JP2009204062A - Fixed type constant velocity universal joint - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fixed type constant velocity universal joint reduced in size and suppressed in the deterioration a load capacity when taking an operating angle even if the size is reduced, and also improved in high-angle strength and durability by restricting the ride of balls on a track edge when taking a high angle. <P>SOLUTION: The fixed type constant velocity universal joint comprises an outward member having a track groove 22 formed at an inner spherical face 21, an inward member having a track groove 25 formed at an outer spherical face 24, a plurality of the balls 27 laid between the track groove 22 of the outward member and the track groove 25 of the inward member for transmitting torque, and a cage 28 mounted between the outward member and the inward member. The number of the balls 27 is six. The ratio t<SB>CAGE</SB>/PCR<SB>BALL</SB>is 0.20-0.23, where t<SB>CAGE</SB>is a cage thickness at the window portion center position of the cage 28 and PCR<SB>BALL</SB>is the pitch circle radius of the ball 27 when the operating angle is 0°. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a fixed type constant velocity universal joint, and more particularly to a fixed type that is used in a power transmission system of automobiles and various industrial machines, and that allows only angular displacement between two axes of a driving side and a driven side. It relates to a universal joint.

For example, there is a fixed type constant velocity universal joint as a kind of constant velocity universal joint used as means for transmitting rotational force from an engine of an automobile to wheels at a constant speed. This fixed type constant velocity universal joint has a structure in which two shafts on the driving side and the driven side are connected and the rotational torque can be transmitted at a constant speed even if the two shafts have an operating angle. In general, as the above-mentioned fixed type constant velocity universal joint, a Barfield type (BJ) and an undercut free type (UJ) are widely known.

  For example, as shown in FIGS. 23 and 24, a UJ type fixed type constant velocity universal joint is an outer member in which a plurality of track grooves 2 are formed on an inner spherical surface 1 along the axial direction at equal intervals in the circumferential direction. An outer ring 3, an inner ring 6 as an inner member in which a plurality of track grooves 5 paired with the track grooves 2 of the outer ring 3 are formed on the outer spherical surface 4 along the axial direction at equal intervals in the circumferential direction, and the outer ring 3 Between the track groove 2 of the inner ring 6 and the track groove 5 of the inner ring 6 to transmit torque, and between the inner spherical surface 1 of the outer ring 3 and the outer spherical surface 4 of the inner ring 6, the balls 7 And a cage 8 for holding the A plurality of window portions 9 in which the balls 7 are accommodated are arranged in the cage 8 along the circumferential direction.

  Further, the track groove 2 of the outer ring 3 has an arcuate portion 2a on the back side and a straight portion 2b on the opening side. As for the track groove 5 of the inner ring | wheel 6, the back side is made into the linear part 5a, and the opening side is made into the circular arc part 5b. The center of curvature O1 of the track groove 5 of the inner ring 6 and the center of curvature O2 of the track groove 2 of the outer ring 3 are offset with respect to the joint center O by an equal distance F, F in the axial direction.

In recent years, in order to reduce the size, there is a ball having eight balls as shown in FIG. 24 (Patent Document 1). In this case, the cage wall thickness at the center position of the cage window is t _CAGE , the pitch circle radius of the ball when the operating angle is 0 ° is PCR _BALL , and the ratio t _CAGE / PCR _BALL is 0. It is set to about 11 to 0.19.
Japanese Patent No. 3859264

If t _CAGE / PCR _BALL is kept at 0.11 to 0.19 and further downsizing, that is, the pitch circle radius is reduced, the thickness of the cage is inevitably reduced. If it becomes thin in this way, the rigidity of the column part between window parts and the side frame (window frame which faces an axial direction) of a window part will fall. For this reason, it becomes difficult to ensure the strength as a constant velocity universal joint at a high operating angle.

  In view of the above-mentioned problems, the present invention can be downsized, and even when downsized, when the operating angle is taken, there is little reduction in load capacity, and the ball on the track edge portion at high angles Provided is a fixed type constant velocity universal joint that can improve the high angle strength and durability by mitigating the run-up.

The fixed type constant velocity universal joint according to the present invention includes an outer member having a plurality of track grooves formed on an inner spherical surface, an inner member having a plurality of track grooves formed on the outer spherical surface, and a track groove of the outer member. A plurality of balls that transmit torque by being interposed between the outer member and the track groove of the inner member, and a cage that has a window portion that accommodates the balls and is interposed between the outer member and the inner member. In the fixed type constant velocity universal joint provided with the above, the pitch circle of the ball when the number of the balls is 6, the cage thickness at the center position of the cage window is t, and the operating angle is 0 °. The radius is PCR _BALL , and the ratio t _CAGE / PCR _BALL is 0.20 or more and 0.23 or less.

In the fixed type constant velocity universal joint of the present invention, since the number of balls is six, relatively large balls can be used, and the column width between the window portions of the cage can be increased. By the way, when t _CAGE / PCR _BALL is less than 0.20, the outer diameter becomes large, making it difficult to make compact, reducing the thickness of the cage, and ensuring the required joint strength at a large angle. It becomes difficult. On the other hand, if t _CAGE / PCR _BALL exceeds 0.23, the inner ring (inner member) of the inner diameter serration part (shaft fitting part) becomes thinner, and the required joint at a large angle (high operating angle) Ensuring strength is difficult, and the spherical surfaces of the inner member and the outer member are reduced, so that the allowable torque level is lowered. As a result, the ball can easily ride on the edge portions of the track grooves of the inner member and the outer member, and the durability may be significantly reduced. For this reason, by satisfying 0.20 ≦ t _CAGE / PCR _BALL ≦ 0.23, it is possible to reduce the size and improve the cage strength, and to prevent the ball from running onto the edge of the track groove.

It is preferable that the pitch circle diameter of the ball is PCD _BALL , the ball diameter is D _BALL , and the ratio PCD _BALL / D _BALL is 3.0 or more and 3.3 or less. The strength and durability as a constant velocity universal joint can be secured.

  If the ratio of the pitch circle diameter to the ball diameter is less than 3.0, if the ball diameter is large, the thickness of the inner member becomes too thin, which raises concerns about strength. When the diameter is small, the surface pressure between the inner member (inner ring) / outer member (outer ring) and the ball increases, which raises concerns about durability. On the contrary, when the ball diameter exceeds 3.3, when the ball diameter is small, the load capacity of the ball is small, and there is a concern in terms of durability. When the pitch circle diameter of the ball is large, the outer diameter of the outer member is It becomes large and cannot be made compact.

It is preferable that the outer diameter of the outer member is D _OUTER , the ball diameter is D _BALL , and the ratio D _OUTER / D _BALL is 4.6 or more and 4.8 or less. If the ratio between the outer diameter of the outer member and the diameter of the ball is less than 4.6, the outer member becomes too thin when the ball diameter is large. When the outer diameter of the one-way member is small, the surface pressure between the inner member / outer member and the ball increases, and there is a concern in terms of durability. On the other hand, if the diameter exceeds 4.8, the load capacity of the ball becomes small when the ball diameter is small, and there is concern about durability, and compactness cannot be achieved when the outer member has a large outer diameter.

  The center of curvature of the track groove of the outer member and the center of curvature of the track groove of the inner member are offset in the axial direction by an equal distance from the joint center, and the center of curvature of the outer spherical surface of the cage and the cage A straight line connecting the center of curvature of the outer spherical surface of the cage and the center of the ball when the working angle is 0 °, offset from the center of curvature of the inner spherical surface by an equal distance from the joint center in the axial direction. The offset angle formed by the straight line connecting the joint center and the ball center, and the offset angle formed by the straight line connecting the center of curvature of the inner spherical surface of the cage and the ball center, and the straight line connecting the joint center and the ball center. Is preferably set to 2.7 ° or more and 5.7 ° or less.

  By setting the offset angle of the cage to 2.7 ° or more and 5.7 ° or less, the thickness of the end portion on the joint opening side of the cage is formed thicker than other portions. When the offset angle of the cage is less than 2.7 °, the end portion on the joint opening side of the cage becomes thin, and sufficient strength cannot be secured. If the angle exceeds 5.7 °, the thickness of the end of the cage on the back side becomes extremely thin. Heat treatment is generally performed in the cage manufacturing process. However, if the cage thickness becomes extremely thin, the uncured layer due to the heat treatment decreases in the thin portion, and the toughness decreases and sufficient strength cannot be secured. . Moreover, if the thickness difference between the end portion on the joint opening side of the cage and the end portion on the back side of the joint is large, the workability may be deteriorated.

  It is preferable to increase the offset amount of the cage substantially the same as the offset amount of the track groove. As a result, it is possible to prevent the depth of the track groove on the deeper side of the joint from becoming shallow, and to increase the thickness (diameter thickness) of the cage on the opening side.

  The track grooves of the inner and outer joint members are disposed at unequal pitches in the circumferential direction, and the plurality of inner spherical surfaces disposed between the track grooves of the outer joint member are disposed within the smallest pitch. Further, the circumferential length of the opening side end of the inner spherical surface may be set smaller than the width of the cage window.

  With this configuration, when the cage is incorporated into the outer joint member, the window portion of the cage is incorporated so as to face the inner spherical surface disposed within the minimum pitch of the outer joint member. In this case, since the circumferential length of the opening side end portion of the inner spherical surface disposed within the minimum pitch is set smaller than the width of the opposing cage window, the inner spherical surface is the outer circumferential surface of the cage. The cage can be easily incorporated into the outer joint member without interfering with the outer joint member.

  Further, among the pitches between the track grooves of the inner and outer joint members, the phase of two pitches positioned symmetrically with respect to the joint center is set to be smaller than 60 °, and the phase of the remaining four pitches is set to 60 °. The circumferential length of the opening-side end portion of the inner spherical surface of the outer joint member disposed within the phase pitch smaller than 60 ° is set smaller than the width of the cage window portion. There may be.

  In such a case, when the cage is assembled into the outer joint member, the cage window portion is assembled so as to face the inner spherical surface of the outer joint member disposed within a pitch of a phase smaller than 60 °. At this time, since the circumferential length of the opening side end portion of the inner spherical surface disposed within the pitch smaller than 60 ° is set to be smaller than the width of the opposing cage window, the inner spherical surface is the cage. The cage can be easily incorporated into the outer joint member without interfering with the outer peripheral surface of the outer joint member. Further, since the inner spherical surface (opening side end portion) having a circumferential length smaller than the width of the window portion is arranged symmetrically with respect to the joint center, it becomes easier to incorporate.

  The cage pillars disposed within the phase pitch smaller than 60 ° are removed to form a long window portion capable of holding the two torque transmitting balls in the cage, and the long window portion The circumferential length may be set larger than the width of the inner joint member.

  In such a case, when the inner joint member is assembled into the cage, one of the outer spherical surfaces disposed between the track grooves of the inner joint member is inserted into the long window portion of the cage, and the inner joint member is inserted into the cage. It will be stored inside. At this time, since the circumferential length of the long window portion is set larger than the width of the inner joint member, the outer spherical surface of the inner joint member can be easily inserted without interfering with the long window portion. is there.

  Further, by removing a part of the pillar portion of the cage disposed within the pitch of the phase smaller than 60 °, forming a long window portion capable of holding the two torque transmission balls in the cage, The circumferential length of the long window portion may be set larger than the width of the inner joint member.

  In this case as well, when the inner joint member is assembled into the cage, one of the outer spherical surfaces arranged between the track grooves of the inner joint member is inserted into the long window portion of the cage, and the inner joint member is inserted into the cage. Will be stored in. At this time, since the circumferential length of the long window portion is set larger than the width of the inner joint member, the outer spherical surface of the inner joint member can be easily inserted without interfering with the long window portion. is there.

  In the present invention, since a relatively large ball can be used, an allowable torque capacity of one ball can be secured, and the ball can be arranged in a small PCD, that is, the outer diameter can be made compact. Since the thickness of the pillar portion between the window portions of the cage can be increased, the strength at a high operating angle can be ensured.

By satisfying 0.20 ≦ t _CAGE / PCR _BALL ≦ 0.23, it is possible to reduce the size and improve the cage strength, and to prevent the ball from climbing onto the edge of the track groove. That is, according to the present invention, it is possible to reduce the size (miniaturization), to ensure the strength of the cage even if the size is reduced, and to prevent damage to the cage when a high-angle torsional torque load is applied. Improvements can be made. For this reason, the joint strength durability can be ensured to be equal to or better than the conventional product (8-ball fixed joint) with a more compact form.

  By setting the ratio between the pitch circle diameter of the ball and the ball diameter to 3.0 or more and 3.3 or less, the strength and durability of the constant velocity universal joint can be ensured, and high precision constant velocity is possible. A joint can be provided. Further, when the ratio between the outer diameter of the outer member and the diameter of the ball is set to 4.6 or more and 4.8 or less, further strength and durability can be secured. By setting the cage offset angle to 2.7 ° or more and 5.7 ° or less, the thickness of the end of the cage on the joint opening side can be made thicker than other parts. Even if the cage is thinly formed in order to reduce the size and weight, the end portion on the joint opening side of the cage can ensure the strength to withstand the load applied when the joint is rotated at a high operating angle.

  By increasing the cage offset amount to be approximately the same as the track groove offset amount, it is possible to prevent the depth of the track groove on the inner side of the joint from being reduced, and to increase the cage thickness (diameter thickness) on the opening side. Can be bigger. For this reason, it is possible to prevent the ball at a high angle from riding on the track edge, and an excessive stress is not applied to the edge. In other words, the torsional torque load capacity at high angles is prevented from decreasing, and the high-angle durability life is improved (improved), and the breaking strength is improved (improved) due to plastic deformation of the inner and outer member track grooves at high angles. Can be planned.

  If the track grooves of the inner member and the track grooves of the outer member are arranged at unequal pitches in the circumferential direction, the window portions of the cage are also arranged at unequal pitches in the circumferential direction. As a result, when the inner ring is assembled into the cage, a window portion having a large circumferential length can be used during the assembly, and assemblability can be improved.

  The circumferential length of the opening side end portion of the inner spherical surface disposed within the minimum pitch is made smaller than the width of the window portion of the cage, or the outer side disposed within the phase pitch smaller than 60 °. By making the circumferential length of the opening side end portion of the inner spherical surface of the joint member smaller than the width of the window portion of the cage, it is possible to improve the assemblability when the cage is assembled into the outer joint member.

  If the cage is formed with a long window portion capable of holding the two torque transmission balls, and the circumferential length of the long window portion is set larger than the width of the inner joint member, the inner joint member is It is possible to improve the assemblability when incorporating into the cage.

  Further, in forming the cage long window portion, the method of removing the column portion may be press working or milling, and can be stably formed by these various plastic workings. .

  Hereinafter, embodiments of the present invention will be described with reference to FIGS.

  As shown in FIGS. 1 and 2, the fixed type constant velocity universal joint includes an outer ring 23 as an outer member in which a plurality (six) of track grooves 22 are formed on the inner spherical surface 21 along the axial direction, An inner ring 26 as an inner member in which a plurality of (six) track grooves 25 that are paired with the track grooves 22 of the outer ring 23 are formed in the spherical surface 24 along the axial direction, and the track grooves 22 and the inner rings 26 of the outer ring 23 are formed. A plurality of (six) balls 27 that are interposed between the track grooves 25 and transmit torque, and a window that holds the balls 27 interposed between the inner spherical surface 21 of the outer ring 23 and the outer spherical surface 24 of the inner ring 26. And a cage 28 having a portion (pocket) 29. In this case, as shown in FIG. 2, six window portions 29 are arranged at an equal pitch (60 ° pitch) along the circumferential direction.

  The track groove 22 of the outer ring 23 includes a back-side track groove 22a in which the track groove bottom is an arc portion and an opening-side track groove 22b in which the track groove bottom is a straight portion parallel to the outer ring axis. The back side track groove 22 a has its center of curvature O 1 shifted from the joint center O in the axial direction toward the opening side of the outer ring 23. The track groove 25 of the inner ring 26 includes a back side track groove 25a in which the track groove bottom is a straight portion parallel to the inner ring axis and an opening side track groove 25b in which the track groove bottom is an arc portion. The center of curvature O2 of the opening side track groove 25b is provided at an equal distance k away from the joint center O in the axial direction on the far side opposite to the center of curvature O1 of the back side track groove 22a of the outer ring 23.

  The track groove 22 of the outer ring 23 and the track groove 25 of the inner ring 26 can be formed by plastic working, cutting, quenching steel cutting, or the like.

  In the cage 28, the center of curvature O3 of the outer spherical surface 28a and the center of curvature O4 of the inner spherical surface 28b are offset in the axial direction by an equal distance k2 with respect to the joint center (cage center) O. The amount is made substantially the same as the offset amount of the track groove.

  For this reason, the outer spherical surface 28a of the cage 28 can form a substantially concentric arc (a concentric arc having different curvature radii) with the groove bottom of the inner track groove 22a of the outer ring 23, and the track groove depth on the inner side of the joint. Can be prevented, and the thickness (diameter thickness) on the opening side of the cage 28 can be increased.

As shown in FIG. 2, the cage thickness at the window center position of the cage 28 with a _{t CAGE,} a pitch circle radius of the balls 27 when the operating angle is 0 ° and _{PCR BALL,} is the ratio _{t CAGE} / PCR _{BALL is set} to 0.20 or more and 0.23 or less.

Further, as shown in FIG. 3, the ratio r1 between the pitch circle diameter PCD _BALL of the ball 27 and the diameter D _{BALL of the} ball 27 is set to 3.0 or more and 3.3 or less. That is, 3.0 ≦ r1 ≦ 3.3. The ratio r2 between the outer diameter D _OUTER of the outer ring 23 and the diameter PCD _{BALL of the} ball 27 is set to 4.6 or more and 4.8 or less. That is, 4.4 ≦ r2 ≦ 4.8.

Here, the pitch circle radius PCR _BALL is the radius of the locus of the circle drawn by the ball center, and the pitch circle diameter PCD _BALL is the diameter of the locus of the circle drawn by the ball center.

As shown in FIG. 4, when the operating angle is 0 °, a straight line L3 connecting the center of curvature O3 of the outer spherical surface 28a of the cage 28 and the ball center O5, and a straight line connecting the joint center O and the ball center O5. An angle θ3 formed by L, and an angle θ4 formed by a straight line L4 connecting the center of curvature O4 of the inner spherical surface 28b of the cage 28 and the ball center O5, and a straight line L connecting the joint center O and the ball center O5, respectively. It is set to 2.7 ° or more and 5.7 ° or less. The angles θ3 and θ4 are called cage offset angles (θ _CAGE ). The operating angle of 0 ° is a state where the axis of the outer ring 23 and the axis of the inner ring coincide.

Further, when the operating angle is 0 °, an angle formed by a straight line L1 connecting the curvature center O1 of the track groove 22 of the outer ring 23 and the ball center O5 and a straight line L connecting the joint center O and the ball center O5. θ1 and an angle θ2 formed by a straight line L2 connecting the center of curvature O2 of the track groove 25 of the inner ring 26 and the ball center O5 and a straight line L connecting the joint center O and the ball center O5 are respectively the offset angles (θ _CAGE ). Note that the angles θ1 and θ2 are referred to as track offset angles (θ _TRACK ). In this embodiment, the center of curvature O1 of the track groove 22 of the outer ring 23 is disposed closer to the anti-joint center side than the center of curvature O3 of the outer spherical surface 28a of the cage 28, and the center of curvature O2 of the track groove 25 of the inner ring 26 is It arrange | positions rather than the curvature center O4 of 28 inner spherical surfaces 28b in the anti-joint center side. For this reason, in this embodiment, the track offset angle (θ _TRACK ) is set slightly larger than the cage offset angle (θ _CAGE ).

  In the present invention, since the number of balls is six, a relatively large ball can be used. For this reason, an allowable torque capacity of one ball can be secured, and the ball can be arranged in a small PCD, that is, the outer diameter can be made compact. Since the thickness of the pillar portion between the window portions of the cage 28 can be increased, the strength at a high operating angle can be ensured.

By the way, when t _CAGE / PCR _BALL is less than 0.20, the outer diameter becomes large, it becomes difficult to make compact, the thickness of the cage becomes thin, and the necessary joint strength at a large angle can be secured. It becomes difficult. On the other hand, if t _CAGE / PCR _BALL exceeds 0.23, the inner ring (inner member) of the inner diameter serration part (shaft fitting part) becomes thinner, and the required joint at a large angle (high operating angle) As a result, it becomes difficult to secure the strength, and the spherical surfaces of the inner ring 26 and the outer ring 23 become smaller, so that the allowable torque level is lowered. As a result, the ball 27 can easily ride on the edge portions of the track grooves 25 and 22 of the inner ring 26 and the outer ring 23, and the durability may be significantly reduced.

For this reason, by satisfying 0.20 ≦ t _CAGE / PCR _BALL ≦ 0.23, it is possible to reduce the size and improve the cage strength, and to prevent the ball 27 from climbing onto the edge of the track groove. . That is, according to the present invention, it is possible to reduce the size (miniaturization), to secure the strength of the cage 28 even if the size is reduced, and to prevent the cage from being damaged when a high-angle torsional torque load is applied. Can be improved. For this reason, the joint strength durability can be ensured to be equal to or higher than that of the conventional product (8-ball fixed joint) with a more compact form.

In addition, by setting the ratio of the pitch circle diameter PCD _BALL of the ball 27 to the diameter of the ball 27 to be 3.0 or more and 3.3 or less, it is possible to ensure the strength and durability as a constant velocity universal joint, A highly accurate constant velocity universal joint can be provided. When the ratio between the pitch circle diameter PCD _BALL and the diameter of the ball 27 is r1, if r1 <3.0, if the diameter of the ball 27 is large, the inner ring 26 is too thin, When the pitch circle diameter of the ball 27 is small, the surface pressure between the inner / outer rings 26 and 23 and the ball increases, and there is a concern in terms of durability. On the contrary, when r1> 3.3, when the diameter of the ball 27 is small, the load capacity of the ball 27 is small, and there is a concern in terms of durability. When the pitch circle diameter of the ball 27 is large, the outer ring Since the thickness of 23 becomes too thin, there is a concern in terms of strength, or the outer diameter of the outer ring becomes large, so that compactness cannot be achieved.

  The ratio between the outer diameter of the outer ring 23 and the diameter of the ball 27 is preferably 4.6 or more and 4.8 or less. Thereby, further strength and durability can be secured. When the ratio r2 between the outer diameter of the outer ring 23 and the diameter of the ball 27 is r2, if r2 <4.6, if the diameter of the ball 27 is large, the thickness of the outer ring 23 becomes too thin, and the strength is increased. When the outer diameter of the outer ring 23 is small, the surface pressure between the inner / outer rings 26 and 23 and the ball 27 increases, and there is a concern in terms of durability. On the other hand, if r2> 4.8, when the diameter of the ball 27 is small, the load capacity of the ball is small, and there is a concern in terms of durability, and when the outer diameter of the outer ring 23 is large, the compactness is reduced. Cannot be achieved.

  By setting the offset angles θ3 and θ4 of the cage 28 to be not less than 2.7 ° and not more than 5.7 °, the thickness of the end portion on the joint opening side of the cage 28 is made thicker than other portions. Even if the cage 28 is thinly formed in order to reduce the size and weight of the joint, the joint opening side end of the cage 28 has sufficient strength to withstand the load applied when the joint is rotated at a high operating angle. be able to. By setting the offset angles θ3 and θ4 of the cage 28 to be not less than 2.7 ° and not more than 5.7 °, the thickness of the end portion on the joint opening side of the cage 28 is formed thicker than other portions. . If the offset angles θ3 and θ4 of the cage 28 are less than 2.7 °, the end portion on the joint opening side of the cage 28 becomes thin, and sufficient strength cannot be ensured. If the angle exceeds 5.7 °, the thickness of the end of the cage 28 on the back side of the joint becomes extremely thin. Heat treatment is generally performed in the cage manufacturing process. However, when the thickness of the cage 28 becomes extremely thin, an uncured layer due to the heat treatment is reduced in the thin portion, and the toughness is lowered and sufficient strength can be secured. Disappear. Further, if the thickness difference between the end portion on the joint opening side of the cage 28 and the end portion on the back side of the joint is large, the workability may be deteriorated.

  Further, in the present invention, the offset amount k of the cage 28 is made substantially the same as the offset amounts of the track grooves 22 and 25. Therefore, it is possible to prevent the depth of the track groove on the back side of the joint from becoming shallow, and to increase the thickness (diameter thickness) of the cage 28 on the opening side. For this reason, it is possible to prevent the ball 27 at a high angle from riding on the track edge, and an excessive stress does not act on the edge. That is, a reduction in torsional torque load capacity at high angles is prevented, and high angle durability life is improved (improved), and breakage strength is improved (improved) due to plastic deformation of the track grooves 25 and 22 of the inner ring 26 and outer ring 23 at high angles. Can be achieved.

  Since the track groove 22 of the outer ring 23 and the track groove 25 of the inner ring 26 can be formed by plastic working, cutting, or hardened steel cutting, the track groove formation of the inner ring 26 or the outer ring 23 is performed by any special forming method. Can be done easily.

  FIG. 5 shows another embodiment, and the cage 28 in this case has four pieces of a pair of long window portions 30 having a large circumferential interval and a pair of short window portions 31 having a small circumferential interval. ing. Then, the pair of long window portions 30 are shifted 180 degrees along the circumferential direction, and the pair of short window portions 31 are shifted 180 degrees along the circumferential direction, so that the long window portion 30 and the short window portion 31 are circumferentially moved. Are arranged alternately. For this reason, the pillar part (cage pillar part) 33 provided between window parts becomes four pieces. The long window portion 30 accommodates two balls 27 and the short window portion 31 accommodates one ball 27.

  The pitch angle e on the PCD of the two balls 27 accommodated in the long window portion 30 is made smaller than 60 degrees, and the pitch angle d of the other balls 27 is made larger than 60 degrees. Therefore, as shown in FIG. 6, the shoulder width dimension f between the two track grooves of the outer ring 23 corresponding to the long window portion 30 of the cage 28 is set smaller than the window width g in the cage axial direction. That is, the track grooves 25 and 22 of the inner ring 26 and the outer ring 23 are arranged at unequal pitches in the circumferential direction, and the smallest pitch among the plurality of inner spherical surfaces arranged between the track grooves of the outer ring 23. A circumferential length (shoulder width dimension between track grooves) f of the opening side end portion of the inner spherical surface disposed inside is set to be smaller than the window width width g of the cage 28. Furthermore, as shown in FIG. 7, the axial length i of the inner ring 26 is shorter than the circumferential interval h of the long window portion 30.

  By the way, as shown in FIGS. 6 and 7, the long window portion 30 has a bulging portion that protrudes inward in the long window portion at the center in the longitudinal direction of the long sides 35 a and 35 b facing the long window portion 30. 36 and 36 are provided to form two ball accommodating portions 38 and 38 that are connected to the long window portion 30 via a slit 37. In addition, the bulging portions 36, 36 are continuous spherical surfaces having the same curvature radius as the outer spherical surface 28 a of the cage 28, and the inner surfaces are continuous spherical surfaces having the same curvature radius as the inner spherical surface 28 b of the cage 28. In this embodiment, the shape of the bulging portion 36 is a trapezoidal shape (so-called Mt. Fuji shape) whose side is an arc surface when viewed from the cage outer peripheral side. For this reason, the projecting end surface 36a of each bulging portion 36 is a plane extending along the circumferential direction of the cage, and is opposed (facing) with a predetermined interval M.

  As shown in FIG. 7, the predetermined interval M is set to a dimension that does not interfere with the shoulder 47 (protrusion between adjacent track grooves) of the inner ring 26 during assembly. Also, the size and shape of the bulging portion 36 must be such that the movement of the ball 27 accommodated in the ball accommodating portion 38 is not hindered when rotating with an operating angle. The bulging portion 36 can be formed by machining or plastic processing when the long window portion 30 is formed.

  Thus, it has four of the pair of long window portions 30 having a large circumferential interval and the pair of short window portions 31 having a small circumferential interval, and the pair of long window portions 30 along the circumferential direction. The pair of short window portions 31 are shifted 180 degrees along the circumferential direction and the long window portions 30 and the short window portions 31 are alternately arranged along the circumferential direction. The number of the column part 33 between parts can be made into four, and the circumferential direction length of the column part 33 per one can be lengthened.

  As a result, the rigidity of each cage post 33 can be increased, so that a large ball 27 can be arranged on a small PCD, and the fixed constant velocity universal joint can be made compact without reducing the load capacity. As a result, the cage 28 can be reduced in size, and the cage 28 can be prevented from being damaged by a torsional torque load at a high angle. Further, by having the long window portion 30, the inner ring 26 can be easily assembled into the cage 28. That is, as shown in FIGS. 6 and 7, when the inner ring 26 is incorporated into the cage 28, one shoulder 47 of the inner ring 26 is dropped into one long window portion 30. By using the long window part 30 for the part 29, the workability can be improved.

  By providing the bulging portions 36, 36 in the long window portion 30, the rigidity of the frame (window frame) for constituting the long window portion 30 can be improved. As a result, deformation of the cage 28 due to insufficient rigidity of the window frame can be prevented, and the operability of the joint can be maintained, and stable operability can be exhibited over a long period of time.

  Further, when the operating angle is taken by the bulging portion 36 on the long side 35a side on the joint opening side, the interference between the inlay edge portion of the opening (inlet) of the outer ring 23 and the window edge portion on the cage outer spherical surface 28a side. Can be delayed or eliminated, and the bulging portion 36 of the long side 35b on the back side of the joint interferes with the back edge portion of the outer spherical surface 24 of the inner ring 26 and the window edge portion on the cage inner spherical surface 28b side. Can be delayed or eliminated. For this reason, it becomes easy to guide to the inner spherical surface 21 of the outer member of the cage 28 and the outer spherical surface 24 of the inner member, so that the operability of the joint can be prevented from being deteriorated, and the operability of the joint is improved by improving the rigidity of the window frame. Combined with the prevention of deterioration, chipping and cracking of the cage 28 can be effectively prevented.

  As described above, in the fixed type constant velocity universal joint shown in FIG. 5 and the like, the track grooves 25 and 22 of the inner ring 26 and the outer ring 23 are arranged at unequal pitches in the circumferential direction, and between the track grooves of the outer ring 23. The circumferential length f of the opening side end portion of the inner spherical surface disposed within the minimum pitch among the plurality of inner spherical surfaces disposed is set smaller than the width g of the window portion 29 of the cage 28. .

  With this configuration, when the cage 28 is incorporated into the outer ring 23, the window portion 29 of the cage 28 is incorporated so as to face the inner spherical surface disposed within the minimum pitch of the outer ring 23. In this case, since the circumferential length of the opening side end portion of the inner spherical surface disposed within the minimum pitch is set to be smaller than the width of the window portion 29 of the opposing cage 28, the inner spherical surface is the cage 28. The cage 28 can be easily incorporated into the outer ring 23 without interfering with the outer peripheral surface.

  Further, among the pitches between the track grooves of the inner ring 26 and the outer ring 23, the phase of two pitches positioned symmetrically with respect to the joint center is set to be smaller than 60 °, and the phase of the remaining four pitches is set to 60. The circumferential length f of the opening side end portion of the inner spherical surface of the outer ring 23 disposed within the pitch of the phase smaller than 60 ° is set to be smaller than the width of the window portion 29 of the cage 28. Will be.

  In such a case, the cage 28 can be easily incorporated into the outer ring 23. In addition, since the inner spherical surface (opening side end portion) having a circumferential length smaller than the width of the window portion 29 is arranged symmetrically with respect to the joint center, it becomes easier to incorporate.

  As shown in FIG. 9A, the long window portion 30 of the above embodiment has a so-called Mt. Fuji shape in the bulging portions 36, 36, but the shape as shown in FIGS. 9B, 9C, and 9D. It may be. That is, the bulging portions 36 and 36 in FIG. 9B are rounded at the corners of the protruding end surface 36a of the bulging portion 36, and the bulging portions 36 and 36 in FIG. 9 is a gentle trapezoidal shape, and the bulging portions 36 and 36 in FIG. 9D are rectangular.

  Even the cage 28 having the long window portion 30 shaped as shown in FIGS. 9B, 9C, and 9D has the same effects as the cage 28 shown in FIG.

  Moreover, as shown in FIG. 10, you may abbreviate | omit either one of a pair of bulging parts 36 and 36. FIG. In FIG. 10A, the bulging portion 36 is provided only on the long side 35a side on the joint opening side, and in FIG. 10B, the bulging portion 36 is provided only on the long side 35b side on the joint opening side.

  In the case shown in FIG. 10A, the interference between the inlay edge portion of the opening (inlet) of the outer ring 23 and the window edge portion on the cage outer spherical surface 28a side can be delayed or eliminated. In the case shown in b), interference between the inner edge 26 of the outer spherical surface 24 of the outer spherical surface 24 and the window edge portion of the inner spherical surface 28b of the cage can be delayed or eliminated.

  Moreover, as shown in FIG. 11 and FIG. 12, it is good also as an oblong hole which does not provide the bulging part 36 in the long window part 30. FIG. In such a thing, although the effect based on the bulging part 36 cannot be enjoyed, the improvement in the incorporating property to the cage 28 of the inner ring | wheel 26 and a lightweight improvement can be achieved.

  By the way, when manufacturing the cage 28 having the long window portion 30, in the existing cage in which the window portions are formed at a pitch of 60 ° along the circumferential direction, the pillar portion between the window portions adjacent in the circumferential direction is removed. Good. That is, the pair of pillars in the opposite direction with respect to the cage center may be removed. As this removal method, it can carry out by press work, milling, etc., for example. In the case of the cage 28 shown in FIGS. 9 and 10, a part of the column part to be removed remains, but in the cage 28 shown in FIGS. 11 and 12, the entire (all) part of the column part to be removed is removed. Yes.

  As described above, the cage 28 can be easily formed by removing the pillar portion in the existing cage, and the removal of the pillar portion can be performed by milling even if it is press working. It may be, and can be stably formed by these various plastic workings.

  As long as the long window part 29 capable of holding the two torque transmission balls 27 is formed in the cage 28 and the circumferential length h of the long window part 30 is set larger than the width i of the inner ring 25, It is possible to improve the assemblability when the inner ring 26 is assembled into the cage 28.

  As shown in FIGS. 13 to 15, a notch 45 may be provided at the back end of one track groove 25 (25 </ b> A) of the inner ring 26 (terminal edge on the joint back side). In this case, the notch 45 is formed by a tapered surface formed at a corner portion between the rear side end and the inner ring end surface 46. In addition, this notch part 45 is comprised from the inclination part. In this case, it may be molding by machining or molding by plastic working.

  By the way, when the inner ring 26 is incorporated into the cage 28, the inner ring 26 is disposed so that the axis is perpendicular to the axis of the cage 28 (a state in which the inner ring 26 is rotated by 90 ° with respect to the cage 28). To do. In this state, as shown in FIG. 16, a part of the outer spherical surface 24 of the inner ring 26 (protrusion 47A between the track grooves 25 adjacent in the circumferential direction) is formed on the window 29 (long window 30) of the cage 28. Drop it. That is, the track groove 25A in which the notch 45 is formed is fitted to the side frame portion 48 on the thinner side than the window portion 30, and the protrusion 47A on the counterclockwise side from the track groove 25A is fitted into the window of the cage 28. Then, the inner ring 26 is rotated in the direction of the arrow X around the bottom of the notch 45. At this time, the turning radius C can be made smaller than the turning radius B (the turning radius of the conventional product) that does not have the notch 45. Here, the rotation radius C is a dimension between the bottom center portion of the notch 45 and one opening edge 50 of the track groove 25B opposite to the track groove 25A by 180 degrees.

  For this reason, when the inlay diameter of the cage 28 is A, the rotational radius of the inner ring 26 is B, and the product of the present invention is C, B> C, and therefore A−B <A−C. Thereby, the inlay diameter A of the product of the present invention can be made smaller than that of the conventional product, and the thickness of the thin side frame portion 48 can be increased.

  After the inner ring 26 is fitted in the cage 28, the inner ring 26 is rotated 90 ° with respect to the cage 28, and the axis of the inner ring 26 is aligned with the axis of the cage 28 and placed in a normal posture. As a result, the inner ring 26 can be incorporated into the cage 28.

  Since the notch 45 is provided at the inner end of the track groove 25, the inner ring 26 can be rotated with the notch 45 as a starting point when assembled in the cage 28, and the radius of rotation of the inner ring 26 can be reduced. Can do. Therefore, a larger space can be ensured between the inner diameter of the cage 28 and the inner ring 26, and accordingly, the inner diameter A of the cage 28 can be set smaller. As a result, the cross-sectional area on the inlay side of the cage 28 can be increased, the rigidity of the thin side frame portion 48 of the cage 28 can be improved, and a spherical contact area can be ensured. An increase in surface pressure can be prevented, heat generation and a decrease in durability can be avoided, and further, deformation of the cage 28 and a decrease in strength can also be avoided. That is, the rigidity of the cage 28 can be improved without reducing the load capacity and the spherical surface area of the inner ring 26. Further, since the area of the inner spherical surface 28b of the cage 28 can be increased, the contact area of the inner ring 26 with the outer spherical surface 24 can be increased, and there is an advantage that the durability is stabilized in addition to the improvement in rigidity.

  The size of the notch 45 can be changed within a range in which the radius of rotation of the inner ring 26 when the inner ring 26 is assembled into the cage 28 can be reduced. However, if the size is too large, the inner ring 26 may have insufficient strength or the track groove 25 If the ball rolling range becomes small or is too small, the turning radius cannot be made too small.

  Next, in FIGS. 17 to 19, a notch 45 is formed at the end on the back side of all the track grooves 25. For this reason, even in the case of this inner ring 26, as in the case of the inner ring 26 shown in FIGS. 13 to 15, when the inner ring 26 is assembled, the inner ring 26 can be rotated with the notch 45 as a starting point. Can be reduced. For this reason, the inner ring 26 shown in FIGS. 17 to 19 has the same effect as the inner ring 26 shown in FIGS. 11 to 13.

  In particular, since the notch 45 is formed at the back end of all the track grooves 25, any protrusion 47 may be inserted into the window 30 when the inner ring 26 is assembled in the cage 28. For this reason, there exists an advantage which can aim at the improvement of an incorporating property.

  By the way, in each said embodiment, although the notch part 45 was formed in the taper surface which diameter-reduces sequentially toward the inner ring end surface 46 side from the opening side track groove 25b side, as the notch part 45, FIG. ) The shape shown in (b) may be used. The cutout 45 shown in FIG. 20A has a concave round shape, and the cutout 45 shown in FIG. 20B has a convex round shape.

  Even when the cutout 45 shown in FIGS. 20A and 20B is incorporated, the inner ring 26 can be rotated with the cutout 45 as a starting point, and the rotation radius of the inner ring 26 can be reduced. it can. Further, as shown in FIGS. 21A and 21B, the notch 45 may be formed at a part of the track groove end (the bottom in the example).

  Although not shown, the notch 45 may be formed of a stepped portion or the like other than those shown in FIGS. 13 to 15 or 20 (a) and 20 (b). Even the cutout 45 such as the stepped portion exhibits the function as the cutout 45.

  Next, FIG. 22 shows another embodiment. In this case, the track groove bottoms of the inner ring 26 and the outer ring 23 are provided with an arc portion and a tapered portion. In other words, the track groove bottom 22c includes an inner side track groove 22c having a circular arc portion as a track groove bottom, and an opening side track groove 22d in which the track groove bottom is inclined from the back side toward the opening side toward the outer diameter side. The back side track groove 22c has its curvature center O1 shifted from the joint center O in the axial direction toward the opening side of the outer ring 23. The track groove 25 of the inner ring 26 includes a back side track groove 25c in which the track groove bottom is inclined from the opening side toward the back side toward the outer diameter side, and an opening side track groove 25d in which the track groove bottom is an arc portion. Become. The center of curvature O2 of the opening side track groove 25b is provided at an equal distance k away from the joint center O in the axial direction on the far side opposite to the center of curvature O1 of the back side track groove 22a of the outer ring 23.

  Also in this case, the center of curvature O3 of the outer spherical surface 28a of the cage 28 and the center of curvature O4 of the inner spherical surface 28b of the cage 28 are offset in the axial direction by an equal distance with respect to the joint center O. The offset amount k is substantially the same as the offset amount k2 of the track grooves 22 and 25.

  Other configurations of the fixed type constant velocity universal joint shown in FIG. 22 are the same as those of the fixed type constant velocity universal joint shown in FIG. 1, and the same members as those in FIG. .

  For this reason, the fixed type constant velocity universal joint shown in FIG. 22 has the same effects as the fixed type constant velocity universal joint shown in FIG. In FIG. 1, the joint operating angle can be increased by adopting an undercut free type in which the track groove bottoms of the inner ring 26 and the outer ring 23 are provided with arc portions and straight portions. On the other hand, if the track groove bottom has an arc portion and a taper portion as in the fixed type constant velocity universal joint shown in FIG. 22, the angle can be further increased.

  As described above, the embodiment of the present invention has been described. However, the present invention is not limited to the above-described embodiment, and various modifications are possible. For example, in the embodiment, the curvature center O1 and the curvature center O3 are slightly different. Although the center of curvature O2 and the center of curvature O4 are disposed at positions slightly deviated from each other, the center of curvature O2 is provided even if the center of curvature O1 and the center of curvature O3 are the same position. And the center of curvature O4 may be at the same position. Further, when the curvature center O1 and the curvature center O3 are shifted, or when the curvature center O2 and the curvature center O4 are shifted, the shift amount can be arbitrarily set, but the offset amount k and the shift amount (k−k2). Is preferably set as (k−k2) /k≦0.3. When (k−k2) / k> 0.3, there is no difference from the conventional fixed type constant velocity universal joint shown in FIG. 23, the depth of the track groove on the inner side of the joint becomes shallower, and the cage 28 on the opening side becomes smaller. It becomes impossible to increase the wall thickness of the joint, which is less than the required strength of the joint.

  Further, the circumferential interval h of the long window portion 30 can be variously set within the range in which the ease of assembling the cage 28 into the inner ring 26 can be improved and the rigidity of the column portion 33 is not lowered. Further, the shoulder width dimension f between the track grooves, the window width g of the cage 28 in the cage axial direction, and the like can be set in consideration of the ease of assembling the cage 28 into the outer ring 23. The protruding end surface 36a of the bulging portion 36 may be a curved surface without being a flat surface.

  In the fixed type constant velocity universal joint shown in FIG. 22, a cage 28 having a long window portion 30 as shown in FIGS. 9 to 12 may be used. Moreover, you may use the inner ring | wheel 26 which has the notch part 45 as shown to FIG. 13 and FIG.

  As shown in FIG. 5 and the like, when the track grooves 25 of the inner ring 26 and the track grooves 22 of the outer ring 23 are arranged at unequal pitches in the circumferential direction, the balls 27 are arranged at unequal pitches in the circumferential direction. It will be. For this reason, in the said embodiment, the two balls arrange | positioned at less than 60 degrees were accommodated in the one long window part 30. FIG. In other words, the shape is such that the column portion between two balls disposed at less than 60 ° is omitted. On the other hand, this pillar part may not be omitted. In this case, as shown in FIG. 1, six pillar parts are formed, and the strength of the entire cage is improved. Increases rigidity.

  The fixed type constant velocity universal joint according to the present invention may be a bar field type (BJ) in which only an arc portion is formed on the track groove bottom.

It is a longitudinal cross-sectional view of the fixed type constant velocity universal joint which shows embodiment of this invention. It is a cross-sectional view of the fixed type constant velocity universal joint. It is a cross-sectional view of the fixed type constant velocity universal joint. It is a longitudinal cross-sectional view of the said fixed type constant velocity universal joint. It is a cross-sectional view of the fixed type constant velocity universal joint which shows other embodiment of this invention. It is a front view which shows the relationship between the outer ring | wheel of the fixed type constant velocity universal joint shown in FIG. 5, and a cage. It is a side view which shows the relationship between the inner ring | wheel of a fixed type constant velocity universal joint shown in FIG. 5, and a cage. FIG. 6 is a side view showing an assembled state of the inner ring in the cage of the fixed type constant velocity universal joint shown in FIG. 5. It is sectional drawing of the inner ring | wheel of the said fixed type constant velocity universal joint. The cage is shown, (a) is a side view of the cage of the fixed type constant velocity universal joint of FIG. 5, (b) is a side view showing a first modification, (c) is a second modification. It is a side view which shows an example, (d) It is a side view which shows a 3rd modification. The cage is shown, (a) is a side view showing a fourth modification, and (b) is a side view showing a fifth modification. It is a side view which shows the 6th modification of a cage. It is a perspective view which shows the 6th modification of a cage. It is a perspective view which shows the modification of an inner ring | wheel. It is a front view of the inner ring | wheel shown in the said FIG. It is sectional drawing of the inner ring | wheel shown in the said FIG. FIG. 14 is a cross-sectional view showing a method of incorporating the cage into the cage using the inner ring shown in FIG. 13. It is a perspective view which shows the other modification of an inner ring | wheel. FIG. 18 is a front view of the inner ring shown in FIG. 17. It is sectional drawing of the inner ring | wheel shown in the said FIG. The notch part in which an inner ring | wheel is formed is shown, (a) is an expanded sectional view which shows a 1st modification, (b) is an expanded sectional view which shows a 2nd modification. The notch part in which an inner ring | wheel is formed is shown, (a) is a front view of a 3rd modification, (b) is sectional drawing of a 3rd modification. It is a longitudinal cross-sectional view of the fixed type constant velocity universal joint which shows another embodiment of this invention. It is a longitudinal cross-sectional view of the conventional fixed type constant velocity universal joint. It is a cross-sectional view of a conventional fixed type constant velocity universal joint.

Explanation of symbols

21 inner spherical surface 22 track groove 24 outer spherical surface 25 track groove 27 ball 28 cage 28a outer spherical surface 28b inner spherical surface 29 window portion 30 long window portion 31 short window portion 36 bulging portion 45 notched portion

Claims (11)

An outer member having a plurality of track grooves formed on the inner spherical surface, an inner member having a plurality of track grooves formed on the outer spherical surface, and between the track grooves of the outer member and the track grooves of the inner member. In a fixed type constant velocity universal joint including a plurality of balls interposed to transmit torque, and a cage having a window portion for accommodating the balls and interposed between an outer member and an inner member,
The number of balls is 6, the cage thickness at the center of the cage window is t _CAGE, and the pitch circle radius of the balls when the operating angle is 0 ° is PCR _BALL. A fixed type constant velocity universal joint characterized in that t _CAGE / PCR _{BALL is set} to 0.20 or more and 0.23 or less. The pitch circle diameter of the ball is PCD _BALL , the ball diameter is D _BALL , and the ratio PCD _BALL / D _{BALL is set} to 3.0 or more and 3.3 or less. Fixed constant velocity universal joint. The outer diameter of the outer member is D _OUTER , the ball diameter is D _BALL , and the ratio D _OUTER / D _BALL is 4.6 or more and 4.8 or less. Item 3. A fixed type constant velocity universal joint according to item 2.   The center of curvature of the track groove of the outer member and the center of curvature of the track groove of the inner member are offset in the axial direction by an equal distance from the joint center, and the center of curvature of the outer spherical surface of the cage and the cage A straight line connecting the center of curvature of the outer spherical surface of the cage and the center of the ball when the working angle is 0 °, offset from the center of curvature of the inner spherical surface by an equal distance from the joint center in the axial direction. The angle formed by the straight line connecting the joint center and the ball center, and the angle formed by the straight line connecting the center of curvature of the inner spherical surface of the cage and the ball center, and the straight line connecting the joint center and the ball center, respectively. The fixed constant velocity universal joint according to any one of claims 1 to 3, wherein the fixed constant velocity universal joint is set to 2.7 ° or more and 5.7 ° or less.   The fixed type constant velocity universal joint according to any one of claims 1 to 4, wherein the offset amount of the cage is increased to be substantially the same as the offset amount of the track groove.   The track grooves of the inner member and the track grooves of the outer member are arranged at unequal pitches in the circumferential direction, and the smallest of the plurality of inner spherical surfaces arranged between the track grooves of the outer member The circumferential length of the opening side end portion of the inner spherical surface disposed in the pitch is set to be smaller than the width of the window portion of the cage. Fixed constant velocity universal joint as described.   Of the pitches between the track grooves of the inner and outer joint members, the phases of two pitches positioned symmetrically with respect to the joint center are set smaller than 60 °, and the phases of the remaining four pitches are larger than 60 °. And the circumferential length of the opening side end of the inner spherical surface of the outer joint member disposed within the phase pitch smaller than 60 ° is set to be smaller than the width of the cage window. The fixed type constant velocity universal joint according to any one of claims 1 to 6.   The cage pillars disposed within the phase pitch smaller than 60 ° are removed to form a long window portion capable of holding the two torque transmitting balls in the cage, and the long window portion The fixed constant velocity universal joint according to claim 7, wherein a circumferential length is set larger than a width of the inner joint member.   A part of the cage pillar portion disposed within the phase pitch smaller than 60 ° is removed to form a long window portion capable of holding the two torque transmitting balls in the cage, and the length The fixed constant velocity universal joint according to claim 7, wherein a circumferential length of the window portion is set larger than a width of the inner joint member.   10. The fixed type constant velocity universal joint according to claim 8, wherein a column portion of the cage disposed in a pitch having a phase smaller than 60 ° is removed by pressing. 11.   10. The fixed type constant velocity universal joint according to claim 8, wherein a pillar portion of the cage disposed in a pitch having a phase smaller than 60 ° is removed by milling. 11.

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