Sliding-type constant velocity universal joint and method for manufacturing same

Abstract

A plunging type constant velocity universal joint includes outer and inner joint members that transmit torque therebetween through intermediation of a ball while allowing angular displacement. The outer joint member is configured to receive an internal component comprising the ball and the inner joint member so that the internal component is slidable in an axial direction. The universal joint also includes a stopper mechanism that has an annular groove, and is configured to restrict axial displacement of the internal component by allowing the ball to interfere with a circlip fitted to the annular groove. The annular groove has a conical surface, which is inclined with respect to an axial direction so that the conical surface and an axial tangent line at a contact point between the ball and the circlip form a wedge angle opened from an opening end portion of the outer joint member toward a far side.

Claims

1. A plunging type constant velocity universal joint, comprising: an outer joint member having a cup shape; an inner joint member configured to transmit torque through intermediation of a rolling element between the outer joint member and the inner joint member while allowing angular displacement, the outer joint member being configured to receive an internal component comprising the rolling element and the inner joint member so that the internal component is slidable in an axial direction; and a stopper mechanism, which has an annular groove formed in an inner peripheral surface at an opening end portion of the outer joint member, and is configured to restrict an amount of axial displacement of the internal component by allowing the rolling element to interfere with a stopper ring fitted to the annular groove, wherein the annular groove of the stopper mechanism has a conical surface, which is inclined with respect to the axial direction so that the conical surface and an axial tangent line at a contact point between the rolling element and the stopper ring form a wedge angle opened from the opening end portion of the outer joint member toward a far side, and wherein the stopper ring is sandwiched between the rolling element and the conical surface of the annular groove so that the axial displacement of the rolling element is restricted.

2. The plunging type constant velocity universal joint according to claim 1, wherein the annular groove of the stopper mechanism extends from the conical surface toward the far side of the outer joint member and has a cylindrical surface held in contact with the stopper ring.

3. The plunging type constant velocity universal joint according to claim 1, wherein an axial dimension of the stopper mechanism from a contact point between the stopper ring and a cylindrical surface of the annular groove to a far side end surface of the annular groove is set so as to be larger than a radius of a wire member forming the stopper ring.

4. The plunging type constant velocity universal joint according to claim 1, wherein the internal component is allowed to be removed from and inserted into the outer joint member through elastic deformation of the opening end portion of the outer joint member under a state in which the stopper ring is fitted to the annular groove.

5. The plunging type constant velocity universal joint according to claim 1, wherein the stopper mechanism has a structure in which an amount of interference of the rolling element with the stopper ring is set so as to be smaller than an amount of elastic deformation of the opening end portion of the outer joint member to allow the internal component to be removed from and inserted into the outer joint member.

6. The plunging type constant velocity universal joint according to claim 1, wherein an axial inlet inner diameter of the annular groove of the stopper mechanism is set so as to be larger than an inner diameter of the stopper ring in a state of being fitted to the annular groove and be smaller than an inner diameter at a contact point between the stopper ring and the annular groove.

7. The plunging type constant velocity universal joint according to claim 1, wherein an axial inlet inner diameter of the annular groove of the stopper mechanism is set so as to be larger than an inner diameter of the stopper ring in a state of being fitted to the annular groove throughout an entire periphery of the opening end portion of the outer joint member.

8. A method of manufacturing a plunging type constant velocity universal joint, the plunging type constant velocity universal joint comprising: an outer joint member having a cup shape; and an inner joint member configured to transmit torque through intermediation of a rolling element between the outer joint member and the inner joint member while allowing angular displacement, the outer joint member being configured to receive an internal component comprising the rolling element and the inner joint member so that the internal component is slidable in an axial direction, wherein an annular groove which receives a stopper ring configured to allow the rolling element to interfere therewith is formed in an inner peripheral surface at an opening end portion of the outer joint member, wherein the annular groove has a conical surface, which is inclined with respect to the axial direction so that the conical surface and an axial tangent line at a contact point between the rolling element and the stopper ring form a wedge angle opened from the opening end portion of the outer joint member toward a far side, and wherein the stopper ring is sandwiched between the rolling element and the conical surface of the annular groove so that the axial displacement of the rolling element is restricted, the method comprising forming the conical surface by only processing with a turning chip.

9. The method of manufacturing a plunging type constant velocity universal joint according to claim 8, wherein the annular groove has a cylindrical surface, which extends from the conical surface toward the far side of the outer joint member and is held in contact with the stopper ring, and the forming comprises forming the cylindrical surface by only the processing with the turning chip.

Description

BRIEF DESCRIPTION OF DRAWINGS

(1) FIG. 1 is a sectional view for illustrating an overall configuration of a double-offset constant velocity universal joint according to an embodiment of the present invention.

(2) FIG. 2 is a sectional view for illustrating a state in which an internal component of FIG. 1 interferes with a stopper mechanism due to axial displacement.

(3) FIG. 3 is a main-part enlarged sectional view of FIG. 2.

(4) FIG. 4 is an enlarged sectional view of the portion A of FIG. 3.

(5) FIG. 5 is a sectional view for illustrating a state in which a stopper ring and the internal component are assembled to an outer joint member of FIG. 1.

(6) FIG. 6 is a side view of the outer joint member of FIG. 1 as seen from an opening side of the outer joint member.

(7) FIG. 7A is an illustration of an annular groove formed in the outer joint member of FIG. 1, and is a side view of the outer joint member as seen from the opening side of the outer joint member.

(8) FIG. 7B is an illustration of the annular groove formed in the outer joint member of FIG. 1, and is a sectional view taken along the line P-P of FIG. 7A.

(9) FIG. 8 is an enlarged sectional view of the portion B of FIG. 7B.

(10) FIG. 9A is an illustration of another example of the annular groove formed in the outer joint member, and is a side view of the outer joint member as seen from the opening side of the outer joint member.

(11) FIG. 9B is an illustration of another example of the annular groove formed in the outer joint member, and is a sectional view taken along the line Q-Q of FIG. 9A.

(12) FIG. 10 is an enlarged sectional view of the portion C of FIG. 9B.

(13) FIG. 11 is a main-part enlarged sectional view for illustrating a state in which an internal component interferes with a stopper mechanism due to axial displacement in another embodiment of the present invention.

(14) FIG. 12 is an enlarged sectional view of the portion G of FIG. 11.

(15) FIG. 13A is an illustration of an annular groove formed in an outer joint member of FIG. 11, and is a side view of the outer joint member as seen from an opening side of the outer joint member.

(16) FIG. 13B is an illustration of the annular groove formed in the outer joint member, and is a sectional view taken along the line S-S of FIG. 13A.

(17) FIG. 14 is an enlarged sectional view of the portion H of FIG. 13B.

(18) FIG. 15A is an illustration of another example of the annular groove formed in the outer joint member, and is a side view of the outer joint member as seen from the opening side of the outer joint member.

(19) FIG. 15B is an illustration of another example of the annular groove formed in the outer joint member, and is a sectional view taken along the line T-T of FIG. 15A.

(20) FIG. 16 is an enlarged sectional view of the portion I of FIG. 15B.

(21) FIG. 17 is a sectional view for illustrating an overall configuration of a cross-groove constant velocity joint according to another embodiment of the present invention.

(22) FIG. 18 is a sectional view for illustrating a state in which an internal component of FIG. 17 interferes with a stopper mechanism due to axial displacement.

(23) FIG. 19 is a sectional view for illustrating an overall configuration of a related-art plunging type constant velocity universal joint.

(24) FIG. 20 is a sectional view for illustrating a state in which an internal component of FIG. 19 interferes with a stopper mechanism due to axial displacement.

(25) FIG. 21 is a main-part enlarged sectional view of FIG. 20.

(26) FIG. 22 is an enlarged sectional view of the portion D of FIG. 21.

(27) FIG. 23 is a sectional view for illustrating a state in which the internal component and a stopper ring are assembled to an outer joint member of FIG. 19.

(28) FIG. 24 is a sectional view for illustrating a state before an annular groove is formed in the outer joint member of FIG. 19.

(29) FIG. 25 is an enlarged sectional view of the portion E of FIG. 24.

(30) FIG. 26A is an illustration of the annular groove formed in the outer joint member of FIG. 19, and is a side view of the outer joint member as seen from an opening side of the outer joint member.

(31) FIG. 26B is an illustration of the annular groove formed in the outer joint member of FIG. 19, and is a sectional view taken along the line R-R of FIG. 26A.

(32) FIG. 27 is an enlarged sectional view of the portion F of FIG. 26B.

DESCRIPTION OF EMBODIMENTS

(33) Now, a plunging type constant velocity universal joint according to an embodiment of the present invention is described in detail with reference to the drawings.

(34) In the following embodiment, description is made of an example case in which the present invention is applied to a double-offset constant velocity universal joint (DOJ) or a cross-groove constant velocity joint (LJ) in which balls are used as rolling elements configured to transmit rotational torque. The present invention is applicable also to other plunging type constant velocity universal joints such as a tripod type constant velocity universal joint (TJ) in which rollers are used as the rolling elements.

(35) It is required that a drive shaft configured to transmit power from an engine to a wheel of an automobile be adaptable to angular displacement and axial displacement caused by changes in relative positional relationship between the engine and the wheel. Therefore, the drive shaft generally has the following structure. A plunging type constant velocity universal joint configured to allow both the axial displacement and the angular displacement is provided on an engine side (inboard side), and a fixed type constant velocity universal joint configured to allow only the angular displacement is provided on a wheel side (outboard side). The constant velocity universal joints are coupled to each other by a shaft.

(36) FIG. 1 is an illustration of an overall configuration of a double-offset constant velocity universal joint (hereinafter simply referred to as “constant velocity universal joint”), which is one of the plunging type constant velocity universal joints, assembled to the drive shaft mentioned above.

(37) The constant velocity universal joint according to the embodiment comprises an outer joint member 11 having a cup shape, an inner joint member 12, a plurality of balls 13 being rolling elements, and a cage 14. An internal component 15 comprising the inner joint member 12, the balls 13, and the cage 14 is received in the outer joint member 11 so that the internal component 15 can be axially displaced. One shaft end portion of a shaft 17 is coupled to a shaft hole 16 of the inner joint member 12 by spline-fitting. An inner joint member of a fixed type constant velocity universal joint is coupled to another shaft end portion (not shown) of the shaft 17 extending from the inner joint member 12, thereby forming the drive shaft.

(38) The outer joint member 11 has linear track grooves 18 extending in an axial direction, which are formed at equal intervals at a plurality of positions in a circumferential direction in an inner peripheral surface 19. The inner joint member 12 has linear track grooves 20 extending in the axial direction, which are formed at equal intervals at a plurality of positions in a circumferential direction in the outer peripheral surface 21 and are paired with the track grooves 18 of the outer joint member 11. The balls 13 are arranged between the track grooves 18 of the outer joint member 11 and the track grooves 20 of the inner joint member 12 to transmit rotational torque. The cage 14 is interposed between the inner peripheral surface 19 of the outer joint member 11 and the outer peripheral surface 21 of the inner joint member 12 to retain the balls 13.

(39) In this constant velocity universal joint, when an operating angle is formed by the shaft 17 between the outer joint member 11 and the inner joint member 12, the balls 13 retained by the cage 14 are, at any operating angles, always maintained within a bisectional plane of the operating angle, thereby keeping constant velocity between the outer joint member 11 and the inner joint member 12. Moreover, the balls 13 retained by the cage 14 roll on the track grooves 18 of the outer joint member 11 so that the internal component 15 is slidable in the axial direction with respect to the outer joint member 11.

(40) Although illustration is omitted, in the constant velocity universal joint, in order to prevent leakage of lubricant such as grease sealed inside the joint and to prevent entry of a foreign substance from the outside of the joint, an extendable and contractable bellows boot made of resin or rubber is provided between the outer joint member 11 and the shaft 17 in a tensioned state to close an opening end portion 22 of the outer joint member 11.

(41) When the drive shaft with the constant velocity universal joints, which have the configuration described above, assembled thereto is to be assembled to a vehicle body, in some cases, the own weight of the drive shaft comprising the fixed type constant velocity universal joint and the shaft is applied as a large load to the constant velocity universal joint in a slide-out direction. Therefore, it is required to prevent slide over in which the internal component 15 flies out from the opening end portion 22 of the outer joint member 11.

(42) Therefore, as illustrated in FIG. 1, the constant velocity universal joint according to the embodiment employs a stopper mechanism 25 in which a recessed annular groove 23 is formed in the track grooves 18 and the inner peripheral surface 19 at the opening end portion 22 of the outer joint member 11, and a circlip 24 being a stopper ring is fitted to the annular groove 23.

(43) In this stopper mechanism 25, when the drive shaft is to be assembled to the vehicle body, in a case in which a large load is applied to the internal component 15 in the slide-out direction, as illustrated in FIG. 2, the balls 13 of the internal component 15 interfere with the circlip 24 so that the amount of axial displacement of the balls 13 is restricted. With this, the slide over in which the internal component 15 flies out from the opening end portion 22 of the outer joint member 11 is prevented.

(44) In particular, when the drive shaft with the constant velocity universal joint assembled thereto is to be assembled to the vehicle body, even in a case in which the own weight of the drive shaft comprising the fixed type constant velocity universal joint and the shaft is applied as a large load to the constant velocity universal joint in the slide-out direction, the balls 13 of the internal component 15 interfere with the circlip 24, thereby being capable of reliably preventing the slide over of the internal component 15. As a result, reliability in assembly of the drive shaft is improved.

(45) The stopper mechanism 25 employed in the constant velocity universal joint according to the embodiment has the following specific configuration.

(46) As illustrated in FIG. 1 and FIG. 2, the stopper mechanism 25 in this embodiment comprises the annular groove 23 and the circlip 24. The annular groove 23 is formed in the track grooves 18 and the inner peripheral surface 19 at the opening end portion 22 of the outer joint member 11, in particular, at a part close to an opening end surface 26. The circlip 24 is fitted to the annular groove 23. FIG. 3 and FIG. 4 are each an illustration of a state in which the ball 13 is brought into contact and interferes with the circlip 24 due to axial displacement of the internal component 15.

(47) As illustrated in FIG. 3 and FIG. 4, the annular groove 23 of the stopper mechanism 25 has a conical surface 27. The conical surface 27 is inclined with respect to the axial direction so that the conical surface 27 and an axial tangent line L.sub.1 at a contact point α between the ball 13 and the circlip 24 form a wedge angle θ opened from the opening end portion 22 of the outer joint member 11 toward the far side. The conical surface 27 has a positional relationship of matching with an axial tangent line L.sub.2 at a contact point β with respect to the circlip 24.

(48) The annular groove 23 has the conical surface 27 described above and an end surface 28 which extends in a direction orthogonal to the axial direction from the track groove 18 of the outer joint member 11. The circlip 24 is retained by the annular groove 23 in a state of being held in contact with the conical surface 27 and the end surface 28 and sandwiched between the conical surface 27 and the end surface 28 in the annular groove 23.

(49) It is preferred that the wedge angle θ be set within a range of from 5° to 25°. When the wedge angle θ is smaller than 5°, a retaining force is not sufficient. As a result, it is difficult to reliably prevent the slide over. Meanwhile, when the wedge angle θ is larger than 25°, a direction of a load applied from the circlip 24 to the annular groove 23 of the outer joint member 11 becomes closer to a slide direction. As a result, it becomes disadvantageous in terms of the groove strength, and it is difficult to reduce the weight.

(50) In the stopper mechanism 25, an axial inlet inner diameter D.sub.1 of the annular groove 23 is set so as to be larger than an inner diameter D.sub.2 of the circlip 24 in the state of being fitted to the annular groove 23 and be smaller than an inner diameter D.sub.3 at the contact point β between the circlip 24 and the annular groove 23. With this, the circlip 24 can be reliably retained in the annular groove 23.

(51) In the stopper mechanism 25 having the configuration described above, in a case in which a large load is applied to the internal component 15 in the slide-out direction, the balls 13 of the internal component 15 are brought into contact and interfere with the circlip 24, thereby restricting the amount of axial displacement of the balls 13 (see FIG. 3 and FIG. 4).

(52) In this case, the axial tangent line L.sub.1 at the contact point α between the ball 13 and the circlip 24 and the axial tangent line L.sub.2 at the contact point β between the circlip 24 and the conical surface 27 of the annular groove 23 form the wedge angle θ opened from the opening end portion 22 of the outer joint member 11 toward the far side. With this, through the interference of the balls 13 with the circlip 24 in the state of being retained in the annular groove 23, the amount of axial displacement of the internal component 15 can be reliably restricted.

(53) Moreover, with the annular groove 23 having the conical surface 27 forming the wedge angle θ as mentioned above, the slide end positions at which the balls 13 of the internal component 15 are brought into contact and interfere with the circlip 24 are each located at a part close to the opening end portion 22 of the outer joint member 11.

(54) That is, as illustrated in FIG. 3, an axial dimension H.sub.1 between a center O.sub.1 of the ball 13 and the opening end surface 26 of the outer joint member 11 is smaller than that given in the case of the related-art constant velocity universal joint (see FIG. 21) (H.sub.1<H.sub.0). With this, the axial dimension of the outer joint member 11 can be reduced as compared to the related art, and reduction of a material and the weight of the outer joint member 11 can be achieved, thereby being capable of easily achieving reduction in weight and size of the constant velocity universal joint.

(55) As described above, with the wedge angle θ of the conical surface 27 of the annular groove 23, a force of removal which acts from the circlip 24 on the conical surface 27 of the annular groove 23 becomes larger in a direction oriented radially outward than in the axial direction of the outer joint member 11 and acts from a center O.sub.2 of the circlip 24 toward the contact point β with the conical surface 27. Therefore, even when the annular groove 23 is formed at a part close to the opening end portion 22 of the outer joint member 11 as mentioned above, a sufficient strength of the annular groove 23 can be secured.

(56) As a result, an axial dimension E.sub.1 from the contact point β between the circlip 24 and the conical surface 27 to the opening end surface 26 of the outer joint member 11 can be set smaller than that given in the case of the related-art constant velocity universal joint (see FIG. 22) (E.sub.1<E.sub.0). Also on this point, the axial dimension of the outer joint member 11 can be reduced, and reduction of the material and the weight of the outer joint member 11 can be achieved, thereby contributing to the reduction in weight and size of the constant velocity universal joint.

(57) Further, with the annular groove 23 having the conical surface 27 forming the wedge angle θ as mentioned above, as illustrated in FIG. 4, the annular groove 23 which receives the circlip 24 fitted thereto can be formed so as to be shallower than that of an annular groove in the related art (see FIG. 22) (D.sub.4<D.sub.0). With this, when the circlip 24 is to be assembled to the annular groove 23, the amount of radial contraction of the circlip 24 can be set smaller than that of the related art, thereby being capable of improving ease of operation of assembly and removal of the circlip 24. Moreover, a difference F.sub.1 between the inner diameter D.sub.2 of the circlip 24 and a circumscribed circle diameter D.sub.5 of the balls 13 is smaller than that given in the case of the related-art constant velocity universal joint (see FIG. 22) (F.sub.1<F.sub.0).

(58) As a result, the internal component 15 can be removed from and inserted into the outer joint member 11 through elastic deformation of the opening end portion 22 of the outer joint member 11 under the state in which the circlip 24 is fitted to the annular groove 23. That is, the amount of elastic deformation of the outer joint member 11 is larger on the opening end portion side than on the far side, and hence the opening end portion 22 of the outer joint member 11 can be easily elastically deformed. Moreover, the annular groove 23 which receives the circlip 24 fitted thereto is formed at a part close to the opening end surface 26.

(59) As described above, through setting of the amount of interference of the balls 13 with the circlip 24, that is, the difference F.sub.1 between the inner diameter D.sub.2 of the circlip 24 and the circumscribed circle diameter D.sub.5 of the balls 13 to be smaller than the amount of elastic deformation of the opening end portion 22 of the outer joint member 11, the internal component 15 can be removed from and inserted into the outer joint member 11.

(60) Thus, as illustrated in FIG. 5, first, the circlip 24 is assembled to the outer joint member 11. After that, the internal component 15 is assembled to the outer joint member 11. Through radial expansion of the opening end portion 22 of the outer joint member 11 within a region of elastic deformation, the balls 13 of the internal component 15 can get over the circlip 24 with a minimum required force of removal. As a result, the internal component 15 can be received in the outer joint member 11.

(61) With this, after the assembly, removal of the internal component 15 from the outer joint member 11 can also be performed under the state in which the circlip 24 is mounted to the annular groove 23. In such a manner, the assembling step of the circlip 24 and the internal component 15 can be easily simplified, and the simplification of the assembling step enables automation of the assembling step.

(62) In the stopper mechanism 25 in this embodiment, as illustrated in FIG. 3 and FIG. 4, the axial inlet inner diameter D.sub.1 of the annular groove 23 is set so as to be larger than the inner diameter D.sub.2 of the circlip 24 in the state of being inserted into the annular groove 23 throughout the entire periphery of the opening end portion 22 of the outer joint member 11. In FIG. 6, only the circlip 24 fitted to the annular groove 23 of the outer joint member 11 is illustrated, and illustration of the internal component 15 is omitted.

(63) With this, as illustrated in FIG. 6, the entire periphery of the circlip 24 in the state of being fitted to the annular groove 23 can be visually checked from the opening side of the outer joint member 11. As a result, the state of assembly of the circlip 24 to the annular groove 23 can be checked. Moreover, the amount of radial contraction of the circlip 24 is small, and hence the circlip 24 can be easily removed from the annular groove 23.

(64) The annular groove 23 of the stopper mechanism 25 described in the embodiment above can be formed by the following procedure. That is, as illustrated in FIG. 7A, FIG. 7B, and FIG. 8, the annular groove 23 can be achieved through processing on the opening end portion 22 of the outer joint member 11 with a turning chip 29 (see the arrow in FIG. 8).

(65) As described above, the annular groove 23 having the conical surface 27 forming the wedge angle θ as mentioned above is formed by only the processing with the turning chip 29. Thus, the annular groove 23 can be formed by only one step of the processing with the turning chip 29, thereby being capable of reducing the number of processing steps as compared to the related art.

(66) In the processing with the turning chip 29 illustrated in FIG. 7A, FIG. 7B, and FIG. 8, the opening end portion 22 of the outer joint member 11 is subjected to turning with the turning chip 29 to the inner peripheral surface 19 of the outer joint member 11 (see the arrow in FIG. 8). However, as illustrated in FIG. 9A, FIG. 9B, and FIG. 10, the opening end portion 22 of the outer joint member 11 may be subjected to the turning with the turning chip 29 only at the opening end surface 26 rather than turning to the inner peripheral surface 19 of the outer joint member 11 (see the arrow in FIG. 10).

(67) With regard to the stopper mechanism 25 in the embodiment described above (see FIG. 3 and FIG. 4), illustration is given of the example case in which the annular groove 23 is formed of only the conical surface 27. However, a stopper mechanism 55 as illustrated in FIG. 11 and FIG. 12 may be employed. Among components illustrated in FIG. 11 and FIG. 12, components which are the same as or correspond to the components illustrated in FIG. 3 and FIG. 4 are denoted by the same reference symbols, and redundant description thereof is omitted.

(68) An annular groove 53 of the stopper mechanism 55 illustrated in FIG. 11 and FIG. 12 comprises the conical surface 27 described above and a cylindrical surface 50. The cylindrical surface 50 extends from the conical surface 27 toward the far side of the outer joint member 11, and is held in contact with the circlip 24. The circlip 24 is retained by the annular groove 53 in a state of being held in contact with the conical surface 27 and the cylindrical surface 50 in the annular groove 53.

(69) The annular groove 53 in this embodiment has the cylindrical surface 50 in addition to the conical surface 27. Therefore, a groove bottom inner diameter of the annular groove 53 can be set smaller than that given in the case in which only the conical surface 27 is formed (see FIG. 4). That is, a thickness of the outer joint member 11 at the opening end portion 22 can be set large. Therefore, a sufficient strength of the annular groove 53 in the stopper mechanism 55 can be secured, and the removal amount in the processing of the annular groove 53 can be reduced.

(70) Moreover, in the stopper mechanism 55 in this embodiment, an axial dimension G from a contact point γ between the circlip 24 and the cylindrical surface 50 toward the far side end surface 28 of the annular groove 53 is set so as to be larger than a radius R of a wire member forming the circlip 24. With this, the circlip 24 which interferes with the balls 13 can be reliably held in contact with the cylindrical surface 50 of the annular groove 53.

(71) Configurations other than the cylindrical surface 50 of the annular groove 53 of the stopper mechanism 55 in this embodiment as well as actions and effects thereof are the same as those of the stopper mechanism 25 in the embodiment illustrated in FIG. 3 and FIG. 4, and hence redundant description is omitted.

(72) The annular groove 53 of the stopper mechanism 55 described in the embodiment above can be formed by the following procedure. That is, as illustrated in FIG. 13A, FIG. 13B, and FIG. 14, the annular groove 53 can be achieved through processing on the opening end portion 22 of the outer joint member 11 with the turning chip 29 (see the arrow in FIG. 14).

(73) As described above, the annular groove 53 having the conical surface 27 and the cylindrical surface 50 forming the wedge angle θ as mentioned above is formed by only the processing with the turning chip 29. Thus, the annular groove 53 can be formed by only one step of the processing with the turning chip 29, thereby being capable of reducing the number of processing steps as compared to the related art.

(74) In the processing with the turning chip 29 illustrated in FIG. 13A, FIG. 13B, and FIG. 14, the opening end portion 22 of the outer joint member 11 is subjected to turning with the turning chip 29 to the inner peripheral surface 19 of the outer joint member 11 to form the annular groove 53 (see the arrow in FIG. 14). However, as illustrated in FIG. 15A, FIG. 15B, and FIG. 16, the opening end portion 22 of the outer joint member 11 may be subjected to the turning with the turning chip 29 only at the opening end surface 26 rather than turning to the inner peripheral surface 19 of the outer joint member 11 to form the annular groove 53 (see the arrow in FIG. 16).

(75) In the embodiment above (see FIG. 1 and FIG. 2), illustration is given of the example case in which the present invention is applied to the double-offset constant velocity universal joint being one of ball types. However, as in the embodiment illustrated in FIG. 17 and FIG. 18, the present invention is applicable also to a cross-groove constant velocity joint of another ball type.

(76) As illustrated in FIG. 17, this constant velocity universal joint comprises an outer joint member 31 having a cup shape, an inner joint member 32, a plurality of balls 33 being rolling elements, and a cage 34. An internal component 35 comprising the inner joint member 32, the balls 33, and the cage 34 is received in the outer joint member 31 so that the internal component 35 can be axially displaced. A shaft end portion of a shaft 37 is coupled to a shaft hole 36 of the inner joint member 32 by spline-fitting.

(77) The outer joint member 31 has linear track grooves 38 extending in the axial direction, which are formed at equal intervals at a plurality of positions in a circumferential direction in the inner peripheral surface 39 under a state in which the linear track grooves 38 are inclined alternately in reverse directions with respect to the axis line. The inner joint member 32 has linear track grooves 40 extending in the axial direction, which are formed at equal intervals at a plurality of positions in a circumferential direction in the outer peripheral surface 41 under a state in which the track grooves 40 are inclined in opposite directions with respect to the track grooves 38 of the outer joint member 31.

(78) The balls 33 are incorporated in an intersecting portion between the track grooves 38 of the outer joint member 31 and the track grooves 40 of the inner joint member 32 to transmit rotational torque. The cage 34 is interposed between the inner peripheral surface 39 of the outer joint member 31 and the outer peripheral surface 41 of the inner joint member 32 to retain the balls 33.

(79) Also in the constant velocity universal joint according to this embodiment, as illustrated in FIG. 17, the stopper mechanism 45 comprising the recessed annular groove 43, which is formed in the track grooves 38 and the inner peripheral surface 39 at the opening end portion 42 of the outer joint member 31, and the circlip 44 fitted to the annular groove 43 is applicable.

(80) Also in this stopper mechanism 45, in a case in which a large load is applied to the internal component 35 in the slide-out direction, as illustrated in FIG. 18, the balls 33 of the internal component 35 interfere with the circlip 44 so that the amount of axial displacement of the balls 33 is restricted. With this, the slide over in which the internal component 35 flies out from the opening end portion 42 of the outer joint member 31 is prevented.

(81) The stopper mechanism 45 has the same configuration as well as actions and effects which are the same as those of the stopper mechanisms 25 and 55 in the constant velocity universal joint illustrated in FIG. 1 and FIG. 2, and hence redundant description thereof is omitted.

(82) The present invention is not limited to the above-mentioned embodiments. As a matter of course, the present invention may be carried out in various modes without departing from the spirit of the present invention. The scope of the present invention is defined in claims, and encompasses equivalents described in claims and all changes within the scope of claims.