WO2022168897A1 - スラスト軸受装置及びターボチャージャ - Google Patents
スラスト軸受装置及びターボチャージャ Download PDFInfo
- Publication number
- WO2022168897A1 WO2022168897A1 PCT/JP2022/004154 JP2022004154W WO2022168897A1 WO 2022168897 A1 WO2022168897 A1 WO 2022168897A1 JP 2022004154 W JP2022004154 W JP 2022004154W WO 2022168897 A1 WO2022168897 A1 WO 2022168897A1
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- WIPO (PCT)
- Prior art keywords
- drive shaft
- land
- thrust
- bearing device
- thrust bearing
- Prior art date
Links
- 230000000149 penetrating effect Effects 0.000 claims description 4
- 230000002093 peripheral effect Effects 0.000 description 36
- 239000003921 oil Substances 0.000 description 23
- 239000010687 lubricating oil Substances 0.000 description 21
- 238000010586 diagram Methods 0.000 description 9
- 230000002542 deteriorative effect Effects 0.000 description 5
- 239000007789 gas Substances 0.000 description 3
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
Images
Classifications
-
- 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
- F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
- F16C17/06—Sliding-contact bearings for exclusively rotary movement for axial load only with tiltably-supported segments, e.g. Michell bearings
-
- 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
-
- 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
- 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
- F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial 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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
-
- 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
- F16C37/00—Cooling of bearings
- F16C37/002—Cooling of bearings of fluid 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
- F05D2220/00—Application
- F05D2220/40—Application in turbochargers
-
- 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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/30—Angles, e.g. inclinations
-
- 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 disclosure relates to thrust bearing assemblies and turbochargers.
- This application claims priority based on Japanese Patent Application No. 2021-017245 filed with the Japan Patent Office on February 5, 2021, the content of which is incorporated herein.
- a turbocharger for an automobile includes a turbine and a compressor, and a turbine rotor blade of the turbine and an impeller of the compressor are connected via a drive shaft.
- the drive shaft is rotatably supported by a thrust bearing device that supports axial loads.
- the thrust bearing device disclosed in Patent Document 1 is a tapered land type thrust bearing device, and includes a thrust collar fitted to a drive shaft and a thrust member that is penetrated by the drive shaft and arranged opposite the thrust collar.
- the thrust member has a plurality of land portions which are parallel to a plane orthogonal to the axis of the drive shaft and are provided at intervals in the circumferential direction of the through hole, and a plurality of land portions provided between the plurality of land portions.
- a tapered portion is provided that connects to the boundary of the land portion on one side in the circumferential direction of the through hole via a step, and continuously connects to the boundary of the land portion on the other side in the circumferential direction of the through hole. ing.
- the present disclosure has been made in view of the above-described problems.
- the purpose is to provide a charger.
- the thrust bearing device includes: a thrust collar fitted with a drive shaft, the thrust collar having a flange portion extending radially outward of the drive shaft; a thrust member penetrating through the thrust collar and provided with a pad portion in a region facing the flange portion; with The pad portion a plurality of land portions parallel to a plane orthogonal to the axis of the drive shaft and provided at intervals in the circumferential direction of the drive shaft; a tapered portion provided between adjacent land portions of the plurality of land portions, connected to a boundary of one land portion via a step in the circumferential direction of the drive shaft, and continuously connected to a boundary of the other land portion; , including The land portion has a circumferential groove that is longer in the circumferential direction than in the radial direction of the drive shaft.
- the thrust bearing device of the present disclosure even if the thrust collar is tilted due to shaft vibration and the thrust collar contacts the thrust member (pad portion) and the lubricating oil is heated between the thrust collar and the thrust member, the lubricating oil is heated. It is possible to suppress the flow of lubricating oil from the outer peripheral side of the land portion to the inner peripheral side thereof. As a result, thinning of the oil film on the inner peripheral side of the land portion is suppressed, so that the load capacity of the thrust bearing device is not significantly lowered, and the load capacity of the thrust bearing device can be ensured.
- FIG. 1 is a vertical cross-sectional view schematically showing the main configuration of a turbocharger according to an embodiment
- FIG. FIG. 4 is a diagram for explaining a mounting structure of a thrust bearing to a drive shaft
- FIG. 4 is a side view schematically showing a thrust member
- 4 is an enlarged view showing an example of a pad shown in FIG. 3
- FIG. 5 is an enlarged perspective view of the pad shown in FIG. 4
- FIG. 5 is an expanded view showing a partial cross section of the pad shown in FIG. 4 taken along line VI-VI
- FIG. FIG. 7 is a diagram showing the pressure distribution of lubricating oil in the tapered portion shown in FIG. 6
- 4 is an enlarged view showing another example of the pad shown in FIG. 3
- FIG. 9 is an expanded view showing an example of a partial cross section of the pad shown in FIG. 8 along line IX-IX;
- FIG. 9 is a diagram showing the pressure distribution of lubricating oil in the circumferential grooves shown in FIG. 8;
- FIG. 4 is a diagram for explaining the mounting structure of the thrust bearing to the drive shaft, and is a diagram showing an example in which a thrust collar having a slit provided in the thrust collar is employed.
- a thrust bearing device according to an embodiment of the present disclosure and a turbocharger equipped with the thrust bearing device will be described below with reference to the accompanying drawings.
- the dimensions, materials, shapes, relative arrangements, etc. of the components described as embodiments or shown in the drawings are not intended to limit the scope of the present invention, and are merely illustrative examples. do not have.
- FIG. 1 is a vertical cross-sectional view schematically showing a turbocharger according to an embodiment.
- a turbocharger is mounted, for example, on an automobile engine.
- the turbocharger has a turbine 10 and a centrifugal compressor 12 .
- the turbine 10 has a turbine housing 14 and a turbine impeller 16 rotatably received within the turbine housing 14
- the compressor 12 is rotatably mounted within the compressor housing 18 and the compressor housing 18 .
- a housed impeller (compressor impeller) 20 .
- Turbine rotor blades 16 , impeller 20 and drive shaft 24 are therefore arranged on the same axis 26 .
- Turbine rotor blades 16 of turbine 10 are rotated, for example, by exhaust gases discharged from an automotive engine, which rotate impeller 20 of compressor 12 via drive shaft 24 . Rotation of the impeller 20 of the compressor 12 compresses the charge air supplied to the vehicle engine.
- the turbine housing 14 is composed of a tubular portion (shroud portion) 28 that houses the turbine rotor blades 16 and a scroll portion 30 that surrounds a portion of the tubular portion 28 on the bearing housing 22 side.
- the scroll portion 30 has an exhaust gas inlet (not shown) and communicates with the cylindrical portion 28 via a throat portion 32 .
- An opening in the cylindrical portion 28 opposite the bearing housing 22 forms an outlet for the exhaust gas.
- the end wall 34 of the bearing housing 22 is fitted into the opening of the turbine housing 14 on the bearing housing 22 side.
- a tubular seal portion 36 is provided integrally and coaxially with the end wall 34 , and the seal portion 36 forms a seal hole penetrating the center of the end wall 34 .
- the end of the drive shaft 24 on the turbine rotor blade 16 side is arranged inside the seal portion 36 , and a seal ring 38 is arranged in the gap between the drive shaft 24 and the seal portion 36 .
- An annular backplate 40 is arranged in an annular recess between the end wall 34 and the back surface of the turbine rotor blade 16 .
- the outer peripheral portion of the back plate 40 is sandwiched between the turbine housing 14 and the bearing housing 22 , and the inner peripheral edge of the back plate 40 surrounds the seal portion 36 .
- a pair of bearing portions 44 and 45 are provided integrally with the peripheral wall 42 inside the bearing housing 22, and a bearing hole is formed in each of the pair of bearing portions 44 and 45.
- Floating bushes 46 and 47 are arranged as radial bearings in the bearing holes of the pair of bearing portions 44 and 45, and the center portion of the drive shaft 24 passes through the floating bushes 46 and 47, and the bearing portion 44 is inserted. It is placed in the bearing bore.
- a plate-shaped thrust member 48 orthogonal to the axis 26 is fixed to the end face of the bearing portion 44 on the compressor 12 side, and the drive shaft 24 passes through the through hole of the thrust member 48 .
- a thrust collar 50 and a thrust sleeve 52 are fitted to the drive shaft 24, and the thrust member 48, the thrust collar 50 and the thrust sleeve 52 constitute a thrust bearing device.
- the peripheral wall 42 of the bearing housing 22 is provided with an oil supply port 54 and an oil discharge port 56, and the bearing portion 44 and the thrust member 48 are provided with lubricating oil for supplying lubricating oil to the bearing clearances of the radial bearing and the thrust bearing.
- An oil supply passage is formed.
- an oil deflector 58 is installed so as to cover the surface of the thrust member 48 on the compressor 12 side.
- a cover member 60 having a seal hole in the center is fitted to the opening of the bearing housing 22 on the compressor 12 side, and the cover member 60 is fixed to the bearing housing 22 by a fixing ring 62 .
- the thrust sleeve 52 passes through the seal hole of the lid member 60, and a seal ring 63 is arranged in the gap between the thrust sleeve 52 and the seal hole.
- the compressor housing 18 is composed of a tubular portion (shroud portion) 64 that houses the impeller 20 and a scroll portion 66 that surrounds a portion of the tubular portion 64 on the bearing housing 22 side.
- the scroll portion 66 has an air supply outlet (not shown) and communicates with the tubular portion 64 via a diffuser portion 68 .
- An opening of the cylindrical portion 64 on the side opposite to the bearing housing 22 forms an inlet for intake air.
- FIG. 2 is a diagram for explaining the mounting structure of the thrust bearing device to the drive shaft 24.
- Impeller 20 consists of a hub 70 and a plurality of blades 72 .
- Hub 70 has a shape that is rotationally symmetrical about axis 26 . In the direction along the axis 26 , one end side of the hub 70 is located on the supply air inlet side, and the other end side of the hub 70 is located on the diffuser portion 68 side.
- An outer peripheral surface 74 of the hub 70 has a trumpet shape that expands from one end side toward the other end side, and the hub 70 has a rear surface 76 facing the lid member 60 on the other end side.
- the hub 70 is provided with mounting holes 78 passing through the hub 70 along the axis 26 , and the mounting holes 78 are open at both ends of the hub 70 .
- a plurality of blades 72 are integrally attached to the outer peripheral surface 74 of the hub 70 and arranged at predetermined intervals in the circumferential direction of the hub 70 .
- the plurality of wings 72 include full blades 72a and splitter blades 72b that are shorter than the full blades 72a in the direction along the axis 26, and the full blades 72a and the splitter blades 72b are alternately arranged in the circumferential direction.
- the drive shaft 24 has a shaft portion 80, a large diameter portion 82, and an intermediate portion 84 that are integrally formed with each other.
- Shaft portion 80 extends inside mounting hole 78 of impeller 20 , and large diameter portion 82 is spaced from impeller 20 .
- the intermediate portion 84 is positioned between the shaft portion 80 and the large diameter portion 82 .
- the intermediate portion 84 has a smaller diameter than the large diameter portion 82 , and a stepped portion 86 is formed at the boundary between the intermediate portion 84 and the large diameter portion 82 .
- a female thread is formed on the tip end side of the shaft portion 80 located on one end side of the impeller 20, and a nut as a fastening member 88 is screwed into the female thread.
- the fastening member 88 abuts on one end side of the impeller 20 and applies an axial force toward the stepped portion 86 in the direction along the axis 26 to the impeller 20 .
- a thrust collar 50 and a thrust sleeve 52 are fitted in series to the intermediate portion 84 of the drive shaft 24, and each of these has a flange portion 90 (90a, 90b).
- the thrust collar 50 and the thrust sleeve 52 each have a sleeve portion 92 (92a, 92b) integrally formed with the flange portion 90 (90a, 90b), and the sleeve portion 92 (92a, 92b) is mated to
- the sleeve portion 92 a is positioned between the flange portion 90 a and the flange portion 90 b
- the sleeve portion 92 b is arranged between the flange portion 90 b and the impeller 20 .
- the thrust collar 50 and the thrust sleeve 52 are sandwiched between the back surface 76 of the impeller 20 and the stepped portion 86 by the axial force of the fastening member 88 and configured to rotate together with the drive shaft 24 .
- the through hole 94 of the thrust member 48 is penetrated by the intermediate portion 84 , and the sleeve portion 92 a is arranged between the inner peripheral surface of the through hole 94 and the outer peripheral surface of the intermediate portion 84 .
- the thrust member 48 has a pad portion 96 around the through-hole 94 facing the flange portions 90 a and 90 b in the direction along the axis 26 and making sliding contact therewith.
- the thrust member 48 has pad portions 96 (96a, 96b) on both sides in the direction along the axis 26. As shown in FIG.
- the thrust member 48 is provided with an oil supply hole 98 that forms an oil supply passage, and the outlet of the oil supply hole 98 opens to the inner peripheral surface of the through hole 94 .
- Lubricating oil flowing out from the outlet of the oil supply hole 98 passes through the gap between the outer peripheral surface of the sleeve portion 92a and the inner peripheral surface of the through hole 94, and flows between the pad portions 96 (96a, 96b) and the flange portions 90 (90a, 90b). configured to be fed between
- FIG. 3 is a side view schematically showing the thrust member 48.
- FIG. FIG. 4 is an enlarged view showing an example of the pad section 96 shown in FIG.
- FIG. 5 is an enlarged perspective view of the pad portion 96 shown in FIG.
- FIG. 6 is an expanded view showing a partial cross section along line VI-VI shown in FIG.
- FIG. 7 is a diagram showing the pressure distribution of lubricating oil in tapered portion 102 shown in FIG. 8 is an enlarged view showing another example of the pad portion 96 shown in FIG. 3.
- FIG. 9 is an expanded view showing a partial cross section along line IX-IX shown in FIG.
- FIG. 10 is a diagram showing the pressure distribution of lubricating oil in the circumferential groove 112 shown in FIG.
- the pad portion 96 provided on the thrust member 48 has a plurality of land portions 100 and a plurality of taper portions 102 alternately arranged in the circumferential direction of the drive shaft 24 .
- Each of the plurality of land portions 100 is parallel to a plane perpendicular to the axis of the drive shaft 24 and is spaced apart in the circumferential direction of the drive shaft 24 .
- each land portion 100 has boundaries 104 and 106 on both circumferential sides of the drive shaft 24 , and each boundary 104 and 106 extends along the radial direction of the drive shaft 24 . Therefore, the contour shape of each land portion 100 has a sector shape, and the sliding surface of each land portion 100 is arranged flush with the plane perpendicular to the axis.
- each of the multiple tapered portions 102 is provided between each of the multiple land portions 100 in the circumferential direction of the drive shaft 24 .
- Each tapered portion 102 connects to a boundary 106 of the land portion 100 on one side in the circumferential direction of the drive shaft 24 via a step 108, and connects to a boundary 104 of the land portion 100 on the other side in the circumferential direction of the drive shaft 24. are continuously connected. Accordingly, one boundary 110 of the tapered portion 102 is separated from the land portion 100 in the axial direction of the drive shaft 24 .
- Each tapered portion 102 spirally extends around the axis of the drive shaft 24 and is inclined at an angle of inclination ⁇ t (see FIG. 6) with respect to a plane orthogonal to the axis of the drive shaft 24 .
- Each of the land portions 100 is provided with a circumferential groove 112 that is longer in the circumferential direction than the radial direction of the drive shaft 24 .
- the land portion 100 since the land portion 100 has the circumferential groove 112 that is longer in the circumferential direction than the radial direction of the drive shaft 24, the land portion 100 is divided into the radially inner and outer circumferential sides of the drive shaft 24. be done. Therefore, even if the thrust collar 50 tilts due to shaft vibration and the thrust collar 50 comes into contact with the thrust member 48 and the lubricating oil is overheated between the thrust collar 50 and the thrust member 48, the heated lubricating oil does not reach the land. It is possible to suppress the flow from the outer peripheral side of 100 to the inner peripheral side. As a result, thinning of the oil film on the inner peripheral side of the land portion 100 is suppressed, so that the load capacity of the thrust bearing device can be ensured without significantly deteriorating.
- Circumferential groove 112 communicates with one tapered portion 102 and the other tapered portion 102 adjacent to land portion 100 . Therefore, the circumferential groove 112 that communicates with the one tapered portion 102 adjacent to the land portion 100 and the other tapered portion 102 is provided over the portion of the tapered portion 102 that is continuously connected to the land portion 100 . According to this configuration, since the circumferential groove 112 communicates with the one tapered portion 102 and the other tapered portion 102 adjacent to the land portion 100 , the lubricating oil flowing into the one tapered portion 102 flows into the circumferential groove 112 . and flows into the other tapered portion 102 .
- the circumferential groove 112 is provided in the central portion of the land portion 100 in the radial direction of the drive shaft 24 . According to this configuration, a sliding surface is secured on the inner peripheral side of the land portion 100, and thinning of the oil film on the sliding surface is suppressed. As a result, the load capacity of the inner peripheral side of the land portion 100 is not significantly lowered, and the load capacity of the thrust bearing device can be ensured.
- the above-described circumferential grooves 112 are, for example, grooves 112a with a uniform depth in the land portion 100. As shown in FIG. Therefore, the grooves 112 a having a uniform depth are provided over the portion of the tapered portion 102 that is continuously connected to the land portion 100 . According to this configuration, since the circumferential grooves 112 are grooves 112a having a uniform depth in the land portion 100, the circumferential grooves 112 can be easily machined. When the circumferential groove 112 is a groove 112a with a uniform depth in the land portion 100, as shown in FIG. converge at
- the above-described circumferential groove 112 is provided, for example, from the land portion 100 to the tapered portion 102 , and extends from the boundary 104 that continues to the land portion 100 at the tapered portion 102 to the land portion 100 .
- the groove 112b gradually becomes shallower toward the boundary 106 continuing through the step 108.
- the circumferential groove 112 is not limited to being provided over the entire tapered portion 102 as long as it is provided from the land portion 100 to the tapered portion 102, and is not limited to being provided halfway from the land portion 100 to the tapered portion 102. It may be provided across.
- a circumferential groove 112 is provided from the land portion 100 to the tapered portion 102 , and gradually becomes shallower from a boundary 104 continuously connected to the land portion 100 in the tapered portion 102 toward a boundary connected to the land portion 100 via a step 108 . 10, the pressure of the lubricating oil is distributed even in the circumferential groove 112, and the decrease in the load capacity of the thrust bearing device due to the provision of the circumferential groove 112 can be suppressed. .
- FIG. 11 is a diagram for explaining the mounting structure of the thrust bearing to the drive shaft, and shows an example in which the thrust collar 50 is provided with slits 114 in the flange portion 90a of the thrust collar 50.
- the flange portion 90 a of the thrust collar 50 has a slit 114 extending along the circumferential direction of the drive shaft 24 on the opposite side of the surface facing the pad portion 96 .
- the thrust collar 50 is tilted by shaft vibration.
- the clearance between the thrust collar 50 and the thrust member 48 is ensured by elastic deformation of the flange portion 90a. As a result, thinning of the oil film between the thrust collar 50 and the thrust member 48 is suppressed, so that the load capacity of the thrust bearing device can be ensured without significantly deteriorating.
- the slit 114 described above is provided outside the center of the flange portion 90a in the radial direction of the drive shaft 24, for example. According to this configuration, the slit 114 is provided outside the center of the flange portion 90a in the radial direction of the drive shaft 24. Therefore, if the thrust collar 50 is tilted due to axial vibration, the flange portion 90a will not move in the radial direction of the drive shaft 24.
- the outer side (peripheral side) of the center is elastically deformed. Therefore, in the radial direction of the drive shaft 24, the rigidity of the inner peripheral side of the flange portion 90a can be ensured.
- the present invention is not limited to the above-described embodiments, and includes modifications of the above-described embodiments and modes in which these modes are combined as appropriate.
- the thrust bearing device comprises: a thrust collar (50) fitted with the drive shaft (24) and provided with a flange portion (90a) extending radially outward of the drive shaft (24); a thrust member (48) penetrating through the thrust collar (50) and provided with a pad portion (96) in a region facing the flange portion (90a); with
- the pad portion (96) is a plurality of land portions (100) parallel to a plane perpendicular to the axis of the drive shaft (24) and provided at intervals in the circumferential direction of the drive shaft (24);
- a step (108) is provided between adjacent land portions (100) of the plurality of land portions (100), and a step (108) is formed at a boundary (106) of one land portion (100) in the circumferential direction of the drive shaft (24).
- the land portion (100) has circumferential grooves (112 (112a, 112b)) longer in the circumferential direction than in the radial direction of the drive shaft (24).
- the land (100) has the circumferential groove (112 (112a, 112b)) longer in the circumferential direction than the radial direction of the drive shaft (24), so that the land (100) It is divided into an inner peripheral side and an outer peripheral side in the radial direction of the drive shaft (24).
- the thrust collar (50) tilts due to axial vibration, and the thrust collar (50) comes into contact with the thrust member (48), and the lubricating oil is heated between the thrust collar (50) and the thrust member (48).
- the heated lubricating oil can be prevented from flowing from the outer peripheral side to the inner peripheral side of the land portion (100).
- thinning of the oil film on the inner peripheral side of the land portion (100) is suppressed, so that the load capacity of the thrust bearing device can be ensured without significantly deteriorating.
- a thrust bearing device is the thrust bearing device according to [1], The circumferential grooves (112 (112a, 112b)) communicate with one tapered portion (102) and the other tapered portion (102) adjacent to the land portion (100).
- the circumferential grooves (112 (112a, 112b)) communicate with one tapered portion (102) adjacent to the land portion (100) and the other tapered portion (102).
- the lubricating oil that has flowed into one tapered portion (102) passes through the circumferential grooves (112 (112a, 112b)) and flows into the other tapered portion (102). Therefore, since the lubricating oil is prevented from being heated on the inner peripheral side of the land portion (100), it is suppressed that the oil film becomes thin on the inner peripheral side of the land portion (100). As a result, the load capacity of the thrust bearing device can be ensured without significantly deteriorating.
- a thrust bearing device is the thrust bearing device according to [1] or [2],
- the circumferential groove (112 (112a, 112b)) is provided at the center of the land (100) in the radial direction of the drive shaft (24).
- the circumferential grooves (112 (112a, 112b)) are provided in the central portion of the land portion (100) in the radial direction of the drive shaft (24).
- a sliding surface is secured on the circumferential side, and thinning of the oil film on the sliding surface is suppressed.
- the load capacity of the inner peripheral side of the land portion (100) does not significantly decrease, and the load capacity of the thrust bearing device can be ensured.
- a thrust bearing device is the thrust bearing device according to any one of [1] to [3], Said circumferential groove (112a) is a groove of uniform depth in said land (100).
- the circumferential groove (112a) has a uniform depth in the land (100), so machining of the circumferential groove (112a) is easy.
- a thrust bearing device is the thrust bearing device according to any one of [1] to [3],
- the circumferential groove (112b) is provided from the land portion (100) to the taper portion (102), and the taper portion (102) extends from a boundary (104) that continues to the land portion (100).
- the groove gradually becomes shallower toward a boundary (106) connected to the land (100) via a step (108).
- the circumferential groove (112b) extends from the boundary (104) continuously connected to the land (100) to the boundary (106) connected to the land (100) via the step (108). Since the groove gradually becomes shallower toward the outer circumference, the pressure of the lubricating oil is distributed even in the circumferential groove (112b), and the reduction in the load capacity of the thrust bearing device due to the provision of the circumferential groove (112) can be suppressed. can.
- a thrust bearing device is the thrust bearing device according to any one of [1] to [5],
- the flange portion (90a) has a slit (114) extending along the circumferential direction of the drive shaft (24) on the opposite side of the surface facing the pad portion (96).
- the flange portion (90a) since the flange portion (90a) has the slit (114) extending along the circumferential direction of the drive shaft (24) on the side opposite to the surface facing the pad portion (96), shaft vibration is reduced.
- the flange portion (90a) is elastically deformed, thereby ensuring the clearance between the thrust collar (50) and the thrust member (48).
- thinning of the oil film between the thrust collar (50) and the thrust member (48) is suppressed. can be secured.
- a thrust bearing device is the thrust bearing device according to [6],
- the slit (114) is provided outside the center of the flange portion (90a) in the radial direction of the drive shaft (24).
- the slit (114) is provided outside the center of the flange (90a) in the radial direction of the drive shaft (24).
- the outer side (peripheral side) of the flange portion (90a) is elastically deformed in the radial direction of the shaft (24). Therefore, it is possible to secure the rigidity of the inner peripheral side of the flange portion (90a) in the radial direction of the drive shaft (24).
- the turbocharger according to the aspect of [8] is A thrust bearing device according to any one of [1] to [7] above.
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Abstract
Description
本願は、2021年2月5日に日本国特許庁に出願された特願2021-017245号に基づき優先権を主張し、その内容をここに援用する。
例えば、特許文献1に開示されたスラスト軸受装置は、テーパランド型スラスト軸受装置であって、駆動軸に嵌合されたスラストカラーと、駆動軸によって貫通されてスラストカラーと対向配置されるスラスト部材とを有している。そして、スラスト部材には、駆動軸の軸線に直交する面にそれぞれ平行であって、貫通穴の周方向に間隔を存して設けられた複数のランド部と、複数のランド部間にそれぞれ設けられ、貫通穴の周方向において一方の側のランド部の境界には段差を介して連なり、貫通穴の周方向において他方の側のランド部の境界には連続的に連なるテーパ部とが設けられている。
駆動軸が嵌合されたスラストカラーであって、前記駆動軸の径方向外側に延びるフランジ部が設けられたスラストカラーと、
前記スラストカラーに貫通され、前記フランジ部と対向する領域にパッド部が設けられたスラスト部材と、
を備え、
前記パッド部は、
前記駆動軸の軸線に直交する面に平行であって、前記駆動軸の周方向に間隔を空けて設けられた複数のランド部と、
前記複数のランド部の隣り合うランド部間にそれぞれ設けられ、前記駆動軸の周方向において一方のランド部の境界に段差を介して連なり、他方のランド部の境界に連続して連なるテーパ部と、
を含み、
前記ランド部は、前記駆動軸の径方向よりも周方向に長い周方向溝を有する。
ターボチャージャは、タービン10と、遠心式のコンプレッサ12とを有する。タービン10は、タービンハウジング14と、タービンハウジング14内に回転可能に収容されたタービン動翼(タービンインペラ)16とを有し、コンプレッサ12は、コンプレッサハウジング18と、コンプレッサハウジング18内に回転可能に収容されたインペラ(コンプレッサインペラ)20とを有する。
インペラ20は、ハブ70と、複数の翼72とからなる。ハブ70は、軸線26の周りに回転対称な形状を有する。軸線26に沿う方向において、ハブ70の一端側は給気の入口側に位置し、ハブ70の他端側はディフューザ部68側に位置している。ハブ70の外周面74は一端側から他端側に向かって拡大するラッパ形状を有し、ハブ70は他端側に蓋部材60と対向する背面76を有する。
また、スラストカラー50及びスラストスリーブ52は、フランジ部90(90a,90b)と一体に形成されたスリーブ部92(92a,92b)をそれぞれ有し、スリーブ部92(92a,92b)は中間部84に嵌合されている。スリーブ部92aは、フランジ部90aとフランジ部90bとの間に位置し、スリーブ部92bは、フランジ部90bとインペラ20との間に配置されている。
スラストカラー50及びスラストスリーブ52は、インペラ20の背面76と段差部86との間において締結部材88の軸力をもって挟まれており、駆動軸24とともに回転するように構成されている。
この構成によれば、ランド部100は駆動軸24の径方向よりも周方向に長い周方向溝112を有することで、ランド部100は駆動軸24の径方向内周側と外周側とに分割される。よって、軸振動によってスラストカラー50が傾いてスラストカラー50がスラスト部材48に接触して、スラストカラー50とスラスト部材48との間で潤滑油が過熱されても、加熱された潤滑油がランド部100の外周側から内周側に流れ込むのを抑制できる。これにより、ランド部100の内周側で油膜が薄くなるのが抑制されるので、スラスト軸受装置の負荷能力が著しく低下することがなく、スラスト軸受装置の負荷能力を確保できる。
この構成によれば、周方向溝112は、ランド部100に隣り合う一方のテーパ部102と他方のテーパ部102とに連通するので、一方のテーパ部102に流入した潤滑油は周方向溝112を通り他方のテーパ部102に流入する。よって、ランド部100の内周側で潤滑油が過熱されるのが抑制されるので、ランド部100の内周側で油膜が薄くなるのが抑制される。これにより、スラスト軸受装置の負荷能力が著しく低下することがなく、スラスト軸受装置の負荷能力を確保できる。
この構成によれば、ランド部100の内周側に摺動面が確保され、該摺動面において油膜が薄くなるのが抑制される。これにより、ランド部100の内周側の負荷能力が著しく低下することがなく、スラスト軸受装置の負荷能力を確保できる。
この構成によれば、周方向溝112は、ランド部100において一様の深さの溝112aであるから、周方向溝112の加工が容易である。
尚、周方向溝112がランド部100において一様の深さの溝112aである場合には、図7に示すように、テーパ部102において潤滑油の圧力が分布し、周方向溝112の入口で収束する。
尚、周方向溝112がランド部100からテーパ部102に亘り設けられ、テーパ部102においてランド部100に連続して連なる境界104からランド部100に段差108を介して連なる境界に向けて漸次浅くなる溝112bである場合には、図10に示すように、周方向溝112内においても潤滑油の圧力が分布し、周方向溝112を設けることによるスラスト軸受装置の負荷能力の低下を抑制できる。
図11に示すように、スラストカラー50のフランジ部90aは、パッド部96と対向する面の反対側に駆動軸24の周方向に沿って延びるスリット114を有する。
この構成によれば、スラストカラー50のフランジ部90aは、パッド部96と対向する面の反対側に駆動軸24の周方向に沿って延びるスリット114を有するので、軸振動によってスラストカラー50が傾くとフランジ部90aが弾性変形することで、スラストカラー50とスラスト部材48の間隔が確保される。これにより、スラストカラー50とスラスト部材48との間で油膜が薄くなるのが抑制されるので、スラスト軸受装置の負荷能力が著しく低下することがなく、スラスト軸受装置の負荷能力を確保できる。
この構成によれば、スリット114は、駆動軸24の径方向においてフランジ部90aの中央よりも外側に設けられるので、軸振動によってスラストカラー50が傾くと駆動軸24の径方向においてフランジ部90aの中央より外側(外周側)が弾性変形する。よって、駆動軸24の径方向において、フランジ部90aの内周側の剛性を確保できる。
駆動軸(24)が嵌合されたスラストカラーであって、前記駆動軸(24)の径方向外側に延びるフランジ部(90a)が設けられたスラストカラー(50)と、
前記スラストカラー(50)に貫通され、前記フランジ部(90a)と対向する領域にパッド部(96)が設けられたスラスト部材(48)と、
を備え、
前記パッド部(96)は、
前記駆動軸(24)の軸線に直交する面に平行であって、前記駆動軸(24)の周方向に間隔を空けて設けられた複数のランド部(100)と、
前記複数のランド部(100)の隣り合うランド部(100)間にそれぞれ設けられ、前記駆動軸(24)の周方向において一方のランド部(100)の境界(106)に段差(108)を介して連なり、他方のランド部(100)の境界(104)に連続して連なるテーパ部(102)と、
を含み、
前記ランド部(100)は、前記駆動軸(24)の径方向よりも周方向に長い周方向溝(112(112a,112b))を有する。
前記周方向溝(112(112a,112b))は、前記ランド部(100)に隣り合う一方のテーパ部(102)と他方のテーパ部(102)とに連通する。
前記周方向溝(112(112a,112b))は、前記駆動軸(24)の径方向において前記ランド部(100)の中央部に設けられる。
前記周方向溝(112a)は、前記ランド部(100)において一様の深さの溝である。
前記周方向溝(112b)は、前記ランド部(100)から前記テーパ部(102)に亘り設けられ、前記テーパ部(102)において前記ランド部(100)に連続して連なる境界(104)から前記ランド部(100)に段差(108)を介して連なる境界(106)に向けて漸次浅くなる溝である。
前記フランジ部(90a)は、前記パッド部(96)と対向する面の反対側に前記駆動軸(24)の周方向に沿って延びるスリット(114)を有する。
前記スリット(114)は、前記駆動軸(24)の径方向において前記フランジ部(90a)の中央よりも外側に設けられる。
上記[1]から[7]のいずれか一つに記載のスラスト軸受装置を備える。
12 コンプレッサ
14 タービンハウジング
16 タービン動翼
18 コンプレッサハウジング
20 インペラ
22 軸受ハウジング
24 駆動軸
26 軸線
28 筒部
30 スクロール部
32 スロート部
34 端壁
36 シール部
38 シールリング
40 バックプレート
42 周壁
44,45 軸受部
46,47 浮動ブッシュ
48 スラスト部材
50 スラストカラー
52 スラストスリーブ
54 給油ポート
56 排油ポート
58 オイルデフレクタ
60 蓋部材
62 固定リング
63 シールリング
64 筒部
66 スクロール部
68 ディフューザ部
70 ハブ
72 翼
72a フルブレード
72b スプリッタブレード
74 外周面
76 背面
78 取付穴
80 軸部
82 大径部
84 中間部
86 段差部
88 締結部材
90,90a,90b フランジ部
92,92a,92b スリーブ部
94 貫通孔
96 パッド部
98 給油孔
100 ランド部
102 テーパ部
104 境界
106 境界
108 段差
110 境界
112 周方向溝
114 スリット
Claims (8)
- 駆動軸が嵌合されたスラストカラーであって、前記駆動軸の径方向外側に延びるフランジ部が設けられたスラストカラーと、
前記スラストカラーに貫通され、前記フランジ部と対向する領域にパッド部が設けられたスラスト部材と、
を備え、
前記パッド部は、
前記駆動軸の軸線に直交する面に平行であって、前記駆動軸の周方向に間隔を空けて設けられた複数のランド部と、
前記複数のランド部の隣り合うランド部間にそれぞれ設けられ、前記駆動軸の周方向において一方のランド部の境界に段差を介して連なり、他方のランド部の境界に連続して連なるテーパ部と、
を含み、
前記ランド部は、前記駆動軸の径方向よりも周方向に長い周方向溝を有する、
スラスト軸受装置。 - 前記周方向溝は、前記ランド部に隣り合う一方のテーパ部と他方のテーパ部とに連通する、
請求項1に記載のスラスト軸受装置。 - 前記周方向溝は、前記駆動軸の径方向において前記ランド部の中央部に設けられる、
請求項1又は2に記載のスラスト軸受装置。 - 前記周方向溝は、前記ランド部において一様の深さの溝である、
請求項1から3のいずれか一項に記載のスラスト軸受装置。 - 前記周方向溝は、前記ランド部から前記テーパ部に亘り設けられ、前記テーパ部において前記ランド部に連続して連なる境界から前記ランド部に段差を介して連なる境界に向けて漸次浅くなる溝である、
請求項1から3のいずれか一項に記載のスラスト軸受装置。 - 前記フランジ部は、前記パッド部と対向する面の反対側に前記駆動軸の周方向に沿って延びるスリットを有する、
請求項1から5のいずれか一項に記載のスラスト軸受装置。 - 前記スリットは、前記駆動軸の径方向において前記フランジ部の中央よりも外側に設けられる、
請求項6に記載のスラスト軸受装置。 - 請求項1から7のいずれか一項に記載のスラスト軸受装置を備えるターボチャージャ。
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CN202280008119.6A CN116615601A (zh) | 2021-02-05 | 2022-02-03 | 推力轴承装置以及涡轮增压器 |
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Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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JPS61202647U (ja) * | 1985-06-10 | 1986-12-19 | ||
WO2015128977A1 (ja) * | 2014-02-27 | 2015-09-03 | 三菱重工業株式会社 | テーパランド型スラスト軸受装置、及び、該軸受装置を備えるターボチャージャ |
JP2015224676A (ja) * | 2014-05-26 | 2015-12-14 | 大豊工業株式会社 | スラスト軸受 |
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Publication number | Priority date | Publication date | Assignee | Title |
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JPS61202647U (ja) * | 1985-06-10 | 1986-12-19 | ||
WO2015128977A1 (ja) * | 2014-02-27 | 2015-09-03 | 三菱重工業株式会社 | テーパランド型スラスト軸受装置、及び、該軸受装置を備えるターボチャージャ |
JP2015224676A (ja) * | 2014-05-26 | 2015-12-14 | 大豊工業株式会社 | スラスト軸受 |
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DE112022000286T5 (de) | 2023-09-14 |
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