WO2017014084A1 - 軸受構造および過給機 - Google Patents
軸受構造および過給機 Download PDFInfo
- Publication number
- WO2017014084A1 WO2017014084A1 PCT/JP2016/070401 JP2016070401W WO2017014084A1 WO 2017014084 A1 WO2017014084 A1 WO 2017014084A1 JP 2016070401 W JP2016070401 W JP 2016070401W WO 2017014084 A1 WO2017014084 A1 WO 2017014084A1
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- Prior art keywords
- bearing
- hole
- shaft
- opening
- oil
- Prior art date
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Classifications
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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
- 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
- F01D25/183—Sealing means
- F01D25/186—Sealing means for sliding contact bearing
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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
- F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
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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
- F16C27/02—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
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/02—Rigid support of bearing units; Housings, e.g. caps, covers in the case of sliding-contact bearings
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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
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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
- 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 bearing structure provided with a semi-floating bearing and a supercharger equipped with the bearing structure.
- a turbocharger in which a shaft is rotatably supported by a bearing housing is known.
- a turbine impeller is provided at one end of the shaft, and a compressor impeller is provided at the other end of the shaft.
- the supercharger is connected to the engine.
- the turbine impeller is rotated by exhaust gas discharged from the engine.
- the rotation of the turbine impeller causes the compressor impeller to rotate through the shaft.
- the supercharger compresses air as the compressor impeller rotates and sends the compressed air to the engine.
- Patent Document 1 discloses a supercharger provided with a full floating bearing which is a kind of bearing.
- the full floating bearing includes an annular main body portion through which a shaft is inserted.
- the main body is rotatably accommodated in a bearing hole formed in the housing.
- a bearing surface that rotatably supports the shaft is formed on the inner peripheral surface of the main body.
- An oil supply passage for supplying lubricating oil to the bearing surface is formed in the housing.
- An object of the present disclosure is to provide a bearing structure and a supercharger that can improve the suppression effect of self-excited vibration.
- a bearing structure includes a housing in which a bearing hole in which an opening of an oil supply passage is formed, an annular shape that is accommodated in the bearing hole and has a bearing surface on an inner peripheral surface thereof.
- One or a plurality of oil guide holes penetrating from the outer peripheral surface to the inner peripheral surface of the main body portion are formed in the main body portion, and at least one of the oil guide holes is partially or entirely opposed to the opening portion of the oil supply passage, and
- a semi-floating bearing which is a special hole whose length in the rotational direction of the shaft is longer than the length in the axial direction.
- two bearing surfaces may be provided apart from each other in the axial direction of the shaft, and the special hole may be opened in one of the two bearing surfaces.
- the oil guide hole may be provided in each of the two bearing surfaces, and one of the two oil guide holes may be a special hole.
- a bearing structure includes a housing in which a bearing hole in which an opening of an oil supply passage is formed, and a housing 2 accommodated in the bearing hole and spaced apart from each other in the axial direction of the shaft.
- An annular main body having two bearing surfaces formed on the inner peripheral surface, and one end of one of the two bearing surfaces is open at one end, and part or all of the other end is an opening of the oil supply passage.
- a semi-floating bearing having an oil guide hole facing the portion.
- a bearing structure includes a housing in which a bearing hole in which an opening of an oil supply passage is formed, and a housing 2 accommodated in the bearing hole and spaced apart from each other in the axial direction of the shaft.
- a semi-floating bearing having an annular main body with two bearing surfaces formed on the inner peripheral surface, and formed in the main body of the semi-floating bearing, with one end opened on the bearing surface and part or all of the other end being an oil supply passage Provided on each of the two bearing surfaces that are different from each other in at least one of an area facing the opening in the radial direction of the shaft, an opening area at the other end, and a position in the rotation direction of the shaft.
- Two oil guide holes formed.
- the turbocharger of the present disclosure includes any one of the above bearing structures.
- the effect of suppressing self-excited vibration can be improved.
- FIG. 3 (a) is a view taken along the arrow III (a) in FIG. 2
- FIG. 3 (b) is a view taken along the arrow III (b) in FIG. 2
- FIG. 3 (c) is a view taken along III (c) in FIG.
- FIG. 3 (d) is a cross-sectional view taken along line -III (c)
- FIG. 3 (d) is a cross-sectional view taken along line III (d) -III (d) in FIG.
- FIGS. 5A and 5B are diagrams for explaining the second modification
- FIGS. 5C and 5D are diagrams for explaining the third modification. is there.
- FIG. 1 is a schematic sectional view of the supercharger C.
- the arrow L direction shown in the figure is the left side of the supercharger C
- the arrow R direction is the right side of the supercharger C.
- the supercharger C includes a supercharger main body 1.
- the supercharger main body 1 includes a bearing housing 2 (housing).
- a turbine housing 4 is connected to the left side of the bearing housing 2 by fastening bolts 3.
- a compressor housing 6 is connected to the right side of the bearing housing 2 by fastening bolts 5.
- the supercharger main body 1 is formed by integrating a bearing housing 2, a turbine housing 4, and a compressor housing 6.
- the bearing housing 2 is formed with a bearing hole 2a that penetrates the supercharger C in the left-right direction.
- the bearing housing 2 is formed with an oil supply passage 7 for introducing lubricating oil from the outside into the bearing hole 2a.
- a semi-floating bearing S is accommodated in the bearing hole 2 a filled with the lubricating oil supplied from the oil supply passage 7.
- a shaft 8 is rotatably supported by the semi-floating bearing S.
- a turbine impeller 9 is integrally fixed to the left end portion of the shaft 8.
- the turbine impeller 9 is rotatably accommodated in the turbine housing 4.
- a compressor impeller 10 is integrally fixed to the right end portion of the shaft 8.
- 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 on the right side of the supercharger C.
- An air cleaner (not shown) is connected to the intake port 11.
- a diffuser flow path 12 that pressurizes air is formed by the facing surfaces of both the housings 2 and 6.
- the diffuser channel 12 is formed in an annular shape from the radially inner side to the outer side of the shaft 8.
- the diffuser flow path 12 communicates with the intake port 11 via the compressor impeller 10 on the radially inner side.
- the compressor housing 6 is provided with an annular compressor scroll passage 13.
- the compressor scroll flow path 13 is located on the outer side in the radial direction of the shaft 8 than the diffuser flow path 12.
- the compressor scroll passage 13 communicates with an intake port of an engine (not shown). Further, the compressor scroll passage 13 communicates with the diffuser passage 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 increased in pressure and pressure in the process of flowing between the blades of the compressor impeller 10. The air is boosted in the diffuser flow path 12 and the compressor scroll flow path 13 and guided to the intake port of the engine.
- a discharge port 14 is formed in the turbine housing 4.
- the discharge port 14 opens on the left side of the supercharger C.
- An exhaust gas purification device (not shown) is connected to the discharge port 14.
- the turbine housing 4 is provided with a flow path 15.
- the turbine housing 4 is provided with an annular turbine scroll passage 16.
- the turbine scroll passage 16 is located on the outer side in the radial direction of the shaft 8 (turbine impeller 9) than the passage 15.
- the turbine scroll passage 16 communicates with a gas inlet (not shown) through which exhaust gas discharged from the exhaust manifold of the engine is guided. Further, the turbine scroll flow path 16 communicates with the flow path 15. 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.
- the exhaust gas rotates the turbine impeller 9 in the flow process.
- the rotational force of the turbine impeller 9 is transmitted to the compressor impeller 10 via the shaft 8.
- the air is pressurized by the rotational force of the compressor impeller 10 and guided to the intake port of the engine.
- FIG. 2 is an extraction diagram of a one-dot chain line portion of FIG.
- the supercharger C includes a bearing structure 20.
- the bearing structure 20 includes a bearing hole 2 a and an oil supply passage 7 formed in the bearing housing 2, and a semi-floating bearing S.
- the bearing structure 20 of the supercharger C that supports the shaft 8 will be described in detail below.
- the semi-floating bearing S includes an annular main body 21 accommodated in the bearing hole 2a.
- a T-side (turbine housing 4 side) bearing surface 21 a and a C-side (compressor housing 6 side) bearing surface 21 b are provided on the inner periphery of the main body 21.
- the T-side bearing surface 21a is located on the turbine housing 4 side.
- the C-side bearing surface 21b is located closer to the compressor housing 6 than the T-side bearing surface 21a.
- the T-side bearing surface 21 a and the C-side bearing surface 21 b are separated in the axial direction of the shaft 8.
- the shaft 8 inserted through the main body 21 is rotatably supported by the T-side bearing surface 21a and the C-side bearing surface 21b.
- a pin hole 21c is formed between the T-side bearing surface 21a and the C-side bearing surface 21b.
- the pin hole 21 c penetrates in the direction intersecting the axial direction of the shaft 8, here, in the radial direction of the shaft 8.
- the bearing housing 2 is formed with a through hole 2b.
- the regulation pin 22 is fixed to the through hole 2b by press fitting, for example.
- the through hole 2b is provided at a position facing the pin hole 21c.
- the regulation pin 22 fixed to the through hole 2b has its tip inserted into the pin hole 21c. Thereby, the semi-floating bearing S is restricted from moving in the rotational direction of the shaft 8.
- a gap 23 is formed between the outer peripheral surface of the main body 21 and the inner peripheral surface of the bearing hole 2a.
- damper surfaces 21 d are formed at both axial ends of the shaft 8.
- the damper surface 21d is a portion where the gap 23 formed between the main body 21 and the bearing hole 2a is the smallest.
- the shaft 8 is provided with a flange portion 8a.
- the flange portion 8a is located in the bearing hole 2a.
- the flange portion 8a has an outer diameter larger than a portion inserted through the main body portion 21 of the semi-floating bearing S.
- the flange portion 8a opposes one end surface of the main body portion 21 in the axial direction of the shaft 8 (here, the left side in FIG. 2).
- the oil draining member 24 is disposed opposite to the other end surface of the main body 21 in the axial direction of the shaft 8 (here, the right side in FIG. 2).
- the oil draining member 24 rotates integrally with the shaft 8.
- the oil draining member 24 is fixed to the shaft 8 by, for example, bolt fastening.
- the oil draining member 24 scatters the lubricating oil from the semi-floating bearing S toward the compressor impeller 10 toward the radially outer side of the shaft 8. Thereby, leakage of the lubricating oil to the compressor impeller 10 side is
- the semi-floating bearing S is located between the flange portion 8a of the shaft 8 and the oil draining member 24. And the both end surfaces of the axial direction of the main-body part 21 are facing the flange part 8a and the oil draining member 24, respectively. Therefore, the semi-floating bearing S receives a thrust load from the flange portion 8a and the oil draining member 24. The semi-floating bearing S receives a radial load of the shaft 8 on the T-side bearing surface 21a and the C-side bearing surface 21b.
- the bearing housing 2 is formed with an oil supply passage 7 for guiding lubricating oil from the outside to the bearing hole 2a.
- the oil supply passage 7 is branched into two passages in the bearing housing 2.
- the branched passages are opened at two different locations of the bearing hole 2a.
- the opening part relatively located in the turbine housing 4 side among the opening parts of the oil supply passage 7 in the bearing hole 2a is referred to as a T-side opening part 7a.
- path 7 in the bearing hole 2a is made into the C side opening part 7b.
- the T-side opening 7 a is located radially outward of the T-side bearing surface 21 a of the main body 21.
- the C-side opening 7b is located radially outward of the C-side bearing surface 21b of the main body 21.
- the main body portion 21 is formed with a T-side oil guide hole 25a and a C-side oil guide hole 25b.
- the T-side oil guide hole 25a penetrates in the radial direction of the shaft 8 from the T-side bearing surface 21a to the damper surface 21d.
- the C-side oil introduction hole 25b penetrates in the radial direction of the shaft 8 from the C-side bearing surface 21b to the damper surface 21d.
- the T-side opening 7a is located radially outward of the T-side bearing surface 21a.
- the T-side oil introduction hole 25a has an inner peripheral surface side of the main body portion 21 that opens to the T-side bearing surface 21a, and an opening on the outer peripheral surface side of the main body portion 21 faces the T-side opening portion 7a.
- the C side opening 7b is located radially outward of the C side bearing surface 21b.
- the C-side oil introduction hole 25b has an inner peripheral surface side of the main body portion 21 that opens to the C-side bearing surface 21b, and an opening on the outer peripheral surface side of the main body portion 21 faces the C-side opening portion 7b.
- each of the T-side opening 7a and the C-side opening 7b maintains a dimensional relationship that does not face the T-side oil introduction hole 25a and the C-side oil introduction hole 25b. Therefore, a part of the lubricating oil guided to the bearing hole 2 a from the T-side opening 7 a and the C-side opening 7 b is guided to the outer peripheral surface side of the main body 21. A damper function is exhibited on the damper surface 21 d by a part of the lubricating oil guided to the outer peripheral surface side of the main body 21.
- the shape of the T side oil guide hole 25a and the C side oil guide hole 25b will be described in detail.
- FIG. 3 is a diagram for explaining the T-side oil introduction hole 25a and the C-side oil introduction hole 25b.
- FIG. 3A shows a view taken along arrow III (a) in FIG.
- FIG. 3B shows a view taken in the direction of arrow III (b) in FIG.
- the bearing housing 2 is omitted.
- FIGS. 3A and 3B only the T-side opening 7a or the C-side opening 7b is indicated by a broken line.
- FIG. 3C shows a cross-sectional view taken along the line III (c) -III (c) in FIG.
- FIG. 3D shows a cross-sectional view taken along line III (d) -III (d) in FIG.
- the T-side opening 7a and the T-side oil introduction hole 25a are both substantially circular. Further, the T-side opening 7a and the T-side oil introduction hole 25a are provided at positions where their centers are substantially coincided with each other. However, the opening area of the T-side oil guide hole 25a is smaller than the opening area of the T-side opening 7a. Therefore, although the center side of the T side opening 7a faces the T side oil guide hole 25a, the outer peripheral edge of the T side opening 7a is not opposed to the T side oil guide hole 25a. That is, the outer peripheral edge side of the T-side opening 7 a faces the outer peripheral surface of the main body 21.
- the opening areas of the T-side oil introduction hole 25a and the T-side opening 7a are different from each other. Thereby, the lubricating oil guided from the T-side oil guide hole 25a to the bearing hole 2a is appropriately distributed to the T-side bearing surface 21a and the damper surface 21d.
- the C-side opening 7b has the same shape as the T-side opening 7a.
- the C-side oil introduction hole 25b has a long hole shape extending in the rotation direction of the shaft 8 (vertical direction in FIG. 3B). More specifically, a part of the C-side oil introduction hole 25 b faces the C-side opening 7 b of the oil supply passage 7. Further, the C-side oil introduction hole 25b is a special hole whose length in the rotation direction of the shaft 8 is longer than the length in the axial direction. In the following, a hole in which the length of the shaft 8 in the rotational direction is longer than the length in the axial direction is simply referred to as a “special hole”.
- Lubricating oil is pumped into the oil supply passage 7 by the discharge pressure of an engine pump or the like. Therefore, a load acts on the shaft 8 downward in the vertical direction, as indicated by a black arrow in FIG. 3D, due to the lubricating oil entering the C-side oil introduction hole 25b from the C-side opening 7b.
- the C-side oil guide hole 25 b has a long hole shape extending in the rotation direction of the shaft 8. Therefore, in the outer peripheral surface of the shaft 8, the area facing the C-side opening 7b via the C-side oil introduction hole 25b (the range indicated by cross hatching in FIG. 3D) is increased.
- the portion of the outer peripheral surface of the shaft 8 that faces the C-side opening 7b through the C-side oil introduction hole 25b is a pressure receiving surface that receives the pressure of the lubricating oil.
- the semi-floating bearing S is employed in the bearing structure 20 of the present embodiment.
- the semi-floating bearing S is less likely to generate self-excited vibration than the full floating bearing, for example.
- the bearing structure 20 further applies the above configuration to such a semi-floating bearing S. Therefore, the bearing structure 20 can reliably suppress self-excited vibration even when the speed is further increased.
- the main body portion 21 of the semi-floating bearing S is provided with two bearing surfaces (T-side bearing surface 21a and C-side bearing surface 21b) that are spaced apart from each other in the axial direction of the shaft 8. And the oil guide hole (T side oil guide hole 25a and C side oil guide hole 25b) is opened to each bearing surface.
- the number of bearing surfaces provided on the inner peripheral surface of the main body 21 is not particularly limited.
- the oil guide holes are opened in each of the two bearing surfaces (T-side bearing surface 21a and C-side bearing surface 21b).
- the C-side oil guide hole 25b is a special hole.
- both the T-side oil introduction hole 25a and the C-side oil introduction hole 25b may be special holes.
- only the T-side oil guide hole 25a may be a special hole.
- the turbine impeller 9 is often made of a heat-resistant alloy
- the compressor impeller 10 is often made of an aluminum-based material.
- a heat-resistant alloy is a metal having a specific gravity greater than that of an aluminum-based material. Therefore, the position of the center of gravity in the axial direction of the shaft 8 is closer to the T-side bearing surface 21a side in the region of the T-side bearing surface 21a or between the T-side bearing surface 21a and the C-side bearing surface 21b. For this reason, the bearing load by the dead weight which acts on the C side bearing surface 21b is small compared with the T side bearing surface 21a.
- the main body portion 21 is provided with two oil guide holes (T-side oil guide hole 25a and C-side oil guide hole 25b).
- T-side opening 7a and the C-side opening 7b of the oil supply passage 7 are opposed to these oil guide holes.
- the number and arrangement of the oil guide holes are not limited to this.
- FIG. 4 is a diagram for explaining the first modification.
- the bearing structure 30 shown in FIG. 4 is provided with an opening 7c instead of the T-side opening 7a and the C-side opening 7b of the above embodiment.
- the bearing structure 30 is provided with an oil guide hole 25c instead of the T-side oil guide hole 25a and the C-side oil guide hole 25b.
- Other configurations of the bearing structure 30 are the same as those in the above embodiment. Therefore, here, the same components as those in the above embodiment are denoted by the same reference numerals, and description thereof is omitted.
- an oil guide hole 25c is formed in the main body portion 21 of the semi-floating bearing S1. As illustrated, the oil guide hole 25c is provided between the T-side bearing surface 21a and the C-side bearing surface 21b.
- the oil guide hole 25c is formed of a special hole in the same manner as the C-side oil guide hole 25b of the above embodiment.
- the oil supply passage 7 formed in the bearing housing 2 opens into the bearing hole 2a at the opening 7c. A part of the opening 7c faces the oil guide hole 25c.
- the oil guide hole for guiding the lubricating oil from the outer peripheral surface side to the inner peripheral surface side of the main body portion 21 is a special hole, the oil guide hole is not necessarily provided on the bearing surface.
- the special hole may be provided at a position different from the bearing surface, like the oil guide hole 25c. That is, the number and arrangement of the oil guide holes formed by the special holes may be appropriately designed.
- the load acting on the shaft 8 is increased and the self-excited vibration is suppressed as in the above embodiment.
- the oil guide hole 25c is provided at a location different from the bearing surface, if the radial distance between the opening 7c and the oil guide hole 25c increases, a load is less likely to act on the shaft 8. . Therefore, it is desirable to reduce the radial distance between the opening 7c and the oil guide hole 25c.
- FIG. 5 is a diagram for explaining the second modification and the third modification.
- FIGS. 5A and 5B show a second modification
- FIGS. 5C and 5D show a third modification.
- the C side oil guide hole 25b of the said embodiment is changed into the C side oil guide hole 25d.
- the T side opening part 7a of the said embodiment is changed into the T side opening part 7d
- the C side oil guide hole 25b is changed into the C side oil guide hole 25e.
- the other configurations of the second modification and the third modification are all the same as in the above embodiment.
- the C-side oil guide hole 25d of the second modification shown in FIG. 5B has a perfect circle shape like the T-side oil guide hole 25a.
- the C-side oil introduction hole 25d has a larger area than the T-side oil introduction hole 25a.
- the area where the C-side opening 7b and the C-side oil guide hole 25d face each other in the radial direction of the shaft 8 is the area where the T-side opening 7a and the T-side oil guide hole 25a face each other in the radial direction of the shaft 8. Bigger than.
- the load acting on the shaft 8 due to the pressure of the lubricating oil is greater on the compressor housing 6 side than on the turbine housing 4 side.
- the amount of eccentricity of the shaft 8 with respect to the C-side bearing surface 21b which often has a small bearing load, is positively increased. Thus, self-excited vibration is suppressed.
- the C-side oil guide hole 25e of the third modification shown in FIG. 5 (d) has a perfect circle shape like the T-side oil guide hole 25a.
- the T-side oil guide hole 25a and the C-side oil guide hole 25e have the same shape.
- the T-side opening 7d has a smaller opening area than the C-side opening 7b.
- the T-side opening 7d is provided at a position slightly shifted in the circumferential direction of the bearing hole 2a with respect to the C-side opening 7b.
- the area where the C-side oil introduction hole 25e and the C-side opening 7b oppose each other in the radial direction of the shaft 8 is such that the T-side oil introduction hole 25a and the T-side opening 7d oppose each other in the radial direction of the shaft 8. It is larger than the area.
- the load acting on the shaft 8 due to the pressure of the lubricating oil is greater on the compressor housing 6 side than on the turbine housing 4 side.
- the amount of eccentricity of the shaft 8 with respect to the C-side bearing surface 21b increases, and self-excited vibration is suppressed.
- FIG. 6 is an explanatory diagram for explaining a fourth modification.
- the T-side oil introduction hole 25a of the above embodiment is changed to the T-side oil introduction hole 25f
- the T-side opening 7a is changed to the T-side opening 7e.
- the fourth modified example except for the position of the center of gravity in the axial direction of the shaft 8, all other configurations are the same as those in the above embodiment.
- the fourth modified example is particularly when the position of the center of gravity in the axial direction of the shaft 8 is located on the turbine impeller 9 side (the direction away from the C-side bearing surface 21b) outside the region of the T-side bearing surface 21a. It is valid.
- the volume of the turbine impeller 9 may be larger than that of the compressor impeller 10 depending on the engine specifications. As the volume of the turbine impeller 9 is larger than that of the compressor impeller 10, the position of the center of gravity in the axial direction of the shaft 8 is closer to the turbine impeller 9 side.
- a T-side oil introduction hole 25f is formed in the main body portion 21 of the semi-floating bearing S2. As shown in the figure, the T-side oil introduction hole 25f opens one end on the inner peripheral surface side of the T-side bearing surface 21a.
- the T-side oil introduction hole 25f differs from the C-side oil introduction hole 25b by about 180 ° in the rotational direction position of the shaft 8, that is, the circumferential position of the main body portion 21.
- the self-excited vibration suppressing effect can be obtained without using the oil guide hole as a special hole as in the above-described embodiment and the first modification.
- the two oil guide holes are an area facing the opening in the radial direction of the shaft 8, an area of the opening facing the opening of the oil supply passage among the oil guide holes, and a position in the rotation direction of the shaft 8. It is sufficient that at least one of the above is different from each other.
- Each of the two oil guide holes faces part or all of the opening of the oil supply passage. Further, in addition to this, it is possible to combine the above-described embodiment or the first modification and make the oil guide hole a special hole.
- the T-side opening 7a and the T-side oil introduction hole 25a are eliminated. And you may provide only the C side opening part 7b and the C side oil guide hole 25b.
- the oil supply may be performed directly from the oil supply passage 7 only on one of the two bearing surfaces. Also in this case, the amount of eccentricity of the shaft 8 with respect to the C-side bearing surface 21b increases, and self-excited vibration can be suppressed.
- the opening 7c and the oil guide hole 25c of the first modification may be additionally formed.
- the oil guide hole formed in the main body portion 21 is only partially opposed to the opening portion of the oil supply passage 7 that opens to the bearing hole 2a.
- the entire oil guide hole may face the opening.
- bearing structure of the above embodiment and each modified example is applicable not only to the supercharger but also to various rotating machines.
- the present disclosure can be used for a bearing structure provided with a semi-floating bearing and a supercharger including the bearing structure.
Abstract
Description
2 ベアリングハウジング(ハウジング)
2a 軸受孔
7 給油通路
7a T側開口部(開口部)
7b C側開口部(開口部)
7c 開口部
7d T側開口部(開口部)
7e T側開口部(開口部)
8 シャフト
20 軸受構造
21 本体部
21a T側軸受面(軸受面)
21b C側軸受面(軸受面)
25a T側導油孔(導油孔)
25b C側導油孔(導油孔)
25c 導油孔
25d C側導油孔(導油孔)
25e C側導油孔(導油孔)
25f T側導油孔(導油孔)
30 軸受構造
40 軸受構造
C 過給機
S セミフローティング軸受
S1 セミフローティング軸受
S2 セミフローティング軸受
Claims (6)
- 給油通路の開口部が開口する軸受孔が形成されたハウジングと、
前記軸受孔に収容され、内周面に軸受面が設けられた環状の本体部に、前記本体部の外周面から内周面まで貫通する1または複数の導油孔が形成され、前記導油孔の少なくとも1つが、前記給油通路の開口部に一部もしくは全部が対向し、かつ、シャフトの回転方向の長さが軸方向の長さよりも長い特殊孔であるセミフローティング軸受と、
を備える軸受構造。 - 前記軸受面は、前記シャフトの軸方向に互いに離隔して2つ設けられ、
前記特殊孔は、2つの前記軸受面のいずれか一方に開口している請求項1に記載の軸受構造。 - 前記導油孔は、2つの前記軸受面それぞれに設けられ、
2つの前記導油孔のうちの一方が前記特殊孔である請求項2に記載の軸受構造。 - 給油通路の開口部が開口する軸受孔が形成されたハウジングと、
前記軸受孔に収容され、シャフトの軸方向に互いに離隔して設けられる2つの軸受面が内周面に形成された環状の本体部、および、前記本体部に形成され、2つの前記軸受面のいずれか一方に一端が開口し、他端の一部もしくは全部が前記給油通路の開口部に対向する導油孔を有するセミフローティング軸受と、
を備える軸受構造。 - 給油通路の開口部が開口する軸受孔が形成されたハウジングと、
前記軸受孔に収容され、シャフトの軸方向に互いに離隔して設けられる2つの軸受面が内周面に形成された環状の本体部を有するセミフローティング軸受と、
前記セミフローティング軸受の本体部に形成され、前記軸受面に一端が開口し、他端の一部もしくは全部が前記給油通路の開口部に対向し、前記開口部に対して前記シャフトの径方向に対向する面積、前記他端の開口面積、および、前記シャフトの回転方向の位置の少なくともいずれかが互いに異なる、2つの前記軸受面それぞれに設けられた2つの導油孔と、
を備える軸受構造。 - 前記請求項1から5のいずれか1項に記載の軸受構造を備える過給機。
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JP2017529555A JP6512296B2 (ja) | 2015-07-21 | 2016-07-11 | 軸受構造および過給機 |
DE112016003295.1T DE112016003295T5 (de) | 2015-07-21 | 2016-07-11 | Lagerstruktur und turbolader |
CN201680039460.2A CN107735554A (zh) | 2015-07-21 | 2016-07-11 | 轴承构造以及增压器 |
US15/862,032 US10465747B2 (en) | 2015-07-21 | 2018-01-04 | Bearing structure and turbocharger |
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JP2015144019 | 2015-07-21 |
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US15/862,032 Continuation US10465747B2 (en) | 2015-07-21 | 2018-01-04 | Bearing structure and turbocharger |
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JP (1) | JP6512296B2 (ja) |
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CN111316008A (zh) * | 2017-11-10 | 2020-06-19 | 三菱重工业株式会社 | 旋转机械、轴颈轴承 |
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JP2014051939A (ja) * | 2012-09-07 | 2014-03-20 | Ihi Corp | 過給機 |
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US7793499B2 (en) * | 2006-10-25 | 2010-09-14 | Honeywell International Inc. | Bearing spacer and housing |
GB0801845D0 (en) * | 2008-02-01 | 2008-03-05 | Cummins Turbo Tech Ltd | A Shaft bearing assembly |
JP2010156214A (ja) | 2008-12-26 | 2010-07-15 | Ihi Corp | 回転機械の軸受構造 |
JP5595346B2 (ja) * | 2011-06-30 | 2014-09-24 | 三菱重工業株式会社 | ターボチャージャの軸受装置 |
JP6070232B2 (ja) * | 2013-02-05 | 2017-02-01 | 株式会社Ihi | 過給機 |
WO2015190364A1 (ja) * | 2014-06-12 | 2015-12-17 | 株式会社Ihi | 軸受構造、および、過給機 |
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JP2008215453A (ja) * | 2007-03-02 | 2008-09-18 | Ihi Corp | 浮動ブッシュ軸受構造 |
JP2014051939A (ja) * | 2012-09-07 | 2014-03-20 | Ihi Corp | 過給機 |
JP2014238009A (ja) * | 2013-06-06 | 2014-12-18 | 株式会社Ihi | 過給機 |
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CN111316008A (zh) * | 2017-11-10 | 2020-06-19 | 三菱重工业株式会社 | 旋转机械、轴颈轴承 |
CN111316008B (zh) * | 2017-11-10 | 2021-11-19 | 三菱重工船用机械株式会社 | 旋转机械、轴颈轴承 |
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CN107735554A (zh) | 2018-02-23 |
JPWO2017014084A1 (ja) | 2018-04-19 |
US10465747B2 (en) | 2019-11-05 |
US20180128318A1 (en) | 2018-05-10 |
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