JP4519686B2 - Sliding constant velocity universal joint - Google Patents

Description

  The present invention is used, for example, in a power transmission mechanism of an automobile or various industrial machines, and is a ball type sliding type constant velocity freely allowing axial displacement and angular displacement between two axes of a driving side and a driven side. Related to fittings.

  Constant velocity universal joints are used to transmit torque at a constant angular speed by connecting a drive-side rotating shaft and a driven-side rotating shaft in power transmission systems of automobiles and various industrial machines. . The fixed type allows only angular displacement, whereas the sliding type allows both angular displacement and axial displacement.

  A double offset type constant velocity universal joint (hereinafter referred to as DOJ) is well known as a ball-type sliding constant velocity universal joint using a ball as a torque transmission element. The DOJ typically has six or eight torque transmitting balls (hereinafter simply referred to as balls), and the circumferential arrangement (pitch) of the balls is six equal pitches (60 °) or Eight pitches (45 °) are normal.

  15 and 16 show a six-ball DOJ. The DOJ has an outer ring 1, an inner ring 2, a ball 3 and a cage 4 as main components. As shown in the figure, the balls are arranged at an equal pitch of 60 °. The outer ring 1, the inner ring 2 and the cage 4 which are the components of the DOJ other than the ball, and the track grooves 5 and 6 formed in the outer ring 1 and the inner ring 2 and the pocket 7 provided in the cage 4 are also described above. The balls 3 are arranged at an equal pitch according to the arrangement of the balls 3. Further, also in the cage 4, the pocket length and the column width between the pockets are the same.

On the other hand, the outer ring 1 in this constant velocity universal joint has various types according to the form of attachment to the vehicle body, and the one shown in the figure is a flange type. This type of outer ring 1 has a plurality of vehicle body mounting flanges 8 integrally projecting at equal intervals in the circumferential direction at the outer diameter end portion, and using bolt holes 9 penetrating each vehicle body mounting flange 8. It is attached to the car body by bolting. In the constant velocity universal joint, for the purpose of light weight and compactness in recent years, a shape in which the outer diameter shape of the outer ring 1 is formed into a flower shape along the inner diameter shape is used (for example, see Patent Document 1).
JP-A-5-231436 Japanese Patent Publication No. 1-50767

  In the conventional DOJ (number of balls: 6) shown in FIGS. 15 and 16, the circumferential arrangement of the balls 3, the track grooves 6, 5 of the inner and outer rings 2, 1 and the pockets 7 of the cage 4 is equal to six pitches ( 60 °). In this type of constant velocity universal joint, a thrust force is induced in the axial direction of the constant velocity universal joint (induced thrust force) when rotating with torque applied, that is, during power transmission. This induced thrust force involves the same number of fluctuations as the number of track grooves 5 and 6 during one rotation. In the conventional DOJ, since the track grooves 5 and 6 are equally distributed at 60 °, it has a rotation sixth-order frequency, which resonates with the natural frequency around the undercarriage of the vehicle, and unpleasant vibrations and noise. May occur.

  On the other hand, in the constant velocity universal joint having this flange type outer ring 1, as described above, a plurality of vehicle body mounting flanges 8 are provided projecting radially outward from the outer diameter of the outer ring 1, and bolt holes of each vehicle body mounting flange 8 are provided. A bolt is inserted into 9 and attached to the vehicle body.

  In the mounting of the outer ring 1 by bolt tightening, as shown in FIGS. 15 and 16, for example, a tightening jig m such as a socket is used. Therefore, a space a in which the jig m can be inserted between the outer diameter of the outer ring 1 is provided. It must be provided. For this reason, considering the attachment with the jig m, the outer diameter of the vehicle body mounting flange 8 is increased due to the necessity to provide a space a between the outer ring 1 and the bolt hole 9 in the vehicle body mounting flange 8. There was a problem that the weight of the joint also increased.

  Therefore, the present invention has been proposed in view of this problem, and the object of the present invention is to suppress the generation of unpleasant vibrations and booming noise caused by the induced thrust force and to reduce the outer diameter of the outer ring by simple means. It is an object of the present invention to provide a sliding type constant velocity universal joint that can be easily made lighter and more compact by making it smaller.

  In order to achieve the above object, the present invention has the following constituent elements.

The present invention provides an outer ring in which a plurality of track grooves extending in the axial direction are formed on a cylindrical inner peripheral surface, and a plurality of wheel mounting flanges projecting in a radial direction along the circumferential direction at an outer diameter end, and a spherical surface An inner ring formed with a plurality of axially extending track grooves on the outer peripheral surface of the ring, n balls each incorporated in a ball track formed by a pair of an outer ring track groove and an inner ring track groove, and holding the ball the pocket possess, and a cage spherical outer circumferential surface is against the cylindrical inner peripheral surface of the outer ring, the center of a spherical inner circumferential surface of the spherical outer peripheral surface of the cage, across the joint center In a constant velocity universal joint that is offset by an equal distance in the opposite direction in the axial direction, the outer diameter shape of the outer ring is formed into a flower shape along the inner diameter shape, and in the outer diameter recess located between the track grooves of the outer ring. forming a body mounting flange and torque rotation Characterized by comprising one of the following configurations (1) (2) as a means of reducing induced thrust of the n-th order components generated.

  First, in the present invention, since the outer diameter shape of the outer ring is formed into a flower shape along the inner diameter shape, it is possible to reduce the weight while maintaining the current load capacity of the constant velocity universal joint. By providing the body mounting flange in the outer diameter recess located between the track grooves in the flower shaped outer ring, the outer diameter of the body mounting flange can be reduced, and the constant velocity universal joint can be made compact. it can.

In the present invention, by provided with the configuration of any one of the following (1) (2) as a means of reducing induced thrust of the n-order component generated at the time of torque rotation, if the ball is n pieces, the induced The n-th order component of thrust can be reduced. For example, when there are six balls, the sixth-order component of induced thrust can be reduced. In order to reduce the sixth-order component of the induced thrust force in a six-ball DOJ, the circumferential arrangement of the ball tracks may be set at unequal pitches (see Patent Document 2). The present invention provides another means for reducing the n-th order component of the induced thrust, and includes any one of the following configurations (1) and (2) .

  (1) First of all, the circumferential arrangement of the ball tracks is set to an equal pitch, and the width of the pillar portion located between the pockets of the cage is made non-uniform at least at one or more places. In this way, with the circumferential arrangement of the ball tracks kept at an equal pitch, the width of the pillars located between the pockets of the cage is made non-uniform at least at one or more locations, so that the outer ring can be rotated when torque is applied. The nth-order component of the induced thrust force can be reduced by making the frictional force between the cage and the cage irregular.

  (2) Secondly, the circumferential arrangement of the ball tracks is set to an equal pitch, the width of the inner diameter portion located between the track grooves of the outer ring is made uneven at least in one place, and between the cage pockets. This is to make the width of the pillars located uniform. In this way, with the circumferential arrangement of the ball tracks kept at an equal pitch, the width of the inner diameter portion located between the track grooves of the outer ring is made uneven at least at one place, and the pillar portion located between the pockets of the cage Since the width of the outer ring is uniform, the contact area between the inner peripheral surface of the outer ring and the outer peripheral surface of the cage is not the same as in the case where the width of the pocket column portion of the cage is non-uniform as described in the previous section (1). Since it becomes uniform and the fluctuation component of the frictional force generated in each phase becomes nonuniform, the n-th order component of the induced thrust force can be reduced.

  In the DOJ having the structure of any one of (1) and (2) described above, the inner peripheral surface of the cage is located at a position shifted in the radial direction from the center of curvature of the outer peripheral surface of the inner ring when viewed in a cross section including the axis of the joint. A structure having a center of curvature and a radius of curvature larger than the radius of curvature of the outer circumferential surface of the inner ring, or the inner circumferential surface of the cage is located on both sides of the cylindrical surface over an arbitrary axial dimension in the center. It is desirable to use one of the structures formed by connecting the outer peripheral surface of the inner ring and the partial spherical surface having the same curvature radius.

  By adopting either structure, an axial clearance is formed between the inner ring and the cage, and the sliding resistance inside the joint becomes very small. Therefore, when this constant velocity universal joint is used for a drive axle of an automobile, even if vibration from the engine side acts with a relatively small torque applied, such as when idling in an automatic transmission vehicle, the vibration Is absorbed and transmission to the vehicle body is cut off, so that vibration of the vehicle body can be suppressed.

  According to the present invention, since the outer ring shape of the outer ring is formed into a flower shape along the inner diameter shape, it is possible to reduce the weight while maintaining the current capacity of the constant velocity universal joint. By providing the body mounting flange in the outer diameter recess located between the track grooves in the flower shaped outer ring, the outer diameter of the body mounting flange can be reduced, and the constant velocity universal joint can be made compact. it can.

In addition, since any one of the above-described configurations (1) and (2) is provided as means for reducing the n-th order component of the induced thrust generated during torque rotation, the n-th order component of the induced thrust force can be reduced. It is possible to suppress the vibration and the booming noise of the vehicle, prevent transmission of vibration to the vehicle interior, and ensure quietness in the vehicle interior.

  As described above, it is possible to easily realize light weight and compactness by suppressing the generation of unpleasant vibrations and booming noise caused by the induced thrust force and reducing the outer ring outer diameter by a simple means.

  1 and 2 show an overall configuration of a six-ball DOJ as one embodiment of the present invention, FIG. 3 shows an inner ring of FIG. 2, and FIG. 4 shows a cage of FIG.

  The DOJ has an outer ring 10, an inner ring 20, a ball 30 and a cage 40 as main components. The outer ring 10 has a cup shape opened at one end, and has a shaft portion 16 coupled to the rotating shaft on the opposite side of the open end (see FIG. 1). The inner peripheral surface 12 of the outer ring 10 is cylindrical, and six track grooves 14 extending in the axial direction are formed on the cylindrical inner peripheral surface 12 (see FIG. 2). The inner ring 20 has a spherical outer peripheral surface 22, and six track grooves 24 extending in the axial direction are formed on the spherical outer peripheral surface 22 (see FIG. 3). The inner ring 20 has a serration hole 26 for coupling with the rotating shaft.

  The track groove 14 of the outer ring 10 and the track groove 24 of the inner ring 20 make a pair to form a ball track, and one ball 30 is incorporated in each ball track. The ball 30 is interposed between the outer ring 10 and the inner ring 20 and plays a role of transmitting torque. Each ball 30 is held in a pocket 46 formed in the circumferential direction of the cage 40. The cage 40 is in contact with the cylindrical inner peripheral surface 12 of the outer ring 10 at the outer peripheral surface 42, and is in contact with the spherical outer peripheral surface 22 of the inner ring 20 at the inner peripheral surface 44.

  Further, the center Oo of the outer peripheral surface 42 of the cage 40 and the center Oi of the inner peripheral surface 44 are offset by an equal distance on the opposite sides in the axial direction across the joint center O (see FIG. 1). Therefore, when torque is transmitted with the joint at an operating angle, the ball 30 is always located in a plane that bisects the angle formed by the rotation axis of the outer ring 10 and the rotation axis of the inner ring 20. This ensures the constant velocity of the joint.

In this embodiment, as shown in FIGS. 2 and 4, the circumferential arrangement of the ball tracks is set to an equal pitch α ₀ , and the width of the column part 47 located between the pockets 46 of the cage 40 is at least one or more. Non-uniform. In this embodiment, the track grooves 24 of the track grooves 14 and the inner ring 20 of the outer ring 10 as shown in FIG. 2 are arranged in the circumferential direction at an equal pitch alpha _0, the pockets 46 of the cage 40 as shown in FIG. 4 is equal It is arranged in the circumferential direction at a pitch α ₀ , and the width W ₂ of the two column portions 47 of the cage 40 is made different from the width W ₁ of the other column portions 47 to make it non-uniform (W ₁ ≠ W ₂ ).

  The induced thrust force that is generated when the DOJ is rotated by being loaded with torque is caused by a frictional force generated between internal components. When the induced thrust generated in the outer ring 10 is taken into consideration, the frictional force between the track groove 14 of the outer ring 10 and the ball 30 and the frictional force between the inner peripheral surface 12 of the outer ring 10 and the outer peripheral surface 42 of the gauge 40 can be cited as generation factors. .

In the above-described embodiment, by a non-uniform by varying the width W ₂ of the two pillar portions 47 of the cage 40 and the width W ₁ of the other bar portion 47, the inner circumferential surface 12 of the outer ring 10 and the cage 40 The contact area with the outer peripheral surface 42 becomes non-uniform, and the fluctuation component of the frictional force generated in each phase also becomes non-uniform. Here, in the induced thrust, which is a composition of the frictional force of each phase (six), the sixth-order component becomes prominent when the fluctuation of the frictional force for each phase draws the same waveform. In this embodiment, since the fluctuation component of the frictional force generated in each phase is also non-uniform, the sixth-order component of the induced thrust force can be reduced.

  FIG. 5 shows the measurement results of the induced thrust force performed on the conventional product with the six-ball DOJ and the product of the present invention. In these drawings, the operating angle (0 ° to 15 °) is plotted on the horizontal axis, the induced thrust (N) is plotted on the vertical axis, and the measured values for the conventional product and the solid line for the actual product are plotted. It is clear that the practical product has a sufficient effect of reducing the sixth component of the induced thrust force.

  Next, the embodiment shown in FIGS. 6 and 7 will be described. 6 shows the overall configuration of the six-ball DOJ, and FIG. 7 shows the outer ring 10 of FIG. Since the basic configuration of the DOJ is the same as that of the embodiment shown in FIGS. 1 to 4 described above, substantially the same components or parts are denoted by the same reference numerals.

In the embodiment shown in FIGS. 6 and 7, the circumferential arrangement of the ball tracks is made equal pitch α _0, and the width of the inner diameter portion 17 located between the track grooves 14 of the outer ring 10 is non-uniform at least at one or more places. And the width W ₀ of the pillar portion 47 located between the pockets 46 of the cage 40 is made uniform. In this embodiment, the track grooves 24 of the track grooves 14 and the inner ring 20 of the outer ring 10 as shown in FIG. 6 are arranged in the circumferential direction at an equal pitch alpha _0, the pockets 46 of the cage 40 as shown in FIG. 7 etc. The width L ₁ of the two inner diameter portions 17 arranged in the circumferential direction at the pitch α ₀ and located between the track grooves 14 of the outer ring 10 is made non-uniform by making it different from the width L ₂ of the other inner diameter portions 17 ( L ₁ ≠ L ₂ ). In this case, the width W ₀ of the column portion 47 of the cage 40 is uniform.

In this way, the width L ₁ of the two inner diameter portions 17 of the outer ring 10 is made different from the width L ₂ of the other inner diameter portions 17 to make it non-uniform, thereby making the width of the column portion 47 of the cage 40 non-uniform. As in the case of the embodiment, the contact area between the inner peripheral surface 12 of the outer ring 10 and the outer peripheral surface 42 of the cage 40 becomes non-uniform, and the fluctuation component of the frictional force generated in each phase also becomes non-uniform. The sixth-order component of the induced thrust force can be reduced.

  In the embodiment shown in FIG. 8 and FIG. 9, the inner ring 20 and the cage 40 can be moved relative to each other in the axial direction, and the ball 30 is released to make it easier to roll. This embodiment can be applied to the above-described embodiments shown in FIGS.

In the embodiment of FIG. 8, the curvature radius r of the outer peripheral surface 22 of the inner ring 20 is set smaller than the curvature radius R of the inner peripheral surface 44 of the cage 40, and the curvature center Oa of the outer peripheral surface 22 of the inner ring 20 and the cage 40 are set. The center of curvature Ob of the inner peripheral surface 44 is shifted in the radial direction. As a result, axial clearances δ ₁ and δ ₁ ′ are formed between the outer peripheral surface 22 of the inner ring 20 and the inner peripheral surface 44 of the cage 40, and due to the presence of these clearances δ ₁ and δ ₁ ′, the inner ring 20 with respect to the cage 40 is formed. Axial displacement is possible.

In the embodiment shown in FIG. 9, the inner peripheral surface 44 of the cage 40 is formed by connecting a cylindrical surface 44a having a diameter D over the axial dimension P of the central portion and partial spherical surfaces 44b on both sides thereof. is there. The radius of curvature R of the partial spherical surface 44b is equal to the radius of curvature r of the outer peripheral surface 22 of the inner ring 20, and the clearances δ ₂ and δ ₂ 'between the outer peripheral surface 22 of the inner ring 20 and the inner peripheral surfaces (44a, 44b) of the cage 40 are as follows. Is formed.

In the embodiment shown in FIGS. 8 and 9, the circumferential arrangement of the ball tracks is made equal pitch α _0, and the width of the pillar portion 47 located between the pockets 46 of the cage 40 is non-uniform at least at one place. Alternatively, the width of the inner diameter portion 17 located between the track grooves 14 of the outer ring 10 is made non-uniform at least at one place, and the width W ₀ of the column portion 47 located between the pockets 46 of the cage 40 is By making it uniform, the effect of reducing the sixth-order component equivalent to that of the above-described embodiment was obtained for the measurement result of the induced thrust force (see FIG. 5).

Furthermore, in these embodiments, the inner ring 20 and the cage 40 can be relatively moved in the axial direction by the clearances δ ₁ , δ ₁ ′ or δ ₂ , δ ₂ ′, and the ball 30 is restrained by the pocket 46 of the cage 40. Since it is easy to roll without sliding, the slide resistance against the axial relative movement of the outer ring 10 and the inner ring 20 is very small. Therefore, when vibration from the engine is applied with torque applied, the vibration is absorbed by the smooth relative motion between the outer ring 10 and the inner ring 20 via the cage 40, and vibration transmission to the vehicle interior is prevented. The

  The outer ring 10 in this constant velocity universal joint is of a flange type because of its attachment to the vehicle body. The flange-type outer ring 10 uses a plurality of vehicle body mounting flanges 18 integrally provided at the outer diameter end portion at equal intervals in the circumferential direction, and bolt holes 19 penetrating the vehicle body mounting flanges 18. It is attached to the vehicle body by inserting and tightening the bolts.

  The outer ring 10 is shaped into a flower shape along the inner diameter (track groove) shape for the purpose of light weight and compactness. Here, the “flower shape” means a shape in which a recess 15 along the track groove 14 is formed in a portion located between the track grooves 14 formed on the inner diameter on the outer diameter surface of the outer ring 10. A vehicle body mounting flange 18 is provided in an outer diameter recess 15 located between the track grooves 14 of the outer ring 10.

  Since the outer diameter shape of the outer ring 10 is formed into a flower shape along the inner diameter shape in this way, it is possible to reduce the weight while maintaining the current load capacity of the constant velocity universal joint. By providing the vehicle body mounting flange 18 in the outer diameter recess 15 located between the track grooves 14 in the outer ring 10, the outer diameter of the vehicle body mounting flange 18 can be reduced, and the constant velocity universal joint can be made compact. Can be planned.

  FIG. 10 compares the size of the outer ring 1 of the conventional product and the outer ring 10 of the product of the present invention. FIG. 10A shows the conventional product on the left side and the implemented product on the right side with the XX line as a boundary. FIG. 4B shows the conventional product on the upper side and the implemented product on the lower side with the YY line as a boundary.

  The conventional product and the actual product are compared when the load capacity (size) of the constant velocity universal joint and the space a for inserting the tool are the same. In comparison of the outer diameter dimensions of the body mounting flanges 8 and 18, The actual product can be reduced in size by about 10% compared to the conventional product, and the weight of the actual product can be reduced by about 20% compared to the conventional product in the weight comparison.

  Here, the outer ring 10 which is an implemented product is formed into a flower shape as an advantageous shape for weight reduction, but the thickness is limited from the viewpoint of securing strength. In other words, in order to satisfy the strength required as a constant velocity universal joint while reducing the weight by the flower shape, the thickness of the track groove portion as well as the thickness of the track groove portion is important.

  Therefore, as shown in FIG. 11, the ratio DN / DT between the outermost diameter dimension DT where the track groove 14 is located and the smallest diameter dimension DN where the vehicle body mounting flange 18 is located between the track grooves 14 is 0.85 to 0.95. Must be set to By defining the ratio between the outermost diameter dimension DT and the minimum diameter dimension DN within the above-described range, the strength of the outer ring 10 can be ensured together with the above-described weight reduction and compactness.

  Here, if the above-mentioned ratio DN / DT is smaller than 0.85, the thickness of the portion of the outer ring 10 where the vehicle body mounting flange 18 is located becomes too thin, and the strength required for the constant velocity universal joint can be ensured. It becomes difficult. Further, if the ratio DN / DT is larger than 0.95, the outer diameter of the vehicle body mounting flange 18 becomes too large, and it is difficult to reduce the weight and size.

  The number of the vehicle body mounting flanges 18 can be arbitrarily set with respect to the number of the track grooves 14 (balls 30) of the outer ring 10 described above. That is, as shown in FIG. 2 and FIG. 6, in addition to providing the vehicle body mounting flanges 18 in all the outer diameter recesses 15 located between the track grooves 14 for all the track grooves 14 in the outer ring 10, It is also possible to provide the vehicle body mounting flange 18 only in the outer diameter recess 15. For example, as shown in FIG. 12, it is possible to provide vehicle body mounting flanges 18 at three outer diameter recesses 15 arranged at equal intervals in the circumferential direction of the outer ring 10.

  In the above description, a constant velocity universal joint incorporating six balls 30 has been illustrated, but the present invention can be applied to a constant velocity universal joint incorporating eight balls 30. When eight balls 30 are used, the ball PCD is made smaller and more compact than the six-ball constant velocity universal joint. Also in this case, as shown in FIG. 13, vehicle body mounting flanges 18 are provided in all eight outer diameter recesses 15, or four places arranged at equal intervals in the circumferential direction of the outer ring 10 as shown in FIG. It is also possible to provide a vehicle body mounting flange 18 in the outer diameter recess 15.

In the embodiment of the DOJ according to the present invention, FIG. It is a right view which shows DOJ of FIG. It is a side view which shows the inner ring | wheel in DOJ of FIG. In one embodiment of the present invention, it is a sectional view of a cage in the DOJ. It is a graph which shows the measurement result of the 6th-order component of induced thrust. It is a side view which shows DOJ in other embodiment of this invention. It is a side view which shows the outer ring | wheel in DOJ of FIG. It is an expanded sectional view showing an inner ring and a cage in other embodiments of the present invention. It is an expanded sectional view showing an inner ring and a cage in other embodiments of the present invention. It is for comparing the size of the outer ring in the conventional product and the actual product. (A) is a side view of the conventional product on the left side of the XX line and the practical product on the right side. (B) is the YY line. It is sectional drawing which has arrange | positioned the conventional goods to the upper side of this, and the implementation goods to the lower side. It is a side view which shows the outer ring | wheel of the implementation goods of FIG. It is a side view which shows 6-ball DOJ which has three vehicle body attachment flanges in other embodiment of this invention. FIG. 6 is a side view showing an 8-ball DOJ having 8 body mounting flanges according to another embodiment of the present invention. FIG. 6 is a side view showing an 8-ball DOJ having four body mounting flanges according to another embodiment of the present invention. It is sectional drawing which shows the conventional DOJ. FIG. 16 is a side view of FIG. 15.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Outer ring 12 Cylindrical inner peripheral surface 14 Track groove 15 Outer diameter recess 17 Inner diameter part 18 Wheel mounting flange 20 Inner ring 22 Spherical outer peripheral surface 24 Track groove 30 Torque transmission ball 40 Cage 42 Spherical outer peripheral surface 44 Spherical inner peripheral surface 46 Pocket 47 Column O Joint center Oo Center of spherical outer peripheral surface of cage Oi Center of spherical inner peripheral surface of cage α ₀ Equal pitch L ₁ , L ₂ Width of inner diameter of outer ring W ₁ , W ₂ Cylinder Width of part

Claims (5)

A plurality of track grooves extending in the axial direction are formed on the cylindrical inner peripheral surface, and an outer ring having a plurality of wheel mounting flanges projecting radially along the circumferential direction at the outer diameter end portion, and a spherical outer peripheral surface. An inner ring having a plurality of track grooves extending in the axial direction, n torque transmission balls each incorporated in a ball track formed by a pair of a track groove of the outer ring and a track groove of the inner ring, and the torque transmission have a pocket for holding the balls, and a cage spherical outer circumferential surface is against the cylindrical inner peripheral surface of the outer ring, the center of a spherical inner circumferential surface of the spherical outer peripheral surface of the cage, the joint In a constant velocity universal joint that is offset by an equal distance in the opposite direction in the axial direction across the center, the outer ring shape of the outer ring is formed into a flower shape along the inner diameter shape, and located between the track grooves of the outer ring. Body mounting flange in outer diameter recess Forming a di, and while the equal pitch in the circumferential direction placement of the ball track, characterized in that the width of the pillar portion positioned between the cage pockets and uneven at least one place or more sliding Dynamic constant velocity universal joint. A plurality of track grooves extending in the axial direction are formed on the cylindrical inner peripheral surface, and an outer ring having a plurality of wheel mounting flanges projecting radially along the circumferential direction at the outer diameter end portion, and a spherical outer peripheral surface. An inner ring having a plurality of track grooves extending in the axial direction, n torque transmission balls each incorporated in a ball track formed by a pair of a track groove of the outer ring and a track groove of the inner ring, and the torque transmission have a pocket for holding the balls, and a cage spherical outer circumferential surface is against the cylindrical inner peripheral surface of the outer ring, the center of a spherical inner circumferential surface of the spherical outer peripheral surface of the cage, the joint In a constant velocity universal joint that is offset by an equal distance in the opposite direction in the axial direction across the center, the outer ring shape of the outer ring is formed into a flower shape along the inner diameter shape, and located between the track grooves of the outer ring. Body mounting flange in outer diameter recess Forming a di, and while the equal pitch in the circumferential direction placement of the ball tracks, the width of the inside diameter portion positioned between the track grooves of the outer ring uneven in at least one or more places, and, cage pockets A sliding type constant velocity universal joint characterized in that the width of the column portion located between them is uniform . When viewed in a cross section including the axis of the joint, the inner circumferential surface of the cage has a curvature center at a position shifted in the radial direction from the curvature center of the outer circumferential surface of the inner ring, and has a radius of curvature larger than the curvature radius of the outer circumferential surface of the inner ring. The sliding type constant velocity universal joint according to claim 1 or 2 , wherein the sliding type constant velocity universal joint is formed. The inner peripheral surface of the cage, and the cylindrical surface over any axial dimension of the central portion, according to claim 1 or 2 are connecting by forming an outer peripheral surface of the same radius of curvature of the partially spherical inner ring located on both sides The sliding constant velocity universal joint described in 1.   The sliding type constant velocity universal joint according to any one of claims 1 to 4, wherein the number n of the torque transmission balls is six.

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