JP2007078149A - High-angle fixed-type constant velocity universal joint - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a high-angle fixed-type constant velocity universal joint which is always the most suitable for high-angle usage, and can prevent the rotational backlash, improve the assembly characteristics, and reduce the manufacturing costs. <P>SOLUTION: The high-angle fixed-type constant velocity universal joint includes a pair of constant velocity universal joints 1A and 1B, and an intermediate shaft 2 to connect the universal joints 1A and 1B. The universal joints 1A and 1B are provided with an outer ring 5 forming a plurality of track groove 4 in a spherical inner surface 3, an inner ring 8 forming a plurality of track grooves 7 in a spherical inner surface 6, a ball 9 arranged in each of a plurality of the ball track grooves, and a retainer 10 arranged between the outer ring 5 and the inner ring 8 to retain the ball 9. Each inner ring 8 is inserted in both the ends of the intermediate shaft 2 to connect the universal joints 1A and 1B. An axial interval packing mechanism 60 is formed in each of the universal joint 1A and 1B. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a high angle fixed type constant velocity universal joint, and more particularly to a high angle fixed type constant velocity universal joint that can be used in a high angle and can be applied to a steering system of an automobile.

  Constant velocity universal joints are broadly classified into fixed types that allow only angular displacement between the input and output shafts, and sliding types that allow angular displacement and axial displacement. Each model is selected according to the application and usage conditions. The

  As a fixed type constant velocity universal joint, a Rzeppa type (hereinafter referred to as “BJ”) and an undercut free type (hereinafter referred to as “UJ”) are widely known.

  Both BJ and UJ have an outer ring having a plurality of curved track grooves on the inner periphery, an inner ring having a plurality of curved track grooves on the outer periphery, and a ball incorporated between the track grooves of the outer ring and the inner ring, It consists of a cage that holds the ball. The outer ring track center is offset from the spherical center of the outer ring inner circumference and the inner ring track center is offset from the spherical center of the inner ring outer circumference by an equal distance in the axial direction. The ball track constituted by the track groove and the track groove of the inner ring has a wedge shape that expands toward the back side or the opening side of the outer ring. In BJ, the entire area of each track groove is curved with the outer ring track center and the inner ring track center as the center. In UJ, one end of each track groove is straight in the axial direction.

  In these fixed type constant velocity universal joints, a gap exists between the outer ring track and the inner ring track because of functional and processing requirements. The clearance between the tracks is the amount of movement when either the inner ring or the outer ring is fixed in the neutral state of the joint and the other non-fixed member is moved in the radial direction or the axial direction. Depending on the direction, they are called radial gaps or axial gaps, respectively.

  The size of the gap between the tracks greatly affects the circumferential play (rotational backlash) between the inner ring and the outer ring (the larger the clearance between the tracks, the larger the rotational backlash). As described above, in the fixed type constant velocity universal joint, the gap between the tracks is indispensable, and therefore, the occurrence of rotation backlash exceeding a certain level is inevitable.

  By the way, there is a structure in which a unit body is formed by connecting the outer rings of two constant velocity universal joints, and this unit body is used for a steering device (steering system) of an automobile that is always used at a high angle. (Patent Document 1).

As shown in the figure, the one described in Patent Document 1 is configured such that the outer ring shaft of one constant velocity universal joint and the outer ring shaft of the other constant velocity universal joint are connected or integrally formed. ing.
German patent DE 4306121A1

  In the one described in Patent Document 1, a gap between tracks remains formed in each constant velocity universal joint, and the occurrence of rotational backlash cannot be avoided. For this reason, it is not suitable for a steering device that dislikes rotating backlash.

  Further, when connecting the outer ring, the outer ring of one constant velocity universal joint is provided with a shaft portion having a tip portion as a spline, and the cylindrical portion provided on the outer ring of the other constant velocity universal joint is provided with a spline. The splines are fitted to each other and fastened so that no looseness occurs in the fitting portion. For this reason, there are many processed parts and the number of parts, it is inferior to assembly workability | operativity, and it becomes high cost. Moreover, when it shape | molds integrally, since an outer ring | wheel shape becomes long in an axial direction, while being inferior to workability, it becomes high cost.

  The present invention was devised in view of such a situation, and the object thereof is to prevent rotating backlash and to improve the assemblability and to reduce the manufacturing cost. An object of the present invention is to provide a high-angle fixed type constant velocity universal joint that is optimal for high-angle use.

  The high-angle fixed type constant velocity universal joint according to the present invention includes a pair of constant velocity universal joints and an intermediate shaft connecting the pair of constant velocity universal joints. An outer ring having a plurality of track grooves formed on a spherical inner surface, an inner ring having a plurality of track grooves formed on a spherical outer surface, and a plurality of ball tracks formed by cooperation of a track groove of the outer ring and a track groove of the inner ring. A high-angle fixed type constant velocity universal joint equipped with a ball arranged in each and a retainer arranged between the outer ring and the inner ring to hold the ball, and each inner ring is fitted to both ends of the intermediate shaft The pair of constant velocity universal joints are connected to each other, and an axial gap filling mechanism between the ball and the ball track is formed in each constant velocity universal joint.

  Since a pair of constant velocity universal joints and an intermediate shaft connecting the pair of constant velocity universal joints are provided, a high angle (large angle) response is possible. In addition, since each of the constant velocity universal joints is provided with an axial gap filling mechanism between the ball and the ball track, a gap (axial gap) between the tracks via the ball can be filled. Moreover, a pair of constant velocity universal joints can be connected via an intermediate shaft without using a bolt member or the like.

  An axial gap filling mechanism between a ball and a ball track includes a pressing portion that causes an elastic pressing force to act in an axial direction, and a receiving portion that receives the pressing force from the pressing portion. One of them is provided at the end of the intermediate shaft, and the other is provided in the cage.

  The bearing device for stabilizing the posture can be provided in the central portion in the axial direction of the intermediate shaft, provided in the outer ring, or further provided in a shaft portion (stem portion) connected to the outer ring. Thereby, the outer ring | wheel etc. with respect to a shaft can maintain the stable attitude | position, and can take the stable operating angle.

  The track position phase and the inter-track pitch phase of the pair of constant velocity universal joints can be made to coincide with each other, or the deviation between them can be in the range of ± 20 °. Thereby, the maximum value of the hysteresis in the torque-torsion angle diagram of the joint can be reduced.

  The high-angle fixed type constant velocity universal joint configured as described above can be used in the steering system.

  The present invention can cope with a high angle (large angle) and can close a gap between tracks via a ball. As a result, it is possible to provide a high-angle fixed type constant velocity universal joint capable of handling a large angle without a so-called rotational direction backlash. That is, it is possible to prevent the occurrence of rotational backlash due to the clearance between the tracks, and to increase the operating angle, which is optimally adopted for an automobile steering device (steering system).

  In addition, since a pair of constant velocity universal joints can be connected via an intermediate shaft without using bolt members or the like, the assembly work can be simplified, and the number of parts is relatively small, and parts management is also possible. It becomes easy to do and can achieve cost reduction.

  A stable operating angle can be obtained by providing the bearing device for posture stabilization at the axial center of the intermediate shaft or the like. Thereby, transmission of a rotational force can be performed smoothly and it becomes a highly accurate rotational force transmission mechanism.

  In addition, by making the track position phase and the inter-track pitch phase of the pair of constant velocity universal joints coincide with each other, or making these deviations in a range of ± 20 °, the hysteresis of the joint torque-torsion angle diagram The maximum value can be reduced. As a result, it is possible to improve the maneuverability of the automobile using the high-angle fixed type constant velocity universal joint in the steering system.

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

  FIG. 1 is an overall view showing a first embodiment of a high angle fixed type constant velocity universal joint according to the present invention. This high angle fixed type constant velocity universal joint includes a pair of constant velocity universal joints 1A and 1B and an intermediate shaft 2 connecting the constant velocity universal joints 1A and 1B.

  Each constant velocity universal joint 1A, 1B includes an outer ring 5 in which a plurality of track grooves 4 are formed on the spherical inner surface 3, an inner ring 8 in which a plurality of track grooves 7 are formed on the spherical outer surface 6, and the track grooves 4 of the outer ring 5. And the track groove 7 of the inner ring 8 are provided with a ball 9 disposed in each of a plurality of ball tracks formed in cooperation with each other and a cage 10 in which a plurality of pockets 11 for holding the balls 9 are formed.

  That is, the track grooves 4 and 7 are linearly extending in the axial direction, and are arranged at an equal pitch along the circumferential direction (see FIG. 4). The cage 10 is slidably interposed between the spherical inner surface 3 of the outer ring 5 and the spherical outer surface 6 of the inner ring 8, and a ball (torque transmission ball) 9 is accommodated in a pocket 11 of the cage 10 and gently moves in the circumferential direction. Are held at an equal pitch.

  A shaft portion (stem portion) 12 is connected to the bottom wall of the outer ring 5, and the outer ring 5 and the shaft portion 12 constitute an outer member 13.

As shown in FIG. 2, the outer spherical surface 15 of the cage 10 is spherically fitted to the spherical inner surface 3 of the outer ring 5, and the inner spherical surface 16 of the cage 10 is spherically fitted to the spherical outer surface 6 of the inner ring. The center of the spherical inner surface 3 of the outer ring 5 and the center of the spherical outer surface 6 of the inner ring 8 coincide with the joint center O. The center O ₁ of the track groove 4 of the outer ring 5 and the center O ₂ of the track groove 7 of the inner ring 8 are offset by an equal distance in the opposite directions in the axial direction. Therefore, the ball track formed by the pair of track grooves 4 and 7 has a wedge shape that decreases from the opening side of the outer ring 5 toward the back side. FIG. 2 shows one constant velocity universal joint 1A, but the other constant velocity universal joint 1B has the same configuration.

  As shown in FIG. 1, the intermediate shaft 2 includes an intermediate large diameter portion 18, spline forming portions 19 and 20 on both ends, and a small diameter portion formed between the spline forming portion 19 and the intermediate large diameter portion 18. 21, and a small diameter portion 22 formed between the spline forming portion 20 and the intermediate large diameter portion 18. Further, a taper portion 23 is provided between the spline forming portion 19 and the small diameter portion 21 to reduce the diameter from the spline forming portion 19 side toward the small diameter portion 21, and between the small diameter portion 21 and the intermediate large diameter portion 18. Is provided with a taper portion 24 whose diameter increases from the small diameter portion 21 toward the intermediate large diameter portion 18. Between the spline forming portion 20 and the small diameter portion 22, a taper portion 25 that is reduced in diameter from the spline forming portion 20 side toward the small diameter portion 22 is provided, and between the small diameter portion 22 and the intermediate large diameter portion 18. In addition, a tapered portion 26 that expands from the small diameter portion 22 toward the intermediate large diameter portion 18 is provided.

  As shown in FIG. 2, each spline forming portion 19, 20 has a spline 27 formed on the outer peripheral surface thereof, and the inner peripheral surface of each inner ring 8 is fitted to the spline 27 of the intermediate shaft 2. A spline 28 is formed. In the spline forming portions 19 and 20, a retaining ring groove 29 is formed in the axial range of the spline 27, and a retaining ring 30 is attached to the retaining ring groove 29, and the intermediate shaft 2 is fitted to the inner ring 8. An anti-separation structure is constructed. The splines 27 and 28 are composed of axial ridges (convex teeth) arranged at a predetermined pitch along the circumferential direction, and axial ridges (concave teeth) arranged between the axial ridges. Become.

  Each of the constant velocity universal joints 1A and 1B includes a pressing portion 52 that applies an elastic pressing force in the axial direction and a receiving portion 58 that receives the pressing force from the pressing portion 52. An axial gap filling mechanism 60 is provided.

  At this time, a pressing member 50 is provided at the shaft end of the shaft 2. The pressing member 50 includes a ball as the pressing portion 52, a compression coil spring as the elastic member 54, and a case 55 for assembling the pressing portion 52 and the elastic member 54. The elastic member 54 acts as an elastic force through the pressing portion 52. The pressing portion 52 may have a convex spherical shape. The case 55 is fixed to the end face of the shaft 2 integrated with the inner ring 8 by serration coupling by an appropriate means such as press fitting or adhesive.

  Further, in the cage 10, a receiving member 56 is attached to the end on the back side of the outer ring 5. The receiving member 56 has a lid shape that covers the end opening of the cage 10, and includes a spherical portion 56 a having a partially spherical shape and a mounting portion 56 b that is formed annularly on the outer periphery thereof. The inner surface (the surface facing the shaft 2) of the spherical portion 56 a is a concave spherical surface, and this concave spherical surface functions as a receiving portion 58 that receives the pressing force from the pressing portion 52. The attachment portion 56b is fixed to the end portion of the cage 10 by appropriate means such as press fitting or welding.

  To smoothly slide the pressing member 50 and the receiving member 56 when the joint takes a bending angle, as shown in FIG. 3, the inner diameter dimension Ro of the concave spherical receiving portion 58 is a ball or convex spherical shape. Larger than the radius r of the pressing portion 52 (see FIG. 2) (Ro> r). Further, in order to prevent interference between the receiving member 56 and the inner ring 8, the inner diameter dimension Ro of the receiving part 58 is made larger than the outer diameter dimension Ri of the spherical outer surface 6 of the inner ring 8 (Ro> Ri).

  Two constant velocity universal joints 1 </ b> A and 1 </ b> B are connected through the intermediate shaft 2 by fitting the retaining ring 30 by spline fitting to the inner ring 8 at both ends of the intermediate shaft 2. In this connected state, the pressing portion 52 of the pressing member 50 and the receiving portion 58 of the receiving member 56 come into contact with each other, and the elastic member 54 is compressed. As a result, the inner ring 8 integrated with the shaft 2 is axially displaced toward the opening side of the outer ring 5 by elastic force, and the ball 9 disposed in the track grooves 4, 7 is reduced by the displacement due to the displacement. Since it is pushed in the direction, the axial gap between the ball 9 and the track grooves 4 and 7 is closed, and rotation backlash is prevented.

  As shown in FIG. 1, in the state where two constant velocity universal joints 1A and 1B are connected via the intermediate shaft 2, as shown in FIG. 4, the track position phase of the pair of constant velocity universal joints 1A and 1B. And the pitch phase between tracks are matched.

  That is, the track grooves 4 and 7 of the constant velocity universal joints 1A and 1B are arranged at a 60 ° pitch along the circumferential direction. The phases of the a1 track grooves 4 and 7 of the constant velocity universal joint 1A and the track grooves of a2 and b2 of the constant velocity universal joint 1B are matched. Further, these phases may be shifted within a range of ± 20 °. The same applies to the track grooves 4 and 7 below.

  A bearing device 35 for posture stabilization is attached to the central portion of the intermediate shaft 2 in the axial direction, that is, the large diameter portion 18. The bearing device 35 includes a rolling bearing 36 and a case 37 that is fitted on the bearing 36.

  The large-diameter portion 18 of the intermediate shaft 2 has a small-diameter first portion 18a and a large-diameter second portion 18b, and a bearing 36 is externally fitted to the first portion 18a. A circumferential groove 38 is formed in the first portion 18 a, and a retaining ring 39 is fitted in the circumferential groove 38. As a result, the inner ring 36a of the bearing 36 is sandwiched between the retaining ring 39 and the end face 40 formed between the first part 18a and the second part 18b.

  The case 37 includes a short cylindrical portion 41 having a small diameter portion 41 a and a large diameter portion 41 b on the inner peripheral surface, and a circumferential groove 42 is formed in the large diameter portion 41 b of the inner peripheral surface. A retaining ring 43 is fitted. As a result, the outer ring 36b of the bearing 36 is sandwiched between the retaining ring 43 and the end surface 44 formed between the small diameter part 41a and the large diameter part 41b. The case 37 is provided with a connecting piece portion 45 protruding from the short cylindrical portion 41, and the connecting piece portion 45 is fixed to a fixing portion (not shown).

  Therefore, when the angle formed by the constant velocity universal joints 1A and 1B is, for example, α as shown in FIG. 1, this α can be stably maintained. In addition, when it bends as shown in FIG. 1, the small diameter parts 21 and 22 of the intermediate shaft 2 correspond to the opening edge part 5a of the outer ring 5, and the rocking | fluctuation range of the outer ring 5 with respect to the shaft 2 is taken large. Can do.

  The high-angle fixed type constant velocity universal joint configured as described above includes a pair of constant velocity universal joints 1A and 1B and an intermediate shaft 2 connecting the pair of constant velocity universal joints 1A and 1B. (Angle) can be supported. In addition, since the axial gap filling mechanism 60 between the ball and the ball track is configured in each constant velocity universal joint 1A, 1B, the gap between the track grooves 4, 7 via the ball 9 can be filled. As a result, it is possible to provide a high-angle fixed type constant velocity universal joint capable of handling a large angle without a so-called rotational direction backlash. That is, it is possible to prevent the occurrence of rotational backlash due to the gap between the tracks, and to increase the operating angle, which is most suitable for use in an automobile steering device (steering system).

  Further, the pair of constant velocity universal joints 1A and 1B can be connected via the intermediate shaft 2 without using a bolt member or the like. As a result, the assembling work can be simplified, the number of parts is relatively small, the parts can be easily managed, and the cost can be reduced.

  By providing the bearing device 35 for posture stabilization at the central portion in the axial direction of the intermediate shaft 2, the posture of the outer ring 5 with respect to the shaft 2 can be stabilized and a stable operating angle can be obtained. As a result, the rotational force can be transmitted smoothly, and a highly accurate rotational force transmission mechanism is obtained.

  The track position phase and the inter-track pitch phase of the pair of constant velocity universal joints 1A and 1B are made to coincide with each other. As a result, the maximum value of the hysteresis in the torque-torsion angle diagram of the joint can be reduced, and the safety of an automobile using the high-angle fixed type constant velocity universal joint in the steering system can be improved. Further, these phases may be shifted within a range of ± 20 °. This is because the hysteresis in the torque-torsion angle diagram of the joint can be reduced within this range. On the other hand, if it exceeds these ranges, the maximum value of hysteresis will increase, and as the hysteresis increases, there is a possibility that the operability will deteriorate.

  FIG. 5 shows a cross-sectional view of the main part of the second embodiment. In this case, a bearing device 35 is mounted on the outer ring 5. That is, a small diameter portion 61 and a large diameter portion 62 are provided on the outer peripheral surface of the outer ring 5, and the bearing 36 is fitted to the small diameter portion 61. In this case, a circumferential groove 63 is formed in the small diameter portion 61, and a retaining ring 64 is fitted in the circumferential groove 63. As a result, the inner ring 36 a of the bearing 36 is sandwiched between the retaining ring 64 and the end face 65 formed between the small diameter part 61 and the large diameter part 62.

  Further, the outer ring 36 b of the bearing 36 is sandwiched between the retaining ring 43 and the end surface 44 formed between the small diameter part 41 a and the large diameter part 41 b of the short cylindrical part 41 of the case 37.

  Thus, a stable operating angle can be obtained also by providing the bearing device 35 for posture stabilization on the outer ring 5 of the constant velocity universal joint 1A or 1B. Thereby, transmission of a rotational force can be performed smoothly and it becomes a highly accurate rotational force transmission mechanism.

  In the high-angle fixed type constant velocity universal joint of the second embodiment, the same parts as those of the high angle fixed type constant velocity universal joint of the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  For this reason, even the high angle fixed type constant velocity universal joint of the second embodiment has the same effects as the high angle fixed type constant velocity universal joint of the first embodiment.

  FIG. 6 shows a cross-sectional view of the main part of the third embodiment. In this high angle fixed type constant velocity universal joint, the axial gap filling mechanism 60 is replaced with a receiving portion 58, contrary to the embodiment of FIGS. This is an example in which the intermediate shaft 2 and the pressing portion 52 are provided in the cage 10. In the third embodiment, a receiving member 56 that protrudes toward the pressing portion 52 is provided on the end surface of the shaft, and the tip of the convex spherical portion of the receiving member 56 is used as the receiving portion 58. That is, the convex spherical receiving portion 58 is formed integrally with the intermediate shaft 2. Note that another receiving member 56 may be attached to the shaft end of the shaft 2.

  In this embodiment, the pressing member 50 having the pressing portion 52 has a lid shape covering the end opening of the cage 10, as in the receiving member shown in FIGS. Attached to the end of the side. The pressing member 50 includes a spherical part 50a having a partially spherical shape and a plurality of leg parts 50b protruding from the outer periphery thereof. The inner surface of the spherical portion 50a (the surface facing the shaft 2) has a concave spherical shape, and this concave spherical portion functions as a pressing portion 52 that applies an elastic force in the axial direction to the receiving portion 58. At this time, in order to prevent interference between the pressing member 50 and the inner ring 8, the concave spherical pressing portion 52 is formed with a larger diameter than the spherical outer surface 6 of the inner ring 8.

  In the axial gap filling mechanism 60 between the ball and the ball track of the third embodiment shown in FIG. 6, the shaft 2 is pressed toward the outer ring opening side. As a result, the ball 9 is pushed into the reduction side of the track grooves 4 and 7, and the axial gap between the ball and the ball track is closed.

  In the high-angle fixed type constant velocity universal joint of the third embodiment, the same parts as those of the high angle fixed type constant velocity universal joint of the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  For this reason, even the high angle fixed type constant velocity universal joint of the third embodiment has the same effects as the high angle fixed type constant velocity universal joint of the first embodiment.

  Incidentally, the bearing device 35 for posture stabilization may be provided on the shaft portion (stem portion) 12. In this case, the axial part 12 should just provide the circumferential groove | channel etc. which a retaining ring fits like the axial direction center part of the intermediate shaft 2 shown in FIG.

  As shown in FIG. 5, when the bearing device 35 is provided on the outer ring 5 of the constant velocity universal joint, it is provided in one constant velocity universal joint 1A in the above embodiment, but is provided in the other constant velocity universal joint 1B. Alternatively, both constant velocity universal joints 1A and 1B may be provided.

  In each embodiment, the constant velocity universal joints 1A and 1B are BJ type, but may be UJ type or other constant velocity universal joints. Further, it is possible to use different types of constant velocity universal joints 1A and 1B. The number of track grooves of the constant velocity universal joints 1A and 1B is not limited to six.

  One of the two constant velocity universal joints 1A, 1B uses the axial gap filling mechanism 60 between the ball and the ball track shown in FIG. 1, and the other uses the axial gap filling mechanism 60 between the ball and the ball track shown in FIG. 60 may be used.

It is sectional drawing of the high angle fixed type constant velocity universal joint which concerns on the 1st Embodiment of this invention. It is a principal part expanded sectional view of the said high angle fixed type constant velocity universal joint. It is a principal part expanded sectional view of the constant velocity universal joint of the said high angle fixed type constant velocity universal joint. It is a simple figure of the constant velocity universal of the said high angle fixed type constant velocity universal joint. It is principal part sectional drawing of the high angle fixed type constant velocity universal joint which concerns on the 2nd Embodiment of this invention. It is principal part sectional drawing of the high angle fixed type constant velocity universal joint which concerns on the 2nd Embodiment of this invention.

Explanation of symbols

1A, 1B Constant velocity universal joint 2 Intermediate shaft 3 Spherical inner surface 4, 7 Track groove 5 Outer ring 6 Spherical outer surface 8 Inner ring 9 Ball 10 Cage 12 Shaft portion 35 Bearing device 52 Pressing portion 58 Receiving portion 60 Axial between ball and ball track Gap filling mechanism

Claims (8)

  A constant velocity universal joint and an intermediate shaft connecting the pair of constant velocity universal joints, and each constant velocity universal joint includes an outer ring having a plurality of track grooves formed on a spherical inner surface, and a plurality of spherical outer surfaces. A ball disposed on each of a plurality of ball tracks formed by cooperation of an inner ring having a track groove, a track groove of the outer ring and a track groove of the inner ring, and a ball disposed between the outer ring and the inner ring. A high-angle fixed type constant velocity universal joint having a retainer for holding, and connecting the pair of constant velocity universal joints by fitting each inner ring to both ends of the intermediate shaft, and each constant velocity universal joint A high angle fixed type constant velocity universal joint characterized in that an axial gap filling mechanism is formed between the ball and the ball track.   The axial gap filling mechanism includes a pressing portion that applies an elastic pressing force in the axial direction and a receiving portion that receives the pressing force from the pressing portion, and any one of the pressing portion and the receiving portion is the intermediate portion. The high angle fixed type constant velocity universal joint according to claim 1, wherein the high angle fixed constant velocity universal joint is provided at an end portion of the shaft and the other is provided in the cage.   The high-angle fixed type constant velocity universal joint according to claim 1, wherein a bearing device for posture stabilization is provided at a central portion in the axial direction of the intermediate shaft.   The high angle fixed type constant velocity universal joint according to claim 1 or 2, wherein a bearing device for posture stabilization is provided on the outer ring.   The high angle fixed type constant velocity universal joint according to claim 1 or 2, wherein a shaft portion is connected to the outer ring, and a bearing device for posture stabilization is provided on the shaft portion.   The high-angle fixed constant velocity universal joint according to any one of claims 1 to 5, wherein the track position phase and the track pitch phase of the pair of constant velocity universal joints are made to coincide with each other. 6. The high-angle fixed constant velocity according to claim 1, wherein a deviation of each of the track position phase and the track pitch phase of the pair of constant velocity universal joints is in a range of ± 20 °. Universal joint.   The high angle fixed type constant velocity universal joint according to any one of claims 1 to 7, which is applied to a steering system.

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