WO2022176105A1 - 等速自在継手及び等速自在継手の製造方法 - Google Patents
等速自在継手及び等速自在継手の製造方法 Download PDFInfo
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- WO2022176105A1 WO2022176105A1 PCT/JP2021/006121 JP2021006121W WO2022176105A1 WO 2022176105 A1 WO2022176105 A1 WO 2022176105A1 JP 2021006121 W JP2021006121 W JP 2021006121W WO 2022176105 A1 WO2022176105 A1 WO 2022176105A1
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- spherical surface
- joint member
- constant velocity
- velocity universal
- press
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- 238000004519 manufacturing process Methods 0.000 title claims description 6
- 238000000034 method Methods 0.000 claims description 4
- 230000002093 peripheral effect Effects 0.000 description 7
- 238000005299 abrasion Methods 0.000 description 4
- 230000007423 decrease Effects 0.000 description 4
- 239000000843 powder Substances 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 239000004519 grease Substances 0.000 description 2
- 239000000314 lubricant Substances 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000000071 blow moulding Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000001746 injection moulding Methods 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 229920003051 synthetic elastomer Polymers 0.000 description 1
- 229920003002 synthetic resin Polymers 0.000 description 1
- 239000000057 synthetic resin Substances 0.000 description 1
- 239000005061 synthetic rubber Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D3/224—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere
- F16D3/2245—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere where the groove centres are offset from the joint centre
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D3/224—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D2003/22313—Details of the inner part of the core or means for attachment of the core on the shaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2250/00—Manufacturing; Assembly
- F16D2250/0061—Joining
Definitions
- the present invention relates to a constant velocity universal joint and a method for manufacturing a constant velocity universal joint.
- a constant velocity universal joint disclosed in Patent Document 1 has been known.
- a sleeve is press-fitted and fixed to an inner joint member.
- the diameter of the convex outer spherical surface of the inner joint member expands and may interfere with the concave inner spherical surface of the retainer, possibly hindering the smooth operation of the constant velocity universal joint. be. Therefore, in a conventional constant velocity universal joint, a portion of the concave inner spherical surface of the retainer is enlarged cylindrically to avoid contact with the convex outer spherical surface of the enlarged inner joint member.
- An object of the present invention is to provide a constant velocity universal joint and a method for manufacturing a constant velocity universal joint that can operate smoothly with a simple structure even when a sleeve is press-fitted.
- the constant velocity universal joint is formed in a cylindrical shape with a bottom having an opening in one axial direction and a bottom in the other axial direction.
- an outer joint member arranged inside the outer joint member and having a plurality of inner locking grooves formed along the circumferential direction on an outer periphery having a convex outer spherical surface; each of the outer locking grooves and a plurality of locking members that roll in the inner locking grooves and transmit torque between the outer joint member and the inner joint member; a retainer arranged between the outer spherical surface and formed with a plurality of windows for accommodating the locking members in the circumferential direction, wherein the inner joint member is the outer joint member;
- On the opening side there is a bottomed concave holding portion into which a sleeve that supports the boot that covers the opening is press-fitted. and a relief portion having a smaller diameter than the outer diameter of the convex outer spherical surface corresponding to the press-fitting range.
- a part of the convex outer spherical surface of the inner joint member of the constant velocity universal joint can be provided with a relief portion having a smaller diameter than the outer diameter of the convex outer spherical surface.
- the relief portion by increasing the diameter of the relief portion, it is possible to suppress a decrease in the contact area between the convex outer spherical surface of the inner joint member and the concave inner spherical surface of the retainer. As a result, it is possible to reduce wear due to contact between the convex outer spherical surface of the inner joint member and the concave inner spherical surface of the retainer, as well as reduce the generation of abrasion powder and prevent the contact between the convex outer spherical surface of the inner joint member and the retainer.
- the smooth operation of the constant velocity universal joint can be maintained by suppressing an increase in the gap with the concave inner spherical surface.
- FIG. 4 is a cross-sectional view of the constant velocity universal joint with the propeller shaft assembled, showing a state where the joint angle is zero degrees; It is a figure for demonstrating the state which assemble
- FIG. 4 is a cross-sectional view for explaining the configuration of an inner joint member;
- FIG. 5 is a diagram for explaining the configuration of a holding portion and a relief portion of the inner joint member of FIG. 4; 5 is a diagram for explaining the configuration of a sleeve that is press-fitted into the holding portion of FIG. 4;
- FIG. FIG. 10 is a diagram for explaining the operation of the constant velocity universal joint when the joint angle is other than zero degrees;
- the constant velocity universal joint 100 of the present example is, as shown in FIG. 1, a joint center fixed ball type (so-called Chopper type) constant velocity universal joint. As shown in FIG. 2, the constant velocity universal joint 100 of this example is assembled by inserting a propeller shaft S of an automobile. The constant velocity universal joint 100 of this example transmits the rotation (and torque) of the propeller shaft S to, for example, a differential of a vehicle (not shown).
- the constant velocity universal joint 100 mainly includes an outer joint member 10, an inner joint member 20, a plurality of balls 30 as locking members, a retainer 40, and a sleeve 50, as shown in FIG. Also, in the constant velocity universal joint 100 of this example, a boot B is assembled (attached) between the inner periphery of the outer joint member 10 and the outer periphery of the sleeve 50 to cover the opening of the outer joint member 10 .
- the outer joint member 10 of this example has an opening on the left side of FIG. 3 (one side in the direction of the axis O1) and a bottomed cylinder on the right side of FIG. 3 (the other side in the direction of the axis O1). It is formed in a shape (cup shape).
- a connecting portion 11 is integrally formed on the outside of the bottom portion of the outer joint member 10 (on the right side in FIG. 3) so as to extend in the direction of the axis O1.
- the coupling portion 11 is coupled to transmit rotation (and torque) to a vehicle differential (not shown).
- the inner periphery 12 of the outer joint member 10 has a return inner spherical surface 12a and an outer ball groove 12b as an outer locking groove.
- the concave inner spherical surface 12a is located at most of the central portion of the inner circumference 12 of the outer joint member 10 in the direction of the axis O1.
- the concave inner spherical surface 12a is formed by part of a spherical surface drawn with the joint center P as the center. That is, the longest portion of the concave inner spherical surface 12a in the radial direction from the axis O1 of the outer joint member 10 is the central portion of the concave inner spherical surface 12a in the direction of the axis O1.
- the concave inner spherical surface 12a decreases in diameter from the central portion in the direction of the axis O1 toward the opening side, and also decreases in diameter from the central portion in the direction of the axis O1 to the bottom side.
- the outer ball groove 12b is formed so as to extend in the direction of the axis O1 of the outer joint member 10.
- a plurality of outer ball grooves 12b are formed at regular intervals along the circumferential direction of the outer joint member 10 .
- the direction of the axis O1 of the outer joint member 10, that is, the axial direction, means the rotation axis direction of the outer joint member 10. As shown in FIG.
- the outer circumference 13 of the outer joint member 10 is formed with a locking portion 13a for locking the support member B2 that holds the boot body B1 of the boot B on the opening side.
- a housing groove for housing a seal member such as an O-ring is formed in the locking portion 13a so as to liquid-tightly lock the support member B2.
- the inner joint member 20 is formed in an annular shape and arranged inside the outer joint member 10, as shown in FIGS.
- a convex outer spherical surface 21 is formed over the entire outer periphery of the inner joint member 20 along the axis O2.
- the convex outer spherical surface 21 of the inner joint member 20 is formed by a portion of a spherical surface drawn around the joint center P during torque transmission.
- a plurality of inner ball grooves 22 as inner locking grooves are formed on the outer periphery of the inner joint member 20 so as to extend in the direction of the axis O2 of the inner joint member 20 .
- the plurality of inner ball grooves 22 are the same in number as the outer ball grooves 12b, and are formed at regular intervals in the circumferential direction.
- the inner ball groove 22 is formed in a generally arcuate concave shape, more specifically, in a Gothic arc shape formed by connecting two arcs.
- an internal spline 23 extending in the direction of the axis O2 is formed on the inner peripheral surface of the inner joint member 20 .
- the internal spline 23 is fitted (engaged) with the external spline S1 (see FIGS. 1 and 2) of the propeller shaft S to be assembled by insertion.
- the propeller shaft S is inserted and connected to the inner joint member 20 so that the central axis is aligned with the rotation axis of the inner joint member 20 .
- the direction of the axis O ⁇ b>2 of the inner joint member 20 means the direction passing through the central axis of the inner joint member 20 , that is, the direction of the rotation axis of the inner joint member 20 .
- the inner joint member 20 has a holding portion 24 that holds the sleeve 50 by press-fitting the sleeve 50, as shown in FIG.
- the holding portion 24 has an opening with a smaller diameter than the outer diameter of the sleeve 50, and is formed in a concave shape with a bottom having a predetermined press-fitting range H as shown in FIG.
- the sleeve 50 is press-fitted into the holding portion 24 before the inner joint member 20 is assembled to the retainer 40, for example.
- the inner joint member 20 is formed with a relief portion 25 in the circumferential direction at the end of the convex outer spherical surface 21 on the opening side (left side in FIG. 4).
- the escape portion 25 is formed by expanding the diameter of the convex outer spherical surface 21 in the radially outward direction due to the material flow resulting from the press-fitting of the sleeve 50 into the holding portion 24 , more specifically, the outer diameter of the convex outer spherical surface 21 It is provided to suppress the diameter from becoming larger than As shown in FIG.
- the relief portion 25 is provided in a range of the convex outer spherical surface 21 corresponding to the press-fit range H provided in the direction of the axis O2.
- the relief portion 25 is chamfered, for example, so as to have a smaller diameter than a virtual surface K (indicated by a two-dotted line in FIG. 5) extending the convex outer spherical surface 21 to the opening side.
- the diameter of the escape portion 25 is increased only up to the outer diameter of the convex outer spherical surface 21 or less. Therefore, by providing the relief portion 25 with a small diameter, there is no portion that protrudes beyond the outer diameter of the convex outer spherical surface 21 when the sleeve 50 is press-fitted. It is possible to rotate smoothly relative to it.
- the plurality of balls 30, which are the locking members of this example, are arranged in the outer ball groove 12b of the outer joint member 10 and the inner ball groove 22 of the inner joint member 20 facing the outer ball groove 12b. are arranged so as to be sandwiched between Each ball 30 is free to roll in each outer ball groove 12b and each inner ball groove 22 in the circumferential direction (around the axis O1 of the outer joint member 10 or around the axis O2 of the inner joint member 20). rotation). Balls 30 therefore transmit torque between outer joint member 10 and inner joint member 20 .
- the retainer 40 is formed in an annular shape, as shown in FIG.
- the outer peripheral surface of the retainer 40 is a convex outer spherical surface 41 corresponding to the concave inner spherical surface 12 a of the outer joint member 10 .
- the inner peripheral surface of the retainer 40 is a concave inner spherical surface 42 corresponding to the convex outer spherical surface 21 of the inner joint member 20 .
- the retainer 40 is arranged with a predetermined gap between the concave inner spherical surface 12a of the outer joint member 10 and the convex outer spherical surface 21 of the inner joint member 20 .
- the length (width) of the retainer 40 in the direction of the axis O1 (or the axis O2) is longer than the concave inner spherical surface 12a of the outer joint member 10 and the length (width) of the inner joint member 20 in the direction of the axis O2. ) is formed longer than That is, as shown in FIG. 1, when the joint angle is zero degrees, the convex outer spherical surface 41 of the retainer 40 faces the entire concave inner spherical surface 12a of the outer joint member 10 in the direction of the axis O1.
- the concave inner spherical surface 42 of the retainer 40 faces the convex outer spherical surface 21 of the inner joint member 20 and the relief portion 25 entirely in the direction of the axis O2.
- the concave inner spherical surface 42 of the retainer 40 can face the convex outer spherical surface 21 and the relief portion 25 of the inner joint member 20 even when the joint angle is other than zero degrees.
- the retainer 40 has a plurality of windows 43 .
- the plurality of windows 43 are rectangular through holes formed at equal intervals in the circumferential direction.
- the windows 43 of the retainer 40 are formed in the same number as the balls 30 .
- One ball 30 is accommodated in each window portion 43 .
- the sleeve 50 is cylindrical, as shown in FIG.
- the sleeve 50 has, on its outer peripheral surface, a press-fitting portion 51 that is press-fitted into the holding portion 24 of the inner joint member 20, and a holding recessed portion 52 that holds an inner peripheral portion of a boot body B1 of the boot B, which will be described later. Further, the sleeve 50 has the propeller shaft S inserted through its inner periphery.
- the press-fit portion 51 has an outer diameter slightly larger than the inner diameter of the holding portion 24 . Also, the press-fit portion 51 is provided longer than the press-fit range H corresponding to the depth of the holding portion 24 . As a result, when the press-fitting portion 51 of the sleeve 50 is press-fitted into the holding portion 24 , the relief portion 25 provided on the convex outer spherical surface 21 of the inner joint member 20 is positioned outside the convex outer spherical surface 21 as described above. The diameter is expanded in the radially outward direction to the diameter or less (the press-fitting step of the manufacturing method).
- the holding recess 52 has an outer diameter slightly larger than the inner diameter of the boot body B1. As shown in FIG. 3, the holding recess 52 supports the boot main body B1 so as to be sandwiched between the support member B2 of the boot B assembled to the outer peripheral surface of the outer joint member 10 and the support member B2. As a result, the holding recess 52 has a sealing margin with the inner peripheral surface of the boot body B1 and supports the boot body B1 in a liquid-tight manner.
- the boot B has a disk-shaped boot body B1, a support member B2 that supports the boot body B1, and a clamp B3.
- the boot body B1 is molded by a known molding method such as blow molding or injection molding using synthetic resin, rubber, or the like. With the propeller shaft S assembled, the boot body B1 liquid-tightly covers and seals the opening side of the outer joint member 10 .
- the support member B ⁇ b>2 supports the boot main body B ⁇ b>1 in a non-separable manner while being engaged with the engaging portion 13 a formed on the outer circumference 13 of the outer joint member 10 .
- the clamp B3 fixes the boot body B1 to the sleeve 50 so as to have a seal margin.
- the inner joint member 20, the balls 30, and the retainer 40 are arranged in the closed space formed by the outer joint member 10 and the boot B (more specifically, the boot body B1). Also, a lubricant such as grease is enclosed in the closed space. As a result, lubricant such as grease enclosed in the closed space leaks from the inside of the outer joint member 10 to the outside through the opening, and water leaks from the outside through the opening to the inside of the outer joint member 10 . , mud, etc. can be prevented from entering.
- the relief portion 25 is formed by pressing the sleeve 50 into the holding portion 24 into the press-fitting range H, so that the relief portion 25 is substantially outside the convex outer spherical surface 21 at an outer diameter equal to or smaller than the outer diameter of the convex outer spherical surface 21 . It expands until it reaches the diameter.
- the inner joint member 20 moves toward the opening, as indicated by the dashed circle in FIG.
- the concave inner spherical surface 42 of the retainer 40 can be contacted.
- the relief portion 25 having an expanded diameter can be regarded as a part of the convex outer spherical surface 21 , and the relief portion 25 is also formed in the concave shape of the retainer 40 in addition to the convex outer spherical surface 21 . It slides on the inner spherical surface 42 . That is, in this case, while only the convex outer spherical surface 21 frictionally slides on the concave inner spherical surface 42 of the retainer 40 , the relief portion 25 also frictionally slides on the concave inner spherical surface 42 of the retainer 40 . Therefore, the contact area with the concave inner spherical surface 42 can be increased.
- the constant velocity universal joint 100 of this example is in a state in which the sleeve 50 is press-fitted into the holding portion 24 and the boot B is assembled to the sleeve 50 in advance before the propeller shaft S is assembled. Accordingly, when assembling the propeller shaft S to the constant velocity universal joint 100, it is only necessary to insert the propeller shaft S into the constant velocity universal joint 100 and assemble it. That is, after assembling the propeller shaft S, for example, it is not necessary to assemble the boot B separately. Therefore, the constant velocity universal joint 100 of this example can easily complete the assembly work of the propeller shaft S.
- a portion of the convex outer spherical surface 21 of the inner joint member 20 has a diameter smaller than the outer diameter of the convex outer spherical surface 21. More specifically, a relief portion 25 having a smaller diameter than the outer diameter of an imaginary surface K obtained by extending the convex outer spherical surface 21 toward the opening can be provided.
- the joint angle is zero degrees. It is possible to prevent interference between the convex outer spherical surface 21 and the relief portion 25 of the inner joint member 20 and the concave inner spherical surface 42 of the retainer 40 in other states.
- the contact area between the convex outer spherical surface 21 of the inner joint member 20 and the concave inner spherical surface 42 of the retainer 40 is reduced by increasing the diameter of the relief portion 25 to substantially the outer diameter of the convex outer spherical surface 21 . can be suppressed.
- it is possible to reduce wear due to contact between the convex outer spherical surface 21 of the inner joint member 20 and the concave inner spherical surface 42 of the retainer 40 and reduce the generation of abrasion powder and the convex outer surface of the inner joint member 20 .
- An increase in the gap between the spherical surface 21 and the concave inner spherical surface 42 of the retainer 40 can be suppressed, and smooth operation of the constant velocity universal joint 100 can be maintained over a long period of time.
- the relief portion 25 of the inner joint member 20 is formed by straight chamfering of the convex outer spherical surface 21 .
- the relief portion 25 is not limited to being formed by linear chamfering of the convex outer spherical surface 21, and can be formed by arcuate chamfering of the convex outer spherical surface 21, for example.
- the relief portion 25 is not limited to being formed by chamfering the convex outer spherical surface 21, and may be formed in a stepped shape, for example, if sufficient strength can be ensured for the pressed sleeve 50 to come off.
- the outer joint member 10 has the outer ball groove 12b formed as an outer locking groove parallel to the direction of the axis O1 on the inner periphery 12 is illustrated.
- the outer ball grooves which are the outer locking grooves, need not be formed parallel to the direction of the axis O1, and the outer ball grooves may be formed as cross grooves.
- the inner ball groove as the inner locking groove of the inner joint member is also formed as a cross groove. Also in this case, the same effects as in the present example described above can be obtained.
- SYMBOLS 10 Outer joint member, 11... Connection part, 12... Inner periphery, 12a... Concave inner spherical surface, 12b... Outer ball groove (outer locking groove), 13... Outer periphery, 13a... Locking part, 20... Inner joint member, 21... Convex outer spherical surface, 22... Inner ball groove (inner locking groove), 23... Internal spline, 24... Holding part, 25... Escape part, 30... Ball (locking member), 40...
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Abstract
Description
本例の等速自在継手100は、図1に示すように、ジョイント中心固定式ボール型(所謂、チェッパ型)の等速自在継手である。本例の等速自在継手100は、図2に示すように、自動車のプロペラシャフトSが挿入されて組み付けられるものである。そして、本例の等速自在継手100は、プロペラシャフトSの回転(及びトルク)を、例えば、図示省略の車両のデファレンシャルに伝達するものである。
次に、上述したように構成された等速自在継手100の作動について説明する。ジョイント角がゼロ度以外に設定された場合、図7にて矢印により示すように、プロペラシャフトSの回転に伴って内側ジョイント部材20及び保持器40が外側ジョイント部材10の開口部側に移動する。この場合、保持器40は外側ジョイント部材10の凹状内球面12aに沿って開口部側に移動し、内側ジョイント部材20の凸状外球面21及び逃がし部25は、図7に示すように、保持器40の凹状内球面42に沿って開口部側に移動する。
上述した本例においては、内側ジョイント部材20の逃がし部25は、凸状外球面21の直線的な面取りにより形成される場合を例示した。しかし、逃がし部25は、凸状外球面21の直線的な面取りにより形成されることに限られず、例えば、凸状外球面21の円弧状の面取りによって形成することも可能である。又、逃がし部25は、凸状外球面21の面取りにより形成されることに限られず、圧入されたスリーブ50の抜け強度が十分確保できる場合、例えば、段状に形成することも可能である。
Claims (5)
- 軸方向の一方に開口部及び軸方向の他方に底部を備える有底筒状に形成され、凹状内球面を有する内周において外側係止溝が周方向に沿って複数形成された外側ジョイント部材と、
前記外側ジョイント部材の内側に配置され、凸状外球面を有する外周において内側係止溝が周方向に沿って複数形成された内側ジョイント部材と、
それぞれの前記外側係止溝及び前記内側係止溝を転動し、前記外側ジョイント部材と前記内側ジョイント部材との間でトルクを伝達する複数の係止部材と、
環状に形成され、前記外側ジョイント部材の前記凹状内球面と前記内側ジョイント部材の前記凸状外球面との間に配置され、周方向に前記係止部材をそれぞれ収容する複数の窓部が形成された保持器と、を備える等速自在継手であって、
前記内側ジョイント部材は、
前記外側ジョイント部材の前記開口部側にて、前記開口部を覆うブーツを支持するスリーブが圧入される有底凹状の保持部と、
前記開口部側にて前記凸状外球面の一部に設けられて、前記保持部に前記スリーブが圧入される圧入範囲に対応して、前記凸状外球面の外径よりも小径となる逃がし部と、
を備えた、等速自在継手。 - 前記逃がし部は、
前記保持部の前記圧入範囲に前記スリーブが圧入された状態で、前記凸状外球面の前記外径以下である、請求項1に記載の等速自在継手。 - 前記保持器の内周は、前記内側ジョイント部材の前記凸状外球面に対応する凹状内球面を有しており、
前記内側ジョイント部材の前記凸状外球面と前記保持器の前記凹状内球面との間には所定の隙間が設定されており、
前記保持部に前記スリーブが圧入された状態で、前記内側ジョイント部材及び前記保持器が前記外側ジョイント部材の前記開口部側に移動した場合、拡径された前記逃がし部が前記保持器の前記凹状内球面に摺接する、請求項2に記載の等速自在継手。 - 前記逃がし部は、
前記凸状外球面の面取りにより形成された、請求項1-3の何れか一項に記載の等速自在継手。 - 請求項1-5の何れか一項に記載の前記等速自在継手の製造方法であって、
前記スリーブを前記内側ジョイント部材の前記保持部に圧入する圧入工程を有する、等速自在継手の製造方法。
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JP2005106233A (ja) * | 2003-10-01 | 2005-04-21 | Ntn Corp | 固定型等速自在継手 |
JP2007139095A (ja) * | 2005-11-18 | 2007-06-07 | Ntn Corp | 固定式等速自在継手 |
JP2008232293A (ja) * | 2007-03-20 | 2008-10-02 | Ntn Corp | 等速自在継手 |
JP2013194895A (ja) * | 2012-03-22 | 2013-09-30 | Hitachi Automotive Systems Kyushu Ltd | プロペラシャフト及びこのプロペラシャフトに用いられる等速ジョイント |
JP2017150549A (ja) * | 2016-02-24 | 2017-08-31 | 日立オートモティブシステムズ株式会社 | プロペラシャフト及びプロペラシャフトの製造方法 |
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JPS6239025U (ja) * | 1985-08-29 | 1987-03-09 | ||
DE19514868C1 (de) * | 1995-04-22 | 1996-05-23 | Loehr & Bromkamp Gmbh | Kugelgleichlaufdrehgelenk |
JP2005106233A (ja) * | 2003-10-01 | 2005-04-21 | Ntn Corp | 固定型等速自在継手 |
JP2007139095A (ja) * | 2005-11-18 | 2007-06-07 | Ntn Corp | 固定式等速自在継手 |
JP2008232293A (ja) * | 2007-03-20 | 2008-10-02 | Ntn Corp | 等速自在継手 |
JP2013194895A (ja) * | 2012-03-22 | 2013-09-30 | Hitachi Automotive Systems Kyushu Ltd | プロペラシャフト及びこのプロペラシャフトに用いられる等速ジョイント |
JP2017150549A (ja) * | 2016-02-24 | 2017-08-31 | 日立オートモティブシステムズ株式会社 | プロペラシャフト及びプロペラシャフトの製造方法 |
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