WO2015186524A1 - 軸受構造、および、過給機 - Google Patents
軸受構造、および、過給機 Download PDFInfo
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- WO2015186524A1 WO2015186524A1 PCT/JP2015/064494 JP2015064494W WO2015186524A1 WO 2015186524 A1 WO2015186524 A1 WO 2015186524A1 JP 2015064494 W JP2015064494 W JP 2015064494W WO 2015186524 A1 WO2015186524 A1 WO 2015186524A1
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- main body
- oil
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- shaft
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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
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
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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
- F01D25/04—Antivibration arrangements
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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
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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
- F01D25/18—Lubricating arrangements
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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
- F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/04—Blade-carrying members, e.g. rotors for radial-flow machines or engines
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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
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/024—Units comprising pumps and their driving means the driving means being assisted by a power recovery turbine
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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
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/053—Shafts
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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
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
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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
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
- F04D29/0563—Bearings cartridges
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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
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
- F04D29/059—Roller bearings
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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
- F04D29/06—Lubrication
- F04D29/063—Lubrication specially adapted for elastic fluid pumps
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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
- F04D29/28—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
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
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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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/668—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps damping or preventing mechanical vibrations
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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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
- F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
- F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
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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
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
- F16C27/045—Ball or roller bearings, e.g. with resilient rolling bodies with a fluid film, e.g. squeeze film damping
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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
- F05D2240/60—Shafts
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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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
- F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
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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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- 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
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
- F16C35/07—Fixing them on the shaft or housing with interposition of an element
- F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
Definitions
- the present invention relates to a bearing structure including an oil film damper that suppresses vibration of a shaft, and a supercharger.
- a turbocharger in which a shaft having a turbine impeller provided at one end and a compressor impeller provided at the other end is rotatably supported by a bearing housing is known.
- a supercharger is connected to the engine, the turbine impeller is rotated by exhaust gas discharged from the engine, and the compressor impeller is rotated through the shaft by the rotation of the turbine impeller.
- the supercharger compresses air and sends it to the engine as the compressor impeller rotates.
- Patent Document 1 describes a configuration in which a rolling bearing that supports a shaft is supported inside an oil film damper.
- the oil film damper has a cylindrical shape and is fitted into a hole formed in the housing of the turbocharger, and an oil film of lubricating oil is formed between the inner peripheral surface of the hole and the outer peripheral surface of the oil film damper. . This oil film suppresses vibration of the shaft.
- the oil film damper is formed with an oil guide passage that penetrates from the outer peripheral surface to the inner peripheral surface and guides the lubricating oil to the rolling bearing. After lubricating the rolling bearing, the lubricating oil is discharged to the outside of the oil film damper through an oil drain hole formed vertically below the oil guide path. At this time, if the lubricating oil stays in the oil film damper without being quickly discharged, the mechanical loss increases due to the rotation resistance of the shaft, or the flow rate of the lubricating oil decreases and the cooling performance is affected. There is a need for improved oil drainage of oil film dampers.
- An object of the present invention is to provide a bearing structure and a supercharger that can improve oil drainage.
- a first aspect of the present invention is a bearing structure that rotatably supports a shaft, and is housed in a bearing hole formed in a housing, and has an oil film damper having a cylindrical main body portion, and a main body portion of the oil film damper. And two bearings arranged opposite to each other in the direction of the rotation axis of the shaft.
- the oil film damper is located between the opposing surfaces of the two bearings.
- the oil film damper protrudes inward in the radial direction from the inner peripheral surface of the main body portion and passes through the two protrusion portions adjacent to the opposing surfaces of the two bearings from the protrusion portion to the outer peripheral surface of the main body portion.
- An oil guide path that guides the lubricating oil from the outer periphery of the bearing to the bearing, and an inclined surface that is provided on the opposite side of the protruding portion from the adjacent surface adjacent to the bearing, and whose inner diameter gradually increases as it is separated from the adjacent surface in the shaft rotation axis direction And an oil drain hole provided between two projecting portions of the main body portion and for discharging the lubricating oil from the main body portion to the outside.
- the oil guide passage may extend linearly in a direction inclined with respect to the rotation axis direction of the shaft.
- the oil guide path may extend in parallel to the inclined surface.
- the protrusion has a curved portion that is continuous with the radially inner end of the adjacent surface and has a curvature center on the side opposite to the side where the bearing adjacent to the adjacent surface is located with respect to the adjacent surface.
- the oil guide path may be opened in the part.
- a second aspect of the present invention is a turbocharger, which is accommodated in a housing in which a bearing hole is formed, a shaft in which a turbine impeller is provided on one end side, and a compressor impeller on the other end side, and a bearing hole.
- an oil film damper having a cylindrical main body, and two bearings that are held in the main body of the oil film damper and are opposed to each other in the rotation axis direction of the shaft so as to rotatably support the shaft. .
- the oil film damper is located between the opposing surfaces of the two bearings.
- the oil film damper protrudes inward in the radial direction from the inner peripheral surface of the main body portion and passes through the two protrusion portions adjacent to the opposing surfaces of the two bearings from the protrusion portion to the outer peripheral surface of the main body portion.
- An oil guide path that guides the lubricating oil from the outer periphery of the bearing to the bearing, and an inclined surface that is provided on the opposite side of the protruding portion from the adjacent surface adjacent to the bearing, and whose inner diameter gradually increases as it is separated from the adjacent surface in the shaft rotation axis direction
- an oil drain hole provided between two projecting portions of the main body portion and for discharging the lubricating oil from the main body portion to the outside.
- FIG. 1 is a schematic cross-sectional view of a supercharger according to an embodiment of the present invention.
- 2A is a diagram showing the bearing structure in FIG. 1
- FIG. 2B is a diagram showing the inside of the broken line in FIG. 2A.
- FIG. 3 is a perspective view of an oil film damper according to an embodiment of the present invention.
- FIG. 4 is a diagram for explaining a comparative example.
- FIG. 5A and FIG. 5B are diagrams for explaining a modification of the embodiment of the present invention.
- FIG. 1 is a schematic sectional view of the supercharger C.
- the arrow L shown in FIG. 1 will be described as a direction indicating the left side of the supercharger C
- the arrow R will be described as a direction indicating the right side of the supercharger C.
- the supercharger C includes a supercharger main body 1.
- the turbocharger body 1 includes a bearing housing 2, a turbine housing 4 connected to the left side of the bearing housing 2 by a fastening mechanism 3, a seal plate 6 connected to the right side of the bearing housing 2 by a fastening bolt 5, and a seal.
- a compressor housing 8 connected to the right side of the plate 6 by fastening bolts 7; These are integrated.
- a protrusion 2 a is provided on the outer peripheral surface of the bearing housing 2 in the vicinity of the turbine housing 4.
- the protrusion 2 a protrudes in the radial direction of the bearing housing 2.
- a projection 4 a is provided on the outer peripheral surface of the turbine housing 4 in the vicinity of the bearing housing 2.
- the protrusion 4 a protrudes in the radial direction of the turbine housing 4.
- the bearing housing 2 and the turbine housing 4 are fixed by fastening the protrusions 2 a and 4 a with the fastening mechanism 3.
- the fastening mechanism 3 includes a coupling (for example, G coupling) that holds the protrusions 2a and 4a.
- the bearing housing 2 is formed with a bearing hole 2b that penetrates the supercharger C in the left-right direction.
- a bearing structure 9 is provided in the bearing hole 2b.
- the bearing structure 9 supports the shaft 10 rotatably.
- a turbine impeller 11 is integrally fixed to the left end (one end, one end side) of the shaft 10.
- the turbine impeller 11 is rotatably accommodated in the turbine housing 4.
- a compressor impeller 12 is integrally fixed to the right end portion (the other end, the other end side) of the shaft 10.
- the compressor impeller 12 is rotatably accommodated in the compressor housing 8.
- An air inlet 13 is formed in the compressor housing 8.
- the intake port 13 opens to the right side of the supercharger C and is connected to an air cleaner (not shown).
- the seal plate 6 and the compressor housing 8 are connected by the fastening bolt 7, the opposing surfaces of the seal plate 6 and the compressor housing 8 that are opposed to each other form a diffuser flow path 14 that pressurizes air.
- the diffuser flow path 14 is formed in an annular shape from the radially inner side to the outer side of the shaft 10.
- the diffuser flow path 14 communicates with the intake port 13 via the compressor impeller 12 on the radially inner side.
- the compressor housing 8 is provided with a compressor scroll passage 15.
- the compressor scroll channel 15 is formed in an annular shape, and is located on the radially outer side of the shaft 10 with respect to the diffuser channel 14.
- the compressor scroll passage 15 communicates with an intake port (not shown) of the engine.
- the compressor scroll passage 15 communicates with the diffuser passage 14. Therefore, when the compressor impeller 12 rotates, air is sucked into the compressor housing 8 from the intake port 13 and is accelerated by the action of centrifugal force in the process of flowing between the blades of the compressor impeller 12, and the diffuser flow path 14 and the compressor The pressure is increased in the scroll flow path 15 and guided to the intake port of the engine.
- a discharge port 16 is formed in the turbine housing 4.
- the discharge port 16 opens on the left side of the supercharger C and is connected to an exhaust gas purification device (not shown).
- the turbine housing 4 is provided with a flow path 17 and annular turbine scroll flow paths 18 a and 18 b positioned on the radially outer side of the turbine impeller 11 with respect to the flow path 17.
- the turbine scroll passages 18a and 18b communicate with a gas inlet (not shown) through which exhaust gas discharged from an engine exhaust manifold (not shown) is guided.
- the turbine scroll flow paths 18 a and 18 b communicate with the flow path 17. Therefore, the exhaust gas is guided from the gas inlet to the turbine scroll passages 18 a and 18 b and further to the discharge port 16 via the passage 17 and the turbine impeller 11. In this distribution process, the exhaust gas rotates the turbine impeller 11.
- the supercharger C of the present embodiment has two turbine scroll flow paths 18a and 18b. In the low speed region, the exhaust gas flows into only one of the two turbine scroll channels 18a and 18b. Thereby, the pressure of the exhaust gas necessary for rotating the turbine impeller 11 is ensured.
- Rotational force of the turbine impeller 11 is transmitted to the compressor impeller 12 through the shaft 10, and the compressor impeller 12 is thereby rotated.
- the air is boosted by the rotational force of the compressor impeller 12 and guided to the intake port of the engine.
- FIG. 2A and FIG. 2B are explanatory views for explaining the bearing structure 9.
- FIG. 2A shows the bearing structure 9 in FIG. 1
- FIG. 2B shows the inside of the broken line in FIG.
- FIG. 3 is a perspective view of the oil film damper 19.
- the oil film damper 19 is accommodated in the bearing hole 2 b formed in the bearing housing 2.
- the oil film damper 19 has a cylindrical main body 19a. Projections 19c and 19d are provided on the outer peripheral surface 19b of the main body 19a.
- the protrusions 19c and 19d protrude outward in the radial direction of the main body 19a and are formed in an annular shape.
- the protrusions 19c and 19d are provided on both ends of the shaft 10 in the rotation axis direction of the shaft 10 (hereinafter simply referred to as the axial direction).
- These annular protrusions 19c and 19d face the inner peripheral surface of the bearing hole 2b. As a result, an oil film is formed between the annular protrusions 19c and 19d and the inner peripheral surface of the bearing hole 2b, and the vibration of the shaft 10 is suppressed by this oil film.
- a tapered surface 19e is formed between the two annular protrusions 19c and 19d.
- the tapered surface 19e is inclined with respect to the axial direction.
- An oil guide path 19f is formed on the tapered surface 19e of the main body 19a.
- the oil guide path 19f extends perpendicularly to the tapered surface 19e and communicates with the inside of the main body 19a.
- the oil guide passage 19f guides the lubricating oil to a rolling bearing 20 (hereinafter referred to as a bearing for convenience of explanation) 20 housed in the main body 19a.
- a rolling bearing 20 (hereinafter referred to as a bearing for convenience of explanation) 20 housed in the main body 19a.
- One bearing 20 is accommodated in each end of the shaft 10 in the axial direction inside the main body 19a.
- the two bearings 20 are provided so as to be separated from each other in the axial direction, and the surfaces (opposing surfaces) 20e of the outer ring 20a are arranged to face each other in the axial direction.
- the bearing 20 includes an outer ring 20a and an inner ring 20b having a smaller diameter than the outer ring 20a, a plurality of balls 20c sandwiched between the outer ring 20a and the inner ring 20b, and a cage 20d that holds the plurality of balls 20c.
- Have Each ball 20c is provided in the circumferential direction of the outer ring 20a (inner ring 20b) and is held by a cage 20d.
- the outer ring 20 a is fixed to the oil film damper 19, and the inner ring 20 b rotates integrally with the shaft 10. At this time, by rolling the ball 20c, the frictional resistance between the outer ring 20a and the inner ring 20b is suppressed, and the outer ring 20a and the inner ring 20b can be rotated relative to each other. Thus, the shaft 10 is rotatably supported by the rolling bearing 20.
- the regulating part 21 is arranged between the two inner rings 20b.
- the restricting portion 21 is a member formed in an annular shape (tubular shape).
- the shaft 10 is inserted through the restriction portion 21. Further, both axial ends of the restricting portion 21 are in contact with the inner ring 20b.
- the restricting portion 21 restricts the movement of the two inner rings 20b in the proximity direction while rotating integrally with the inner ring 20b.
- Two protrusions 19h and 19h are formed on the inner peripheral surface 19g of the oil film damper 19. Each protrusion 19h protrudes inward in the radial direction of the oil film damper 19 and is formed in an annular shape. The two protrusions 19h are located between the opposing surfaces 20e, 20e of the outer rings 20a, 20a in the two bearings 20, 20. Each protrusion 19h is adjacent to the facing surface 20e of the outer ring 20a of the adjacent bearing 20.
- the two bearings 20 and 20 are fitted from both ends of the main body portion 19a into the main body portion 19a until they abut against the protruding portion 19h. Further, the oil guide passage 19f penetrates from the radially inner tip of the protruding portion 19h to the tapered surface 19e through the protruding portion 19h.
- the protrusion 19h has an inclined surface 19j formed on the opposite side of the adjacent surface 19i adjacent to the bearing 20. As shown in FIG. The inner diameter of the inclined surface 19j gradually increases as the distance from the adjacent surface 19i increases in the axial direction. In the present embodiment, the inclined surface 19j is parallel to the extending direction of the oil guide passage 19f in the cross section including the rotation axis of the shaft 10.
- the protruding portion 19h is continuous with the radially inner end (inner diameter side end) 19k of the adjacent surface 19i and is adjacent to the adjacent surface 19i with reference to the adjacent surface 19i.
- a curved portion 19l having a center of curvature is provided on the side opposite to the side where the bearing 20 is located.
- the oil guide path 19f opens to the bending portion 19l and passes through the center of curvature of the bending portion 19l.
- the oil guide path 19f ejects lubricating oil toward the outer peripheral surface 20f of the inner ring 20b of the bearing 20.
- an oil drain hole 19m is provided between the two protrusions 19h and 19h.
- the upper side substantially coincides with the vertical upper side
- the lower side substantially coincides with the lower vertical side
- the oil drain hole 19m is formed on the lower vertical side than the oil guide passage 19f.
- Lubricating oil is supplied to the bearing 20 from the oil guide path 19f, and a part of the lubricating oil bounces off the ball 20c and the like, and is discharged from the main body 19a to the outside through the oil drain hole 19m.
- FIG. 4 is an explanatory diagram for explaining a comparative example, and shows a cross section of a portion corresponding to FIG. 2A in the above-described embodiment.
- the protrusion h extends in the axial direction from one bearing 20 to the other bearing 20. Therefore, for example, depending on the attitude of the supercharger, the lubricating oil is supplied from the oil guide path f, hits the ball 20c and bounces off, and then becomes difficult to flow toward the oil discharge hole k, resulting in a decrease in oil discharge performance. There is a fear.
- the two projecting portions 19h and 19h are separated from each other, and each projecting portion 19h is provided with an inclined surface 19j. Yes. Therefore, the lubricating oil is supplied from the oil guide path 19f, bounces off the ball 20c and the like, and then is guided to the inclined surface 19j of the projecting portion 19h to be quickly discharged from the oil discharge hole 19m. Thus, in the bearing structure 9, it becomes possible to improve oil drainage.
- the oil guide passage 19f extends linearly in a direction inclined with respect to the axial direction and is perpendicular to the tapered surface 19e. Accordingly, the oil guide passage 19f can be formed by one drilling process, and the processing cost can be reduced.
- the oil guide passage 19f extends in parallel to the inclined surface 19j. Therefore, the inclined surface 19j can have a shape in which the protruding portion 19h is cut along the oil guide passage 19f to a thickness that can maintain the strength. That is, the thickness of the protruding portion 19h in the axial direction can be reduced as much as the strength permits. Therefore, it is possible to secure a larger space for oil drainage to improve oil drainage and to reduce the weight. Moreover, since the space is ensured as much as possible outside the shaft 10 in the radial direction, the frictional resistance with the lubricating oil accompanying the rotation of the shaft 10 can be reduced. As a result, the mechanical loss of the bearing can be reduced.
- the oil guide passage 19f is open to the curved portion 19l, the oil guide passage 19f is concentrated toward a predetermined position of the bearing 20 (for example, the outer peripheral surface 20f of the inner ring 20b in this embodiment) while suppressing diffusion. Lubricating oil can be ejected.
- FIG. 5A and FIG. 5B are explanatory diagrams for explaining a modification of the present embodiment, and show a cross section corresponding to a portion within a broken line in FIG. 2A in the above-described embodiment. .
- the curved part 19l like embodiment mentioned above is not provided in the 1st modification.
- the protrusion part 19h has the innermost diameter part 19n as an inner peripheral surface located in the innermost radial direction.
- the oil guide passage 29f of the first modified example opens in the projecting portion 19h across the adjacent surface 19i and the innermost diameter portion 19n.
- a chamfered portion 391 is provided instead of the curved portion 19l.
- the chamfered portion 391 has a linear shape in a cross section including the rotation axis of the shaft 10 (for example, a cross section shown in FIG. 5B).
- the chamfered portion 39l is not perpendicular to the oil guide passage 39f.
- the oil guide passage 39f does not extend perpendicular to the chamfered portion 39l. That is, the oil guide passage 39f may be inclined with respect to the vertical direction of the chamfered portion 39l.
- the drilling process is performed from the tapered surface 19e side by forming the oil guide passages 19f, 29f, and 39f perpendicular to the tapered surface 19e. Can be carried out easily. Further, the inclination of the opening surface on the bearing 20 side (curved portion 19l, chamfered portion 39l, etc.) may be finely adjusted according to the supply mode of the lubricating oil to the bearing 20.
- oil guide passages 19f, 29f, and 39f have been described as extending in parallel to the inclined surface 19j, but may be inclined with respect to the inclined surface 19j. .
- the oil guide passage 19f has been described as passing through the center of curvature of the curved portion 19l.
- the oil guide path 19f may not pass through the center of curvature of the curved portion 19l.
- the first modification, and the second modification it is possible to intensively eject the lubricating oil toward the predetermined position of the bearing 20 while suppressing diffusion.
- the oil guide passage 39f has been described as not extending perpendicularly to the chamfered portion 391. However, even if the oil guiding passageway 39f extends perpendicular to the chamfered portion 391l. Good. In this case, as in the above-described embodiment, the lubricating oil can be intensively ejected toward a predetermined position of the bearing 20 while suppressing diffusion.
- the oil guide passage 29f opens to both the adjacent surface 19i and the innermost diameter portion 19n of the protruding portion 19h has been described.
- the oil guide passage 29f may be opened only in one of the adjacent surface 19i and the innermost diameter portion 19n.
- the present invention can be used for a bearing structure including an oil film damper that suppresses vibration of a shaft, and a supercharger.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Supercharger (AREA)
- Support Of The Bearing (AREA)
Abstract
Description
Claims (5)
- シャフトを回転自在に支持する軸受構造であって、
ハウジングに形成された軸受孔に収容され、円筒形状の本体部を有するオイルフィルムダンパと、
前記オイルフィルムダンパの前記本体部内に保持され、前記シャフトの回転軸方向に離隔して対向配置される2つの軸受と
を備え、
前記オイルフィルムダンパは、
前記2つの軸受の、互いに対向する対向面間に位置し、
前記オイルフィルムダンパは、
前記本体部の内周面から径方向内側に突出して前記2つの軸受の対向面のそれぞれに隣接する2つの突出部と、
前記突出部から前記本体部の外周面まで貫通するとともに、前記本体部の外周から前記軸受まで潤滑油を導く導油路と、
前記突出部のうち前記軸受に隣接する隣接面とは反対側に設けられ、前記隣接面から前記シャフトの回転軸方向に離隔するにつれて内径が漸増する傾斜面と、
前記本体部のうち2つの前記突出部の間に設けられ、前記本体部内から外部に潤滑油を排出する排油孔と、を備えたことを特徴とする軸受構造。 - 前記導油路は、前記シャフトの回転軸方向に対し傾斜する方向に直線状に延在することを特徴とする請求項1に記載の軸受構造。
- 前記導油路は、前記傾斜面に対して平行に延在していることを特徴とする請求項2に記載の軸受構造。
- 前記突出部は、前記隣接面における径方向内側の端部に連続するとともに、前記隣接面を基準にして前記隣接面に隣接する前記軸受が位置する側とは反対側に曲率中心をもつ湾曲部を有し、前記湾曲部に前記導油路が開口していることを特徴とする請求項1から3のいずれか1項に記載の軸受構造。
- 過給機であって、
軸受孔が形成されたハウジングと、
一端側にタービンインペラが設けられ、他端側にコンプレッサインペラが設けられたシャフトと、
前記軸受孔に収容され、円筒形状の本体部を有するオイルフィルムダンパと、
前記オイルフィルムダンパの前記本体部内に保持され、前記シャフトの回転軸方向に離隔して対向配置され、前記シャフトを回転自在に支持する2つの軸受と
を備え、
前記オイルフィルムダンパは、
前記2つの軸受の、互いに対向する対向面間に位置し、
前記オイルフィルムダンパは、
前記本体部の内周面から径方向内側に突出して前記2つの軸受の対向面のそれぞれに隣接する2つの突出部と、
前記突出部から前記本体部の外周面まで貫通するとともに、前記本体部の外周から前記軸受まで潤滑油を導く導油路と、
前記突出部のうち前記軸受に隣接する隣接面とは反対側に設けられ、前記隣接面から前記シャフトの回転軸方向に離隔するにつれて内径が漸増する傾斜面と、
前記本体部のうち2つの前記突出部の間に設けられ、前記本体部内から外部に潤滑油を排出する排油孔と、
を備えたことを特徴とする過給機。
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JP2016525763A JP6288267B2 (ja) | 2014-06-02 | 2015-05-20 | 軸受構造、および、過給機 |
DE112015002605.3T DE112015002605B4 (de) | 2014-06-02 | 2015-05-20 | Lageraufbau und Turbolader |
CN201580027322.8A CN106460653B (zh) | 2014-06-02 | 2015-05-20 | 轴承构造及增压器 |
US15/358,682 US10316691B2 (en) | 2014-06-02 | 2016-11-22 | Bearing structure and turbocharger |
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