JP2011117532A - Ball-type constant velocity joint - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a ball-type constant velocity joint capable of elongating life of a retainer by avoiding generation of a sliding defect of the retainer and an inner ring even when swelling occurs on an outer peripheral surface of the inner ring. <P>SOLUTION: The ball-type constant velocity joint includes an outer ring 20 having an outer ring ball groove 23, the inner ring 30 having an inner ring ball groove 32, a ball 40 rolling on the outer ring ball groove 23 and the inner ring ball groove 32, and the retainer 50 disposed between the outer ring 20 and the inner ring 30 to retain the ball 40. A recessed part 55 for avoiding interference with a swelling part occurring on the outer peripheral surface 31 of the inner ring 30 during torque transmission is provided on an inner peripheral surface 52 of an opening opposite side (a deep side) of the outer ring 20 than a width direction center of a window part 53 of the retainer 50. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a ball-type constant velocity joint used for a driving force transmission shaft portion of a vehicle.

  As conventional ball type constant velocity joints, for example, those described in Japanese Patent Application Laid-Open No. 11-190354 (Patent Document 1) are known. This ball type constant velocity joint is formed in a cylindrical shape having an opening in one axial direction and has an outer ring having a plurality of outer ring ball grooves extending in the axial direction on the inner circumferential surface, and disposed on the inner side of the outer ring. An inner ring having a plurality of inner ring ball grooves extending in the axial direction, a plurality of balls that roll the outer ring ball groove and the inner ring ball groove and transmit torque between the outer ring and the inner ring, and an annularly formed circumferential direction And a retainer disposed between the outer ring and the inner ring.

  The cage interposed between the outer ring and the inner ring is disposed so as to make spherical contact with the concave spherical inner peripheral surface of the outer ring and the convex spherical outer peripheral surface of the inner ring. That is, the outer peripheral surface of the cage is formed in a convex spherical shape, and the inner peripheral surface of the cage is formed in a concave spherical shape. Further, the outer ring ball groove and the inner ring ball groove are formed in an arc shape, and their centers of curvature are offset in the axial direction by an equal distance in the opposite direction from the joint center. Thereby, the depth of the outer ring ball groove and the inner ring ball groove gradually decreases from the opening side of the outer ring toward the back side.

Japanese Patent Application Laid-Open No. 11-190354

  By the way, the above-mentioned ball type constant velocity joint is used as an outboard joint of a drive shaft in a vehicle. Usually, the ball type constant velocity joint installed on the front side of the vehicle can cope with steering of the front wheels. In addition, the maximum joint operating angle is set to a large value of about 45 ° to 50 °. For this reason, when a large joint operating angle is applied, the contact ellipse of the ball protrudes particularly near the shallow end where the ball of the inner ring ball groove is located, and the stress at the edge of the inner ring ball groove increases. At this time, if an excessive input is applied when the vehicle is turned off, the inner ring ball groove is deformed, and a raised portion 37 is generated on the outer peripheral surface 31a of the inner ring 30a as shown in FIG. When the raised portion 37 occurs, a sliding failure of the cage occurs between the inner circumferential surface 52a of the cage 50a and the outer circumferential surface 31a of the inner ring 30a, and as shown in FIG. 6, the window portion of the cage 50a. Since the stress of the column part 54a between 53a increases, the lifetime of the cage 50a is reduced.

  The present invention has been made in view of the above circumstances, and even when a raised portion is generated on the outer peripheral surface of the inner ring, the occurrence of sliding failure between the cage and the inner ring is avoided, and the long life of the cage is achieved. It is a problem to be solved to provide a ball-type constant velocity joint that can be made simple.

The structural feature of the invention according to claim 1 for solving the above-mentioned problem is as follows.
An outer ring having a plurality of outer ring ball grooves formed in a bottomed cylindrical shape having an opening in one axial direction and extending in the axial direction on the inner peripheral surface;
An inner ring disposed inside the outer ring and having a plurality of inner ring ball grooves extending in the axial direction on the outer peripheral surface;
A plurality of balls that roll on the outer ring ball groove and the inner ring ball groove and transmit torque between the outer ring and the inner ring;
A cage formed in an annular shape and having a plurality of windows that respectively accommodate the balls in the circumferential direction, and disposed between the outer ring and the inner ring;
In the ball-type constant velocity joint with
The retainer is provided with a recess for avoiding interference with a raised portion generated on the outer peripheral surface of the inner ring at the time of torque transmission on the inner peripheral surface on the inner side of the outer ring from the center in the width direction of the window portion. That is.

  The structural feature of the invention according to claim 2 is that, in the ball type constant velocity joint according to claim 1, the concave portion is formed continuously in the circumferential direction on the inner peripheral surface of the cage. is there.

  The structural feature of the invention according to claim 3 is that, in the ball type constant velocity joint according to claim 1, the concave portion is intermittently formed in the circumferential direction on the inner peripheral surface of the cage. is there.

  The structural feature of the invention according to claim 4 is the ball type constant velocity joint according to any one of claims 1 to 3, wherein the inner peripheral surface of the cage is an intersection of the outer ring axis and the inner ring axis. It is formed by a concave spherical surface centered on O, and the concave portion is formed by a curved surface having a curvature radius R2 different from the curvature radius R1 of the concave spherical surface.

  The structural feature of the invention according to claim 5 is the ball type constant velocity joint according to any one of claims 1 to 4, wherein the outer ring ball groove is in an undercut free state when viewed from the outer ring opening side. Is formed.

  According to the first aspect of the present invention, the cage avoids interference between the inner circumferential surface on the inner side of the outer ring with respect to the center in the width direction of the window portion and the raised portion generated on the outer circumferential surface of the inner ring during torque transmission. Are provided. Therefore, even when a bulging portion is generated on the outer peripheral surface of the inner ring, it is possible to avoid the occurrence of poor sliding between the cage and the inner ring and to extend the life of the cage. Furthermore, the intensity | strength of the column part located between adjacent window parts is securable by providing a recessed part in the internal peripheral surface of the outer ring | wheel back side rather than the center of the width direction of a window part.

  According to the second aspect of the present invention, since the recess is continuously formed in the circumferential direction on the inner peripheral surface of the cage, it is possible to easily and easily perform a shaving process or the like when forming the recess. . Further, by forming one concave portion that is continuous in the circumferential direction, it is possible to cope with all of the raised portions that occur at a plurality of locations in the circumferential direction. Furthermore, it is possible to deal with all of the swelled portions that are generated at different locations during the forward rotation and the reverse rotation of the constant velocity joint.

  According to the invention which concerns on Claim 3, the recessed part is intermittently formed in the circumferential direction on the internal peripheral surface of the said holder | retainer. In this case, since it is only necessary to form a concave portion only at a predetermined location corresponding to the raised portion generated on the outer peripheral surface of the inner ring, a decrease in strength of the cage can be minimized. Furthermore, since it is possible to secure a sufficient area in sliding contact with the outer peripheral surface of the inner ring in the inner peripheral surface of the cage, it is easy to ensure the operational stability of the constant velocity joint.

  According to the invention of claim 4, the inner peripheral surface of the cage is formed by a concave spherical surface centering on the intersection O of the outer ring axis and the inner ring axis, and the concave portion has a curvature different from the curvature radius R1 of the concave spherical surface. It is formed by a curved surface having a radius R2. Thereby, a recessed part can be easily and easily formed in the predetermined location of the internal peripheral surface of a holder | retainer.

  According to the invention of claim 5, since the outer ring ball groove is formed in an undercut free state when viewed from the outer ring opening side, a ball type constant velocity joint having a larger maximum joint operating angle can be easily realized. can do. Therefore, the problem of sliding failure between the cage and the inner ring, which is particularly likely to occur in a ball type constant velocity joint having a large maximum joint operating angle, can be solved by the present invention. In other words, for a ball-type constant velocity joint having a large maximum joint operating angle, the occurrence of a sliding failure between the cage and the inner ring is more effectively avoided by providing a recess on the inner peripheral surface of the cage. be able to. Thereby, the lifetime improvement of a holder | retainer can be achieved more advantageously.

It is sectional drawing which follows the axial direction of the ball | bowl type | mold constant velocity joint of embodiment. It is a fragmentary sectional view in alignment with the axial direction of the holder | retainer which concerns on the ball | bowl type constant velocity joint of embodiment. It is data which shows the relationship between the amount of bulging of the inner ring outer peripheral surface and the cage column portion stress increase value which were examined when setting the concave portion on the inner peripheral surface of the cage. It is a fragmentary sectional view which follows the axial direction of the holder | retainer which concerns on the modification of embodiment. It is a fragmentary sectional view in alignment with the axial direction of the inner ring | wheel which concerns on the conventional ball type | mold constant velocity joint. It is a fragmentary sectional view in alignment with the axial direction of the holder | retainer which concerns on the conventional ball type | mold constant velocity joint.

  Hereinafter, an embodiment in which the ball type constant velocity joint of the present invention is embodied will be described with reference to the drawings.

  A configuration of the ball type constant velocity joint 10 (hereinafter, simply referred to as “constant velocity joint”) of the present embodiment will be described with reference to FIG. FIG. 1 is an axial sectional view of the constant velocity joint 10 according to the present embodiment in a state where the maximum joint angle θ is taken. FIG. 2 is a partial cross-sectional view along the axial direction of the cage 50 in the present embodiment. In the following description, the opening side (outer ring opening side) of the outer ring 20 means the right side in FIG. 1, and the back side (outer ring back side) of the outer ring 20 means the left side in FIG.

  As shown in FIG. 1, the constant velocity joint 10 of the present embodiment is a joint center fixed ball type constant velocity joint (also referred to as a “Zepper type constant velocity joint”), and is a drive installed on the front side in a vehicle. It is preferably used as an outboard joint of a shaft. Therefore, the maximum joint operating angle of the constant velocity joint 10 is set to be a large angle range of 50 ° or more. The constant velocity joint 10 includes an outer ring 20 having a plurality of outer ring ball grooves 23, an inner ring 30 having a plurality of inner ring ball grooves 32, a plurality of balls 40, and a cage 50. Hereinafter, each component will be described in detail.

  The outer ring 20 is formed in a cup shape (bottomed cylindrical shape) having an opening on the right side of FIG. A connecting shaft 21 is integrally formed on the outer side of the cup bottom of the outer ring 20 (on the left side in FIG. 1) so as to extend in the outer ring axial direction. The connecting shaft 21 is connected to another power transmission shaft. The inner peripheral surface 22 of the outer ring 20 is formed in a concave spherical shape. Specifically, the concave spherical inner peripheral surface 22 of the outer ring 20 is formed by a part of a spherical surface drawn with the intersection O between the outer ring axis L1 and the inner ring axis L2 as the center of curvature, and is cut in the direction of the outer ring axis. When viewed in cross section, it is formed in an arc concave shape.

  On the concave spherical inner peripheral surface 22 of the outer ring 20, a plurality of outer ring ball grooves 23 whose outer ring axis orthogonal cross section is substantially arc-shaped are formed in an arc shape so as to extend substantially in the outer ring axis direction. These outer ring ball grooves 23 (six in this embodiment) are formed at equal intervals in the circumferential direction (60 ° intervals in this embodiment) when viewed in a cross section cut in the radial direction. Here, the outer ring axial direction means a direction passing through the central axis of the outer ring 20, that is, a rotation axis direction of the outer ring 20.

  A groove bottom 23a on the outer ring inner side of the outer ring ball groove 23 is formed by an arcuate curve drawn with a point a offset by a predetermined distance from the intersection O to the opening side of the outer ring 20 on the outer ring axis L1. The groove bottom 23b at the end of the outer ring ball groove 23 on the outer ring opening side is formed by a straight line extending from the groove bottom 23a on the outer ring rear side to the outer ring opening side substantially parallel to the outer ring axis L1. Therefore, the groove bottom of the outer ring ball groove 23 is formed in a state where the end portion on the outer ring opening side is located most radially outward, that is, in an undercut-free state when viewed from the outer ring opening side. Thereby, the maximum joint operating angle can be set large. Further, the outer ring ball groove 23 gradually decreases in depth from the outer ring opening side toward the outer ring back side.

  The inner ring 30 is formed in an annular shape and is disposed inside the outer ring 20. The outer peripheral surface 31 of the inner ring 30 is formed in a convex spherical shape. Specifically, the convex spherical outer peripheral surface 31 of the inner ring 30 is formed by a part of a spherical surface drawn with the intersection O between the outer ring axis L1 and the inner ring axis L2 as the center of curvature, and is a cross section cut in the direction of the inner ring axis. Are formed in a uniform arc, that is, a convex partial spherical shape.

  A plurality of inner ring ball grooves 32 having a substantially arc-shaped cross section in the direction perpendicular to the inner ring axis are formed in an arc shape on the outer peripheral surface of the inner ring 30 so as to extend substantially in the inner ring axis direction. The plurality of (six in this embodiment) inner ring ball grooves 32 are equally spaced in the circumferential direction (60 degrees in the present embodiment) and viewed from the outer ring 20 when viewed in a cross section cut in the radial direction. The same number of outer ring ball grooves 23 are formed. That is, each inner ring ball groove 32 is positioned so as to face each outer ring ball groove 23 of the outer ring 20.

  The groove bottom 32a on the outer ring opening side of the inner ring ball groove 32 is formed by an arcuate curve drawn with a point b offset from the intersection O to the inner side of the outer ring 20 by a predetermined distance on the inner ring axis L2. The offset distance from the intersection point O of the point b is the same as the offset distance from the intersection point O of the point a. A groove bottom 32b on the outer ring inner side of the inner ring ball groove 32 is formed by a straight line continuously extending from the groove bottom 32a on the outer ring opening side to the outer ring inner side substantially parallel to the inner ring axis L2. Thereby, the inner ring ball groove 32 gradually decreases in depth from the opening side of the outer ring 20 toward the back side.

  Between the adjacent inner ring ball grooves 32, protrusions 33 that protrude radially outward are formed. Further, an inner peripheral spline 35 extending in the inner ring axial direction is formed on the inner peripheral surface of the inner ring 30. The inner peripheral spline 35 is fitted (engaged) with the outer peripheral spline of the power transmission shaft 36. Here, the inner ring axial direction means a direction passing through the central axis of the inner ring 30, that is, a rotation axis direction of the inner ring 30.

  Each of the plurality of balls 40 is disposed so as to be sandwiched between the outer ring ball groove 23 of the outer ring 20 and the inner ring ball groove 32 of the inner ring 30 facing the outer ring ball groove 23. Each ball 40 is rotatable with respect to each outer ring ball groove 23 and each inner ring ball groove 32 and is engaged in a circumferential direction (around the outer ring axis or around the inner ring axis). Therefore, the ball 40 transmits torque between the outer ring 20 and the inner ring 30.

  The cage 50 is formed in an annular shape and is disposed between the concave spherical inner peripheral surface 22 of the outer ring 20 and the convex spherical outer peripheral surface 31 of the inner ring 30. The outer peripheral surface 51 of the cage 50 is formed in a partial spherical shape substantially corresponding to the concave spherical inner peripheral surface 22 of the outer ring 20, that is, a convex spherical shape. On the other hand, the inner peripheral surface 52 of the cage 50 is formed in a partial spherical shape that substantially corresponds to the convex spherical outer peripheral surface 31 of the inner ring 30, that is, a concave spherical shape. The outer peripheral surface 51 and the inner peripheral surface 52 of the cage 50 are formed by spherical surfaces centering on the intersection O between the outer ring axis L1 and the inner ring axis L2.

  The cage 50 has a plurality of window portions 53 that are substantially rectangular through holes arranged at equal intervals in the circumferential direction (the circumferential direction of the cage axis). The same number of the window portions 53 as the balls 40 are formed. One ball 40 is accommodated in each window 53. Arc concave shapes R are provided at four corners of each window 53. Thereby, the strength improvement of each pillar part 54 (refer FIG. 2) located between the adjacent window parts 53 is achieved.

  Then, as shown in FIG. 2, the inner peripheral surface 52 of the cage 50 avoids interference with the raised portion 37 (see FIG. 5) generated on the convex spherical outer peripheral surface 31 of the inner ring 30 during torque transmission. A recess 55 is provided. Specifically, the concave portion 55 is formed continuously between the end surface of the inner peripheral surface 52 of the cage 50 on the back side of the outer ring 20 and the window portion 53 so as to make one round in the circumferential direction with a predetermined width. Has been. The recess 55 is formed by a curved surface having a curvature radius R2 different from the curvature radius R1 of the spherical surface forming the inner peripheral surface 52 of the cage 50. In this case, the radius of curvature is R1> R2, but it is also possible to satisfy R1 <R2.

  The concave portion 55 is located on the back side of the outer ring 20 with respect to the center in the width direction of the window portion 53 and includes opposing portions 57a and 57b facing the raised portion 37 generated on the convex spherical outer peripheral surface 31 of the inner ring 30. Is formed. Here, one opposing portion 57a is a portion facing the raised portion 37 that is generated when the constant velocity joint 10 is rotated forward (rotation in the direction in which the vehicle moves forward), and the other opposing portion 57b is a constant velocity joint. 10 is a portion that faces the raised portion 37 that is generated at the time of 10 reverse rotation. The positions of the facing portions 57a and 57b may be shifted when the positions where the raised portions 37 are generated due to changes in the axial length and the radial size of the inner ring 30 and the retainer 50.

  In setting the recess 55 in the inner peripheral surface 52 of the cage 50, the relationship between the amount of swelling of the outer peripheral surface 31 of the inner ring 30 and the stress increase value of the column portion 54 of the cage 50 when the constant velocity joint 10 is operated. Upon examination, the results shown in FIG. 3 were obtained. As is apparent from FIG. 3, the stress of the column portion 54 of the cage 50 increases when the outer circumferential surface 31 bulge amount of the inner ring 30 is 0.08 mm or more. Therefore, by ensuring a clearance of 0.08 mm or more between the outer peripheral surface 31 of the inner ring 30 and the inner peripheral surface 52 of the cage 50, an increase in stress of the column portion 54 can be suppressed. Moreover, what is necessary is just to make said clearance into 0.14 mm or less in order to suppress the stress of the column part 54 to 100 Mpa or less.

  The constant velocity joint 10 of the present embodiment configured as described above is used as an outboard joint of a drive shaft installed on the front side in a vehicle. When an excessive input is applied at the time of steering up and off with a large joint operating angle θ applied while the vehicle is running, the inner ring ball groove 32 is deformed, and the convex spherical outer peripheral surface of the inner ring 30 is deformed. A raised portion 37 (see FIG. 5) is generated at 31a. At this time, on the inner peripheral surface of the retainer 50 that slides on the convex spherical outer peripheral surface 31a of the inner ring 30, opposed portions 57a and 57b that face the raised portion 37 generated on the convex spherical outer peripheral surface 31a of the inner ring 30 are provided. By providing the recess 55 so as to include, occurrence of poor sliding between the cage 50 and the inner ring 30 is avoided. Thereby, the lifetime of the retainer 50 can be extended.

  As described above, according to the constant velocity joint 10 of the present embodiment, the raised portion 37 generated on the convex spherical outer peripheral surface 31 of the inner ring 30 is transmitted to a predetermined portion of the inner peripheral surface 52 of the cage 50 when torque is transmitted. Since the concave portion 55 for avoiding interference is provided, even when the raised portion 37 occurs on the convex spherical outer peripheral surface 31 of the inner ring 30, the occurrence of poor sliding between the cage 50 and the inner ring 30 is avoided. Thus, the life of the cage 50 can be extended. Furthermore, since the recessed part 55 is provided in the inner peripheral surface 52 of the outer ring | wheel 20 rather than the center of the width direction of the window part 53, the intensity | strength of the pillar part 54 is securable.

  Moreover, since the recessed part 55 in this embodiment is continuously formed in the circumferential direction on the internal peripheral surface 52 of the holder | retainer 50, the cutting process etc. at the time of forming the recessed part 55 can be performed easily and easily. . Further, by forming one concave portion 55 that is continuous in the circumferential direction, it is possible to cope with all of the raised portions 37 that occur at a plurality of locations in the circumferential direction (six locations in the present embodiment). Furthermore, it is possible to cope with the bulge portion 37 that occurs at different locations during the forward rotation and the reverse rotation of the constant velocity joint 10. It is possible to deal with all the swelled portions 37 that are generated at different locations during the forward rotation and the reverse rotation of the constant velocity joint 10.

  Moreover, since the recessed part 55 in this embodiment is formed of the curved surface of the curvature radius R2 different from the curvature radius R1 of the concave spherical surface which forms the inner peripheral surface 52 of the holder | retainer 50, the inner peripheral surface of the holder | retainer 50 is provided. The concave portion 55 can be easily and easily formed at a predetermined location 52.

  Moreover, the constant velocity joint 10 of this embodiment can set the maximum joint operating angle larger because the inner peripheral surface of the opening end of the outer ring 20 is formed in an undercut-free state. Therefore, the sliding failure between the cage 50 and the inner ring 30 that is particularly likely to occur in a ball-type constant velocity joint having a large maximum joint operating angle is more effective by providing the concave portion 55 on the inner peripheral surface 52 of the cage 50. Can be avoided. Thereby, the lifetime improvement of the holder | retainer 50 can be achieved more advantageously.

  The present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the spirit of the present invention.

  For example, in the above-described embodiment, the recess 55 is continuously formed in the circumferential direction on the inner peripheral surface 52 of the cage 50. However, as in the modification shown in FIG. It may be formed intermittently in the circumferential direction on the 50 inner peripheral surfaces 52. The concave portion 56 of the present modified example includes a facing portion 57a facing the raised portion 37 generated on the convex spherical outer peripheral surface 31 of the inner ring 30 during the forward rotation of the constant velocity joint 10, and is spaced apart in the circumferential direction. It is formed in 6 places. The concave portion 56 is formed by a curved surface having a curvature radius R3 different from the curvature radius R1 of the concave spherical surface forming the inner peripheral surface 52 of the cage 50. In this case, the radius of curvature is R1> R3.

  According to the present modification, the concave portion 56 is intermittently formed in the circumferential direction on the inner circumferential surface 52 of the cage 50, and therefore corresponds to the raised portion 37 generated on the convex spherical outer circumferential surface 31 of the inner ring 30. Since it is only necessary to partially form the concave portion 56 only at the predetermined location, the strength reduction of the cage 50 can be minimized. Furthermore, since the sufficient area of the inner peripheral surface 52 of the cage 50 that is in sliding contact with the convex spherical outer peripheral surface 31 of the inner ring 30 can be ensured, it is easy to ensure the operational stability of the constant velocity joint 10.

  In this modification, the concave portion 56 is provided only for the facing portion 57a that faces the raised portion 37 that is generated when the constant velocity joint 10 is rotated forward. However, the concave portion 56 is generated when the constant velocity joint 10 is reversely rotated. You may make it provide also in the opposing site | part 57b facing the swelling part 37. FIG.

  10: Ball type constant velocity joint, 20: Outer ring, 21: Connecting shaft, 22: Concave spherical inner peripheral surface, 23: Outer ring ball groove, 30: Inner ring, 31: Convex spherical outer peripheral surface, 32: Inner ring ball groove, 33: Projection, 35: Inner peripheral spline, 36: Power transmission shaft, 40: Ball, 50: Cage, 51: Outer peripheral surface, 52: Inner peripheral surface, 53: Window portion, 54: Column portion, 55, 56 : Recess, 57a, 57b: facing part, L1: outer ring axis, L2: inner ring axis.

Claims (5)

An outer ring having a plurality of outer ring ball grooves formed in a bottomed cylindrical shape having an opening in one axial direction and extending in the axial direction on the inner peripheral surface;
An inner ring disposed inside the outer ring and having a plurality of inner ring ball grooves extending in the axial direction on the outer peripheral surface;
A plurality of balls that roll on the outer ring ball groove and the inner ring ball groove and transmit torque between the outer ring and the inner ring;
A cage formed in an annular shape and having a plurality of windows that respectively accommodate the balls in the circumferential direction, and disposed between the outer ring and the inner ring;
In the ball-type constant velocity joint with
The retainer is provided with a recess for avoiding interference with a raised portion generated on the outer peripheral surface of the inner ring at the time of torque transmission on the inner peripheral surface on the inner side of the outer ring from the center in the width direction of the window portion. A ball-type constant velocity joint. In claim 1,
The ball-type constant velocity joint, wherein the concave portion is formed continuously in the circumferential direction on the inner peripheral surface of the cage. In claim 1,
The ball-type constant velocity joint, wherein the recess is intermittently formed in an inner peripheral surface of the cage in a circumferential direction. In any one of Claims 1-3,
The inner peripheral surface of the cage is formed by a concave spherical surface centering on an intersection O between the outer ring axis and the inner ring axis, and the concave portion is formed by a curved surface having a curvature radius R2 different from the curvature radius R1 of the concave spherical surface. A ball-type constant velocity joint. In any one of Claims 1-4,
The ball type constant velocity joint, wherein the outer ring ball groove is formed in an undercut-free state when viewed from the outer ring opening side.

Images