JP2012149684A - Shaft for constant velocity universal joint - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a shaft for constant velocity universal joint that absorbs torsional vibration (vibration in the rotation direction) and which does not spoil a feeling of rigidity.SOLUTION: A shaft for constant velocity universal joint in which a constant velocity universal joint is connected to an output side end part 1a and an input side end part 1b, respectively. The center part 3 of the shaft for constant velocity universal joint between the output side end part 1a and the input side end part 1b is provided with a damping mechanism 4 configured to suppress torque variation from the input side end part 1b by resistance in the rotating direction The damping mechanism 4 includes a roller 20 as a member to generate rotation resistance.

Description

  The present invention relates to a constant velocity universal joint shaft that can suppress torsional vibration generated in a drive system.

  Power transmission means to drive wheels for automobiles is smoothly transmitted without torque fluctuation by a fixed type constant velocity universal joint and a sliding type constant velocity universal joint connected by a half shaft. As described above, in the drive system including the constant velocity universal joint, the vibration from the engine is mainly absorbed by the sliding type constant velocity universal joint so that the vibration is not transmitted to the vehicle body as an unpleasant vibration.

  However, the vibration absorption direction in the sliding type constant velocity universal joint is all in the sliding direction (axial direction) and cannot absorb the displacement in the twisting direction (rotating direction). That is, it is not possible to absorb torque fluctuations accompanying rotation fluctuations from the engine side, so-called torsional vibrations.

  For this reason, conventionally, the outer joint member (outer ring) has a two-layer structure of an outer cylinder part and an inner cylinder part, and relative movement in the axial direction and around the axis center between the outer cylinder part and the inner cylinder part. There is a constant velocity universal joint that interposes a guide device that allows relative rotation (Patent Document 1). The constant velocity universal joint includes a suppression device (made of a rubber material) that suppresses relative movement in the axial direction between the outer cylinder portion and the inner cylinder portion and relative rotation around the axis.

  As shown in FIGS. 12 and 13, the guide device 102 described in Patent Document 1 includes a sliding body 106 disposed between an outer cylinder portion 76 and an inner cylinder portion 82. An axial groove 108 is formed between the sliding body 106 and a circumferential groove 110 is formed between the inner cylinder portion 82 and the sliding body 106, and the rolling elements 112, 114 are fitted into the grooves 108, 110. It is to be combined.

  Further, as shown in FIG. 13, a relative restraining device having a first spring 96 and a second spring 98 interposed between the sliding plates 100, 100 is disposed in the vicinity of the sliding body 106 in the guide device 102. ing. This relative suppression device suppresses relative rotation of the outer cylinder portion 76 and the inner cylinder portion 82 around the axis.

  In the constant velocity universal joint described in Patent Document 1, the configuration as described above, “the torsional rigidity of the constant velocity universal joint for a vehicle that is a part of the drive system is reduced and the resonance frequency of the drive system is reduced. The torsional resonance of the drive shaft is suppressed, and the lockup rotation speed of the lockup clutch can be reduced while suppressing the generation of noise such as a lockup booming noise. Furthermore, “a damping element that generates a relative movement resistance according to the relative rotational speed of the outer cylinder portion and the inner cylinder portion around the axis center is provided, and the torsional vibration generated in the drive system is absorbed by the damping element. Therefore, the vibration generated in the drive system can be sufficiently suppressed. "

JP 2010-144663 A

However, in Patent Document 1, the amount of relative displacement with respect to the rotation direction of the outer ring is regulated by the operating range of the rolling element 114, and the torsional rigidity during this period is determined by the spring force of the relative restraining device. You will tune it to get it.

  Further, since the rubber element (relative rotation suppressing device) is provided in the circumferential gap between the outer cylinder portion 76 and the inner cylinder portion 82, the torsional vibration generated in the drive system is always transmitted through the rubber element. It propagates between the outer cylinder part 76 and the inner cylinder part 82. For this reason, the torsional vibration generated in the drive system can be suppressed.

  However, since the torsional vibration absorbing structure described in Patent Document 1 is a structure that is largely twisted in the rotational direction in the low torque region, the displacement in the rotational direction becomes large in a situation where the torque input changes between positive and negative. For this reason, in a traveling state in which acceleration / deceleration is repeated (load torque is switched between positive and negative), the feeling of rigidity (= direct feeling) is impaired.

  An object of the present invention is to propose a shaft for a constant velocity universal joint that absorbs torsional vibration (vibration in the rotational direction) and does not impair rigidity.

  The constant velocity universal joint shaft of the present invention is a constant velocity universal joint shaft in which a constant velocity universal joint is connected to an output side end and an input side end, respectively, and includes an output side end and an input side end. Is provided with a damping mechanism (that is, a damping mechanism using a torsional displacement of the shaft) that suppresses torque fluctuation from the input side end portion by a resistance in the rotational direction. A roller is provided as a member for generating rotational resistance.

  By providing the damping mechanism, the constant velocity universal joint shaft according to the present invention can suppress the rotational fluctuation accompanying the fluctuation of the input torque, that is, can absorb the vibration in the torsional direction. In addition, by providing a roller as a member that generates rotational resistance, the roller and the mating member are in line contact, and a large resistance can be ensured in a relatively small space.

  The damping mechanism includes a first member, a second member, and the roller interposed between the first member and the second member, and the first member includes an output side end and an input side end. It is preferable that it is integrally formed with.

  The second member is externally fitted to the first member, or the second member is coupled to the first member on the torque input side or the torque output side, and is not coupled to the first member. Alternatively, it is set so as to be displaced relative to the first member on the torque input side.

  It is preferable that the roller is fitted with a tightening margin at a relative displacement portion between the first member and the second member. Further, three or more rollers may be arranged at a predetermined pitch along the circumferential direction. Furthermore, it may be provided with a cage that holds the rollers arranged at a predetermined pitch along the circumferential direction.

  The damping mechanism includes a first member formed of a solid shaft that connects the output side end and the input side end, and a second member formed of a cylindrical outer member that is fitted on the first member. A roller as a sliding member fitted with a tightening margin to a relative displacement portion between the first member and the outer member, and a cage that holds the roller, and the outer member as the second member is the Even if it is a relative displacement portion that is coupled to the torque input side or torque output side of the first member and in which the roller is disposed on the torque output side or torque input side that is not coupled to the second member. Good.

  The rollers may be arranged in a plurality of rows along the shaft axis for the constant velocity universal joint. Further, the cage may have a pocket for accommodating the roller, and the radial gap between the roller and the pocket may be a negative clearance. Further, the rollers adjacent to each other in the circumferential direction may be brought into close contact with each other and the cage may be omitted.

  The roller may be disposed in a state in which a preload is applied between the first member and the second member with an outer diameter surface being a tapered surface.

  The second member may be a tapered portion that is press-fitted into the roller and the outer diameter surface of the press-fitting start end portion of the second member expands toward the press-fitting start end edge.

  The connection between the first member and the second member may be a serration connection or a connection by welding.

  A sliding type constant velocity universal joint can be attached to the input side end, a fixed type constant velocity universal joint can be attached to the output side end, and a sliding type constant velocity universal joint can be attached to the input side end and output side end. Can be attached.

  In the constant velocity universal joint shaft according to the present invention, by providing a mechanism that attenuates torque fluctuation, torsional vibration due to torque fluctuation can be absorbed. If this constant velocity universal joint shaft is used as a means for transmitting power to the drive wheels of an automobile, excellent drivability is exhibited without impairing rigidity (= direct feeling) even when the vehicle is repeatedly accelerated and decelerated. Moreover, torsional vibration can be suppressed. In particular, by using a roller, a large resistance can be secured in a relatively small space, and torsional vibration can be more stably suppressed.

  Since the damping mechanism includes a first member and a second member, and the first member includes a torque transmission shaft formed integrally with the output side end portion and the input side end portion, the configuration can be simplified. Since the second member is fitted on the first member that functions as a torque transmission shaft, the second member can be made compact.

  The second member can be set so that one end side is coupled to the first member and the other end side is relatively displaced with the first member, and the function of absorbing vibration in the torsional direction can be effectively exhibited. Further, by providing the roller, it is possible to improve the reliability of the function of absorbing the vibration in the torsional direction. In particular, the reliability can be further improved by arranging three or more rollers at a predetermined pitch along the circumferential direction. Furthermore, in the case of having a cage, the roller is stably held.

  As described above, a device including the first member, the second member, a roller, and the like can effectively exhibit the function of absorbing vibration in the torsional direction, and can exhibit a highly reliable function.

  By arranging the rollers in a plurality of rows along the shaft center for the constant velocity universal joint, the resistance force in the rotational direction can be adjusted, so that a large torque fluctuation can be suppressed. By making the gap in the radial direction between the roller and the pocket negative, a stable resistance can be exerted, and in addition, the rollers adjacent to each other in the circumferential direction are in close contact with each other (the total roller) More resistance can be secured.

  In the case of applying a preload, an optimum resistance value can be secured by adjusting the amount of preload. By making the outer diameter surface of the press-fitting start end portion of the second member a tapered portion, it is possible to prevent the rigidity of the press-fitting start end portion from being lowered and to ensure a uniform resistance force in the axial direction.

  Further, the connection between the first member and the second member may be a serration connection or a connection by welding, and a known or public one can be used for this connection means, and the cost can be reduced. Can do.

  A sliding type constant velocity universal joint can be attached to the input side end, a fixed type constant velocity universal joint can be attached to the output side end, and it can slide to the input side end and output side end. Since a constant velocity universal joint can be attached, various types of power transmission means can be configured, and the versatility is excellent.

It is a longitudinal cross-sectional view of the shaft for constant velocity universal joints which shows the 1st Embodiment of this invention. It is a principal part cross-sectional view of the shaft for constant velocity universal joints. It is a principal part expanded sectional view of the fixed side of the said shaft for constant velocity universal joints. It is a principal part expanded sectional view by the side of the damping mechanism of the said constant velocity universal joint shaft. It is a simplified sectional view of the constant velocity universal joint shaft. It is the YY line expanded sectional view of FIG. FIG. 6 is an enlarged sectional view taken along line ZZ in FIG. 5. It is a principal part expanded sectional view which shows 2nd Embodiment of the shaft for constant velocity universal joints of this invention. It is a principal part expanded sectional view which shows 3rd Embodiment of the shaft for constant velocity universal joints of this invention. It is a principal part expanded sectional view which shows 4th Embodiment of the shaft for constant velocity universal joints of this invention. It is a principal part expanded sectional view which shows 5th Embodiment of the shaft for constant velocity universal joints of this invention. It is principal part sectional drawing of the conventional constant velocity universal joint for vehicles. It is a principal part expanded sectional view of the constant velocity universal joint for vehicles shown in the said FIG.

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

  FIG. 1 is a longitudinal sectional view of a constant velocity universal joint shaft according to the present invention. The constant velocity universal joint shaft includes a shaft main body 1 and an outer member 2 fitted on the shaft main body 1. The shaft central portion 3 is provided with a damping mechanism 4.

  The shaft main body 1 includes an output side end 1a, an input side end 1b, a main body 1c, and a small diameter portion 1d and a large diameter portion 1e disposed between the output side end 1a and the main body 1c. The small-diameter portion 1f and the large-diameter portion 1g are disposed between the input-side end portion 1b and the main body portion 1c.

  In this case, a fixed type constant velocity universal joint (not shown) is connected to the output side end 1a, and a sliding type constant velocity universal joint (not shown) is connected to the input side end 1b. As the fixed type constant velocity universal joint, various types such as a bar field type in which the track groove bottom is only an arc portion and an undercut free type having a linear portion in a part of the track groove bottom can be used. . As the sliding constant velocity universal joint, various types such as a double offset type, a tripod type, and a cross groove type can be used.

  For this reason, the output side end portion 1a has a male spline 5 formed on the outer diameter surface thereof and a circumferential groove 6 into which a retaining ring (not shown) is fitted. Similarly, the input side end portion 1b is formed with a male spline 7 on its outer diameter surface and a circumferential groove 8 into which a retaining ring (not shown) is fitted.

  The large-diameter portion 1e on the output side end portion 1a constitutes a mounting portion for a boot (not shown) for closing the opening of a fixed type constant velocity universal joint (not shown). For this reason, the circumferential groove 9 is formed in the large diameter portion 1e. The large-diameter portion 1g on the input side end 1b side constitutes a mounting portion for a boot (not shown) for closing the opening of a sliding type constant velocity universal joint (not shown). For this reason, the circumferential groove 10 is formed in the large diameter portion 1g.

  The main body 1c has a central main body 12 and a large-diameter portion 13 connected to the large-diameter portion 1g on the input side end 1b side. The outer member 2 includes a main body cylindrical portion 2a and a supporting small-diameter portion 2b on the input side of the main body cylindrical portion 2a. As shown in FIG. 3, the supporting small-diameter portion 2b is coupled to the large-diameter portion 13 of the main body portion 1c. The coupling in this case is a so-called serration coupling 15. That is, a male serration is formed on the outer peripheral surface of the large diameter portion 13 to constitute a male coupling portion, and a female serration is formed on the inner peripheral surface of the supporting small diameter portion 2b to constitute a female coupling portion. The shape coupling portion and the female coupling portion are coupled (engaged) to be coupled. In addition, the connection means of the large diameter part 13 and the support small diameter part 2b is not limited to the serration connection 15, and may be other means such as welding. In addition, the male serration in the male coupling portion in the serration coupling 15 includes a male spline, and the female serration in the female coupling portion in the serration coupling 15 includes a female spline. For this reason, the serration connection 15 includes a spline connection.

  In addition, a plurality of rollers 20 as sliding members are provided at a predetermined pitch along the circumferential direction in the opening on the side opposite to the small diameter portion for supporting the main body cylindrical portion 2a of the outer member 2, as shown in FIG. (In the example shown in the figure, six at a pitch of 60 degrees) are arranged. In this case, a cage 21 is interposed between the central main body 12 of the main body 1c and the main body cylindrical portion 2a of the outer member 2 on the side of the opening on the side of the small diameter portion for support. The roller 20 is held. That is, the cage 21 is a short cylindrical body, and pockets 22 are formed in the circumferential wall at a pitch of 60 degrees along the circumferential direction, and the rollers 20 are fitted and held in the pockets 22. The roller 20 is fitted between the central main body 12 of the main body 1c and the main body cylindrical portion 2a of the outer member 2 with a margin. Further, the radial gap between the roller 20 and the pocket 22 is a negative gap.

  As shown in FIG. 4, locking portions 25 and 26 are provided on the shaft body 1 side and the outer member 2 side, respectively. The locking portion 25 on the shaft main body 1 side can be constituted by a large diameter portion 25 a provided between the large diameter portion 1 e on the output side end portion 1 a side and the central main body 12. The enlarged diameter portion 25a has a concave cross section. Further, the locking portion 26 on the outer member 2 side has a large-diameter portion 27 as an inner diameter surface on the opening side of the outer member 2, and is configured by a concavely curved portion 27 a provided on the back side of the large-diameter portion 27. can do.

  Thus, by providing the locking portions 25 and 26, the roller 20 as the sliding member can be prevented from coming off in the axial direction. That is, the locking portion 25 restricts the movement of the roller 20 to the output side, and the locking portion 26 restricts the movement of the roller 20 to the input side. In addition, a tapered portion 27b whose diameter increases toward the output side is formed at the opening end of the large diameter portion 27.

  The shaft main body 1 is made of, for example, the same material as the shaft for the drive shaft, and medium carbon steel, case-hardened steel, or the like is appropriate. Further, the outer member 2 is made of the same material as the shaft main body 1 or a material having a torsional rigidity equal to or higher than the material of the shaft main body 1. For example, a CFRP (carbon fiber reinforced plastic) material having high torsional rigidity is suitable. ing.

  By the way, the damping mechanism 4 includes a first member 31 that is the central body 12 of the shaft body 1, a second member 32 that is the outer member 2, and a roller 20 that is held by the cage 21. Is done.

  Next, a method for assembling the shaft will be described. First, the roller 20 and the cage 21 are assembled to the shaft body 1. In this case, after the retainer 21 is externally fitted to the central body 12 of the main body 1c of the shaft body 1, the rollers 20 of the respective pockets 22 of the retainer 21 are fitted. Next, the outer member 2 as the second member 32 is inserted from the input side into the shaft body 1 in which the roller 20 and the cage 21 are assembled. At this time, the opening side of the outer member 2 is pressed into the sliding member that is the roller 20, and the small diameter for supporting the outer member 2 with respect to the male coupling portion of the large-diameter portion 13 of the shaft body 1. The female coupling part of the part 2b is press-fitted. Thus, the constant velocity universal joint shaft shown in FIG. 1 is completed. In addition, since the taper part 27b is formed in the opening edge of the outer member 2 as mentioned above, when the outer member 2 is inserted, this taper part 27b can serve as a guide and can be assembled smoothly.

  Next, the function of the damping mechanism 4 will be described with reference to FIGS. An arbitrary predetermined dimension A is set between the serration coupling 15 on the input side and the relative displacement portion on the output side. On the input side, the first member 31 and the second member 32 are coupled by the serration coupling 15. Therefore, when a torque load is applied on the input side as shown in FIG. 5, as shown in FIG. In addition, the second member 32 is synchronized with the torsional displacement (θt) of the first member 31. In FIG. 6, P1 shows the phase of the 1st member 31 and the 2nd member 32 at the time of torque load. On the other hand, since they are not coupled on the output side, a phase difference (θt) is generated between the first member 31 and the second member 32 as shown in FIG. However, since the roller 20 is fitted with a tightening margin between the first member 31 and the second member 32 on the output side, the torsional direction that fluctuates instantaneously due to the generated frictional force (resistance force). Fluctuating energy will be offset (absorbed). For this reason, torsional vibration can be suppressed (damped). In FIG. 7, P2 indicates the phase of the first member 31 at the time of torque load, and P3 indicates the phase of the second member 32 at the time of torque load.

  Thus, in the present invention, by providing the damping mechanism 4 for suppressing torque fluctuation, torsional vibration due to torque fluctuation can be absorbed. For this reason, if this constant velocity universal joint shaft is used as a power transmission means to drive wheels in an automobile, excellent drivability without impairing rigidity (= direct feeling) in a running state where acceleration and deceleration are repeated And torsional vibration can be suppressed. In particular, by using the roller 20, a large resistance force can be secured in a relatively small space, and torsional vibration can be suppressed more stably.

  Since the damping mechanism 4 includes a first member 31 and a second member 32, and the first member 31 is composed of a torque transmission shaft formed integrally with the output side end 1a and the input side end 1b, the configuration is simplified. Can be achieved. Since the second member 32 is externally fitted to the first member 31 that functions as a torque transmission shaft, the second member 32 can be made compact.

  Since the second member 32 can be set so that one end side is coupled to the first member 31 and the other end side is displaced relative to the first member 31, the function of absorbing vibration in the torsional direction can be effectively exhibited. Further, since the roller 20 is fitted with a tightening allowance, a frictional force can be generated at the tightening allowance, and the reliability of the function of absorbing the vibration in the torsional direction can be improved. For this reason, as this interference, what is necessary is just to generate | occur | produce the frictional resistance which a phase difference produces in this relative displacement part between the 1st member 31 and the 2nd member 32. FIG.

  Further, in the case where the cage 21 is provided, the roller 20 is stably held. In addition, a more stable resistance force can be obtained by setting the radial gap between the roller 20 and the pocket 22 to be a negative clearance.

  As described above, the device including the first member 31, the second member 32, the roller 20, and the like can effectively exhibit the function of absorbing vibration in the torsional direction, and can exhibit a highly reliable function.

  By the way, in the above embodiment, a plurality (six in the illustrated example) of rollers 20 are arranged at a 60 ° pitch along the circumferential direction, that is, a plurality of such rollers 20 are provided. A plurality of rows may be arranged along the shaft axis for the constant velocity universal joint. In this case, the number of the plurality of columns can be arbitrarily set. Further, the interval between the rows is arbitrary, and when there are three or more rows, the arrangement pitch may be equal pitch or unequal pitch. By arranging in this way, larger torque fluctuations can be suppressed.

  In the embodiment, the constant velocity universal joint shaft has a sliding type constant velocity universal joint attached to the input side end 1b and a fixed type constant velocity universal joint attached to the output side end 1a. However, as another embodiment, a sliding type constant velocity universal joint can be attached to the output side end 1a and the input side end 1b. Also, as the sliding type constant velocity universal joint in this case, various types such as a double offset type, a tripod type, and a cross groove type can be used. As described above, the constant velocity universal joint shaft of the present invention can constitute various types of power transmission means and is excellent in versatility.

  In the embodiment, the second member 32 is coupled to the input side of the first member 31. However, as another embodiment, the second member 32 is coupled to the output side of the first member 31, and the second member 32 is coupled. The roller 20 may be arranged on the input side. Even in such a case, rotational fluctuation due to torque load from the input side end can be suppressed, and vibration in the torsional direction can be absorbed.

  In FIG. 8, the holder 21 that holds the roller 20 is not provided. That is, the rollers 20 adjacent to each other in the circumferential direction are brought into contact with or in close contact with each other. That is, the number of rollers 20 is the maximum number that can be arranged in the circumferential direction (circumferential direction). By setting in this way, it is possible to secure more resistance force of the roller that is the rolling element of the sliding portion, and to improve the function of absorbing vibration in the torsional direction.

  By the way, in the said embodiment, although the roller 20 was comprised by the cylindrical roller 20A, as shown in FIG. 9, the taper roller (conical roller) 20B whose outer diameter surface is a taper surface may be sufficient.

  In this case, a taper surface 40 whose diameter increases toward the opening side (start end side) is provided on the inner diameter surface of the press-fitting start end portion of the main body cylindrical portion 2a of the outer member 2, and the tapered surface is provided on the shaft main body 1. A tapered surface 41 that decreases toward the opening side (start end side) is provided at a portion corresponding to 40. The tapered roller 20B is press-fitted into a wedge-shaped gap 42 formed between the tapered surfaces 40 and 41.

  As shown in FIG. 9, by using the taper roller 20B, pressure input (resistance force) can be ensured or pressure input can be adjusted. That is, the amount of axial preload can be adjusted, and an optimal resistance value can be secured by this adjustment.

  Further, as shown in FIG. 10, the preload adjusting member 45 may be attached to the shaft body 1. The preload adjusting member 45 is configured by a ring body in which an internal thread portion 46 is formed on the inner diameter surface. In this case, the preload adjusting member 45 includes a disc-shaped main body 45a and a tapered section 45b having a trapezoidal cross section that tapers from the main body 45a toward the taper roller 20B. A portion 46 is formed.

  A male threaded portion 47 is formed on the outer diameter surface of the shaft body 1, and the female threaded portion 46 of the preload adjusting member 45 is screwed to the male thread 47. Thereby, the end surface 48 of the taper part 45b of the preload adjusting member 45 can press the large-diameter side end surface 50 of the taper roller 20B in the arrow direction. That is, the preload can be applied by the preload adjusting member 45. At this time, the amount of preload can be adjusted by adjusting the screwing amount, and the preload adjusting member 45 and the shaft body 1 are screw-fitted, so that the adjustment is stable.

  In FIG. 11, the outer diameter surface of the press-fitting start end portion of the second member 32 is a tapered portion 51 whose diameter increases toward the press-fitting start end edge. For this reason, the rigidity large part 52 whose thickness becomes large toward the press-fitting start edge is formed. That is, when the thickness of the counter press-fit start end of the large rigid portion 52 is t2, and the thickness of the press fit start end edge of the large rigid portion 52 is t1, t1> t2.

  In this way, by setting, it is possible to prevent a decrease in rigidity of the press-fitting start end portion and to ensure a uniform resistance force in the axial direction. In this case, the axial length of the rigid large portion 52 and the difference between t1 and t2 can be variously changed according to the material of the outer member, the outer diameter dimension and the thickness dimension other than the rigid large portion 52, and the like.

  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, the number of rollers 20 can be increased or decreased, and at least along the circumferential direction. It is sufficient if there are three arranged at a pitch of 120 degrees. When a plurality of rollers 20 are arranged, the number of rollers 20 in each row may be the same or different.

DESCRIPTION OF SYMBOLS 1a Output side edge part 1b Input side edge part 2 Outer member 3 Shaft center part 4 Damping mechanism 15 Serration coupling 20 Roller 21 Cage 22 Pocket 31 First member 32 Second member 51 Tapered part

Claims (17)

A constant velocity universal joint shaft to which a constant velocity universal joint is connected to each of an output side end and an input side end,
A damping mechanism is provided in the central portion of the constant velocity universal joint shaft between the output side end and the input side end to suppress the torque fluctuation from the input side end by the resistance in the rotational direction. A constant velocity universal joint shaft comprising a roller as a member to be generated.   The damping mechanism includes a first member, a second member, and the roller interposed between the first member and the second member, and the first member includes an output side end and an input side end. The constant velocity universal joint shaft according to claim 1, wherein the constant velocity universal joint shaft is formed integrally with the shaft.   The constant velocity universal joint shaft according to claim 2, wherein the second member is externally fitted to the first member.   The second member is coupled to the first member on the torque input side or the torque output side, and is relatively displaced from the first member on the torque output side or the torque input side not coupled to the first member. The shaft for a constant velocity universal joint according to claim 2 or claim 3.   The constant velocity freely according to any one of claims 2 to 4, wherein the roller is fitted with a tightening margin at a relative displacement portion between the first member and the second member. Joint shaft.   The shaft for a constant velocity universal joint according to any one of claims 1 to 5, wherein three or more rollers are arranged at a predetermined pitch along the circumferential direction.   The constant velocity universal joint shaft according to claim 1, further comprising a cage that holds a state in which the rollers are arranged at a predetermined pitch along a circumferential direction.   The damping mechanism includes a first member made of a solid shaft that connects the output side end and the input side end, and a second member made of a cylindrical outer member that is fitted on the first member. A roller serving as a sliding member that fits into a relative displacement portion between the first member and the outer member with a tightening margin; a retainer that holds the roller; and the outer member serving as the second member is the first member. 2. A relative displacement portion that is coupled to a torque input side or a torque output side of a member and that has the roller disposed on a torque output side or a torque input side that is not coupled to a second member. The shaft for constant velocity universal joints according to 1.   The shaft for constant velocity universal joints according to any one of claims 1 to 8, wherein the rollers are arranged in a plurality of rows along a shaft axis for constant velocity universal joints.   9. The constant velocity universal joint shaft according to claim 7, wherein the cage has a pocket for accommodating the roller, and a radial clearance between the roller and the pocket is a negative clearance.   The shaft for a constant velocity universal joint according to claim 1, wherein the rollers adjacent to each other in the circumferential direction are brought into close contact with each other and the cage is omitted.   The roller according to any one of claims 2 to 11, wherein an outer diameter surface of the roller is a tapered surface and a preload is applied between the first member and the second member. The shaft for constant velocity universal joints described.   3. The second member is press-fitted into a roller, and a press-fitting start end outer diameter surface of the second member is a tapered portion that expands toward the press-fitting start end edge. The constant velocity universal joint shaft according to claim 12.   14. The constant velocity universal joint shaft according to claim 2, wherein the first member and the second member are connected by serration.   14. The constant velocity universal joint shaft according to claim 2, wherein the first member and the second member are joined by welding.   The sliding constant velocity universal joint is attached to the input side end portion, and the fixed type constant velocity universal joint is attached to the output side end portion. Quick universal joint shaft.   The shaft for a constant velocity universal joint according to any one of claims 1 to 15, wherein a sliding type constant velocity universal joint is attached to the input side end portion and the output side end portion.

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