cross-sectional area of the downstream region 132 c connected to the downstream side of the communication hole 108 in the rotation direction R of the floating bush 130 increases as it approaches the communication hole 108 in the circumferential direction of the floating bush 130.
- the cross-sectional area of the downstream region 132c increases as it approaches the communication hole 108, and when lubricating oil is supplied from the oil supply hole 102 when the floating bush 130 is stopped, As shown by the thick arrow u, it flows into the communicating hole 108 from the downstream region 132c.
- lubricating oil is supplied from the downstream region 132c to the communication hole 108, a rotational force is applied to the floating bush 46 by the lubricating oil. Therefore, if the lubricating oil is supplied at the start of the rotation of the drive shaft 24, the rotation start of the floating bush 46 can be assisted by the rotational force from the lubricating oil.
- the bottom surface of the downstream region 132 c that is continuous with the communication hole 108 in the circumferential groove 132 is formed by an inclined surface 132 d that is inclined with respect to the outer peripheral surface 114.
- the circumferential groove 132 is inclined so that the depth of the circumferential groove 132 becomes deeper as it approaches the communication hole 108 in the circumferential direction of the floating bush 46.
- the cross-sectional area of the downstream region 132 c can be easily enlarged toward the communication hole 108.
- the width of the downstream region 132c becomes narrower as it approaches the communication hole 108 in the circumferential direction.
- FIG. 11 is a diagram schematically illustrating the outer peripheral surface 114 of the floating bush 140 according to some embodiments.
- a circumferential groove 142 is formed on the outer circumferential surface 114 of the main body portion 106 in place of the circumferential groove 110.
- the width of the circumferential groove 142 in the axial direction of the floating bush 140 changes continuously in the circumferential direction, and the width of the first region 142a is larger than the width of the second region 142b.
- FIG. 12 schematically illustrates a cross-section of a floating bush 150 according to some embodiments, along with a drive shaft 24.
- the inner peripheral surface 152 of the floating bush 150 has a rouleau polygonal shape in a cross section orthogonal to the axis of the floating bush 150.
- the vibration stability should be higher than when the inner peripheral surface 152 of the floating bush 150 has a perfect circular shape in cross section. And bearing loss can be reduced.
- the inner peripheral surface 152 of the floating bush 150 has a Roule polygonal shape in cross section
- the inner surface of the floating bush 150 has a more inner shape than the case where the inner peripheral surface 152 of the floating bush 150 has a perfect circular shape in cross section.
- a gap between the peripheral surface 152 and the outer peripheral surface of the drive shaft 24 is increased. For this reason, it is necessary to share more lubricating oil in the gap between the inner peripheral surface 152 of the floating bush 150 and the outer peripheral surface of the drive shaft 24.
- the circumferential groove 110 having a different cross-sectional area according to the circumferential position is formed on the outer circumferential surface 114 of the floating bush 150, a sufficient amount of lubricating oil is supplied to the inner circumferential surface 152 of the floating bush 150 through the communication hole 108.
- the gap can be supplied to the outer peripheral surface of the drive shaft 24.
- the Reuleaux polygon is a kind of monospace figure.
- the rouleau polygon is a rouleau triangle formed by three envelopes.
- the communication hole 108 is a region where the radial clearance between the outer peripheral surface of the large diameter portion 80 and the inner peripheral surface 112 of the main body portion 106 is maximized, that is, a Rouleau polygon. Open in the area corresponding to the apex of. In FIG. 12, three communication holes 108 are provided in the main body portion 106.
- FIG. 13 schematically illustrates the inner peripheral surface 100 of the bearing hole 45 according to some embodiments.
- a circumferential groove 160 is formed at a position facing the communication hole 108 on the inner peripheral surface 100 of the bearing hole 45. It is formed over the entire circumference.
- the cross-sectional area of the circumferential groove 160 in a cross section orthogonal to the circumferential direction of the bearing hole 45 differs depending on the circumferential position. Also with this configuration, as in the case of the circumferential groove 110, it is possible to prevent unstable vibration of the drive shaft 24 and to supply a sufficient amount of lubricating oil to the inside of the floating bush.
- the circumferential groove 160 extends through the opening of the fill hole 102 or the recess 104.
- the circumferential groove 160 includes a plurality of first regions 160a provided at intervals corresponding to the circumferential interval of the plurality of communication holes 108, and a second region extending between the plurality of first regions 160a. 160b.
- the plurality of first regions 160a are formed by the plurality of recesses 162, respectively.
- the opening shape of the plurality of recesses 162 is either a circle, an ellipse, or a rectangle.
- 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 possibility of the combination of the embodiments is also disclosed by a combination of claims at the beginning of the application of the present application, or a combination of claims at the beginning of the application in the basic application when the application is accompanied by a priority claim.
- the circumferential groove 160 in FIG. 13 has a shape corresponding to the circumferential groove 110, but the inner circumferential surface 100 of the bearing hole 45 has a shape corresponding to the circumferential groove 122 and the circumferential groove 142.
- Circumferential grooves may be formed.
- the cross-sectional area, width, and depth of the circumferential groove are periodically changed in the circumferential direction, but the cross-sectional area may be different depending on the circumferential position. For example, it may change randomly.
- the centrifugal compressor may be a variable displacement type.
Abstract
Description
例えば特許文献1に記載されたラジアル軸受は、浮動ブッシュ軸受であり、浮動ブッシュ軸受は、ロータ軸に隙間をもって嵌合される浮動ブッシュを有する。浮動ブッシュは、軸受孔内に配置され、軸受孔の内周面には油路(給油孔)が開口している。
ところで、浮動ブッシュ軸受では、軸受孔の内周面に開口した給油孔から潤滑油を浮動ブッシュに向けて供給することにより、浮動ブッシュの周方向にて潤滑油の静圧に分布を生じさせている。この潤滑油の静圧分布により、浮動ブッシュ及びロータ軸が径方向にて軸受孔の内周面に向かって一方向に押され、ロータ軸の不安定振動が抑制される。
そこで、本発明の少なくとも一実施形態の目的は、浮動ブッシュの外周面に全周に渡って周方向溝を設けながら、潤滑油による浮動ブッシュに対する押し付け力が確保されて振動が抑制される浮動ブッシュ軸受装置、及び、該軸受装置を備えるターボチャージャを提供することにある。
軸受孔を有するケーシングと、
前記軸受孔内に回転可能に配置された回転軸と、
前記軸受孔内に回転可能に配置され、前記回転軸を囲む浮動ブッシュと、
前記軸受孔の内周面に開口する潤滑油の給油孔と、
前記浮動ブッシュに形成され、前記浮動ブッシュの内周面と外周面の間をそれぞれ延び、前記浮動ブッシュの周方向に間隔を存して配列された複数の連通孔と、
前記浮動ブッシュの外周面又は前記軸受孔の内周面に形成され、前記複数の連通孔の開口を通過するか又は前記複数の連通孔の開口と対向して、前記浮動ブッシュの外周面又は前記軸受孔の内周面の全周に渡って延在する周方向溝とを備え、
前記周方向溝は、周方向位置に応じて異なる断面積を有する。
一方、この構成によれば、断面積が相対的に狭くなった部分が存在する一方で、断面積が相対的に大きくなっている部分が存在する。この断面積が大きくなっている部分に潤滑油が一時的に蓄えられることで、断面積が小さい部分が存在していても、連通孔を通じて浮動ブッシュの内部に十分な量の潤滑油を供給することができる。
前記周方向溝は、前記浮動ブッシュの周方向にて前記複数の連通孔の開口と位置がそれぞれ重なる複数の第1領域と、前記複数の第1領域間をそれぞれ延びる複数の第2領域とを有し、
前記複数の第1領域の各々の断面積は、前記複数の第2領域の各々の断面積よりも大きい。
前記周方向溝は、前記軸受孔の周方向にて前記複数の連通孔の間隔に対応して設けられた複数の第1領域と、前記複数の第1領域間をそれぞれ延びる複数の第2領域とを有し、
前記複数の第1領域の各々の断面積は、前記複数の第2領域の各々の断面積よりも大きい。
この構成によれば、第1領域の幅を第2領域の幅よりも大きくすることで、第1領域の断面積を第2領域の断面積よりも容易に大きくすることができる。
前記複数の第1領域のうち少なくとも一つは、前記周方向溝の幅が最大幅となる部分を含み、
前記複数の第2領域の各々の幅は前記周方向溝の最大幅の0.2倍以上0.4倍以下の範囲に入っている。
一方、第2領域の幅が周方向溝の最大幅の0.2倍以上0.4倍以下であるため、第2領域において、周方向での潤滑油の流れを確実に規制することができる。
前記複数の凹部の各々の開口形状は、円形、楕円形又は矩形のうちいずれか一つである。
この構成によれば、第1領域の開口形状が円形、楕円形又は矩形であるため、第1領域を容易に形成することができる。
この構成によれば、周方向位置に応じて幅が変化する周方向溝を形成したことにより浮動ブッシュの重量バランスが崩れることが防止され、周方向溝を形成したことによる振動の発生を防止することができる。
この構成によれば、第1領域の深さを第2領域の深さよりも大きくすることで、第1領域の断面積を第2領域の断面積よりも容易に大きくすることができる。
また、この構成によれば、第1領域の深さを第2領域に比べて相対的に深くすることで、連通孔に向かう潤滑油の流れを誘起し、より効果的に潤滑油を浮動ブッシュの内側に供給することができる。
前記周方向溝の最大深さは、前記浮動ブッシュの外周面と前記軸受孔の内周面との間の半径方向隙間の50倍以下であり、
前記周方向溝の最小深さは、前記半径方向隙間の2倍以上3倍以下の範囲に入っている。
前記傾斜面は、前記浮動ブッシュの周方向にて前記連通孔に近づくほど前記周方向溝の深さが深くなるように傾斜している。
この構成によれば、連通孔に連なる下流領域の底面を傾斜面によって形成することで、下流領域の断面積を連通孔に向かって容易に拡大することができる。
浮動ブッシュの内周面が断面にてルーローの多角形形状を有する場合、浮動ブッシュの内周面が断面にて真円形状を有する場合に比べて、振動安定性を高くすることができるとともに、軸受損失を少なくすることができる。
一方、浮動ブッシュの内周面が断面にてルーローの多角形形状を有する場合、浮動ブッシュの内周面が断面にて真円形状を有する場合に比べて、浮動ブッシュの内周面と回転軸の外周面との間の隙間が大きくなる。このため、浮動ブッシュの内周面と回転軸の外周面との隙間に、より多くの潤滑油を共有する必要がある。この点、浮動ブッシュの外周面に周方向位置に応じて断面積が異なる周方向溝を形成すれば、連通孔を通じて十分な量の潤滑油を浮動ブッシュの内周面と回転軸の外周面との隙間に供給することができる。
上記した何れか一つの浮動ブッシュ軸受装置と、
インペラを有する遠心式コンプレッサと、
タービン動翼を有するタービンとを備え、
前記回転軸を介して前記タービン翼と前記インペラが連結されている。
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。
駆動軸24は、軸受孔45内に配置された大径部80と、軸受孔45とインペラ20の間を延びる小径部82とを有し、大径部80と小径部82との境界に段差部84が形成されている。
また、スラストカラー50及びスラストスリーブ52は、鍔部86(86a,86b)と一体に形成されたスリーブ部88(88a,88b)をそれぞれ有し、スリーブ部88(88a,88b)は小径部82に嵌合されている。スリーブ部88aは、鍔部86aと鍔部86bの間に位置し、スリーブ部88bは、鍔部86bとインペラ20の間に配置されている。
スラスト部材48の貫通孔90は、小径部82によって貫通されており、貫通孔90の内周面と小径部82の外周面の間にはスリーブ部88aが配置されている。スラスト部材48は、貫通孔90の周囲に、軸線26に沿う方向にて鍔部86a,86bと対向して摺接するスラスト部92を有する。幾つかの実施形態では、スラスト部材48は、軸線26に沿う方向にて両側にスラスト部92(92a,92b)を有する。
図3に示したように、浮動ブッシュ46及び駆動軸24の大径部(回転軸)80は、軸受室98内、即ち軸受孔45内に回転可能に同軸に配置され、浮動ブッシュ46が大径部80を囲んでいる。軸受孔45の内周面100には、給油路を形成する給油孔102が開口し、軸受室98内には、給油孔102を通じて、浮動ブッシュ46の径方向に沿って潤滑油が供給される。
また、幾つかの実施形態では、図3に示したように、内周面100には、内周面100に沿って円弧状に延びる凹部104が形成され、凹部104の底面に給油孔102が開口している。換言すれば、給油孔102の開口が、凹部104の存在によって内周面100の周方向に拡大されている。
浮動ブッシュ46は、本体部106と、複数の連通孔108と、周方向溝110とを有する。
本体部106は、円筒形状を有し、内周面112及び外周面114を有する。幾つかの実施形態では、内周面112及び外周面114は、横断面でみて真円形状を有する。つまり、本体部106の径方向での厚さは、周方向にて一定である。
図3中の複数の太線矢印Pは、潤滑油の静圧の分布を概略的に表しており、周方向溝110内での潤滑油の流れが抑制されることで、給油孔102の開口近傍における潤滑油の圧力低下が抑制される。この結果として、図3中に白抜き矢印Fで示したように、給油孔102から供給される潤滑油によって、浮動ブッシュ46及び駆動軸24を給油孔102と反対側に向かって一方向に押し付ける力が発生し、駆動軸24の不安定振動を防止することができる。
そして、上述したターボチャージャは、浮動ブッシュ軸受装置の振動が抑制されていることから、静音性に優れている。
この構成によれば、第1領域110aの幅を第2領域110bの幅よりも大きくすることで、第1領域110aの断面積を第2領域110bの断面積よりも容易に大きくすることができる。
一方、第2領域110bの幅Wbが周方向溝110の最大幅Wmaxの0.2倍以上0.4倍以下であるため、第2領域110bにおいて、周方向での潤滑油の流れを確実に規制することができる。
この構成によれば、第1領域110aの幅Waが連通孔108の各々の幅Wcの約1.1倍であるため、第1領域110aに十分な量の潤滑油を蓄えることができる。一方、第2領域110bの幅Wbが周方向溝110の最大幅の約1/3であるため、第2領域110bにおいて、周方向での潤滑油の流れを確実に規制することができる。
幾つかの実施形態では、図7及び図8に示したように、浮動ブッシュ120の本体部106の外周面114に、周方向溝110に代えて周方向溝122が形成されている。周方向溝122は、複数の連通孔108の開口を通過して外周面114の全周に渡って延びている。浮動ブッシュ120の半径方向での周方向溝122の深さは、周方向位置に応じて異なっている。
また、この構成によれば、第1領域122aの深さDaを第2領域122bの深さDbに比べて相対的に深くすることで、図7中に太線矢印uで示したように、連通孔108に向かう潤滑油の流れを誘起し、より効果的に潤滑油を浮動ブッシュ120の内側に供給することができる。
この構成によれば、最大深さDmaxを半径方向隙間Gの50倍以下に設定し、最小深さDminを半径方向隙間Gの2倍以上3倍以下の範囲に設定することで、連通孔108に向かう潤滑油の流れを誘起し、より効果的に潤滑油を浮動ブッシュ120の内側に供給することができる。
幾つかの実施形態では、図9及び図10に示したように、浮動ブッシュ130の本体部106の外周面114に、周方向溝110に代えて周方向溝132が形成されている。周方向溝132は、複数の連通孔108の開口を通過して外周面114の全周に渡って延びている。周方向溝132においては、浮動ブッシュ130の回転方向Rにて連通孔108の下流側に連なる下流領域132cの断面積は、浮動ブッシュ130の周方向にて連通孔108に近づくほど拡大している。
この構成によれば、連通孔108に連なる下流領域132cの底面を傾斜面132dによって形成することで、下流領域132cの断面積を連通孔108に向かって容易に拡大することができる。
幾つかの実施形態では、下流領域132cの幅は、周方向にて連通孔108に近づくほど狭くなっている。
幾つかの実施形態では、図12に示したように、浮動ブッシュ150の内周面152は、浮動ブッシュ150の軸線と直交する断面にてルーローの多角形形状を有する。
浮動ブッシュ150の内周面152が断面にてルーローの多角形形状を有する場合、浮動ブッシュ150の内周面152が断面にて真円形状を有する場合に比べて、振動安定性を高くすることができるとともに、軸受損失を少なくすることができる。
なお、ルーローの多角形は、等幅図形の一種である。幾つかの実施形態では、ルーローの多角形は、3つの包絡線によって形成されたルーローの三角形である。本体部106の内周面112において、連通孔108は、大径部80の外周面と本体部106の内周面112との間の径方向隙間が最大となる領域、すなわち、ルーローの多角形の頂点に相当する領域にて開口している。図12では、3つの連通孔108が本体部106に設けられている。
幾つかの実施形態では、浮動ブッシュ46の外周面114に代えて、図13に示したように、軸受孔45の内周面100において、連通孔108と対向する位置に、周方向溝160が全周に渡って形成されている。軸受孔45の周方向と直交する断面での周方向溝160の断面積は、周方向位置に応じて異なっている。
この構成によっても、周方向溝110の場合と同様に、駆動軸24の不安定振動を防止することができるとともに、浮動ブッシュの内部に十分な量の潤滑油を供給することができる。
幾つかの実施形態では、周方向溝160は、複数の連通孔108の周方向間隔に対応する間隔で設けられた複数の第1領域160aと、複数の第1領域160a間を延びる第2領域160bとを有する。
幾つかの実施形態では、複数の第1領域160aは、複数の凹部162によってそれぞれ形成される。複数の凹部162の開口形状は円形、楕円形または矩形のいずれかからなる。
また、上述した幾つかの実施形態では、周方向溝の断面積、幅及び深さが、周方向にて周期的に変化していたが、周方向位置に応じて断面積が異なってさえいれば、ランダムに変化していてもよい。
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(ケーシング)
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
74 外周面
76 背面
78 締結部材
80 大径部(回転軸)
82 小径部
84 段差部
86(86a,86b) 鍔部
88(88a,88b) スリーブ部
90 貫通孔
92(92a,92b) スラスト部
94 給油孔
96 隔壁リング
98 軸受室
100 内周面
102 給油孔
104 凹部
106 本体部
108 連通孔
110 周方向溝
110a 第1領域
110b 第2領域
112 内周面
114 外周面
116 凹部
Claims (13)
- 軸受孔を有するケーシングと、
前記軸受孔内に回転可能に配置された回転軸と、
前記軸受孔内に回転可能に配置され、前記回転軸を囲む浮動ブッシュと、
前記軸受孔の内周面に開口する潤滑油の給油孔と、
前記浮動ブッシュに形成され、前記浮動ブッシュの内周面と外周面の間をそれぞれ延び、前記浮動ブッシュの周方向に間隔を存して配列された複数の連通孔と、
前記浮動ブッシュの外周面又は前記軸受孔の内周面に形成され、前記複数の連通孔の開口を通過するか又は前記複数の連通孔の開口と対向して、前記浮動ブッシュの外周面又は前記軸受孔の内周面の全周に渡って延在する周方向溝とを備え、
前記周方向溝は、周方向位置に応じて異なる断面積を有する
ことを特徴とする浮動ブッシュ軸受装置。 - 前記周方向溝は、前記浮動ブッシュの外周面に形成され、
前記周方向溝は、前記浮動ブッシュの周方向にて前記複数の連通孔の開口と位置がそれぞれ重なる複数の第1領域と、前記複数の第1領域間をそれぞれ延びる複数の第2領域とを有し、
前記複数の第1領域の各々の断面積は、前記複数の第2領域の各々の断面積よりも大きい
ことを特徴とする請求項1に記載の浮動ブッシュ軸受装置。 - 前記周方向溝は、前記軸受孔の内周面に形成され、
前記周方向溝は、前記軸受孔の周方向にて前記複数の連通孔の間隔に対応して設けられた複数の第1領域と、前記複数の第1領域間をそれぞれ延びる複数の第2領域とを有し、
前記複数の第1領域の各々の断面積は、前記複数の第2領域の各々の断面積よりも大きい
ことを特徴とする請求項1に記載の浮動ブッシュ軸受装置。 - 前記複数の第1領域の各々の幅は前記複数の第2領域の各々の幅よりも大きい
ことを特徴とする請求項2又は3に記載の浮動ブッシュ軸受装置。 - 前記複数の第1領域の各々の幅は前記複数の連通孔の各々の幅の0.9倍以上1.3倍以下の範囲に入っており、
前記複数の第1領域のうち少なくとも一つは、前記周方向溝の幅が最大幅となる部分を含み、
前記複数の第2領域の各々の幅は前記周方向溝の最大幅の0.2倍以上0.4倍以下の範囲に入っている
ことを特徴とする請求項4に記載の浮動ブッシュ軸受装置。 - 前記複数の第1領域は複数の凹部によってそれぞれ形成され、
前記複数の凹部の各々の開口形状は、円形、楕円形又は矩形のうちいずれか一つである
ことを特徴とする請求項2乃至5の何れか一項に記載の浮動ブッシュ軸受装置。 - 前記周方向溝の一の部分の断面積は、前記一の部分と180°反対側の他の部分の断面積と略等しい
ことを特徴とする請求項2乃至6の何れか一項に記載の浮動ブッシュ軸受装置。 - 前記複数の第1領域の各々の深さは前記複数の第2領域の各々の深さよりも深い
ことを特徴とする請求項2乃至7の何れか一項に記載の浮動ブッシュ軸受装置。 - 前記周方向溝の幅は略一定であり、
前記周方向溝の最大深さは、前記浮動ブッシュの外周面と前記軸受孔の内周面との間の半径方向隙間の50倍以下であり、
前記周方向溝の最小深さは、前記半径方向隙間の2倍以上3倍以下の範囲に入っている
ことを特徴とする請求項1乃至8の何れか一項に記載の浮動ブッシュ軸受装置。 - 前記周方向溝において、前記浮動ブッシュの回転方向にて前記連通孔の下流側に連なる下流領域の断面積は、前記浮動ブッシュの周方向にて前記連通孔に近づくほど拡大していることを特徴とする請求項1乃至9の何れか一項に記載の浮動ブッシュ軸受装置。
- 前記連通孔に連なる下流領域の底面は、前記外周面に対し傾斜した傾斜面によって形成され、
前記傾斜面は、前記浮動ブッシュの周方向にて前記連通孔に近づくほど前記周方向溝の深さが深くなるように傾斜している
ことを特徴とする請求項10に記載の浮動ブッシュ軸受装置。 - 前記浮動ブッシュの内周面は、前記浮動ブッシュの軸線と直交する断面にてルーローの多角形形状を有する
ことを特徴とする請求項1乃至11の何れか一項に記載の浮動ブッシュ軸受装置。 - 請求項1乃至12の何れか一項に記載の浮動ブッシュ軸受装置と、
インペラを有する遠心式コンプレッサと、
タービン動翼を有するタービンとを備え、
前記回転軸を介して前記タービン翼と前記インペラが連結されている
ことを特徴とするターボチャージャ。
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Also Published As
Publication number | Publication date |
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EP3112707A1 (en) | 2017-01-04 |
JPWO2015128978A1 (ja) | 2017-03-30 |
CN105940229B (zh) | 2018-09-28 |
US10330152B2 (en) | 2019-06-25 |
EP3321527A1 (en) | 2018-05-16 |
EP3321527B1 (en) | 2019-12-18 |
JP6250787B2 (ja) | 2017-12-20 |
EP3112707B1 (en) | 2019-12-11 |
US20170009810A1 (en) | 2017-01-12 |
EP3112707A4 (en) | 2017-02-15 |
CN105940229A (zh) | 2016-09-14 |
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