JP2014009781A - Power transmission shaft and method of manufacturing the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a power transmission shaft capable of reducing backlash between the shaft and an inner race, and provide a method of manufacturing the same.SOLUTION: A power transmission shaft 1 includes: a snap ring 71 that is fitted at an end portion of a shaft 60 and retains an inner race 30 press-fitted to the shaft 60; and a restriction member 72 that is arranged on an outer peripheral surface of the shaft 60 and abuts on an end face of the inner race 30 on the shaft central part side to restrict movement of the inner race 30. After the inner race 30 is axially moved with respect to the shaft 60 to a position where the movement of the inner race 30 toward the end portion of the shaft 60 is restricted by the snap ring 71 fitted at the end portion of the shaft 60, an axial load is applied to the restriction member 72 from the shaft central part side toward the end portion of the shaft to which the inner race 30 is press-fitted. The restriction member 72 thereby abuts on the end face of the inner race 30 on the shaft central part side to restrict the axial movement of the inner race 30.

Description

  The present invention relates to a power transmission shaft and a manufacturing method thereof.

  As the constant velocity joint of the drive shaft, for example, a ball type is known. Here, the inner ring in the ball mold is fixed to the shaft. As a fixing method, the shaft is press-fitted into the inner ring, and the outer spline of the shaft and the inner spline of the inner ring are fitted together. The inner ring is prevented from coming off by a retaining ring mounted in a retaining ring groove formed at the tip of the shaft.

  In such a structure in which the inner ring is fixed to the shaft, a gap is provided between the retaining ring groove and the retaining ring or between the retaining ring and the inner ring in order to securely attach the retaining ring to the retaining ring groove of the shaft. It has been. For this reason, when the spline wears due to aging of the constant velocity joint, axial play due to the gap may occur. If there is a backlash between the shaft and the inner ring, an abnormal noise or the like may occur. Therefore, for example, Patent Document 1 discloses a constant velocity joint having a regulating member arranged on the opening side of the outer ring. According to this, it is supposed that the regulating member can regulate the displacement of the shaft toward the outer ring opening side with respect to the inner ring.

JP 2011-80556 A

  The constant velocity joint of Patent Document 1 is configured such that an elastically deformable ring-shaped regulating member is fitted into the shaft in advance before the shaft is press-fitted into the inner ring. Therefore, when the shaft is assembled to the inner ring, it is necessary to press-fit against the elastic force of the restricting member, and a large press-fitting load is required as compared with a configuration without the restricting member. Therefore, in order to reduce the backlash in the axial direction, it is preferable to set the elastic force of the restricting member large. However, if the elastic force is increased, there is a concern that the press-fit load increases and the assembling property is lowered.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a constant velocity joint capable of suppressing the occurrence of axial play of the inner ring with respect to the shaft and a method for manufacturing the same.

  (Claim 1) A power transmission shaft according to the present invention is formed in a cylindrical shape having an opening in at least one axial direction, and is disposed inside an outer ring having a plurality of outer ring ball grooves formed on an inner peripheral surface. An inner ring having a plurality of inner ring ball grooves formed on the outer peripheral surface, and a plurality of balls that roll the respective outer ring ball grooves and the inner ring ball grooves and transmit torque between the outer ring and the inner ring, A constant velocity joint comprising: a cage formed in an annular shape, and disposed between the outer ring and the inner ring and having a plurality of windows formed therein to accommodate the balls in the circumferential direction; and A power transmission shaft having a shaft coupled to the inner ring, a retaining ring attached to a tip of the shaft and preventing the inner ring press-fitted into the shaft, and an outer periphery of the shaft A regulating member that regulates axial movement of the inner ring in contact with the end surface on the shaft center portion side of the end surface on the shaft tip portion side and the end surface on the shaft center portion side of the inner ring, The inner ring is moved in the axial direction with respect to the shaft to a position regulated by the retaining ring attached to the distal end of the shaft. An axial load is applied to the restricting member from the side toward the shaft tip portion into which the inner ring is press-fitted, thereby bringing the restricting member into contact with the end surface of the inner ring on the shaft central portion side so that the shaft of the inner ring Regulate direction movement.

(Claim 2) Further, the restricting member is formed in a cylindrical shape that is press-fitted to the outer peripheral side of the shaft, and is moved to an axial position of the shaft that contacts the inner ring by an axial load. Good.
(Claim 3) Further, the restricting member is formed in a bowl shape integrally formed so as to protrude in the radial direction from the outer peripheral surface of the shaft, and an outer peripheral edge is in contact with the inner ring by an axial load. It may be plastically deformed.
(Aspect 4) An axial load applied to the restricting member may be set smaller than a load when the inner ring is press-fitted into the shaft.

  (Claim 5) A method for manufacturing a power transmission shaft according to the present invention is formed in a cylindrical shape having an opening at least in one axial direction, and an outer ring having a plurality of outer ring ball grooves formed on an inner peripheral surface; An inner ring that is arranged on the inner side and has a plurality of inner ring ball grooves formed on the outer peripheral surface, and a plurality of rollers that roll the outer ring ball groove and the inner ring ball groove, respectively, and transmit torque between the outer ring and the inner ring. A constant velocity joint comprising: a ball; and a cage formed in an annular shape and disposed between the outer ring and the inner ring, and formed with a plurality of windows that respectively accommodate the balls in the circumferential direction; A power transmission shaft having a shaft coupled to the inner ring of a speed joint, wherein the power transmission shaft is attached to a distal end portion of the shaft and press-fitted into the shaft. A retaining ring for retaining the outer ring, disposed on the outer peripheral surface of the shaft, and in contact with an end surface on the shaft central portion side of the end surface on the shaft central portion side and the end surface on the shaft central portion side of the inner ring, A regulating member that regulates axial movement of the inner ring, and the method of manufacturing the power transmission shaft includes attaching a retaining ring to a retaining ring groove at a tip of the shaft, press-fitting the inner ring into the shaft, The press-fitting and slip-off preventing process for preventing the shaft and the inner ring from coming off with the retaining ring, and the movement toward the shaft tip end side to the position regulated by the retaining ring attached to the tip end of the shaft, An axial backlashing process for moving the inner ring in the axial direction with respect to the shaft, and an axial direction on the restriction member from the shaft central part side toward the shaft tip part side where the inner ring is press-fitted By applying a weight, and a regulating step of regulating the axial movement of the inner ring of the regulating member in contact with the shaft center side end surface of the inner ring.

  (Claim 1) According to the present invention, the restricting member is brought into contact with the inner ring that is prevented from coming off by the retaining ring to restrict the axial movement of the inner ring. In this way, the inner ring is preliminarily filled with a clearance provided for attaching the retaining ring, and the axial movement from the press-fitted side of the inner ring at the tip of the shaft toward the center of the shaft is regulated by the regulating member. The Therefore, it is possible to suppress the backlash in the axial direction of the inner ring with respect to the shaft. Further, when the restricting member is applied with an axial load and comes into contact with the inner ring, it is moved in advance to the axial position of the shaft where the inner ring contacts the retaining ring and is prevented from coming off. That is, when the constant velocity joint is assembled, the inner ring is press-fitted and prevented from coming off and the movement of the regulating member is a separate process, so that it can be assembled with a load necessary for each process.

  (Claim 2) According to the present invention, the cylindrical restricting member is press-fitted into the outer peripheral side of the shaft to restrict the axial movement of the inner ring that is prevented from coming off by the retaining ring. Thereby, in addition to the press-fit load between the inner rings, the inner ring is restricted from moving in the axial direction by the press-fit load between the regulating member and the shaft. Therefore, it is possible to more reliably suppress the occurrence of backlash between the shaft and the inner ring.

  (Claim 3) According to the present invention, the outer peripheral edge of the flange-shaped restricting member is plastically deformed so as to come into contact with the inner ring, and the axial movement of the inner ring that is prevented from coming off by the retaining ring is restricted. Thereby, in addition to the press-fit load between the inner ring and the shaft, the inner ring is brought into contact with the outer peripheral edge of the restricting member and the axial movement is restricted. Therefore, it is possible to more reliably suppress the occurrence of backlash between the shaft and the inner ring.

  (Claim 4) According to the present invention, when an axial load is applied to the regulating member from the shaft central portion side to the press-fitted side of the inner ring on the shaft tip portion side, the other member is interposed via the regulating member. The load applied to the inner ring can be made smaller than the load when the inner ring is press-fitted into the shaft. Thereby, it can prevent that an excessive load is applied to another member.

(Claim 5) According to the present invention, the restricting member is brought into contact with the inner ring that is prevented from coming off by the retaining ring, and the restricting step for restricting the axial movement of the inner ring is provided. As described above, the inner ring is preliminarily filled with a clearance provided for mounting the retaining ring, and the axial movement of the outer ring toward the opening side of the outer ring is restricted by the restriction member. Therefore, generation | occurrence | production of the axial play of the inner ring | wheel with respect to a shaft can be suppressed. In addition, before the regulating step of applying an axial load to the regulating member and bringing it into contact with the inner ring, an axial backlashing process in which the inner ring is moved in advance to the axial position of the shaft that comes into contact with the retaining ring and is prevented from coming off is performed. Is going. That is, when the constant velocity joint is assembled, the inner ring press-fitting and the movement of the restricting member are separate processes, and therefore can be assembled with a load necessary for each process.
Further, other characteristic portions in the power transmission shaft can be similarly applied to the manufacturing method of the present invention. In this case, the same effect is obtained.

It is an axial sectional view of a drive shaft in an embodiment. FIG. 2 is an enlarged view showing a state where an inner ring is prevented from being detached by a retaining ring in FIG. 1. It is an enlarged view which shows the control state of the axial direction movement of the inner ring | wheel by the ring member in FIG. It is an axial sectional view showing the assembled state of the drive shaft. It is an enlarged view which shows the A section of FIG. 4 in a press injection process. It is an enlarged view which shows the B section of FIG. 4 in a press injection process. It is an enlarged view which shows the A section of FIG. 4 in an axial backlash filling process. It is an enlarged view which shows the B section of FIG. 4 in an axial backlash filling process. It is an enlarged view which shows the A section of FIG. 4 in a control process. It is an enlarged view which shows the control state of the inner ring | wheel by the collar part in the deformation | transformation aspect of embodiment.

<Embodiment>
(Overall configuration of drive shaft)
The structure of the drive shaft 1 (corresponding to the “power transmission shaft” of the present invention) of the present embodiment will be described with reference to FIGS. FIG. 1 is an axial cross-sectional view of a ball type constant velocity joint 10 (hereinafter simply referred to as “constant velocity joint”) according to the present embodiment in a state where a joint operating angle is set to a predetermined angle θ. The joint operating angle is a relative angle between the outer ring axis L1 and the inner ring axis L2.

  As shown in FIG. 1, the constant velocity joint 10 of the present embodiment is a fixed ball type constant velocity joint (also referred to as “Zepper type constant velocity joint”). The joint center is an intersection O between the outer ring axis L1 and the inner ring axis L2, and the constant velocity joint 10 is a fixed type that does not allow axial displacement of the joint center. The constant velocity joint 10 is preferably used as an outboard joint in a front or rear drive shaft of an automobile. In particular, in this embodiment, an undercut free type (UF) fixed ball type constant velocity joint will be described as an example.

  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 (corresponding to the “inner ring” of the present invention), a plurality of balls 40, and a cage. 50, a retaining ring 71, and a ring member 72 (corresponding to a “regulating member” of the present invention).

  The outer ring 20 is formed in a cup shape (bottomed tubular 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 portion (left side in FIG. 1) of the outer ring 20 so as to extend in the direction of the outer ring axis L1. The connecting shaft 21 is connected to another power transmission shaft. Further, the inner peripheral surface 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 having an intersection O between the outer ring axis L1 and the inner ring axis L2 as a center of curvature, and is cut in the direction of the outer ring axis L1. When viewed in a cross section, it is formed in a concave arc shape.

  Further, a plurality of outer ring ball grooves 23 having a substantially concave arc-shaped cross section in the direction orthogonal to the outer ring axis L1 are formed on the inner peripheral surface of the outer ring 20 so as to extend substantially in the direction of the outer ring axis L1. These outer ring ball grooves 23 (six in this embodiment) are formed at equal intervals in the circumferential direction (60-degree intervals in this embodiment) when viewed in a cross section cut in the radial direction.

  The inner ring 30 is a member formed in an annular shape and 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 having an intersection O between the outer ring axis L1 and the inner ring axis L2 as a center of curvature, and is cut in the direction of the inner ring axis L2. When viewed in cross section, it is formed in a convex arc shape.

  A plurality of inner ring ball grooves 32 having a substantially arc-shaped cross section in the direction orthogonal to the inner ring axis L2 are formed on the outer peripheral surface of the inner ring 30 so as to extend in the direction of the inner ring axis L2. The plurality of (six in this embodiment) inner ring ball grooves 32 are equally spaced in the circumferential direction (60 degree intervals 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.

  Further, an inner spline 35 extending in the direction of the inner ring axis L2 is formed on the inner peripheral surface of the inner ring 30. The internal spline 35 is fitted (engaged) with the external spline 61 of the shaft 60. Further, among the end portions of the inner peripheral surface of the inner ring 30, the bottom side (the left side in FIG. 1) of the outer ring 20 where the inner spline 35 is not formed is axially extended over the entire circumference of the inner spline 35. An annular portion 36 having an inner diameter larger than the diameter is formed. The annular portion 36 has a cylindrical shape, and the end surface 36a on the inner tooth spline 35 side is formed in a tapered shape with an inner diameter gradually decreasing toward the inner tooth spline 35 side. Further, a chamfer 37 having an inner diameter gradually increasing toward the end side is formed on the opening side (right side in FIG. 1) of the outer ring 20 in the end portion of the inner peripheral surface 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 the circumferential direction (around the outer ring axis L1 or the inner ring axis L2). Therefore, the inner ring 30 is connected by a plurality of balls 40 so that the relative angle can be varied and torque can be transmitted while the joint center with respect to the outer ring 20 is fixed.

  The cage 50 is formed in an annular shape. 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 cage 50 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 cage 50 includes 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 number of window portions 53 of the cage 50 is the same as the number of balls 40. One ball 40 is accommodated in each window 53. Four corners of each window 53 are formed in a circular arc concave shape. Thereby, the improvement of the intensity | strength and rigidity of each pillar part located between the adjacent window parts 53 is achieved.

  The shaft 60 has an axial shape, can transmit a driving force, and constitutes the drive shaft 1. An external spline 61 extending in the axial direction is formed on the outer peripheral surface on one end side of the shaft 60. As described above, the external spline 61 is fitted to the internal spline 35 of the inner ring 30. Further, when the inner ring 30 is press-fitted and fixed to the shaft 60, a retaining ring groove 62 is formed at the distal end portion of the shaft 60 protruding from the axial end portion of the inner ring 30.

  Further, when the inner ring 30 is fixed to the shaft 60, a stopper portion 63 having a gradually increasing outer diameter is provided on the outer peripheral surface located closer to the shaft central portion side than the inner ring 30 press-fitted to the shaft tip portion side. A diameter portion 64 is formed in a continuous manner. When the inner ring 30 is press-fitted into the shaft 60, the stopper portion 63 is a part that contacts the chamfer 37 of the inner ring 30 and restricts the inner ring 30 from being further press-fitted from a predetermined axial position. The large diameter portion 64 has a cylindrical outer peripheral surface, and is a portion into which a ring member 72 described later is press-fitted as shown in FIG.

  The retaining ring 71 has an annular shape as a whole and is attached to the retaining ring groove 62 of the shaft 60. The retaining ring 71 passes through the inner circumference of the inner ring 30 in a state where the retaining ring 71 is reduced in diameter and embedded in the retaining ring groove 62, and is mounted with an increased diameter at an axial position where the annular portion 36 is formed. The retaining ring 71 is formed such that the outer diameter in the mounted state is larger than the inner diameter of the inner ring 30 and smaller than the inner diameter of the annular portion 36.

  With such a configuration, the retaining ring 71 is formed in a circular cross section as shown in FIG. 2, and the inner ring 30 is tapered with the cylindrical portion of the annular portion 36 formed at the end of the inner peripheral surface of the inner ring 30. It contacts at two points with the shaped end surface 36a, and contacts with the shaft 60 at one point with the corner of the retaining ring groove 62 formed on the shaft 60, fixes the inner ring 30 and pulls out to the shaft 60. The inner ring 30 and the shaft 60 cannot be disassembled even when applied.

  The ring member 72 is formed in a cylindrical shape, and is press-fitted into the large diameter portion 64 of the shaft 60 and fixed. More specifically, the ring member 72 has an axis toward the front end side of the shaft 60 after the inner ring 30 is moved to an axial position where the inner ring 30 is prevented from moving toward the front end side of the shaft 60 and is prevented from coming off. As shown in FIG. 3, a load in the direction is applied to contact the inner ring 30 to restrict the axial movement of the inner ring 30.

(Installation of drive shaft)
Next, assembly of the drive shaft 1 will be described with reference to FIGS. First, as shown in FIG. 4, the drive shaft 1 is placed on the assembly base 91 so that the opening of the outer ring 20 faces upward. Then, the inner ring 30, the plurality of balls 40, and the cage 50 are arranged at predetermined positions inside the outer ring 20, and the constant velocity joint 10 is assembled. Thereafter, the shaft 60 is fixed to the inner ring 30 of the constant velocity joint 10. The shaft 60 is fixed after the step of arranging the inner ring 30 and the like in this manner because the angle between the outer ring 20 and the inner ring 30 required when the ball 40 is inserted into the window 53 of the cage 50 is constant velocity joint 10. This is because the maximum joint angle (the angle at which the shaft 60 interferes with the opening of the outer ring 20) is exceeded.

  Subsequently, in the press-fitting / removing prevention process, the shaft 60 is press-fitted into the inner ring 30 with the end face held by the jig 92. First, in a state where the retaining ring 71 is temporarily fixed in the retaining ring groove 62 of the shaft 60, the shaft 60 is moved from above to the inner ring 30 side. Then, the outer peripheral edge of the retaining ring 71 comes into contact with the inner peripheral surface of the jig 92, and the retaining ring 71 is gradually reduced in diameter and embedded in the retaining ring groove 62. When a predetermined press-fit load Fi is applied to the shaft 60, the inner ring 30 and the shaft 60 are relatively axially moved until the chamfer 37 of the inner ring 30 contacts the stopper portion 63 of the shaft 60, as shown in FIG. Moving.

  In this way, the shaft 60 is press-fitted into the inner ring 30 and the inner tooth spline 35 and the outer tooth spline 61 are fitted. Further, as shown in FIG. 6, the retaining ring 71 expands due to elasticity when it passes the end surface 36 a of the annular portion 36. As described above, the press-fitting and retaining step also serves as a step of attaching the retaining ring 71 for retaining the inner ring 30 press-fitted to the shaft 60 to the tip portion of the shaft 60.

  Here, in the state where the chamfer 37 of the inner ring 30 and the stopper portion 63 of the shaft 60 are in contact, as shown in FIG. 6, the axial distance between the end surface 36 a of the annular portion 36 and the side surface of the front end side groove of the retaining ring groove 62. Ln is larger than the axial width Wd of the retaining ring 71 (Ln> Wd). This is because a certain amount of clearance (Ln−Wd) is provided so that the retaining ring 71 can be suitably mounted by absorbing dimensional errors in manufacturing. In the axial backlash filling step, this gap is filled in advance.

  In the axial backlashing step, as shown in FIG. 7, an upward pulling load Fc is applied to the shaft 60 with the end face of the inner ring 30 held by a jig 92. As a result, as shown in FIG. 8, the inner ring 30 is moved to the axial position where the inner ring 30 is prevented from moving toward the tip side of the shaft 60 by the stop ring 71, and the inner ring 30 is prevented from coming off from the shaft 60. Here, the punching load Fc is a load that is approximately the same in the opposite direction to the press-fitting load Fi in the press-fitting / removing prevention process. Moreover, this axial backlash filling process also serves as confirmation that the retaining ring 71 has an appropriate diameter expansion.

  Subsequently, in the restricting step, the ring member 72 is press-fitted to restrict the axial movement of the inner ring 30. First, the shaft 60 is supported so that the inner ring 30 does not tilt with respect to the outer ring 20. Then, the ring member 72 is press-fitted into the large diameter portion 64 of the shaft 60 from above. As shown in FIG. 9, the ring member 72 is moved to an axial position where it comes into contact with the end face of the inner ring 30 by applying a predetermined moving load Fm from the jig 92. This moving load Fm is parallel to the axial direction of the shaft 60 and is set to be smaller than the press-fit load Fi when the inner ring 30 is press-fitted into the shaft 60 (Fm <Fi). Thus, the constant velocity joint 10 is assembled | attached by each process.

(Effects of the configuration of the embodiment)
According to the constant velocity joint 10 described above, the ring member 72 is brought into contact with the inner ring 30 that is prevented from coming off by the retaining ring 71 to restrict the axial movement of the inner ring 30. As a result, the inner ring 30 is preliminarily filled with a clearance provided for mounting the retaining ring 71, and the axial movement of the outer ring 20 toward the opening side is restricted by the ring member 72. Therefore, it is possible to suppress the backlash in the axial direction of the inner ring 30 with respect to the shaft 60.

  Further, when the ring member 72 is applied with the axial movement load Fm and comes into contact with the inner ring 30, the inner ring 30 is moved in advance to the axial position of the shaft 60 where the inner ring 30 comes into contact with the retaining ring 71 and is prevented from coming off. . That is, in the assembly of the constant velocity joint 10, the press-fitting / removing prevention process, the axial backlashing process, and the regulation process are separate processes. Therefore, it can be assembled with a load necessary for each process.

  In the present embodiment, the regulating member is a cylindrical ring member 72. Thus, the inner ring 30 is restricted from moving in the axial direction by the press-fit load (moving load Fm) between the ring member 72 and the shaft 60 in addition to the press-fit load Fi between the inner ring 30 and the shaft 60. Therefore, it is possible to more reliably suppress the occurrence of backlash between the shaft 60 and the inner ring 30.

  Further, in the constant velocity joint 10 of the present embodiment, since it is premised that the gap (Ln-Wd) is reduced after the press-fitting / removing prevention process, the end surface of the inner ring 30 and the groove side surface of the retaining ring groove 62 in the shaft 60 are used. Since a sufficient clearance can be provided between the retaining ring 71 and the retaining ring 71, the diameter of the retaining ring 71 can be increased, and the retaining ring 71 can be easily mounted in the press-fitting / removing prevention process. Further, the inner ring 30 and the intermediate shaft 60 have a structure that cannot be disassembled even if a pulling load is applied. Thereby, in the axial backlash filling step, it is possible to prevent the retaining ring 71 from being reduced in diameter even if a pulling load Fc is applied to the intermediate shaft 60, so that the gap can be reliably filled in a state where the inner ring 30 is prevented from coming off. it can.

  In the present embodiment, the moving load Fm applied to the ring member 72 in the regulation process is set to be smaller than the press-fit load Fi applied to the shaft 60 in the press-fitting / retaining process. Thereby, the load applied to the other members via the ring member 72 is also smaller than the load when the inner ring 30 is press-fitted into the shaft 60. Therefore, it is possible to prevent an excessive load from being applied to other members.

<Modification of Embodiment>
In the present embodiment, the configuration using the ring member 72 separate from the shaft 60 as the regulating member has been described as an example. On the other hand, as shown by the broken line in FIG. 10, the restricting member is a flange portion 165 having a hook shape integrally formed so as to protrude in the radial direction from the outer peripheral surface of the large diameter portion 64 of the shaft 160. It is good also as a structure.

  In the regulating step, the flange 165 of the shaft 160 is applied with an axial movement load Fm, and the outer peripheral edge of the flange 165 is brought into contact with the inner ring 30 that has been previously filled with a gap and prevented from coming off by the retaining ring 71. Plastically deformed. Thereby, in addition to the press-fit load Fi between the inner ring 30 and the shaft 60, the inner ring 30 comes into contact with the outer peripheral edge of the regulating member and is restricted from moving in the axial direction. Therefore, it is possible to more reliably suppress the occurrence of backlash between the shaft 160 and the inner ring 30.

  The power transmission shaft of this embodiment has been described by exemplifying a drive shaft of an automobile. On the other hand, the structure and manufacturing method for fixing the inner ring 30 to the shaft 60 in this embodiment can be applied to any power transmission shaft having a ball-type constant velocity joint. Therefore, the present invention can be similarly applied to, for example, a propeller shaft and a steering shaft in addition to the drive shaft. Even in such a configuration, the same effect can be obtained.

  1: drive shaft (power transmission shaft), 10: constant velocity joint, 20: outer ring, 30: inner ring, 60: shaft, 165: collar (regulating member), 71: retaining ring, 72: ring member (regulating member) , Fi: press-fit load, Fm: moving load

Claims (5)

An outer ring formed in a cylindrical shape having an opening in at least one of the axial directions, an inner ring having a plurality of outer ring ball grooves formed on the inner peripheral surface, and an inner ring disposed inside the outer ring and having a plurality of inner ring ball grooves formed on the outer peripheral surface A plurality of balls that roll in each of the outer ring ball grooves and the inner ring ball grooves and transmit torque between the outer ring and the inner ring, and are formed in an annular shape between the outer ring and the inner ring. A constant velocity joint comprising: a cage formed with a plurality of windows that are arranged and each of which accommodates the balls in the circumferential direction;
A shaft coupled to the inner ring of the constant velocity joint;
In a power transmission shaft having
A retaining ring that is attached to the tip of the shaft and prevents the inner ring that is press-fitted into the shaft;
It is arranged on the outer peripheral surface of the shaft, and contacts the end surface on the shaft center portion side of the end surface on the shaft tip portion side and the end surface on the shaft center portion side of the inner ring to restrict the axial movement of the inner ring. A regulating member,
After moving the inner ring in the axial direction with respect to the shaft to a position regulated by the retaining ring attached to the distal end of the shaft, the movement toward the shaft distal end side,
By applying an axial load to the restriction member from the shaft central part side toward the shaft tip part side where the inner ring is press-fitted, the restriction member is brought into contact with the end face of the inner ring on the shaft central part side. A power transmission shaft for restricting axial movement of the inner ring.   2. The power transmission shaft according to claim 1, wherein the restriction member has a cylindrical shape that is press-fitted into an outer peripheral side of the shaft, and is moved to an axial position of the shaft that contacts the inner ring by an axial load.   The restriction member has a hook shape integrally formed so as to protrude in a radial direction from an outer peripheral surface of the shaft, and is plastically deformed so that an outer peripheral edge contacts the inner ring by an axial load. Item 1. The power transmission shaft according to Item 1.   The power transmission shaft according to any one of claims 1 to 3, wherein an axial load applied to the restriction member is set to be smaller than a load when the inner ring is press-fitted into the shaft. An outer ring formed in a cylindrical shape having an opening in at least one of the axial directions, an inner ring having a plurality of outer ring ball grooves formed on the inner peripheral surface, and an inner ring disposed inside the outer ring and having a plurality of inner ring ball grooves formed on the outer peripheral surface A plurality of balls that roll in each of the outer ring ball grooves and the inner ring ball grooves and transmit torque between the outer ring and the inner ring, and are formed in an annular shape between the outer ring and the inner ring. A constant velocity joint comprising: a cage formed with a plurality of windows that are arranged and each of which accommodates the balls in the circumferential direction;
A shaft connected to the inner ring of the constant velocity joint;
A power transmission shaft manufacturing method comprising:
The power transmission shaft is
A retaining ring that is attached to the tip of the shaft and prevents the inner ring that is press-fitted into the shaft;
It is arranged on the outer peripheral surface of the shaft, and contacts the end surface on the shaft central portion side of the end surface on the shaft central portion side of the inner ring and the end surface on the shaft central portion side to restrict axial movement of the inner ring. A regulating member,
The method of manufacturing the power transmission shaft is as follows:
A press-fitting and retaining step of attaching a retaining ring to a retaining ring groove at the tip of the shaft, press-fitting the inner ring into the shaft, and preventing the shaft and the inner ring from coming off with the retaining ring;
An axial backlashing step of moving the inner ring in the axial direction with respect to the shaft to a position regulated by the retaining ring attached to the tip of the shaft;
By applying an axial load to the restriction member from the shaft central part side toward the shaft tip part side where the inner ring is press-fitted, the restriction member is brought into contact with the end face of the inner ring on the shaft central part side. A regulation step for regulating axial movement of the inner ring;
A method of manufacturing a power transmission shaft comprising:

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