JP2007078124A - Fixed type constant velocity universal joint - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fixed type constant velocity universal joint having improved strength while securing the area and the spherical angle of the inner spherical face of an outer ring as well as securing a corner R required for the strength of a cage. <P>SOLUTION: The fixed type constant velocity universal joint comprises the outer ring 10 having a plurality of ball grooves 14 opening at at least one end and extending to the inner spherical face 12 in the axial direction, an inner ring 20 having a plurality of ball grooves 24 extending to an outer spherical face 22 in the axial direction, a torque transmission ball 30 incorporated between a pair of the ball groove 14 of the outer ring 10 and the ball groove 24 of the inner ring 20, and the cage 40 laid between the inner peripheral face 12 of the outer ring 10 and the outer spherical face 22 of the inner ring 20 for holding the torque transmission ball 30 in the axial direction. A plane, which is located adjacent to the inner spherical face 12 on the side of an outer ring opening between the adjacent ball grooves 14 in the inner spherical face 12 to form an minimum inner diameter A<SB>1</SB>of the outer ring opening, is a cylindrical portion 16b. On a boundary between the cylindrical portion 16b and the ball groove 14, an obliquely chamfered portion 16c is formed parallel to the axis of the outer ring. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The fixed type constant velocity universal joint according to the present invention is a type that allows only angular displacement between two connected drive and driven shafts, and is used in power transmission systems of automobiles and various industrial machines.

A fixed type constant velocity universal joint is generally used for an axle connecting portion of a drive shaft of an automobile and a shaft bending connecting portion of a steering shaft. Conventionally known as this fixed type constant velocity universal joint are a Zepper type constant velocity universal joint and an undercut free type (hereinafter referred to as UJ type) constant velocity universal joint.

A zeppa type constant velocity universal joint which is a fixed type constant velocity universal joint includes an outer ring, an inner ring, a ball and a cage. A plurality of curved ball grooves are formed at equal intervals on the inner spherical surface of the outer ring. The same number of curved ball grooves are formed on the outer spherical surface of the inner ring. The center of curvature of the outer ring ball groove and the center of curvature of the inner ring ball groove are offset equidistant from side to side with respect to the center O of the joint. The ball is assembled between the outer ring ball groove and the inner ring ball groove, and the cage is assembled between the outer ring and the inner ring. The cage has inner and outer spherical surfaces that are in contact with and guided by the inner spherical surface of the outer ring and the outer spherical surface of the inner ring. The cage also has pockets for accommodating balls at equal intervals in the circumferential direction.

The UJ type constant velocity universal joint was invented to have a higher operating angle than the Zepper type constant velocity universal joint, and the ball center locus of the guide groove of the outer ring is the outer ring of the arc of the Zepper meridian. The portion on the opening side of the outer ring is a straight line parallel to the joint axis from the cross section perpendicular to the axis passing through the center of the guide groove.

  When assembling the cage to the outer ring of such a fixed type constant velocity universal joint, a method of inserting the cage from the axial direction of the outer ring in a state where the axis of the cage is rotated by 90 ° with respect to the outer ring axis (see FIG. 12, refer to FIG. 5 of Patent Document 2), and a method of inserting the cage and the outer ring from the axial direction with the axis of the outer ring coaxial (see FIG. 5 of Patent Document 3).

As shown in FIG. 20, on the opening side of the conventional outer ring 10, the inner spherical surface 12 between the ball grooves 14 and the interference of the outer ring opening edge when the shaft coupled to the inner ring takes the maximum operating angle. A cylindrical portion 16b is formed between the chamfer 16a. If you charged cage 40 of Figure 21 in a coaxial direction to the outer ring 10, since the pocket edge portion of the cage outer diametric surface becomes minimum diameter E _3, charged with by aligning the cage pocket outer edge to the cylindrical portion 16b To do. The width W ₁ of the cylindrical portion 16b in FIG. 20 is designed to be within the range of the width W ₂ of the pocket outer edge in FIG. 21 (W ₁ <W ₂ ). The start position of the cylindrical portion 16b so as to satisfy a predetermined spherical angle alpha _0, is from the center of the outer ring 10 and the position of the D _0.

The fixed type constant velocity universal joints described in Patent Document 2 and Patent Document 3 are formed by forming, on the outer peripheral surface of the cage, a cut groove or a flat surface that continues to the pocket outer edge in the axial direction. When inserting the cage into the outer ring from the coaxial direction, the notch groove and the flat surface, like the cylindrical portion 16b of FIG. 20, are protruded radially inward on the opening side of the outer ring inner spherical surface, The cage is allowed to pass along the “division wall 9”.
JP-A-6-193645 Japanese Utility Model Publication No. 5-45253 Japanese Utility Model Publication No. 54-93850

As shown in FIG. 20, the inside of the cylindrical portion 16b of the outer ring 10 and subsequently the inner spherical surface 12, the boundary _{B 3} between the cylindrical portion 16b and the inner spherical surface 12, as shown in FIG. 20 (B) when viewed from the side It is almost straight. When the inner diameter of the cylindrical portion 16b is enlarged to increase the area, the opening side area of the inner spherical surface 12 is deprived by that amount. When incorporating the cage 40 with respect to the outer ring 10 in the axial direction, in order to avoid interference with the cage outer diameter E _3, it is necessary to increase the inner diameter of the cylindrical portion 16b. However, increasing the inner diameter of the cylindrical portion 16b, after unavoidable area reduction of the outer ring in the spherical 12 as described above, also small spherical angle alpha ₀ of FIG. 20 (B). This means that the area in which the cage 40 is retained by the outer ring 10 is reduced and the surface pressure is increased, resulting in a loss of strength and durability of the fixed type constant velocity universal joint.

In order to secure the predetermined outer ring inner spherical surface 12 area and spherical angle, it is necessary to make the inner diameter of the outer ring cylindrical portion 16b equal to or less than a certain value. To reduce the outer cylindrical portion 16b inner diameter, it is necessary to reduce the minimum diameter E ₃ of the cage 40. As described in Patent Documents 2 and 3, the minimum diameter of the cage can be reduced if the portion continuing in the axial direction on the pocket outer edge of the cage outer diameter surface can be reduced, but the strength reduction of the cage 40 is inevitable.

On the other hand, the minimum diameter of the cage 40, as shown in FIG. 21 (A), are shown in E ₃ corresponding to the pocket 42 the outer edge, the minimum diameter E ₃ is the size and relationship of the corner R of the cage pocket 42. Increasing the corner R of the cage pockets 42, 21 the height of the pocket edge as indicated by the broken line in (A) increases the minimum diameter E ₃ is increased. For this reason, the corner R is suppressed to a relatively small value. However, if the corner R is small, the cage 40 is easily damaged due to stress concentration, and the cage strength is reduced.

  It is an object of the present invention to secure the outer ring inner spherical surface area and the spherical angle, and at the same time secure the corner R necessary for the cage strength, thereby improving the strength of the fixed type constant velocity universal joint.

  The fixed type constant velocity universal joint of the present invention according to claim 1 comprises an outer ring having a plurality of ball grooves that are open at least at one end and extend in the axial direction on the inner spherical surface, and a plurality of ball grooves that extend in the axial direction on the outer spherical surface. The inner ring formed with the inner ring, the torque transmission ball incorporated between the ball groove of the outer ring and the ball groove of the inner ring, and the torque transmission ball interposed between the inner spherical surface of the outer ring and the outer spherical surface of the inner ring. In a fixed type constant velocity universal joint having a cage that holds in a direction, a cylindrical surface that is adjacent to the inner spherical surface on the outer ring opening side and is between adjacent ball grooves formed on the inner spherical surface to form the minimum inner diameter of the outer ring opening And an inclined chamfered portion parallel to the outer ring axis is formed at the boundary between the cylindrical portion and the ball groove.

In the present invention, the inclined chamfered portion parallel to the outer ring axis is formed at the boundary between the cylindrical portion forming the minimum inner diameter of the outer ring opening and the ball groove as described above. Although the inner diameter of the cylindrical part of the outer ring could not be reduced due to interference, the inclined chamfered part provided a margin in the interference part with the cage pocket outer edge corner R, making the inner diameter of the outer ring cylindrical part smaller than before, and the area of the outer ring inner spherical surface It is possible to increase the spherical angle (“A ₀ ” in FIG. 20 (A) → “A ₁ ” in FIG. 2, “α ₀ ” in FIG. 20 (B) → “α ₁ ” in FIG. 2). .

The invention according to claim 2 is the invention according to claim 1, wherein the cage outer diameter surface is an adjacent surface adjacent to the outer edge of the ball holding pocket, and a circumferential intermediate region of the adjacent surface is defined as the cylindrical portion of the outer ring. A cylindrical chamfered edge centered on the center of the cage so as to be parallel to each other, and both sides in the circumferential direction of the adjacent surface are inclined chamfered edges so as to be parallel to the inclined chamfered portion of the outer ring. To do.
As a result, an increase in the cage pocket corner R and a reduction in the inner diameter of the outer ring cylindrical portion can be promoted. The cage strength is improved, and the cage retaining force or ball retaining force is secured by securing the area and spherical angle of the outer ring inner spherical surface. It is possible to improve the strength and life of the fixed type constant velocity universal joint.

The invention according to claim 3 is characterized in that, in the invention of claim 2, the inclined chamfered edge is shorter than the cylindrical chamfered edge.
In a normal fixed type constant velocity universal joint having 6 or 8 holes, the distribution relationship in which the inclined chamfered edge is shorter than the cylindrical chamfered edge is effective in reducing the inner diameter of the cylindrical portion of the outer ring.

  In the present invention, as described above, since the inclined chamfered portion parallel to the outer ring axis is formed at the boundary between the cylindrical portion forming the minimum inner diameter of the outer ring opening and the ball groove, conventionally, interference with the cage pocket outer edge corner R is prevented. Therefore, the cylindrical portion inner diameter of the outer ring could not be reduced, but the inclined chamfered portion provides a margin in the interference portion with the cage pocket outer edge corner R, and the inner diameter of the outer ring cylindrical portion can be made smaller than before. Further, the corner R of the pocket outer edge which becomes the passing portion on the cage side facing the inclined chamfered portion when the cage is inserted in the coaxial direction with respect to the outer ring can be increased, and thereby the cage strength can be increased. The strength and durability of the fixed type constant velocity universal joint can be increased. The present invention is particularly useful for a fixed type constant velocity universal joint using eight balls. When eight balls are used, the ball diameter is reduced and the joint becomes compact. And there is no room between the cage and the minimum outer diameter. Even under such constrained design conditions, a sufficient opening-side inner spherical surface area and spherical angle can be ensured.

  Further, the present invention further reduces the inner diameter of the outer ring cylindrical portion and increases the cage pocket corner R by forming a “cylindrical chamfered edge” and an “inclined chamfered edge” in a portion of the cage outer diameter surface adjacent to the pocket outer edge. It is possible to improve the cage strength and to improve the cage retaining force or ball retaining force by securing the area and spherical angle of the outer ring inner spherical surface, thereby further increasing the strength and life of the fixed type constant velocity universal joint.

  Embodiments of the present invention will be described below with reference to the drawings.

  FIG. 1 shows a longitudinal section of a UJ (undercut free) type fixed constant velocity universal joint. As shown in the figure, the fixed type constant velocity universal joint includes an outer ring 10, an inner ring 20, a ball 30 and a cage 40 as main components.

  The outer ring 10 includes a mouse portion 10a and a stem portion 10b. As shown in FIGS. 2 and 3, the mouse portion 10 a has a bowl shape opened at one end, and its inner peripheral surface (hereinafter referred to as “inner spherical surface”) is an inner spherical surface 12. A plurality (eight in this case) of ball grooves 14 extending in the axial direction are formed on the inner spherical surface 12 at equal intervals in the circumferential direction. As shown in FIG. 1, a concave spherical surface is used as a support for receiving the outer spherical surface 22 of the inner ring 20 in the inner bottom of the mouse part 10a, that is, the inner surface of the mouse part 10a and including the outer ring axis. A spherical seat 18 is formed. An annular space 19 exists around the spherical seat 18. In this embodiment, the stem portion 10b includes a serration portion and a screw portion.

  In addition, the diameter of the spherical seat 18 is made larger than the diameter of the shaft 50, and the stem portion 10b including the expanded spherical seat 18 is manufactured separately from the outer ring 10 with the surface indicated by the broken line P in FIG. In the final assembly stage of the fixed type constant velocity universal joint, the outer ring 10 may be integrated with a coupling means such as a screw. If such a separate stem portion or the expanded spherical seat 18 is used, when the shaft 50 is inserted into the inner ring 20 inserted into the outer ring 10, the inner ring 20 is not inclined as shown in FIG. That's it.

As shown in FIG. 2, a chamfer 16 a that comes into contact with the shaft 50 at the maximum operating angle of the shaft 50 coupled to the inner ring 20 is continuously formed in the peripheral edge of the outer ring 10 on the opening side edge of the mouse portion 10 a. . Between this chamfer 16a and the opening side of the inner spherical surface 12 of the mouse portion 10a, a cylindrical portion 16b similar to the conventional one is formed as shown in FIGS. The cylindrical portion 16b forms a minimum inner diameter A ₁ of the mouth section 10a opening, mutual distance between the opposite side of the cylindrical portion 16b which face each other across the outer ring center is minimized inside diameter A _1. As shown in FIG. 3, the cylindrical portion 16b is positioned between adjacent ball grooves 14 formed on the inner spherical surface 12 of the mouse portion 10a. The cylindrical portion 16b, as shown in FIG. 3, conventionally are formed slightly wide central angle theta ₁ of the narrow than (the width of the cylindrical portion 16b is smaller than W ₁ in FIG. 20). The outer boundary B ₁ of the cylindrical portion 16 b is a boundary with the chamfer 16 a, and the inner boundary B ₂ is a boundary with the inner spherical surface 12. As shown in FIG. 2, the outer boundary B ₁ and the inner boundary B ₂ are substantially linear in a side view. As shown in FIG. 2, the spherical angle α ₁ is determined by the distance D ₁ from the center of the outer ring 10 to the inner boundary B ₂ .

An inclined chamfered portion 16 c is formed between both sides of the cylindrical portion 16 b in the circumferential direction and the ball groove 14. The inclined chamfered portion 16c is a chamfered portion in which the ridgeline between the conventional cylindrical portion 16b and the ball groove 14 becomes a protruding edge 17 toward the inner side of the outer ring 10 as shown in FIG. is there. Inclined chamfered portion 16c forms a parallel to the outer ring axis, but a cylindrical portion 16b and the ball grooves 14, forming a ridge line at the boundary B ₄ and boundary B _5. The inner end of the inclined chamfered portion 16c leads the inner spherical surface 12 at the boundary B ₆ forming the ridgeline. The outer end of the inclined chamfered portion 16c leads the chamfer 12a at the boundary _{B 7} forming the ridge. The inclination angle of the inclined chamfered portion 16c, as shown in FIG. 3, ₂ theta bisector _{L 1} of the cylindrical portion 16b as the reference and a width of _{W 3.}

The inner ring 20 has a spherical shape as shown in FIGS. 1 and 4, and a plurality of, here, eight ball grooves 24 extending in the axial direction are formed on the partial spherical outer peripheral surface (hereinafter referred to as “outer spherical surface”) 22. It is formed at equal intervals in the direction. The inner ring 20 is coupled to the shaft 50 by a spline hole 26 so that torque can be transmitted. In FIG. 4, symbols F ₁ and F ₂ indicate the outer diameter of the outer spherical surface 22 of the inner ring 20 and the minimum projected diameter in the central cross section of the outer spherical surface 22, respectively.

  The radius of curvature of the spherical seat 18 of the outer ring 10 is substantially equal to the radius of curvature of the outer spherical surface 22 of the inner ring 20. Further, in the assembled state of the fixed type constant velocity universal joint shown in FIG. 1, the end portion of the spline hole 26 of the inner ring 20 located on the spherical seat 18 side is made larger than the outer diameter of the spherical seat 18. The spherical seat 18 of the outer ring 10 and the outer spherical surface 22 of the inner ring 20 are provided with a hardened surface layer by heat treatment. As can be seen from FIG. 1, the end surface of the shaft 50 is a spherical surface having substantially the same radius of curvature as the outer spherical surface 22 of the inner ring 20, and both form one spherical surface when the shaft 50 is assembled to the inner ring 20.

As shown in FIG. 1, the center of curvature O ₁ of the ball groove 14 of the outer ring 10 and the center of curvature O ₂ of the ball groove 24 of the inner ring 20 are offset from the joint center O by an equal distance f in the axial direction. Therefore, the ball grooves 14 and 24 of the inner and outer rings 10 and 20 forming a pair have a wedge shape that expands toward the large end face side opening of the outer ring 10.

The fixed type constant velocity universal joint of this embodiment has no undercut in the ball grooves 14 and 24 (undercut free). That is, the ball groove 14 of the outer ring 10 is composed of a circular arc bottom 14a parallel straight bottom 14b to the axis positioned on the large end face positioned on the small end face side to the center of curvature O ₁ as a boundary. Similarly, the ball groove 24 of the inner ring 20 has an arc bottom 24a located on the large end face side of the outer ring 10 and a straight bottom 24b parallel to the axis located on the small end face side of the outer ring 10 with the center of curvature O ₂ as a boundary. Composed.

The cage 40 is interposed between the inner spherical surface 12 of the outer ring 10 and the outer spherical surface 22 of the inner ring 20. A plurality of, here, eight pockets 42 are arranged in the circumferential direction of the cage 40. The shape of the pocket 42 is substantially rectangular, but the circumferentially opposed surface is an arc surface substantially equal to the curvature of the ball 30, and corners R (curvature radius R ₁ ) are provided at the four corners to alleviate stress concentration. Is formed. The outer spherical surface 44 of the cage 40 is in contact with the inner spherical surface 12 of the outer ring 10. As shown in FIGS. 5 and 6, the diameter E ₂ of the corners 41 and 43 formed by the outer spherical surface 44 of the cage 40 and the side walls facing the axial direction of the pocket 42 is the outer diameter of the outer spherical surface 44 of the cage 40. smaller than E _1. Diameter E ₂ is are smaller than the inner diameter _{A 1} of the cylindrical portion 16b of the outer ring 10 (E _{2 <A} 1). This is a dimensional relationship required when the cage 40 is inserted coaxially with the outer ring 10. However, even if this dimensional relationship is slightly reversed such that A ₁ <E ₂ , it can be inserted if the cage 40 is shrink-fitted or pinched to the outer ring 10.

As shown in FIGS. 5A and 5B, a pair of chamfered edges 49 that are adjacent to the outer edge of the pocket 42 and separated on both sides in the axial direction of the cage 40 are formed on the outer diameter surface of the cage 40. Is formed. Chamfered edges facing in the axial direction 49, 49 are formed symmetrically shaped center line L ₂ of the pocket 42 as a boundary. Each chamfered edge 49 includes three portions 49 a, 49 b, and 49 b that extend in the circumferential direction of the cage 40. As shown in FIGS. 6B and 6C, a cylindrical chamfer with a radius R ₃ centered on the center O _{3 of the} cage 40 so that the circumferential intermediate region is parallel to the cylindrical portion 16b of the outer ring 10. This is the edge 49a. The width of the cylindrical chamfered edge 49a is _{W 4,} as shown in FIG. 6 (B). Width _{W 4} of the cylindrical chamfered edge 49a, as can be seen from FIG. 6 (C), the substantially equal to the width of the cylindrical portion 16b of the outer ring 10. The both sides in the circumferential direction of the chamfered edge 49 are inclined chamfered edges 49b and 49b that are located on both sides of the cylindrical chamfered edge 49a and are parallel to the inclined chamfered portion 16c of the outer ring 10. The inclined chamfered edge 49b, the width of 49b is _{W 5,} the inclination angle, the bisector _{L 3} of the cylindrical chamfered edge 49a is theta ₃ as a reference ( "theta _2" in FIG. 3 = FIG 6 (C ) “Θ ₃ ”). The cylindrical chamfer edge 49a occupies most of the chamfer edge 49 in terms of area, and the inclined chamfer edges 49b and 49b are shorter than the cylindrical chamfer edge 49a. Chamfered edges 49 be those may be appropriately formed if necessary, cylindrical and its object is to define a minimum inner diameter A ₁ of the outer ring 10 as, when inserting the cage 40 into the outer ring 10 in the FIG. 11 avoiding interference with the part 16b, in order to as much as possible reduce the inner diameter a ₁ of the cylindrical portion 16b. By reducing the inner diameter A ₁ of the cylindrical portion 16b, it is possible to enlarge the area of the inner spherical surface 12 on the opening side, the holding force of the cage 40 and thus the ball 30 by extending this deep inner spherical surface 12 to the opening side Rise.

Here, even if the diameter E ₂ (the diameter on the cage insertion side) of the portion indicated by reference numeral 41 in FIG. 5B is slightly larger, it can be entered by slightly tilting the cage 40 from the same axis, but the diameter E of the portion indicated by reference numeral 43. ₂ (diameter opposite to the cage insertion side) requires the above dimensional relationship (E ₂ <A ₁ ). It is also possible to provide a portion to be cut to reduce the diameter E ₂ such chamfered corners 41, 43 of the cage 40. The inner diameter A ₁ of the cylindrical portion 16b of the outer ring 10 if it is possible to reduce the diameter E ₂ can also be reduced, since thereby expanding the range of the outer ring in the sphere 12 which guides the cage outer spherical surface 44 on the opening side, the spherical angle alpha ₁ Can be increased. As a result, the axial clearance is reduced, and the constant speed and durability are improved.

  As can be seen from FIG. 5, the inner peripheral surface of the cage 40 is composed of a combination of an inner spherical surface 46 a and a cylindrical surface 46 b that are smoothly continuous with each other at the axial center (coincident with the joint center O in FIG. 1). That is, the large end surface side of the outer ring 10 from the axial center is an inner spherical surface 46a that contacts the outer spherical surface 22 of the inner ring 20 and supports the inner ring 20 in the radial direction and the axial direction, and the small end surface of the outer ring 10 from the axial center. The side is a cylindrical surface 46b that is in contact with the outer ring spherical surface and supports the inner ring 20 in the radial direction. The cylindrical surface 46b is required to retract the inner ring 20 from the normal position in the axial direction during the assembly process (see FIG. 8). Accordingly, the accuracy may be rough except for a narrow range in which the inner ring 20 is supported in the radial direction at the normal position.

A protrusion 48 protruding toward the inner diameter side is provided at the end of the cage cylindrical surface 46b. As shown in FIG. 8, when the inner ring 20, the ball 30 and the cage 40 are used as a temporary assembly unit, the protrusion 48 is used to prevent the inner ring 20 from falling off, in other words, the stroke end of the axial movement of the inner ring 20. It functions as a prescribed stopper (see FIGS. 8 and 9). Therefore, the inner diameter E _{5 of the} protrusion 48 is set smaller than the outer diameter F ₁ of the outer spherical surface 22 of the inner ring 20.

  The ball groove 14 of the outer ring 10 and the ball groove 24 of the inner ring 20 make a pair, and a ball 30 is incorporated between each pair of ball grooves 14, 24. One ball 30 is accommodated in each pocket 42 of the cage 40. The cage 40 acts so that all the balls 30 are positioned on the bisector of the angle formed by the outer ring 10 and the inner ring 20, that is, the operating angle of the joint, whereby the constant velocity of the joint is maintained. .

  Next, a manufacturing method of the fixed type constant velocity universal joint having the above-described configuration, that is, an assembling procedure of components including the outer ring 10, the inner ring 20, the ball 30, and the cage 40 will be described.

First, as shown in FIG. 7, the inner ring 20 is inserted into the cage 40 with the axes orthogonal to each other. At this time, the magnitude relationship (F ₂ <E ₅ ) between the minimum projected diameter F ₂ (FIG. 4) in the central cross section of the outer spherical surface 22 of the inner ring 20 and the inner diameter E ₅ (FIG. 8) of the projection 48 of the cage 40 is expressed. Use. Then, the inner ring 20 is turned so that the two axes coincide with each other to be coaxial. If the diameter difference (E ₅ −F ₂ ) is small, it may be pushed in the coaxial direction from the beginning.

  The inner ring 20 is moved in the axial direction within the cylindrical surface 46b of the cage 40, and the outer spherical surface 22 of the inner ring 20 is brought into contact with the projection 48 of the cage 40, and the two are in the positional relationship shown in FIG. At this time, the inner ring 20 stops at the position where the outer spherical surface 22 hits the protrusion 48 of the cage 40, that is, the position retracted by the distance indicated by the symbol X from the normal position by the stopper function of the protrusion 48 described above.

As shown in FIGS. 9 and 10, the ball 30 is inserted into the pocket 42 from the outside in a state where the phase of the ball groove 24 of the inner ring 20 and the phase of the pocket 42 of the cage 40 are matched. Push the ball 30 to abut against the ball grooves 24 of the inner ring 20, ball circumscribed circle diameter _{D 3} is the diameter E ₂ (FIG. 5, FIG. 6) of the corner 41, 43 of the pocket 42 of the cage 40 to be equal to or less than. In other words, the ball circumscribed circle is set within the outer contour of the cage 40 when the inner ring 20 is at the stroke end of the axial movement.

At this time, indicated at D ₂ in FIG. 9, the distance from the bottom of the ball grooves 24 to the corner portion formed between the spherical portion side wall of the inner spherical surface 46a and the pocket 42 of the cage 40 of the inner ring 20 is smaller than the ball diameter When the dimensions are set, the ball 30 does not fall off to the inner diameter side, unit handling is possible, and handling becomes very easy. The dimensional relationship depends on the position (X) of the protrusion 48 of the cage 40 described above with reference to FIG. Normally, there is an interference between the ball 30 and the pocket 42, so that it is difficult for the ball 30 and the pocket 42 to drop off.

  Next, as shown in FIG. 11, the temporary assembly unit of the inner ring 20, the cage 40, and the ball 30 is inserted from the opening of the outer ring 10. As shown in FIG. 12, this insertion is performed in a state where the phases of the ball groove 14 of the outer ring 10 and the ball groove 24 of the inner ring 20 are shifted by β / 2, where β is the angle between adjacent balls. As a result, the outer spherical surface 44 of the cage 40 abuts on the inner spherical surface 12 of the outer ring 10, and at that time, the outer spherical surface 22 of the inner ring 20 occupies the annular space 19 at the bottom of the outer ring 10, as shown in FIGS. 13 and 14. Become.

  The ball 30 of the temporary assembly unit only needs to be within the outer contour of the cage 40 when passing through the cylindrical portion 16b of the outer ring 10, and after passing through this, the radius 30 along the inner spherical surface 12 of the outer ring 10 is sufficient. Can move outward in the direction. Here, the axial position of the outer ring side contact portion where the outer spherical surface 22 of the inner ring 20 hits the bottom of the outer ring 10 is more advantageous in terms of reducing the axial size of the joint. Since there is little difference in level between the seat 18 and the bottom of the annular space 19, it is advantageous in terms of processing. Therefore, after the ball 30 passes through the outer ring cylindrical portion 16b, the outer spherical surface 22 of the inner ring 20 hits the bottom of the outer ring 10 before the outer spherical surface 44 of the cage 40 hits the inner spherical surface 12 of the outer ring 10, and more than that of the inner ring 20 As a result, the contact portion can be positioned on the larger end face side by allowing the ball 30 to jump outward in the radial direction as the cage 40 further advances to the inner side of the outer ring mouse portion 10a.

  Next, as shown in FIG. 15, the phases of the temporary assembly units (20, 30, 40) and the outer ring 10 are shifted by β / 2 to match the phases of the ball grooves 14, 24 of the inner / outer rings 10, 20. Then, as shown in FIG. 16, a jig 54 is hooked on the clip groove 27 formed in the spline hole 26 of the inner ring 20 to move the inner ring 20 in the axial direction toward the opening side of the outer ring 10. 22 is brought into contact with the inner spherical surface 46 a of the cage 40. At this time, the ball 30 moves radially outward as the inner ring 20 moves in the axial direction, and the inner ring 20 and the ball 30 occupy the normal position.

  Next, as shown in FIG. 17, the shaft 50 is inserted into the spline hole 26 of the inner ring 20 while the inner ring 20 is inclined with respect to the outer ring 10 and the outer spherical surface 22 of the inner ring 20 is in contact with the spherical seat 18 of the outer ring 10. Insert and prevent the clip 52 from coming off. The reason why the inner ring 20 is tilted at this time is that the inner ring 20 escapes into the annular space 19 in the coaxial state. Then, the fixed constant velocity universal joint is completed by returning the shaft 50 to the same axis as the outer ring 10 (FIG. 1).

  In the embodiment shown in FIGS. 18 and 19, a collar 28 is provided on the inner ring 20 '. The collar 28 is positioned on the opening side of the outer ring 10 and has a recess 29 for hooking the jig 56. Using the jig 56, the inner ring 20 is pulled in the axial direction toward the opening side of the outer ring 10, and the shaft 50 is pushed into the spline hole 26 of the inner ring 20 as it is and the clip 52 prevents the inner ring 20 from coming off.

  In either embodiment, the spherical surface 18 provided on the outer ring 10 supports the outer spherical surface 22 of the inner rings 20, 20 'in the axial direction, and the outer spherical surface 22 of the inner rings 20, 20' is supported by the cylindrical surface 46b of the cage 40. Since the structure is supported in the radial direction, generation of vibrations and abnormal noise can be prevented, and constant velocity can be maintained.

  The present invention is not limited to the embodiments described and illustrated above, and various modifications can be made without departing from the scope of the claims. For example, although the illustrated embodiment exemplifies one using eight torque transmitting balls, it is also possible to use six torque transmitting balls. Further, as a method of assembling the fixed type constant velocity universal joint, in addition to the method of assembling the inner ring 20, the ball 30, and the cage 40 as a temporary assembly unit as described above, the cage 40 is inserted into the outer ring 10 in the coaxial direction. Thereafter, the inner ring 20 and the ball 30 can be assembled by a method of assembling. Furthermore, as described above, the present invention can be applied to an assembling method in which the cage is inserted in the coaxial direction with respect to the outer ring, and the axis of the cage is perpendicular to the outer ring.

The longitudinal cross-sectional view of the fixed type constant velocity universal joint which shows embodiment of this invention. The principal part longitudinal cross-sectional view of an outer ring | wheel. The principal part enlarged view of an outer ring | wheel. The end view of an inner ring. (A) is a side view of the cage, (B) is a longitudinal sectional view of the cage. 5A is a left side view of the cage of FIG. 5B, FIG. 5B is an enlarged view of the main part of FIG. 5A, and FIG. 6C is a partially enlarged view of the cage inserted into the outer ring. Explanatory drawing which shows the process in which an inner ring | wheel is integrated in a cage. The principal part longitudinal cross-sectional view which shows the positional relationship of an inner ring | wheel and a cage. The longitudinal cross-sectional view which shows the process in which a ball | bowl is integrated in the subassembly of an inner ring | wheel and a cage, and it is set as a temporary assembly unit. FIG. 10 is a right side view of the subassembly of FIG. 9. The principal part longitudinal cross-sectional view which shows the process in which the temporary assembly unit of an inner ring | wheel, a cage, and a ball | bowl is integrated in an outer ring | wheel. The end view of the state which installed the temporary assembly unit in the outer ring. XIII-XIII sectional drawing of FIG. XIV-XIV sectional drawing of FIG. FIG. 13 is an end view similar to FIG. 12 in a state where the phases of the ball grooves of the inner and outer rings are matched. The principal part longitudinal cross-sectional view of the coupling of FIG. The principal part longitudinal cross-sectional view of the coupling of FIG. 15 of the state which pushed in the shaft. Sectional drawing similar to FIG. 14 which shows another embodiment. Sectional drawing similar to FIG. 17 which shows another embodiment. (A) is a side view of a conventional outer ring, (B) is a longitudinal sectional view of the outer ring. (A) is a front view of a conventional cage, (B) is a side view of the cage. The fragmentary end view of the state which assembled the cage from the coaxial direction in the outer ring | wheel of the conventional fixed type constant velocity universal joint.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Outer ring 10a Mouse | mouth part 10b Stem part 12 Inner spherical surface 14, 24 Ball groove 14a Arc bottom 14b Straight bottom 16a Chamfer 16b Cylindrical part 16c Inclined chamfered part 17 Projection edge 18 Spherical seat 19 Annular space 20, 20 'Inner ring 22 Outer spherical surface 24 Ball Groove 24a Arc bottom 24b Straight bottom 26 Spline hole 27 Clip groove 29 Recess 30 Ball 40 Cage 41, 43 Corner 42 Pocket 44 Outer spherical surface 46a Inner spherical surface 46b Cylindrical surface 48 Protrusion 49 Chamfered edge 49a Cylindrical chamfered edge 49b Inclined chamfered edge 50 shaft 52 clip 54 jig _B 1 .about.B ₇ boundary _{A 1} minimum inner diameter O joint center O ₁ of curvature center O ₂ of curvature centered R corner alpha ₀ spherical angle

Claims (3)

An outer ring having a plurality of ball grooves extending in the axial direction on the inner spherical surface that is opened at at least one end, an inner ring having a plurality of ball grooves extending in the axial direction on the outer spherical surface, and a ball groove and an inner ring of a pair of outer rings. In a fixed type constant velocity universal joint comprising a torque transmission ball incorporated between a ball groove and a cage for holding the torque transmission ball in an axial direction interposed between the inner spherical surface of the outer ring and the outer spherical surface of the inner ring ,
A surface adjacent to the inner spherical surface on the outer ring opening side and between the adjacent ball grooves formed on the inner spherical surface and forming the minimum inner diameter of the outer ring opening is a cylindrical portion, and the outer ring axis is at the boundary between the cylindrical portion and the ball groove. A fixed type constant velocity universal joint characterized in that an inclined chamfered portion parallel to the surface is formed.   A cylindrical chamfered edge that is adjacent to the outer edge of the ball holding pocket on the outer diameter surface of the cage and that is centered on the cage center so that the circumferential intermediate region of the adjacent surface is parallel to the cylindrical portion of the outer ring. The fixed type constant velocity universal joint according to claim 1, wherein both circumferential regions of the adjacent surface are inclined chamfered edges so as to be parallel to the inclined chamfered portion of the outer ring.   The fixed type constant velocity universal joint according to claim 2, wherein the inclined chamfered edge is shorter than the cylindrical chamfered edge.