JP2023041415A - Sliding-type constant velocity universal joint - Google Patents

Abstract

To provide a sliding-type constant velocity universal joint of DOJ type which has good assembling workability even when a positive axial clearance is formed between pockets of a cage and balls.SOLUTION: In a sliding-type constant velocity universal joint includes: an outer joint member having a plurality of track grooves formed therein; an inner joint member having a plurality of track grooves formed therein; a plurality of torque transmission balls; and a cage 5 that accommodates the torque transmission balls in pockets 5a. A curvature center of a spherical external peripheral face of the cage 5 and a curvature center of a spherical internal peripheral face are offset to a side opposite to an axial direction with respect to a joint center. A positive axial clearance is formed between wall faces 5c of the pockets 5a of the cage 5 facing in a joint axial direction and the torque transmission balls. A rising part is formed on least at either of the wall faces 5c of the wall faces 5c of the pockets 5a facing in the joint axial direction, and a portion serving as a fastening margin is formed by the rising part between the wall faces 5c and the torque transmission balls.SELECTED DRAWING: Figure 5

Description

TECHNICAL FIELD The present invention relates to a sliding constant velocity universal joint used in automobiles and various industrial machines.

Constant velocity universal joints applied to automobile drive shafts are broadly classified into fixed type constant velocity universal joints that allow only angular displacement between two axes, and sliding type that allows both angular displacement and axial displacement. There is a quick universal joint. The drive shaft of an automobile usually uses a fixed constant velocity universal joint on the drive wheel side (also called the outboard side), and uses a sliding constant velocity universal joint on the differential side (also called the inboard side). It is configured by connecting these two constant velocity universal joints with an intermediate shaft.

Dove offset type constant velocity universal joints (DOJ) and tripod type constant velocity universal joints (TJ) are typical sliding type constant velocity universal joints. The DOJ type sliding constant velocity universal joint is widely used because of its low manufacturing cost and little backlash in the rotational direction inside the joint. Further, as the DOJ type sliding constant velocity universal joint, those having 6 or 8 balls are known.

DOJ type sliding constant velocity universal joints are used in situations where angular displacement or axial displacement occurs while transmitting torque from the drive shaft, such as when driving or idling when an automatic transmission vehicle is stopped. Since the sliding resistance inside the joint during displacement is large, an axial clearance is provided between the spherical outer peripheral surface of the inner joint member and the spherical inner peripheral surface of the retainer in order to reduce sliding resistance and reduce torque loss. In addition, there has been proposed one in which a slight pocket clearance is provided between the ball and the pocket of the retainer (Patent Documents 1 and 2).

In the standard DOJ, which does not require countermeasures against slide resistance, there is interference between the balls and the pockets of the retainer.

Japanese Utility Model Publication No. 5-6420 JP 2007-100797 A

By the way, when assembling the DOJ type sliding constant velocity universal joint, the balls are inserted into the pockets of the cage after the inner joint member and the cage are assembled. The assembly of the inner joint member, cage, and balls in this state is inserted into the outer joint member. can be easily assembled without the ball falling off.

A DOJ of standard specification in which the pockets and balls of the cage are used as the interference will be described with reference to FIG. 11 . After incorporating the inner joint member 53 into the cage 55, the balls 54 are inserted into the pockets 55a from the outside of the cage 55 in the radial direction. Assuming that the diameter of the ball 54 is D _BALL and the width of the pocket 55a of the cage 55 is Lw, in the standard DOJ, Lw<D _BALL , and there is interference between the ball 54 and the pocket 55a. Therefore, since the ball 54 is held in the pocket 55a with a tight margin, the ball can be easily assembled without falling off when it is inserted into the outer joint member.

However, in the slide resistance reduction specification where there is a gap between the pocket of the cage and the ball, it is necessary to assemble carefully so that the ball does not fall off. Therefore, it is necessary to take countermeasures in anticipation of ball drop-out, which also causes deterioration in assembly workability.

In view of the above problems, the present invention is characterized in that a positive axial clearance is provided between the cage pocket and the ball to reduce the slide resistance, and the cage pocket and the ball act as interference during assembly. To provide a sliding constant velocity universal joint of DOJ type which can be handled in the same way as existing specifications and has good assembling workability.

As a technical means for achieving the above object, the present invention provides an outer joint member having a plurality of linear track grooves formed along the axial direction on a cylindrical inner peripheral surface; an inner joint member in which a plurality of linear track grooves facing the plurality of linear track grooves are formed along the axial direction; a plurality of linear track grooves in the outer joint member and the inner joint member; A plurality of torque transmission balls incorporated between a plurality of linear track grooves, and the torque transmission balls are housed in a pocket and come into contact with the cylindrical inner peripheral surface of the outer joint member and the spherical outer peripheral surface of the inner joint member. It consists of a cage having a spherical outer peripheral surface to be guided and a spherical inner peripheral surface, and the center of curvature of the spherical outer peripheral surface and the center of curvature of the spherical inner peripheral surface of the cage are offset in the axial direction opposite to the center of the joint. In the sliding constant velocity universal joint, a positive axial clearance is formed between the wall surface of the pocket of the cage facing in the joint axial direction and the torque transmission ball, and the wall surface of the pocket facing in the joint axial direction has a positive axial clearance. A raised portion is formed on the outer diameter side of at least one of the wall surfaces, and the raised portion forms a portion that serves as an interference between the wall surface and the torque transmission ball. With the above configuration, a positive axial clearance is provided between the cage pocket and the ball to reduce sliding resistance. It is possible to realize a sliding constant velocity universal joint of the DOJ type with good assembling workability.

Specifically, it is desirable that the wall surfaces on which the raised portion is formed are both of the wall surfaces of the pocket facing in the joint axial direction. As a result, even if the height of the raised portion is suppressed, the ball can be reliably prevented from falling off, and the raised portion can be easily processed.

An axial clearance can be formed between the spherical inner peripheral surface of the cage and the spherical outer peripheral surface of the inner joint member to allow relative axial movement of the cage and the inner joint member. Thereby, the slide resistance can be reduced under general vibration conditions.

A spherical clearance that enables contact guidance can be formed between the spherical inner peripheral surface of the cage and the spherical outer peripheral surface of the inner joint member. As a result, it is suitable for reducing slide resistance under conditions of use in which low vibration has progressed.

By setting the number of the plurality of torque transmission balls to 5 to 10, it is possible to construct a sliding constant velocity universal joint suitable for power transmission systems of automobiles, various industrial machines, and the like.

According to the sliding constant velocity universal joint of the present invention, a positive axial clearance is provided between the pockets of the cage and the balls to reduce sliding resistance, and the pockets of the cage and the balls are tightened during assembly. It is possible to realize a sliding constant velocity universal joint of the DOJ type that can be handled in the same manner as the existing specifications and has good assembling workability.

FIG. 3 is a vertical cross-sectional view of the sliding constant velocity universal joint according to the first embodiment of the present invention, taken along line BNB of FIG. 2; FIG. 2 is a cross-sectional view of the sliding constant velocity universal joint according to the first embodiment of the present invention, taken along line AA of FIG. 1; FIG. 2 is a longitudinal sectional view showing an enlarged assembly of the inner joint member, cage, and balls in FIG. 1; FIG. 4 is a partial longitudinal sectional view enlarging the E section of FIG. 3; FIG. 4 is a vertical cross-sectional view showing a raised portion formed on the outer diameter side of the wall surface of the pocket of the cage in the sliding constant velocity universal joint of the present embodiment. (a) is a partial longitudinal sectional view enlarging part C of FIG. 5, and (b) is a partial longitudinal sectional view enlarging part D of FIG. FIG. 4 is a plan view showing the dimensional relationship between the wall surface of the pocket of the cage, the raised portion, and the ball. It is a longitudinal cross-sectional view which shows the modification of a swelling part. FIG. 7 is a vertical cross-sectional view showing an assembly of an inner joint member, a cage, and balls in a sliding constant velocity universal joint according to a second embodiment of the present invention; FIG. 10 is a vertical cross-sectional view showing an assembly of an inner joint member, a cage, and balls in a sliding constant velocity universal joint according to a third embodiment of the present invention; FIG. 4 is a vertical cross-sectional view showing an assembly of the inner joint member, cage, and balls in a standard DOJ in which pockets and balls of the cage serve as interference.

A sliding constant velocity universal joint according to a first embodiment of the present invention will be described with reference to FIGS. 1 to 7. FIG. FIG. 1 is a vertical cross-sectional view of a sliding constant velocity universal joint according to a first embodiment of the present invention, and is a vertical cross-sectional view taken along line BNB of FIG. 2. FIG. 1 is a cross-sectional view of the sliding constant velocity universal joint according to the first embodiment, taken along the line AA of FIG. 1. FIG. FIG. 3 is a longitudinal sectional view showing an enlarged assembly of the inner joint member, cage, and balls in FIG. FIG. 4 is a partial longitudinal sectional view enlarging the E section of FIG. FIG. 5 is a vertical cross-sectional view showing a raised portion formed on the outer diameter side of the wall surface of the pocket of the cage in the sliding constant velocity universal joint of the present embodiment, and FIG. 6(b) is a partial longitudinal sectional view enlarging part D of FIG. FIG. 7 is a plan view showing the dimensional relationship between the wall surface of the pocket of the cage, the raised portion and the balls.

As shown in FIGS. 1 and 2, the sliding constant velocity universal joint 1 is a so-called double-offset sliding constant velocity universal joint (also abbreviated as DOJ). The inner joint member 3, the torque transmission balls 4 and the cage 5 are the main components. Six track grooves 7 are formed in the cylindrical inner peripheral surface 6 of the outer joint member 2 at equal intervals in the circumferential direction and linearly along the axial direction. Track grooves 9 facing the track grooves 7 of the outer joint member 2 are formed on the spherical outer peripheral surface 8 of the inner joint member 3 at regular intervals in the circumferential direction and linearly along the axial direction. Between the track grooves 7 of the outer joint member 2 and the track grooves 9 of the inner joint member 3, six torque transmission balls (hereinafter also simply referred to as balls) 4 are incorporated one by one. Balls 4 are housed in pockets 5 a of cage 5 .

The cage 5 has a spherical outer peripheral surface 11 and a spherical inner peripheral surface 12. The spherical outer peripheral surface 11 is fitted and guided in contact with the cylindrical inner peripheral surface 6 of the outer joint member 2, and the spherical inner peripheral surface 12 is inside. It is engaged with and guided by the spherical outer peripheral surface 8 of the joint member 3 . The spherical outer peripheral surface 11 of the cage 5 is formed with a curvature radius Rc1 with a curvature center Oc1, and the spherical inner peripheral surface 12 is formed with a curvature radius Rc2 with a curvature center Oc2. A spherical outer peripheral surface 8 of the inner joint member 3 is formed with a radius of curvature Ri with a center of curvature Oi2. The centers of curvature Oc1, Oi2 are located on the axis N and are axially offset from the joint center O by the same distance F (see FIG. 3). Further, the center of curvature Oc2 of the spherical inner peripheral surface 12 of the cage 5 is located radially offset from the axis N with respect to the center of curvature Oi2 so that Rc2>Ri, and is axially offset from the center O of the joint. It is offset by F (see FIG. 3).

With the above configuration, a spherical gap is formed at the axially central portion of the spherical outer peripheral surface 8 of the inner joint member 3 to enable contact guidance with respect to the spherical inner peripheral surface 12 of the cage 5. An axial clearance is formed that allows the inner joint member 3 and the cage 5 to move relative to each other in the axial direction. As a result, the sliding resistance can be reduced in combination with the positive axial clearance between the ball 4 and the pocket 5a of the cage 5, which will be detailed later. Also, when the joint has an operating angle, the balls 4 are always guided on a plane that bisects the angle between the axes of the outer joint member 2 and the inner joint member 3, and the two shafts rotate at a constant speed. be done.

A retaining ring groove (not shown) is provided at the opening side end of the outer joint member 2, and a retaining ring is attached to the retaining ring groove to form the assembly of the inner joint member 3, the balls 4, and the cage 5 shown in FIG. prevents it from slipping out of the opening side end of the outer joint member 2 . A boot mounting groove 16 is provided on the outer circumference of the opening-side end of the outer joint member 2 . A stem portion (shaft portion) 2b is integrally formed on the side opposite to the opening of the outer joint member 2, and is connected to a differential (not shown). A spline (including serrations, the same shall apply hereinafter) 14 is formed in the connecting hole 13 of the inner joint member 3 , and an axial end of an intermediate shaft (not shown) is spline-fitted so that the inner joint member 3 is attached to the intermediate shaft shoulder. It is fixed in the axial direction by the part and the retaining ring.

Six pockets 5a are provided at equal intervals in the circumferential direction at the axial center of the cage 5 indicated by line AA in FIG. 1, and columns 5b (see FIG. 2) are provided between adjacent pockets 5a. . A notch 5c for incorporating the inner joint member 3 is provided on the inner periphery of the large-diameter end of the cage 5 .

The overall configuration of the sliding constant velocity universal joint 1 of this embodiment is as described above. Next, a characteristic configuration will be described with reference to FIGS. 3 to 7. FIG. As shown in FIG. 3, which is an enlarged vertical cross-sectional view showing an assembly of the inner joint member, cage, and balls, there is a gap between the wall surface 5c of the pocket 5a of the cage 5 and the torque transmission ball 4, which faces in the joint axial direction. A positive axial clearance δ2 is formed. Assuming that the diameter of the balls 4 is D _BALL and the width between the wall surfaces 5c of the pockets 5a of the cage 5 facing in the joint axial direction is Lw, the axial clearance δ2 is δ2=Lw-D _BALL .

The positive axial clearance δ2 between the ball 4 and the wall surface 5c of the pocket 5a of the cage 5 facing in the joint axial direction is desirably +0.001 mm to +0.050 mm. This allows the ball 4 to roll smoothly in the pocket 5a, increasing the rolling area of the ball 4 on the track grooves 7 and 9 of the outer joint member 2 and the inner joint member 3, thereby reducing slide resistance. In the sliding constant velocity universal joint 1 of this embodiment, δ2 is set to +0.001 mm to +0.050 mm.

As shown in FIG. 3, the spherical outer peripheral surface 11 of the cage 5 is formed with a curvature radius Rc1 with a curvature center Oc1, and the spherical inner peripheral surface 12 is formed with a curvature radius Rc2 with a curvature center Oc2. A spherical outer peripheral surface 8 of the inner joint member 3 is formed with a radius of curvature Ri with a center of curvature Oi2. The centers of curvature Oc1, Oi2 are located on the axis N and are axially offset by an equal distance F with respect to the joint center O. Further, the center of curvature Oc2 of the spherical inner peripheral surface 12 of the cage 5 is located radially offset from the axis N with respect to the center of curvature Oi2 so that Rc2>Ri, and is axially offset from the center O of the joint. Offset by F.

As shown in FIG. 4, the spherical outer peripheral surface 8 of the inner joint member 3 has a spherical clearance δ3 that enables contact guidance with the spherical inner peripheral surface 12 of the cage 5 at the center in the axial direction. is formed with an axial clearance δ4 that allows the inner joint member 3 and the cage 5 to move relative to each other in the axial direction. The spherical clearance δ3 is about 0.050 mm in median. The axial clearance δ4 is about 1 mm. The movable amount in the axial direction of the inner joint member 3 with respect to the outer joint member 2 is about 2 mm, which is twice the axial clearance δ4 of about 1 mm, and vibration is absorbed in this range of movable amount in the axial direction. That is, it is possible to reduce the slide resistance for general-purpose vibration conditions. The spherical clearance δ3 and the axial clearance δ4 are shown exaggerated.

The axial clearance δ4 between the cage 5 and the inner joint member 3 and the positive axial clearance δ2 between the ball 4 and the wall surface 5c of the pocket 5a of the cage 5 facing the joint axial direction are , the sliding resistance can be reduced.

Next, the raised portion 5d will be described with reference to FIGS. 5 to 7. FIG. As shown in FIG. 5, the raised portions 5d are formed in portions C and D in FIG. As shown in FIGS. 6A and 6B, which are enlarged portions of C and D in FIG. It is about 0.06 mm.

FIG. 7 shows the dimensional relationship between the wall surface 5c of the pocket 5a of the cage 5, the raised portion 5d and the balls 4. As shown in FIG. FIG. 7 is a plan view of the assembly of the inner joint member 3, cage 5, and balls 4 shown in FIG. The width between the wall surfaces 5c facing each other in the joint axial direction is Lw, and an axial clearance δ2 (δ2=Lw−D _BALL ) is formed between the wall surfaces 5c and the balls 4 . On the other hand, the width between the raised portions 5d is Lw', and Lw' is slightly smaller than _DBALL , and the width Lw' between the raised portions 5d and the ball 4 becomes the interference f. In this manner, the raised portion 5d forms a portion that serves as an interference f between the wall surface 5c and the torque transmission ball 4. As shown in FIG.

Since the interference f between the width Lw' between the protruding portions 5d and the balls 4 is about 0.04 mm, the balls 4 move radially outwardly of the cage 5 after the inner joint member 3 and the cage 5 are assembled. It can be built into the pocket 5a by overcoming the raised portion 5d by elastic deformation. When the assembly of the inner joint member 3, the cage 5, and the balls 4 is inserted into the outer joint member 2, the interference f prevents the balls 4 from falling off, making it possible to easily assemble the assembly, thereby improving assembly workability. . When the joint is in operation, the balls 4 are positioned radially inward and out of contact with the raised portion 5d. Slide resistance is reduced.

The raised portion 5d can be processed by, for example, tumble processing. The tumbler treatment is originally performed for deburring after the cage 5 is quenched. The amount of swelling changes depending on the amount of media and the number of workpieces input during tumble processing. This is because when the media collide and the works collide with each other, the amount of swelling increases. Further, as shown in FIG. 7, the flat portion of the pocket 5a is more likely to swell than the arc-shaped portion. The minimum width of the raised portion 5d in the circumferential direction is about 2 to 3 mm. If it is a tumbler process, it is easy to process to form the raised portion 5d, and it is advantageous in terms of cost. However, the processing of the raised portion 5d is not limited to the tumble processing, and may be performed by machining such as cutting.

A modification of the raised portion will be described with reference to FIG. The raised portion 5d of this modified example is formed by milling, which is mechanical processing. A raised portion 5d is formed only on one side of the wall surfaces 5c of the pocket 5a facing in the joint axial direction. In this way, the raised portion 5d can be formed only on one side.

As shown in FIG. 8, in this modification, the width between the raised portion 5d and the wall surface 5c is Lw'. The width Lw′ between the raised portions 5d when the raised portions 5d are provided on both sides of the wall surface 5c described above is equal to the width Lw′ between the raised portions 5d when the raised portion 5d is provided on one side of the wall surface 5c as in the present modification. The width Lw' with respect to the wall surface 5c is assumed to be treated in the same way. Therefore, the width Lw' between the raised portion 5d and the wall surface 5c and the ball 4 become the interference. That is, also in this case, a portion that becomes the interference f between the wall surface 5c and the torque transmission ball 4 is formed by the raised portion 5d. Since the raised portion 5d is only on one side, it is desirable to increase the height h' of the raised portion 5d to a maximum of about 0.12 mm.

As described above, the raised portion 5d is formed only on one side of the wall surface 5c. ' is used in this specification, and the expression 'the portion that becomes the interference f between the wall surface 5b and the torque transmission ball 4 is formed by the raised portion 5c' is used in this specification.

A sliding constant velocity universal joint according to a second embodiment of the present invention will be described with reference to FIG. The sliding constant velocity universal joint of this embodiment differs from the sliding constant velocity universal joint of the first embodiment in the shape of the spherical inner circumferential surface of the cage. Since other configurations are the same as those of the first embodiment, portions having similar functions are denoted by the same reference numerals, and only the main points will be described.

FIG. 9 illustrates a state in which the inner joint member 3 is arranged in the center of the cage 5 in the axial direction. As shown in FIG. 9, the spherical inner peripheral surface 12 of the cage 5 includes a spherical portion 12a having a curvature radius Rc2 having a center of curvature Oc2, a spherical portion 12b having a curvature radius Rc2 having a center of curvature Oc3, a spherical portion 12a and a spherical surface. It is composed of a cylindrical portion 12c connecting the portion 12b with a tangential line. The center of curvature Oc2 and the center of curvature Oc3 are located on the axis N, and the center point of the center of curvature Oc2 and the center of curvature Oc3 in the axial direction is offset from the center O of the joint by F. A spherical outer peripheral surface 8 of the inner joint member 3 is formed with a radius of curvature Ri having a center of curvature Oi2. In the arrangement shown in FIG. 9, the axial center point between the center of curvature Oc2 and the center of curvature Oc3 of the spherical inner peripheral surface 12 of the cage 5 coincides with the center of curvature Oi2 of the spherical outer peripheral surface 8 of the inner joint member 3. .

A spherical clearance δ3 is formed at the axially central portion of the spherical outer peripheral surface 8 of the inner joint member 3 to enable contact guidance with the cylindrical portion 12c of the cage 5, and the inner joint member 3 and the cage are formed on both sides of the central portion. An axial clearance .delta.4 is formed which allows relative axial movement with 5. As shown in FIG. The length of the cylindrical portion 12c is approximately 1 mm, and the axial clearance δ4 corresponds to the length of the cylindrical portion 12c. The movable amount in the axial direction of the inner joint member 3 with respect to the outer joint member 2 is about 2 mm, which is twice the length of about 1 mm of the cylindrical portion 12c, and vibration is absorbed in this range of movable amount in the axial direction. That is, it is possible to reduce the slide resistance for general-purpose vibration conditions.

In this embodiment, the spherical inner peripheral surface 12 of the cage 5 includes a spherical portion 12a having a curvature radius Rc2 with a curvature center Oc2, a spherical portion 12b having a curvature radius Rc2 with a curvature center Oc3, and a spherical portion 12a and a spherical portion 12b. and a cylindrical portion 12c that connects the two with a tangential line. Since the curvature radius Rc2 and the curvature radius Ri are substantially the same, contact guidance between the spherical inner peripheral surface 12 of the cage 5 and the spherical outer peripheral surface 8 of the inner joint member 3 is smooth and stable.

Also in the present embodiment, a positive axial clearance δ2 is formed between the wall surface 5c of the pocket 5a of the cage 5 facing in the joint axial direction and the torque transmission ball 4, as in the first embodiment. A raised portion 5d (not shown) is formed on the outer diameter side of at least one wall surface 5c of the wall surfaces 5c of the pocket 5a of the cage 5 that face each other in the joint axial direction. Other configurations, effects, etc., whose explanations are omitted, are the same as those of the first embodiment, so the contents explained in the first embodiment are applied mutatis mutandis to this embodiment.

A sliding constant velocity universal joint according to a third embodiment of the present invention will be described with reference to FIG. In the sliding constant velocity universal joint of this embodiment, the radius of curvature of the spherical inner peripheral surface of the cage and the radius of curvature of the spherical outer peripheral surface of the inner joint member are substantially the same. It differs from the sliding constant velocity universal joint of the first embodiment in that it is a standard type spherical surface specification in which a spherical clearance is formed to enable contact guidance with the outer peripheral surface. Since other configurations are the same as those of the first embodiment, portions having similar functions are denoted by the same reference numerals, and only the main points will be described.

As shown in FIG. 10, the spherical inner peripheral surface 12 of the cage 5 is formed with a curvature radius Rc2 with a curvature center Oc2, and the spherical outer peripheral surface 8 of the inner joint member 3 is formed with a curvature radius Ri with a curvature center Oi2. there is A spherical clearance δ3 between the spherical inner peripheral surface 12 of the cage 5 and the spherical outer peripheral surface 8 of the inner joint member 3 is δ3=2×(Rc2−Ri). The spherical clearance δ3 enables contact guidance with respect to the spherical inner peripheral surface 12 of the cage 5 at the axially central portion of the spherical outer peripheral surface 8 of the inner joint member 3 in the first and second embodiments described above. The spherical clearance δ3 is approximately 0.050 mm in median. The spherical clearance δ3 means the spherical clearance that enables contact guidance between the spherical outer peripheral surface of the inner joint member and the spherical inner peripheral surface of the cage in the present specification and claims.

Due to the spherical clearance δ3, a small amount of axial movement of the inner joint member 3 with respect to the outer joint member 2 is obtained. can absorb vibrations. Therefore, the combination of the spherical clearance δ3 between the cage 5 and the inner joint member 3 and the positive axial clearance δ2 between the balls 4 and the pocket 5a of the cage 5 can reduce the sliding resistance. can. That is, it is suitable for reducing slide resistance under conditions of use in which low vibration has progressed.

Also in this embodiment, a positive axial clearance δ2 is formed between the torque transmission balls 4 and the wall surfaces 5c of the pockets 5a of the cage 5 facing in the joint axial direction, as in the first embodiment. A raised portion 5d (not shown) is formed on the outer diameter side of at least one of the wall surfaces 5c of the pocket 5a of the cage 5 that face each other in the joint axial direction. Other configurations, effects, etc., whose explanations are omitted, are the same as those of the first embodiment, so the contents explained in the first embodiment are applied mutatis mutandis to this embodiment.

In the above-described embodiment and modification, the DOJ type sliding constant velocity universal joint 1 using six torque transmission balls 4 was exemplified. It can be carried out as appropriate within the range of one. A sliding constant velocity universal joint suitable for power transmission systems of automobiles and various industrial machines can be configured.

The present invention is by no means limited to the above-described embodiments and modifications, and can of course be embodied in various forms without departing from the scope of the present invention. are indicated by the claims and include all changes within the meaning and range of equivalents set forth in the claims.

1 Sliding constant velocity universal joint 2 Outer joint member 3 Inner joint member 4 Torque transmission ball 5 Cage 5a Pocket 5c Wall surface 5d Raised portion 6 Cylindrical inner peripheral surface 7 Track groove 8 Spherical outer peripheral surface 9 Track groove 11 Spherical outer peripheral surface 12 Spherical inner peripheral surface D _BALL ball diameter F Offset amount Lw Width between walls Lw' Width between raised parts O Joint center Oc1 Curvature center Oc2 Curvature center Oc3 Curvature center Oi1 Curvature center Oi2 Curvature center f Interference δ2 Between ball and pocket Positive axial clearance δ3 Spherical clearance δ4 Axial clearance between cage and inner joint member

Claims (5)

An outer joint member having a plurality of linear track grooves formed along the axial direction on a cylindrical inner peripheral surface, and a plurality of linear track grooves facing the plurality of linear track grooves of the outer joint member on a spherical outer peripheral surface. track grooves are formed along the axial direction; and a plurality of torques incorporated between the plurality of linear track grooves of the outer joint member and the plurality of linear track grooves of the inner joint member. a transmission ball, a cage that houses the torque transmission ball in a pocket, and has a spherical outer peripheral surface that is guided in contact with the cylindrical inner peripheral surface of the outer joint member and the spherical outer peripheral surface of the inner joint member, and a spherical inner peripheral surface. A sliding constant velocity universal joint in which the center of curvature of the spherical outer peripheral surface and the center of curvature of the spherical inner peripheral surface of the cage are offset on opposite sides in the axial direction with respect to the center of the joint,
A positive axial clearance is formed between wall surfaces of the pockets of the cage facing in the joint axial direction and the torque transmission balls,
A raised portion is formed on an outer diameter side of at least one wall surface of the pocket facing the joint axial direction,
A sliding constant velocity universal joint, wherein the raised portion forms a portion that serves as an interference between the wall surface and the torque transmission ball. 2. The sliding constant velocity universal joint according to claim 1, wherein the wall surfaces on which the raised portion is formed are both wall surfaces of the pocket facing each other in the joint axial direction. An axial clearance is formed between the spherical inner peripheral surface of the cage and the spherical outer peripheral surface of the inner joint member to enable relative axial movement of the cage and the inner joint member. The sliding constant velocity universal joint according to claim 1 or 2. 3. The sliding according to claim 1, wherein a spherical clearance is formed between the spherical inner peripheral surface of the cage and the spherical outer peripheral surface of the inner joint member to enable contact guidance. constant velocity universal joint. The sliding constant velocity universal joint according to any one of claims 1 to 4, characterized in that the number of said plurality of torque transmission balls is 5-10.

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