WO2020065921A1 - センターベアリング - Google Patents
センターベアリング Download PDFInfo
- Publication number
- WO2020065921A1 WO2020065921A1 PCT/JP2018/036275 JP2018036275W WO2020065921A1 WO 2020065921 A1 WO2020065921 A1 WO 2020065921A1 JP 2018036275 W JP2018036275 W JP 2018036275W WO 2020065921 A1 WO2020065921 A1 WO 2020065921A1
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- WO
- WIPO (PCT)
- Prior art keywords
- stopper
- bracket
- radial
- bellows
- radial bearing
- Prior art date
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/22—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or type of main drive shafting, e.g. cardan shaft
- B60K17/24—Arrangements of mountings for shafting
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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
- F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
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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
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/02—Shafts; Axles
-
- 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
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
Definitions
- the present disclosure relates to a center bearing for supporting a rotary drive shaft on a fixed system such as a vehicle body.
- the center bearing described in Patent Literature 1 includes a cylindrical bracket, a radial bearing arranged on the inner peripheral side of the bracket, a pair of bellows provided on the bracket and the radial bearing so as to be spaced apart from each other in the axial direction, and A block-like stopper disposed between the bellows.
- the center bearing described in Patent Document 2 includes a bracket, a radial bearing, a pair of bellows, and a film-like stopper extending inward from the inner surface of each of the bellows.
- the stopper of the center bearing described in Patent Document 1 is relatively hard because it is formed in a block shape. For this reason, when the stopper collides with the bracket, the behavior of the radial bearing can be regulated, but the impact cannot be absorbed. Furthermore, when the stopper collides with the bellows, there is a problem that the bellows are easily damaged. In particular, when the radial bearing moves in the axial direction with respect to the bracket or when the radial bearing is inclined, the stopper pushes and extends the bellows locally, so that the bellows are easily damaged.
- the stopper of the center bearing described in Patent Document 2 is formed in a film shape extending from the inner surface of the bellows, and thus is relatively soft. For this reason, when the stopper collides with the bracket, there is a problem that the stopper cannot completely absorb the impact, and vibration is likely to occur. Furthermore, when the radial bearing is inclined with respect to the bracket, the inclination of the radial bearing cannot be restricted by the film-shaped stopper, and the outer peripheral surface of the bellow is rubbed against the yoke of the rotary drive shaft, and the bellow is easily damaged. There is a problem that.
- an object of the present disclosure is to provide a center bearing that can achieve both reduction in vibration and improvement in durability.
- a cylindrical bracket attached to the fixed system A radial bearing disposed in the bracket and provided coaxially with the power transmission shaft; A pair of bellows provided between the bracket and the radial bearing and spaced apart in the axial direction of the radial bearing, A stopper disposed between the bellows and restricting movement of the radial bearing with respect to the bracket,
- the bellows includes a film portion in which an intermediate portion in the radial direction of the radial bearing expands outward in the axial direction,
- the stopper is directly or indirectly fixed to the radial bearing or the bracket and formed so as to protrude in the radial direction.
- the stopper extends in one or both of the axial directions of the radial bearing.
- a center bearing is provided, wherein a flange is formed.
- the stopper is provided with a cushioning void for absorbing a radial impact.
- the cushioning gap is formed in the stopper on the tip side of the flange.
- the cushioning gap is formed in the stopper so as to penetrate in the axial direction of the radial bearing.
- a plurality of the cushioning gaps are formed in the circumferential direction, and ribs are formed in the buffering gaps adjacent in the circumferential direction.
- the flange is formed in a semi-elliptical or V-shaped cross section.
- the flange portion is arranged close to an inner surface of the bellows.
- the stopper is formed to extend in a circumferential direction of the radial bearing.
- the tip of the stopper is formed in a curved shape.
- the stopper is formed separately from the bracket and the bellows.
- FIG. 2 is a schematic side view illustrating a use state of the center bearing according to the embodiment of the present disclosure. It is a side sectional view of a center bearing attached to a rotation drive shaft. It is a side sectional view of a center bearing.
- FIG. 4 is a sectional view taken along line AA of FIG. 3. It is sectional drawing of the center bearing in which the radial bearing was moved axially with respect to the bracket. It is sectional drawing of the center bearing in which the radial bearing was moved with respect to the bracket in the radial direction. It is sectional drawing of the center bearing in which the radial bearing was inclined with respect to the bracket.
- the power transmission system shown in FIG. 1 includes a propeller shaft 1 that transmits power from a transmission T / M disposed at the front of the vehicle to differential gear DIFF disposed at the rear of the vehicle.
- the left side in the figure is the front of the vehicle, and the upper side in the figure is the upper side of the vehicle.
- the rotation drive shaft is not limited to the propeller shaft 1.
- the rotary drive shaft may be another shaft that receives a radial force from its output side. In this case, the rotary drive shaft may be other than the vehicle.
- the center bearing 2 is attached to a propeller shaft 1 which is a rotary drive shaft.
- the propeller shaft 1 includes a first universal joint 3 connected to an output shaft (not shown) of the transmission T / M, a main shaft portion 4 connected to an output side of the first universal joint 3, and a main shaft portion 4
- a second universal joint 6 connected to the output shaft 5, a main shaft portion 7 connected to the output side of the second universal joint 6, a third universal joint 8 connecting the main shaft portion 7 and the differential gear DIFF. Is provided.
- the output shaft 5 of the main shaft portion 4 includes a small diameter portion 5a fitted into an inner race 10 of the radial bearing 9 described later, and a large diameter portion 5b formed forward of the small diameter portion 5a.
- the step 5c formed between the large diameter portion 5b and the small diameter portion 5a abuts on the front end face 10a of the inner race 10. This restricts the radial bearing 9 from moving forward with respect to the propeller shaft 1.
- a male screw portion 5d is formed at the rear end of the small diameter portion 5a.
- the second universal joint 6 includes an input shaft 6a fastened to the small diameter portion 5a, a first yoke 6b provided on the input shaft 6a and bifurcated and extending rearward, and a cross-shaped connecting shaft (spider) attached to the first yoke 6b.
- the input shaft 6a is formed in a cylindrical shape into which the small diameter portion 5a is inserted.
- the small diameter portion 5a is inserted into the input shaft 6a, and is crimped to the rear end face 10b of the inner race 10 by screwing the nut 11 into the male screw portion 5d.
- the rearward movement of the radial bearing 9 with respect to the propeller shaft 1 is restricted.
- the propeller shaft 1 is not limited to this.
- the propeller shaft 1 may not include the second universal joint 6.
- the center bearing 2 has a cylindrical bracket 12 attached to a fixed system (not shown) such as a vehicle body, and a coaxial shaft disposed on the bracket 12 and coaxial with the propeller shaft 1.
- the vehicle includes a radial bearing 9 provided, a pair of bellows 13 provided between the bracket 12 and the radial bearing 9 in the front-rear direction, and a stopper 14 provided between the pair of bellows 13.
- the bracket 12 is formed of metal and forms an outer shell of the center bearing 2. On the outer periphery of the bracket 12, there is provided a fixture 12b for fixing the center bearing to a fixed system.
- the bellows 13 are formed substantially symmetrically in the front-back direction.
- the bellows 13 includes a first fitting member 17 fitted on the inner periphery of the bracket 12, a second fitting member 18 fitted on the outer periphery of the outer race 15 of the radial bearing 9, and a first fitting member 17. And a film part 19 provided between the second fitting members 18.
- the first fitting member 17 is formed of metal.
- the first fitting member 17 is formed into a tubular shape, and is fitted to the inner periphery of the bracket 12 by press-fitting, and is bent radially outward from one end of the first fitting tubular portion 17a.
- a first flange portion (17b) abutting on an end surface of the bracket (12).
- the axial length of the first fitting cylindrical portion 17a is set to be shorter than half the axial length of the bracket 12. That is, a gap is formed between the first fitting cylinder portions 17a that are press-fitted to the front and rear of the bracket 12.
- the first fitting member 17 is positioned in the axial direction by the first flange portion 17b abutting on the end face of the bracket 12.
- the second fitting member 18 is formed of metal.
- the first fitting member 17 is formed into a tubular shape, and is fitted radially inward from one end of the second fitting tubular portion 18a with a second fitting tubular portion 18a press-fitted to the outer periphery of the outer race 15.
- a second flange portion 18b abutting on an end surface of the outer race 15, an outer cylindrical portion 18c extending axially outward of the outer race 15 from an inner peripheral end of the second flange portion 18b, and a distal end of the outer cylindrical portion 18c.
- a claw portion 18d bent radially inward.
- the axial length of the second fitting cylindrical portion 18a is set to be slightly shorter than half the axial length of the outer race 15. That is, a small gap is formed between the second fitting cylinder portions 18a which are press-fitted into the front and rear of the outer race 15.
- the second fitting member 18 is positioned in the axial direction by the second flange portion 18b abutting on the end surface of the outer race 15.
- the film portion 19 is formed in a bellows shape in which a radially intermediate portion expands in a direction away from the radial bearing 9 (outward in the axial direction).
- the film portion 19 is made of an elastomer material such as rubber having elasticity.
- the film part 19 is vulcanized and bonded to the first fitting member 17 and the second fitting member 18.
- the stopper 14 is formed separately from the bracket 12 and the bellows 13. Accordingly, when it is desired to manufacture a plurality of types of center bearings 2 having different characteristics, a plurality of types of center bearings 2 having different characteristics are formed in advance, and the plurality of types of center bearings 2 can be easily changed only by changing the stopper 14 to one having different characteristics. Can manufacture bearings.
- the stopper 14 is formed in a ring shape as a whole.
- the stopper 14 is indirectly fixed to the radial bearing via the second fitting cylinder 18a.
- the stopper 14 is formed to extend in the circumferential direction of the radial bearing 9.
- the stopper 14 includes a third fitting cylindrical portion 22 that is press-fitted on the outer peripheral surface of the second fitting cylindrical portion 18a, and a stopper that is provided integrally with the third fitting cylindrical portion 22 and that protrudes outward in the radial direction.
- the main body portion 23 includes a pair of flange portions 24 extending forward and rearward from the stopper main body portion 23, and a cushioning gap 25 formed in the stopper main body portion 23 to absorb a radial impact.
- the stopper body 23 and the flange 24 are integrally formed of an elastomer material. Further, three notches 26 are formed in the stopper body 23 and the flange 24 in the circumferential direction. The notch 26 is formed to engage a tool (not shown) for chucking with the third fitting cylinder 22. For example, chucking is required when adjusting the rotational balance of the propeller shaft after attaching the center bearing 2 to the propeller shaft 1.
- the flange portion 24 is formed substantially in a semi-elliptical cross section or a V-shaped cross section, and is formed at an intermediate position in the radial direction of the stopper 14.
- the distal end 23a of the stopper main body 23 projects radially outward from the flange 24.
- the tip 23a of the stopper body 23 is formed in an arc shape. Thereby, when the tip portion 23a of the stopper main body portion 23 hits the film portion 19, the film portion 19 is prevented from being damaged.
- the inner peripheral surface 24a of the flange portion 24 is slightly separated from the inner surface 19a of the film portion 19, and is formed substantially along the inner surface 19a of the film portion 19.
- the flange portion 24 may extend in the front-rear direction, and may be formed in a V-shaped cross section with a sharper tip, for example, as shown in FIG. Further, in the above description, the pair of flanges 24 extend forward and rearward from the stopper main body 23. However, the flanges 24 may be provided only in one of the front and rear as needed.
- the buffer space 25 is formed in the stopper 14 on the tip side of the flange 24, that is, the tip end 23a of the stopper body 23 in the front-rear direction.
- the buffer space 25 is formed in the distal end portion 23 a of the stopper main body 23 in a slit shape extending in the circumferential direction.
- a plurality of cushioning voids 25 are formed in the stopper body 23 in the circumferential direction.
- a rib 27 is formed between the circumferentially adjacent buffer spaces 25. Thereby, the radial hardness of the stopper 14 is adjusted.
- the hardness of the stopper 14 in the radial direction is set so that when the distal end 23a of the stopper main body 23 hits the bracket 12 or the like, the shock is absorbed and the vibration is minimized.
- the radial hardness of the stopper 14 is set in advance by experiments, simulations, or the like.
- FIG. 5 shows a case where the propeller shaft 1 according to the present embodiment has moved forward from the reference position shown in FIG.
- the propeller shaft 1 pushes the radial bearing 9 forward, and moves the second fitting member 18 and the stopper 14 of the bellows 13 forward.
- the inner peripheral sides of the front and rear film portions 19 are moved forward, and the film portion 19 is deformed.
- the front side membrane portion 19 abuts on the inner peripheral surface 24a of the front side flange portion 24 over the entire circumference.
- the deformation of the film portion 19 is regulated.
- the flange portion 24 contacts the film portion 19 with a large area, and is elastically deformed over the entire circumference according to the force received from the film portion 19. Therefore, the force acting on the film portion 19 as the amount of deformation of the film portion 19 increases can be increased while preventing or suppressing the film portion 19 from being damaged.
- FIG. 6 shows a case where the propeller shaft 1 according to the present embodiment has moved upward (radially) from the reference position shown in FIG.
- the propeller shaft 1 pushes up the radial bearing 9 to move the second fitting 18 and the stopper 14 of the bellows 13 upward.
- the membrane portion 19 is pulled upward and extends, and the inner peripheral surface 24 a of the flange portion 24 of the stopper 14 starts to extend when the membrane portion 19 starts to extend.
- the deformation of the film portion 19 is suppressed by contacting the inner surface 19a.
- the flange portion 24 exerts a force on the bellows 13 in a direction opposite to the moving direction of the stopper 14 before the distal end portion 23 a of the stopper main body portion 23 hits the upper end portion of the bracket 12. Can be reduced beforehand when it hits the upper end portion of the.
- the membrane 19 is crushed upward, and the stopper 14 is crushed in the vertical direction by hitting the upper end of the bracket 12.
- the shock absorbing gap 25 absorbs an impact by being crushed vertically. That is, the stopper 14 becomes more flexible in the up-down direction due to the presence of the buffer space 25, and more effectively absorbs an impact than when there is no buffer space 25.
- FIG. 8 shows a comparative example in which the stopper 40 has a film shape and the propeller shaft 1 moves upward.
- the bellows 41 are stretched by being pulled up and down, but the stoppers 40 are hardly deformed. Therefore, the stopper 40 hardly affects the deformation of the bellows 41 at a position vertically below the propeller shaft 1 and the movement of the propeller shaft 1. Further, at a position vertically above the propeller shaft 1, the stopper 40 buckles from the base end and collapses. For this reason, the impact absorbing effect of the stopper 40 is only equivalent to the thickness of the stopper 40, and the impact when the stopper 40 is crushed as in the present embodiment cannot be effectively absorbed.
- FIG. 7 shows a case where the propeller shaft 1 according to the present embodiment has been turned so as to jump up from the center bearing 2 to a rear part from a state of being moved upward as shown in FIG.
- the distal end 23 a of the stopper main body 23 that has been in contact with the upper end of the bracket 12 in FIG. 6 is moved forward and is in contact with the membrane 19.
- the distal end portion 23a of the stopper main body 23 is formed in an arc shape, even if the inner surface 19a of the film portion 19 is rubbed, it is possible to prevent or suppress the film portion 19 from being damaged.
- the inner peripheral surface 24 a of the rear flange portion 24 is strongly pressed by the inner surface 19 a of the rear film portion 19 to regulate the rotation of the propeller shaft 1 and The deformation (upward extension) of the film portion 19 on the side is suppressed.
- the inner peripheral surface 24a of the flange portion 24 has a large area and abuts against the inner surface 19a of the rear film portion 19, so that damage to the rear film portion 19 is prevented or suppressed.
- the film portion 19 is pulled and hardened. Therefore, the rear and upper film portion 19 is also pulled and hardened, and the film portion 19 is prevented from being crushed and falling down. This prevents or suppresses the rear and upper membrane portion 19 from being damaged by contact with the propeller shaft 1 or the like.
- the inner peripheral surface 24 a of the front flange 24 is in contact with the inner surface 19 a of the front membrane 19.
- the front flange portion 24 is elastically deformed, thereby restricting the rotation of the propeller shaft 1 and suppressing the deformation of the front film portion 19.
- FIG. 9 shows a case where the propeller shaft 1 is rotated so as to jump up a rear portion from the center bearing 42 from a state where the propeller shaft 1 is moved upward as shown in FIG.
- the stopper 40 hardly deforms at a position vertically below the propeller shaft 1 and does not affect the deformation of the bellows 41.
- the front stopper 40 substantially returns to the original shape according to the deformation of the bellows 41. That is, the front stopper 40 hardly interferes with the rotation of the propeller shaft 1.
- the rear stopper 40 substantially returns to the original shape in accordance with the deformation of the bellows 41. That is, the rear stopper 40 hardly interferes with the rotation of the propeller shaft 1. For this reason, the stopper 40 according to the comparative example cannot restrict the rotation of the propeller shaft 1 as in the present embodiment when the propeller shaft 1 rotates beyond a predetermined angle.
- the stopper 40 according to the comparative example only deforms following the deformation of the bellows 41 at any position, the deformation of the bellows 41 is hardly suppressed. For this reason, when the propeller shaft 1 rotates beyond a predetermined angle, the stopper 40 according to the comparative example prevents or suppresses the bellows 13 from contacting the propeller shaft 1 like the stopper 14 according to the present embodiment. I can't.
- the stopper 14 is indirectly fixed to the radial bearing via the second fitting cylindrical portion 18a, the invention is not limited to this.
- the stopper 14 may be fixed to the radial bearing 9 with another member interposed between the radial bearing 9 and the stopper 14.
- the stopper 14 may be directly fixed to the radial bearing 9 without interposing the second fitting cylindrical portion 18a between the stopper 14 and the radial bearing 9. That is, the stopper 14 may be fixed directly or indirectly to the radial bearing 9.
- the stopper 14 may be directly or indirectly fixed to the bracket 12. In this case, as shown in FIG. 11, the stopper 14 may be directly fitted and fixed to the inner peripheral surface 12a of the bracket 12.
- the stopper 14 When the inner peripheral surface 17c of the first fitting member 17 is exposed in the space S between the bellows 13, the stopper 14 may be fixed to the inner peripheral surface 17c of the first fitting member 17. That is, the stopper 14 may be indirectly fixed to the bracket 12 via the first fitting member 17.
- the rib 27 is formed between the buffer spaces 25 adjacent in the circumferential direction. However, as shown in FIG. 12, a rib 45 for partitioning the buffer space 46 in the front and rear directions may be formed.
- the buffer space 25 is formed in a slit shape, it may be formed in another shape.
- the buffer space 25 may be spherical, for example, or may be formed in a porous shape like a sponge.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Ocean & Marine Engineering (AREA)
- Motor Power Transmission Devices (AREA)
- Support Of The Bearing (AREA)
- Sealing Of Bearings (AREA)
Abstract
Description
固定系に取り付けられる筒状のブラケットと、
前記ブラケット内に配置され動力伝達シャフトに同軸に設けられるラジアルベアリングと、
前記ブラケット及び前記ラジアルベアリング間に前記ラジアルベアリングの軸方向に離間して設けられる一対のベローと、
前記ベロー間に配設され前記ブラケットに対する前記ラジアルベアリングの移動を規制するストッパとを備え、
前記ベローは、前記ラジアルベアリングの径方向における中間部が軸方向外方に膨らむ膜部を備え、
前記ストッパは、前記ラジアルベアリング又は前記ブラケットに対して直接的又は間接的に固定されると共に径方向に突起して形成され
前記ストッパには、前記ラジアルベアリングの軸方向の一方又は両方に延出する鍔部が形成された
ことを特徴とするセンターベアリングが提供される。
Claims (10)
- 固定系に取り付けられる筒状のブラケットと、
前記ブラケット内に配置され動力伝達シャフトに同軸に設けられるラジアルベアリングと、
前記ブラケット及び前記ラジアルベアリング間に前記ラジアルベアリングの軸方向に離間して設けられる一対のベローと、
前記ベロー間に配設され前記ブラケットに対する前記ラジアルベアリングの移動を規制するストッパとを備え、
前記ベローは、前記ラジアルベアリングの径方向における中間部が軸方向外方に膨らむ膜部を備え、
前記ストッパは、前記ラジアルベアリング又は前記ブラケットに対して直接的又は間接的に固定されると共に径方向に突起して形成され
前記ストッパには、前記ラジアルベアリングの軸方向の一方又は両方に延出する鍔部が形成された
ことを特徴とするセンターベアリング。 - 前記ストッパには、径方向の衝撃を吸収する緩衝用空隙が形成された
請求項1に記載のセンターベアリング。 - 前記鍔部よりも先端側のストッパに前記緩衝用空隙が形成された
請求項2に記載のセンターベアリング。 - 前記緩衝用空隙は、前記ストッパに前記ラジアルベアリングの軸方向に貫通して形成された
請求項2又は3に記載のセンターベアリング。 - 前記緩衝用空隙は、周方向に複数形成され、周方向に隣り合う前記緩衝用空隙間には、リブが形成された
請求項2から4のいずれか一項に記載のセンターベアリング。 - 前記鍔部は、断面半楕円状又はV字状に形成された
請求項1から5のいずれか一項に記載のセンターベアリング。 - 前記鍔部は、前記ベローの内面に近接して配置された
請求項1から6のいずれか一項に記載のセンターベアリング。 - 前記ストッパは、前記ラジアルベアリングの周方向に延びて形成された
請求項1から7のいずれか一項に記載のセンターベアリング。 - 前記ストッパの先端部は曲面状に形成された
請求項1から8のいずれか一項に記載のセンターベアリング。 - 前記ストッパは、前記ブラケット及び前記ベローとは別体に形成された
請求項1から9のいずれか一項に記載のセンターベアリング。
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU2018443014A AU2018443014A1 (en) | 2018-09-27 | 2018-09-28 | Center bearing |
ZA2021/02200A ZA202102200B (en) | 2018-09-27 | 2021-03-31 | Center bearing |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2018182037A JP6875345B2 (ja) | 2018-09-27 | 2018-09-27 | センターベアリング |
JP2018-182037 | 2018-09-27 |
Publications (1)
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WO2020065921A1 true WO2020065921A1 (ja) | 2020-04-02 |
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ID=69950497
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2018/036275 WO2020065921A1 (ja) | 2018-09-27 | 2018-09-28 | センターベアリング |
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JP (1) | JP6875345B2 (ja) |
AU (1) | AU2018443014A1 (ja) |
WO (1) | WO2020065921A1 (ja) |
ZA (1) | ZA202102200B (ja) |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH025606B2 (ja) * | 1985-02-15 | 1990-02-05 | Tokai Gomu Kogyo Kk | |
JPH0454344A (ja) * | 1990-06-22 | 1992-02-21 | Bridgestone Corp | 防振装置 |
JPH0454342A (ja) * | 1990-06-22 | 1992-02-21 | Bridgestone Corp | 防振装置 |
-
2018
- 2018-09-27 JP JP2018182037A patent/JP6875345B2/ja active Active
- 2018-09-28 WO PCT/JP2018/036275 patent/WO2020065921A1/ja active Application Filing
- 2018-09-28 AU AU2018443014A patent/AU2018443014A1/en active Pending
-
2021
- 2021-03-31 ZA ZA2021/02200A patent/ZA202102200B/en unknown
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH025606B2 (ja) * | 1985-02-15 | 1990-02-05 | Tokai Gomu Kogyo Kk | |
JPH0454344A (ja) * | 1990-06-22 | 1992-02-21 | Bridgestone Corp | 防振装置 |
JPH0454342A (ja) * | 1990-06-22 | 1992-02-21 | Bridgestone Corp | 防振装置 |
Also Published As
Publication number | Publication date |
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JP6875345B2 (ja) | 2021-05-26 |
ZA202102200B (en) | 2023-03-29 |
AU2018443014A1 (en) | 2021-03-04 |
JP2020050164A (ja) | 2020-04-02 |
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