WO2015166806A1 - 過給機、および、過給機給油システム - Google Patents
過給機、および、過給機給油システム Download PDFInfo
- Publication number
- WO2015166806A1 WO2015166806A1 PCT/JP2015/061587 JP2015061587W WO2015166806A1 WO 2015166806 A1 WO2015166806 A1 WO 2015166806A1 JP 2015061587 W JP2015061587 W JP 2015061587W WO 2015166806 A1 WO2015166806 A1 WO 2015166806A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- bearing surface
- bearing
- shaft
- diameter portion
- supercharger
- Prior art date
Links
Images
Classifications
-
- 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
-
- 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
- F01D25/20—Lubricating arrangements using lubrication pumps
-
- 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
-
- 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
- F16C27/02—Sliding-contact bearings
-
- 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
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
- F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure
- F16C32/0644—Details of devices to control the supply of liquids to the bearings
-
- 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
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
- F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure
- F16C32/0651—Details of the bearing area per se
- F16C32/0659—Details of the bearing area per se of pockets or grooves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
-
- 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
- F05D2240/10—Stators
- F05D2240/14—Casings or housings protecting or supporting assemblies within
-
- 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
-
- 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
-
- 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
-
- 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
-
- 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
Definitions
- the present invention relates to a supercharger whose shaft is supported by a semi-floating metal, and a supercharger oiling system.
- a turbocharger in which a turbine shaft provided with a turbine impeller at one end and a compressor impeller 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 turbine shaft by the rotation of the turbine impeller.
- the supercharger compresses air and sends it to the engine as the compressor impeller rotates.
- a bearing hole is formed in the bearing housing, and a bearing is disposed in the bearing hole.
- the bearing has an insertion hole through which the turbine shaft is inserted, and a bearing surface that receives a radial load is formed on an inner peripheral surface thereof.
- the supercharger described in Patent Document 1 is a kind of such a bearing, and is provided with a semi-floating metal in which the movement of the turbine shaft in the rotational direction is restricted.
- Lubricating oil that lubricates the semi-floating metal has foreign matter removed by the filter, but there is a risk that very fine foreign matter may enter. As described above, when the lubricating oil mixed with minute foreign matter is supplied to the semi-floating metal, the foreign matter may enter the bearing surface of the semi-floating metal.
- An object of the present invention is to provide a supercharger and a supercharger oiling system capable of suppressing foreign matter mixed in the lubricating oil from entering the bearing surface and improving the performance against foreign matter.
- a first aspect of the present invention is a supercharger, which is accommodated in a supercharger main body, a supercharger main body, provided with impellers at both ends, and formed on both sides of the small diameter portion and the rotation axis direction in the small diameter portion.
- Two bearing surfaces that support the shaft, a non-bearing surface that is formed on the inner peripheral surface of the main body and is located between the two bearing surfaces and has a larger inner diameter than the bearing surface, and opens to the non-bearing surface and is formed between the non-bearing surface and the shaft.
- a semi-floating metal that includes an oil passage that supplies lubricating oil to the gap in the radial direction, and the lubricating oil supplied to the gap lubricates the two bearing surfaces. At least one of the two bearing surfaces One bearing surface is a large-diameter portion that faces the one bearing surface in the radial direction. Also, the gist that extends proximally of the two bearing surfaces.
- the large-diameter portion includes a tapered portion that is continuous from a boundary portion with the small-diameter portion and has an outer diameter that increases as the distance from the small-diameter portion increases, and a parallel portion that is continuous from the tapered portion and has an outer diameter equal to the maximum diameter of the tapered portion.
- the bearing surface that extends in the proximity direction rather than the large diameter portion that faces the bearing surface in the radial direction has one end positioned on the end side in the separation direction of the two bearing surfaces and the other end in the proximity direction.
- a bearing groove that is located on the end side and extends in the proximity direction may be formed rather than the parallel portion of the large diameter portion.
- the bearing surface that extends in the proximity direction rather than the large-diameter portion that faces the bearing surface in the radial direction is adjacent to the other end of the bearing groove in the proximity direction and has a non-groove portion that is flush with the bearing surface. It may be.
- the bearing surface that extends in the proximity direction rather than the large diameter portion that faces the bearing surface in the radial direction is closer to the portion that extends in the proximity direction than the parallel portion of the large diameter portion that faces the bearing surface in the radial direction.
- the groove recessed in the radial direction from the inner peripheral surface of the semi-floating metal may extend in the circumferential direction of the semi-floating metal.
- a groove recessed in the radial direction from the inner peripheral surface of the semi-floating metal may extend in the circumferential direction of the semi-floating metal.
- At least one end face of both ends of the semi-floating metal in the rotation axis direction is provided with a collar that faces the one end face and rotates integrally with the shaft. You may receive a load.
- a second aspect of the present invention is a supercharger refueling system that removes foreign matter from a storage part in which lubricating oil is stored, a pump that sends out lubricating oil from the storing part, and the lubricating oil that is sent out by the pump.
- a filter unit a supercharger to which lubricating oil from which foreign matter has been removed by the filter unit is supplied, and a valve that bypasses the filter unit and opens and closes an oil passage that supplies the lubricating oil sent by the pump to the supercharger
- the supercharger is housed in the supercharger main body, the supercharger main body, the impellers are provided at both ends, and the small diameter portion is formed on both sides of the small diameter portion in the rotation axis direction than the small diameter portion.
- a non-bearing surface that is located between the two bearing surfaces and has a larger inner diameter than the bearing surface; and an oil passage that opens to the non-bearing surface and supplies lubricating oil to a radial gap between the non-bearing surface and the shaft;
- a semi-floating metal in which the lubricating oil supplied to the gap lubricates the two bearing surfaces, and at least one of the two bearing surfaces is large in size facing the one bearing surface in the radial direction.
- the gist is that it extends in the direction closer to the two bearing surfaces than the diameter portion.
- FIG. 1 is a conceptual diagram showing an outline of a supercharger refueling system according to an embodiment of the present invention.
- FIG. 2 is a schematic cross-sectional view of the supercharger according to the embodiment of the present invention.
- FIG. 3 is an extraction diagram of a broken line portion of FIG.
- FIG. 4 is a cross-sectional view of a portion corresponding to FIG. 3 in the comparative example.
- FIG. 5 is a cross-sectional view of a semi-floating metal according to an embodiment of the present invention.
- FIG. 6 is a cross-sectional view of a portion corresponding to FIG. 3 according to a first modification of the embodiment of the present invention.
- FIG. 1 is a conceptual diagram showing an outline of a supercharger refueling system according to an embodiment of the present invention.
- FIG. 2 is a schematic cross-sectional view of the supercharger according to the embodiment of the present invention.
- FIG. 3 is an extraction diagram of a broken line portion of FIG.
- FIG. 7 is a cross-sectional view of a semi-floating metal according to a second modification of the embodiment of the present invention.
- 8 is a cross-sectional view of a portion corresponding to the one-dot chain line portion of FIG. 3 according to a third modification of the embodiment of the present invention.
- FIG. 1 is a conceptual diagram showing an outline of a supercharger refueling system 100.
- the supercharger refueling system 100 includes a storage unit 102 that stores lubricating oil.
- the storage part 102 is comprised, for example with an oil pan.
- the pump 104 delivers lubricating oil from the reservoir 102.
- the filter unit 106 removes foreign matter from the lubricating oil sent from the storage unit 102 by the pump 104.
- the supercharger C is supplied with lubricating oil from which foreign matter has been removed by the filter unit 106. The supercharger C will be described later.
- an oil passage 108 is provided in the supercharger refueling system 100. In the unlikely event that a failure occurs in the filter unit 106, the oil passage 108 bypasses the filter unit 106 and supplies the lubricating oil sent out by the pump 104 to the supercharger C.
- the oil passage 108 is provided with a valve 110 for opening and closing the oil passage 108, and the valve 110 is closed while the filter unit 106 is functioning normally.
- FIG. 2 is a schematic sectional view of the supercharger C.
- the arrow L shown in FIG. 2 is described as a direction indicating the left side of the supercharger C
- the arrow R is 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, and a compressor housing 6 connected to the right side of the bearing housing 2 by fastening bolts 5. Have. 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 to each other by band fastening the protrusions 2 a and 4 a by the fastening mechanism 3.
- the fastening mechanism 3 includes a fastening band (for example, G coupling) that holds the protrusions 2a and 4a.
- the bearing housing 2 has a bearing hole 2b.
- the bearing hole 2 b extends in the left-right direction of the supercharger C and penetrates the bearing housing 2.
- a semi-floating metal 7 is provided in the bearing hole 2b, and the shaft 8 is rotatably supported by the semi-floating metal 7.
- a turbine impeller 9 is integrally fixed to the left end (one end) of the shaft 8, and the turbine impeller 9 is rotatably accommodated in the turbine housing 4.
- a compressor impeller 10 is integrally fixed to the right end (the other end) of the shaft 8, and the compressor impeller 10 is rotatably accommodated in the compressor housing 6.
- the compressor housing 6 has an intake port 11 formed therein.
- the intake port 11 opens to the right side of the supercharger C and is connected to an air cleaner (not shown). Further, in a state where the bearing housing 2 and the compressor housing 6 are connected by the fastening bolt 5, a diffuser flow path 12 that pressurizes air is formed by the facing surfaces of both the housings 2 and 6.
- the diffuser flow path 12 is formed in an annular shape from the radially inner side to the outer side of the shaft 8 (compressor impeller 10), and communicates with the intake port 11 via the compressor impeller 10 on the radially inner side. Yes.
- the compressor housing 6 is provided with a compressor scroll passage 13.
- the compressor scroll passage 13 is formed in an annular shape, and is located on the outer side in the radial direction of the shaft 8 (compressor impeller 10) than the diffuser passage 12.
- the compressor scroll flow path 13 communicates with an intake port (not shown) of the engine and also communicates with the diffuser flow path 12. Therefore, when the compressor impeller 10 rotates, air is taken into the compressor housing 6 from the intake port 11. The sucked air is accelerated by the action of centrifugal force in the process of flowing between the blades of the compressor impeller 10, is boosted in the diffuser flow path 12 and the compressor scroll flow path 13, and is guided to the intake port of the engine.
- the turbine housing 4 is formed with a discharge port 14 that opens to the left side of the supercharger C and is connected to an exhaust gas purification device (not shown). Further, the turbine housing 4 is provided with a flow path 15 and an annular turbine scroll flow path 16 positioned on the radially outer side of the shaft 8 (turbine impeller 9) with respect to the flow path 15.
- the turbine scroll passage 16 communicates with a gas inlet (not shown) through which exhaust gas discharged from an engine exhaust manifold (not shown) is guided, and also communicates with the passage 15 described above. Therefore, the exhaust gas guided from the gas inlet to the turbine scroll passage 16 is guided to the discharge port 14 via the passage 15 and the turbine impeller 9, and the turbine impeller 9 is rotated in the flow process. . Then, the rotational force of the turbine impeller 9 is transmitted to the compressor impeller 10 via the shaft 8, and the air is boosted by the rotational force of the compressor impeller 10 as described above to the intake port of the engine. Led.
- FIG. 3 is an extraction diagram of a broken line portion of FIG.
- the semi-floating metal 7 has a cylindrical main body 7a, and a shaft 8 is inserted through the main body 7a.
- Two bearing surfaces 7b and 7b are provided on the inner peripheral surface of the main body 7a. These bearing surfaces 7 b and 7 b are separated from each other in the rotation axis direction of the shaft 8.
- a non-bearing surface 7c is provided on the inner peripheral surface of the main body 7a.
- the non-bearing surface 7 c is located between the two bearing surfaces 7 b and 7 b in the rotation axis direction of the shaft 8.
- the inner diameter of the bearing surface 7b is smaller than the inner diameter of the non-bearing surface 7c.
- a small diameter portion 8 a and two large diameter portions 8 b and 8 b are formed in a portion inserted through the main body 7 a of the semi-floating metal 7.
- Each large-diameter portion 8b has a larger diameter than the small-diameter portion 8a and is formed on both sides of the small-diameter portion 8a in the rotation axis direction.
- Each large diameter portion 8 b faces the bearing surface 7 b of the semi-floating metal 7 in the radial direction of the shaft 8.
- the large-diameter portion 8b is continuous from the boundary portion with the small-diameter portion 8a, and has a tapered portion 8d whose outer diameter increases as the distance from the small-diameter portion 8a increases.
- a parallel portion 8e having an equal outer diameter.
- the non-bearing surface 7c of the semi-floating metal 7 and the shaft 8 are separated from each other in the radial direction of the shaft 8, and as a result, a gap S is formed in the main body 7a.
- the semi-floating metal 7 is provided with an oil passage 7 d penetrating in the radial direction of the shaft 8.
- the oil passage 7d faces the oil passage 2c formed in the bearing housing 2 and opens to the non-bearing surface 7c, and supplies the lubricating oil to the gap S.
- the relative movement of the semi-floating metal 7 with respect to the bearing housing 2 is restricted by the pin 17, and when the shaft 8 rotates, the semi-floating metal 7 is relatively disposed between the large diameter portion 8 b of the shaft 8 and the bearing surface 7 b of the semi-floating metal 7. Rotational movement occurs. At this time, the lubricating oil supplied to the gap S lubricates the two bearing surfaces 7b, so that the shaft 8 is pivotally supported by the bearing surfaces 7b.
- the shaft 8 is provided with a collar 8c.
- the collar 8c is continuously formed on the turbine impeller 9 side in the large-diameter portion 8b on the turbine impeller 9 side (left side in FIG. 3).
- the collar 8c has an outer diameter larger than that of the large diameter portion 8b.
- the collar 8 c faces the end surface 7 e on the turbine impeller 9 side in the rotation axis direction of the semi-floating metal 7 and rotates integrally with the shaft 8.
- the semi-floating metal 7 receives a thrust load of the shaft 8 through the collar 8c.
- FIG. 4 is a cross-sectional view of a portion corresponding to FIG. 3 in the comparative example.
- the large-diameter portion B of the shaft Sa extends from the bearing surface Ma of the semi-floating metal M in the proximity direction of the two bearing surfaces Ma.
- the proximity direction means a direction in which one of the two objects faces the other.
- Lubricating oil approaches the bearing surface Ma while flowing in the rotation direction of the shaft Sa as the shaft Sa rotates.
- the lubricating oil contains foreign matter
- the foreign matter moves along the flow of the lubricating oil in the axial direction of the shaft Sa as indicated by the white arrow in FIG. It is easy to go to the inner peripheral surface side of the metal M. For this reason, in the comparative example, a part of the foreign matter mixed in the lubricating oil may reach the bearing surface Ma.
- the bearing surface 7 b extends in the direction closer to the two bearing surfaces 7 b than the tapered portion 8 d of the large-diameter portion 8 b that faces the bearing surface 7 b in the radial direction.
- the foreign matter moves in the axial direction of the shaft 8 while moving radially outward of the shaft 8 due to centrifugal force, and approaches the bearing surface 7b. And the movement to the bearing surface 7b side is inhibited by the taper part T formed in the boundary of the bearing surface 7b and the non-bearing surface 7c.
- a region indicated by cross-hatching is a gap formed in a portion where the outer diameter on the shaft 8 side is smaller than the maximum diameter among the facing portions of the bearing surface 7 b and the shaft 8.
- the lubricating oil flows mainly in the radially outward direction rather than in the axial direction of the shaft 8. It has become.
- FIG. 5 is a cross-sectional view of the semi-floating metal 7. As shown in FIG. 5, a bearing groove 18 is formed in each of the two bearing surfaces 7b. Four bearing grooves 18 are provided at equal intervals in the circumferential direction on the bearing surface 7b, and are formed at intervals of approximately 90 degrees.
- the bearing groove 18 extends parallel to the axial direction of the shaft 8.
- One end 18a of the bearing groove 18 is located on the end portion 7g side in the separation direction of the two bearing surfaces 7b, and the other end 18b of the bearing groove 18 is located on the end portion 7h side in the proximity direction of the two bearing surfaces 7b. .
- non-groove part 19 is provided in the two bearing surfaces 7b, respectively.
- the non-groove portion 19 is adjacent to the bearing groove 18 from the bearing groove 18 to the other end 18b of the two bearing grooves 18 in the proximity direction and is flush with the bearing surface 7b.
- the bearing groove 18 extends in the direction closer to the two bearing surfaces 7b than the parallel portion 8e of the large diameter portion 8b. Therefore, even if a part of the foreign matter stays in the area indicated by cross-hatching in FIG. 3, it is possible to suppress the foreign matter from entering the bearing surface 7 b of the semi-floating metal 7.
- the bearing groove 18 does not penetrate to the taper portion T formed at the boundary between the bearing surface 7b and the non-bearing surface 7c and is retained by the taper portion T. Intrusion of foreign matter into the bearing groove 18 can be suppressed.
- FIG. 6 is a cross-sectional view of a portion corresponding to FIG. 3 according to a first modification of the present embodiment.
- the bearing surface 7b is semi-floating at a portion extending to the center side in the rotation axis direction from the parallel portion 8e of the large diameter portion 8b facing in the radial direction.
- a groove 8 f that is recessed in the radial direction of the metal 7 is formed.
- the groove 8f extends in the circumferential direction of the semi-floating metal 7, and is formed in an annular shape, for example.
- a groove 8g recessed in the radial direction of the semi-floating metal 7 is formed on the non-bearing surface 7c.
- the groove 8g extends in the circumferential direction of the semi-floating metal 7 like the groove 8f, and is formed in, for example, an annular shape.
- the lubricating oil rotates and flows as the shaft 8 rotates, so that the foreign matter also rotates with the lubricating oil and approaches the inner peripheral surface of the semi-floating metal 7 by centrifugal force. To do. As described above, by providing the grooves 8f and 8g, the foreign matter in the vicinity of the inner peripheral surface enters the grooves 8f and 8g and is blocked by the wall surfaces of the grooves 8f and 8g, so that the progression toward the bearing surface 7b is suppressed. .
- FIG. 7 is a cross-sectional view of the semi-floating metal 7 according to the second modification of the present embodiment.
- the bearing surface 7 b faces the bearing surface 7 b in the radial direction of the two large-diameter portions 8 b as in the above embodiment. It extends in the direction closer to the two bearing surfaces 7b than the larger diameter portion 8b.
- inhibition part 20 is provided in non-bearing surface 7c of semi floating metal 7 further.
- the inhibition portion 20 is configured by a groove that is recessed in the radial direction of the semi-floating metal 7, and is inclined with respect to the circumferential direction of the shaft 8.
- the obstruction part 20 is in a direction closer to the center side in the rotation axis direction, that is, away from the bearing surface 7b as the front side in the rotation direction of the shaft 8 (downwardly indicated by an arrow in FIG. 4). Inclined in the direction.
- the inhibition part 20 is formed in a spiral shape, and the foreign matter is guided toward the center side in the rotation axis direction of the semi-floating metal 7 without being detached from the inhibition part 20.
- the blocking unit 20 blocks foreign substances contained in the lubricating oil supplied to the gap S from moving to the bearing surface 7b side (in FIG. 7, the end surfaces 7e and 7f side of the semi-floating metal 7).
- FIG. 8 is a cross-sectional view of a portion corresponding to the one-dot chain line portion of FIG. 3 according to a third modification of the present embodiment.
- An outer peripheral projection 21 protruding in the radial direction extends in the circumferential direction of the shaft 8 in the small diameter portion 8 a of the shaft 8.
- the radial tip of the outer peripheral protrusion 21 extends from the proximal end of the outer peripheral protrusion 21 in the proximity direction (right side in FIG. 8) of the two bearing surfaces 7b. That is, the right side surface 21a in FIG.
- the inhibition part 22 is formed in the non-bearing surface 7c.
- the inhibition part 22 is constituted by a protrusion protruding in the radial direction of the semi-floating metal 7, and the outer peripheral protrusion 21 faces the inhibition part 22 in the radial direction.
- tip of the outer periphery protrusion 21 is extended in the right side in FIG.
- the foreign matter contained in the lubricating oil from the oil passage 7d toward the bearing surface 7b stays under the influence of the obstructing portion 22, so that it is difficult to reach the bearing surface 7b. Further, depending on the flow of the lubricating oil, the foreign matter may be brought near the outer peripheral surface of the shaft 8. In this case, the foreign matter proximate to the side surface 21 a of the outer peripheral protrusion 21 is caused by the obstructing portion 22 to be It is possible to guide in a direction away from the surface 7b.
- both of the two bearing surfaces 7b have two bearing surfaces than the large-diameter portion 8b of the two large-diameter portions 8b that faces the bearing surface 7b in the radial direction.
- the case of extending in the proximity direction of 7b has been described. However, only one of the two bearing surfaces 7b extends in a direction closer to the two bearing surfaces 7b than the large-diameter portion 8b that faces the bearing surface 7b in the radial direction. May be.
- the bearing groove 18 formed in any one of the bearing surfaces 7b may extend in the direction closer to the two bearing surfaces 7b than the parallel portion 8e of the large diameter portion 8b.
- the non-groove part 19 is good to be formed adjacent to the bearing groove 18 formed in any one bearing surface 7b.
- the groove 8g may be formed in any one of the bearing surfaces 7b at a portion extending to the center side in the rotation axis direction from the parallel portion 8e of the large diameter portion 8b opposed in the radial direction.
- the bearing groove 18 is not an essential configuration. Even when the bearing groove 18 is provided, the non-groove portion 19 may not be provided.
- the collar 8c that rotates integrally with the shaft 8 is provided, and the semi-floating metal 7 receives the thrust load of the shaft 8 through the collar 8c.
- the collar 8c is not essential in the above-described embodiments and modifications.
- the bearing surface 7b has two bearing surfaces than the large-diameter portion 8b. A configuration that extends in the proximity direction of 7b and suppresses the movement of foreign matter toward the bearing surface 7b is preferable.
- the present invention can be used for a supercharger whose shaft is supported by a semi-floating metal and a supercharger oiling system.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Supercharger (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
Description
Claims (7)
- 過給機本体と、
前記過給機本体に収容され、両端にインペラが設けられ、小径部と、該小径部における回転軸方向の両側に形成され該小径部よりも径が大きい2つの大径部とを有するシャフトと、
円筒形状であって前記シャフトが挿通される本体と、該本体の内周面に形成され該シャフトの前記大径部に対向し該シャフトを軸支する2つの軸受面と、該本体の内周面に形成され該2つの軸受面の間に位置し該軸受面よりも内径の大きい非軸受面と、該非軸受面に開口し該非軸受面と該シャフトの径方向の間隙に潤滑油を供給する油路とを有し、該間隙に供給された潤滑油が該2つの軸受面を潤滑するセミフローティングメタルと、
を備え、
前記2つの軸受面のうち、少なくともいずれか一方の軸受面は、該一方の軸受面に径方向に対向する前記大径部よりも、該2つの軸受面の近接方向に延在することを特徴とする過給機。 - 前記大径部は、前記小径部との境界部分から連続し、該小径部から離隔するにつれて外径が大きくなるテーパ部と、該テーパ部から連続し該テーパ部の最大径と等しい外径を有する平行部とを備え、
前記軸受面に径方向に対向する前記大径部よりも、前記近接方向に延在する該軸受面には、一端が前記2つの軸受面の離隔方向の端部側に位置し、他端が前記近接方向の端部側に位置し、かつ、前記大径部の平行部よりも、該近接方向に向かって延在する軸受溝が形成されていることを特徴とする請求項1に記載の過給機。 - 前記軸受面に径方向に対向する前記大径部よりも、前記近接方向に延在する該軸受面には、
前記軸受溝の他端に対して前記近接方向に隣接し、前記軸受面と面一な非溝部が形成されていることを特徴とする請求項2に記載の過給機。 - 前記軸受面に径方向に対向する前記大径部よりも、前記近接方向に延在する該軸受面には、該軸受面に径方向に対向する前記大径部の平行部よりも、前記近接方向に延在する部位に、前記セミフローティングメタルの内周面から径方向に窪んだ溝が、該セミフローティングメタルの周方向に延在していることを特徴とする請求項2または3に記載の過給
機。 - 前記非軸受面には、前記セミフローティングメタルの内周面から径方向に窪んだ溝が、
該セミフローティングメタルの周方向に延在していることを特徴とする請求項1から4のいずれか1項に記載の過給機。 - 前記セミフローティングメタルの前記回転軸方向の両端面のうち、少なくとも一方の端面側には、該一方の端面に対向し、前記シャフトと一体回転するカラーが設けられ、
前記セミフローティングメタルは、前記カラーを介して前記シャフトのスラスト荷重を受けることを特徴とする請求項1から5のいずれか1項に記載の過給機。 - 潤滑油が貯留される貯留部と、
前記貯留部から前記潤滑油を送出するポンプと、
前記ポンプによって送出された前記潤滑油から異物を除去するフィルタ部と、
前記フィルタ部によって異物を除去された前記潤滑油が供給される過給機と、
前記フィルタ部をバイパスして、前記ポンプによって送出された前記潤滑油を前記過給機に供給する油路を開閉するバルブと、
を備え、
前記過給機は、
過給機本体と、
前記過給機本体に収容され、両端にインペラが設けられ、小径部と、該小径部における回転軸方向の両側に形成され該小径部よりも径が大きい2つの大径部とを有するシャフトと、
円筒形状であって前記シャフトが挿通される本体と、該本体の内周面に形成され該シャフトの前記大径部に対向し該シャフトを軸支する2つの軸受面と、該本体の内周面に形成され該2つの軸受面の間に位置し該軸受面よりも内径の大きい非軸受面と、該非軸受面に開口し該非軸受面と該シャフトの径方向の間隙に潤滑油を供給する油路とを有し、該間隙に供給された潤滑油が該2つの軸受面を潤滑するセミフローティングメタルと、
を備え、
前記2つの軸受面のうち、少なくともいずれか一方の軸受面は、該一方の軸受面に径方向に対向する前記大径部よりも、該2つの軸受面の近接方向に延在することを特徴とする過給機給油システム。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201580008347.3A CN105980686B (zh) | 2014-04-30 | 2015-04-15 | 增压器及增压器供油系统 |
DE112015002038.1T DE112015002038B4 (de) | 2014-04-30 | 2015-04-15 | Turbolader und Turboladerölzuführsystem |
JP2016515929A JP6660293B2 (ja) | 2014-04-30 | 2015-04-15 | 過給機、および、過給機給油システム |
US15/233,063 US10352232B2 (en) | 2014-04-30 | 2016-08-10 | Turbocharger and turbocharger oil supply system |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2014093745 | 2014-04-30 | ||
JP2014-093745 | 2014-04-30 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US15/233,063 Continuation US10352232B2 (en) | 2014-04-30 | 2016-08-10 | Turbocharger and turbocharger oil supply system |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2015166806A1 true WO2015166806A1 (ja) | 2015-11-05 |
Family
ID=54358541
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2015/061587 WO2015166806A1 (ja) | 2014-04-30 | 2015-04-15 | 過給機、および、過給機給油システム |
Country Status (5)
Country | Link |
---|---|
US (1) | US10352232B2 (ja) |
JP (2) | JP6660293B2 (ja) |
CN (1) | CN105980686B (ja) |
DE (1) | DE112015002038B4 (ja) |
WO (1) | WO2015166806A1 (ja) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2018138938A1 (ja) * | 2017-01-27 | 2018-08-02 | 三菱重工エンジン&ターボチャージャ株式会社 | 軸受の給油装置および排気タービン過給機 |
JP2019178765A (ja) * | 2018-03-30 | 2019-10-17 | 株式会社Ihi | 軸受構造 |
JPWO2019155797A1 (ja) * | 2018-02-08 | 2021-01-14 | 株式会社Ihi | 軸受構造 |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE112015003175T5 (de) * | 2014-07-09 | 2017-03-16 | Ihi Corporation | Lagerstruktur und Turbolader |
CN107923439B (zh) * | 2015-08-11 | 2019-08-16 | 株式会社Ihi | 轴承构造以及增压器 |
DE112017005884T5 (de) | 2016-11-21 | 2019-08-08 | Ihi Corporation | Lagerstruktur und Turbolader |
US10190634B1 (en) * | 2017-07-11 | 2019-01-29 | GM Global Technology Operations LLC | Turbo-charger bearing |
US10557498B1 (en) * | 2018-10-12 | 2020-02-11 | Borgwarner Inc. | Full-floating bearing and turbocharger including the same |
CN109372597B (zh) * | 2018-11-30 | 2021-05-18 | 江苏理工学院 | 一种可调式涡轮增压器 |
DE102019108223A1 (de) * | 2019-03-29 | 2020-10-01 | Bayerische Motoren Werke Aktiengesellschaft | Verbrennungskraftmaschine für ein Kraftfahrzeug, insbesondere für einen Kraftwagen, sowie Kraftfahrzeug |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4411531Y1 (ja) * | 1965-08-24 | 1969-05-14 | ||
JPS606838U (ja) * | 1983-06-25 | 1985-01-18 | 三菱重工業株式会社 | 排気タ−ビン過給機の軸受構造 |
JP2000087753A (ja) * | 1998-09-11 | 2000-03-28 | Toyota Motor Corp | 排気駆動式過給機の潤滑油供給装置 |
JP2013245663A (ja) * | 2012-05-29 | 2013-12-09 | Ihi Corp | 過給機 |
JP2014047700A (ja) * | 2012-08-31 | 2014-03-17 | Daihatsu Motor Co Ltd | ターボ過給機 |
JP2014051898A (ja) * | 2012-09-05 | 2014-03-20 | Ihi Corp | 過給機 |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH06586Y2 (ja) * | 1983-06-28 | 1994-01-05 | 日野自動車工業株式会社 | エンジンのスワ−ル制御装置 |
JP2009167803A (ja) * | 2008-01-10 | 2009-07-30 | Jtekt Corp | 過給機 |
DE102008020067A1 (de) * | 2008-04-22 | 2009-10-29 | Schaeffler Kg | Lageranordnung mit einem doppelreihigen Wälzlager, Turbolader und Verfahren zur Zuführung eines Schmiermittels zu den Wälzkörperreihen eines doppelreihigen Wälzlagers |
JP2012193709A (ja) * | 2011-03-17 | 2012-10-11 | Toyota Industries Corp | ターボチャージャの軸受構造 |
JP6145959B2 (ja) | 2011-07-12 | 2017-06-14 | 株式会社Ihi | ターボチャージャ |
WO2013173220A1 (en) * | 2012-05-15 | 2013-11-21 | Honeywell International Inc. | Turbocharger with journal bearing |
JP5996301B2 (ja) * | 2012-06-29 | 2016-09-21 | ダイハツ工業株式会社 | ターボ過給機 |
-
2015
- 2015-04-15 JP JP2016515929A patent/JP6660293B2/ja active Active
- 2015-04-15 DE DE112015002038.1T patent/DE112015002038B4/de active Active
- 2015-04-15 WO PCT/JP2015/061587 patent/WO2015166806A1/ja active Application Filing
- 2015-04-15 CN CN201580008347.3A patent/CN105980686B/zh active Active
-
2016
- 2016-08-10 US US15/233,063 patent/US10352232B2/en active Active
-
2018
- 2018-11-09 JP JP2018211582A patent/JP6610753B2/ja active Active
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4411531Y1 (ja) * | 1965-08-24 | 1969-05-14 | ||
JPS606838U (ja) * | 1983-06-25 | 1985-01-18 | 三菱重工業株式会社 | 排気タ−ビン過給機の軸受構造 |
JP2000087753A (ja) * | 1998-09-11 | 2000-03-28 | Toyota Motor Corp | 排気駆動式過給機の潤滑油供給装置 |
JP2013245663A (ja) * | 2012-05-29 | 2013-12-09 | Ihi Corp | 過給機 |
JP2014047700A (ja) * | 2012-08-31 | 2014-03-17 | Daihatsu Motor Co Ltd | ターボ過給機 |
JP2014051898A (ja) * | 2012-09-05 | 2014-03-20 | Ihi Corp | 過給機 |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2018138938A1 (ja) * | 2017-01-27 | 2018-08-02 | 三菱重工エンジン&ターボチャージャ株式会社 | 軸受の給油装置および排気タービン過給機 |
US11066983B2 (en) | 2017-01-27 | 2021-07-20 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Lubricating device for bearing, and exhaust turbosupercharger |
JPWO2019155797A1 (ja) * | 2018-02-08 | 2021-01-14 | 株式会社Ihi | 軸受構造 |
JP7056676B2 (ja) | 2018-02-08 | 2022-04-19 | 株式会社Ihi | 軸受構造 |
JP2019178765A (ja) * | 2018-03-30 | 2019-10-17 | 株式会社Ihi | 軸受構造 |
JP7003809B2 (ja) | 2018-03-30 | 2022-01-21 | 株式会社Ihi | 軸受構造 |
Also Published As
Publication number | Publication date |
---|---|
DE112015002038T5 (de) | 2017-03-09 |
DE112015002038B4 (de) | 2021-03-18 |
JP2019056376A (ja) | 2019-04-11 |
US20160348577A1 (en) | 2016-12-01 |
CN105980686A (zh) | 2016-09-28 |
US10352232B2 (en) | 2019-07-16 |
CN105980686B (zh) | 2018-11-30 |
JP6610753B2 (ja) | 2019-11-27 |
JPWO2015166806A1 (ja) | 2017-04-20 |
JP6660293B2 (ja) | 2020-03-11 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP6610753B2 (ja) | 過給機、および、過給機給油システム | |
EP2500544B1 (en) | Bearing device | |
US10024361B2 (en) | Bearing structure and turbocharger | |
US20170198713A1 (en) | Centrifugal compressor and turbocharger | |
JP6248479B2 (ja) | ロータ軸支持構造及び過給機 | |
US10480575B2 (en) | Bearing structure and turbocharger | |
JP6206592B2 (ja) | 軸受構造、および、過給機 | |
US20170328236A1 (en) | Oil discharging structure for bearing | |
JP2012237254A (ja) | 潤滑油路構造及び過給機 | |
JP4981372B2 (ja) | 軸受装置 | |
WO2017026293A1 (ja) | 軸受構造、および、過給機 | |
US20190107052A1 (en) | Turbocharger | |
JP2015151900A (ja) | 軸受構造、および、過給機 | |
JP2013177900A (ja) | 軸受装置 | |
JP6459247B2 (ja) | スラスト軸受、および、過給機 | |
JP2015209837A (ja) | 過給機、および、過給機給油システム | |
JP2016008600A (ja) | 軸受機構および過給機 | |
JP6512296B2 (ja) | 軸受構造および過給機 | |
JP2016113937A (ja) | ターボチャージャ用軸受機構 | |
JP2015048756A (ja) | ロータ軸支持構造及び過給機 | |
WO2022107519A1 (ja) | 遠心圧縮機および過給機 | |
US11371512B2 (en) | Centrifugal compressor and seal unit | |
JP2019178765A (ja) | 軸受構造 | |
JP2020051393A (ja) | 排気ターボ過給機の軸受の構造 | |
JPWO2019039338A1 (ja) | 過給機 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 15785645 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2016515929 Country of ref document: JP Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 112015002038 Country of ref document: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 15785645 Country of ref document: EP Kind code of ref document: A1 |