JP2007292169A - Constant velocity universal joint - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a constant velocity universal joint on which an end plate (a seal plate) functioning as a sliding stopper can be mounted having improved assembling efficiency on a vehicle. <P>SOLUTION: In the constant velocity universal joint, linear track grooves 26, 27 are formed on the outer peripheral face of an inner ring 21 and in the inner peripheral face of an outer ring 22, respectively, in the axial direction in a state of being inclined in mutually opposite directions with respect to the axial direction, and balls are incorporated in a crossing between both track grooves 26, 27 and held by a cage 24. A joint assembly 30 is composed of the inner ring 21, the outer ring 22, the balls 23 and the cage 24. At the end of the outer ring on the inward side of a hollow member, an axial shock absorbing mechanism 50 is provided between the outer diameter face 51 of the outer ring 22 and the inner diameter face 52 of the hollow member 31 for allowing the movement of the joint assembly 30 to which the end plate 37 is mounted in the hollow member 31 inward in the axial direction. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention is a power transmission device used for automobiles, various industrial machines, and the like, and is particularly incorporated in a propeller shaft or the like used in 4WD vehicles, FR vehicles, etc., and has a structure capable of absorbing axial displacement, etc. It relates to a universal joint.

  Propeller shafts used in automobiles such as 4WD vehicles and FR vehicles include a constant velocity universal joint so as to be able to cope with axial displacement and angular displacement due to a relative position change between the transmission and the differential. Usually, from the viewpoint of reducing the weight of the entire vehicle, a sliding type constant velocity universal joint called a Lebro type (or cross groove type) that is lightweight and has good rotational balance and vibration characteristics is incorporated (Patent Document 1). ).

  The Lebro type constant velocity universal joint is roughly classified into two types, a float type and a non-float type, and both types are properly used according to the characteristics (slide amount, etc.) of the vehicle equipped with the propeller shaft.

  As shown in FIG. 8, the constant velocity universal joint described in Patent Document 1 and the like includes an inner ring 1, an outer ring 2, a ball 3, and a cage 4 as main components. FIG. 8 shows a float type in which the minimum inner diameter of the cage 4 is smaller than the maximum outer diameter of the inner ring 1, that is, the inner ring incorporated in the cage does not come out in the axial direction.

  The inner ring 1 has a plurality of track grooves 6 formed on the outer peripheral surface thereof. A stub shaft 8 of a propeller shaft is inserted into the center hole 5 of the inner ring 1 and is spline-fitted, and torque can be transmitted between the two by the spline fitting.

  The outer ring 2 is located on the outer periphery of the inner ring 1, and the same number of track grooves 7 as the track grooves 6 of the inner ring 1 are formed on the inner peripheral surface thereof. The track groove 6 of the inner ring 1 and the track groove 7 of the outer ring 2 form an angle inclined in opposite directions with respect to the axis, and the ball 3 is formed at the intersection of the track groove 6 of the inner ring 1 and the track groove 7 of the outer ring 2 that make a pair. Is incorporated. A cage 4 is disposed between the inner ring 1 and the outer ring 2, and the ball 3 is held in a pocket 9 of the cage 4.

  The outer ring 2 is attached to a vehicle attachment flange (companion flange) 16. That is, the bolt member 18 inserted through the insertion hole 17 of the outer ring 2 is screwed into the screw hole 19 of the vehicle mounting flange 16. Thus, the constant velocity universal joint is fastened to the vehicle mounting flange 16.

  A sealing device 15 is mounted on the opposite side of the outer ring 2 from the flange side. The sealing device 15 includes a boot 12 and a metal boot adapter 13 in order to suppress the rotational expansion of the boot during high-speed rotation. The boot 12 has a small end portion 12b and a large end portion 12a, and is shaped like a V-shape in the middle. The boot adapter 13 includes a large-diameter cylindrical portion 13a, a small-diameter cylindrical main body portion 13b, and a radial wall portion 13c extending in the inner diameter direction from the cylindrical portion 13a toward the cylindrical main body portion 13b. 13a is externally fitted to the outer ring end on the opposite flange side. A through hole 18a through which the bolt member 18 is inserted is provided in the radial wall portion 13c.

  Accordingly, the bolt adapter 18 is used to fasten the boot adapter 13 to the outer ring 2, and the outer ring 2 to which the boot adapter 13 is attached is attached to the vehicle mounting flange 16. At this time, the radial wall portion 13 c of the boot adapter 13 abuts on the end surface 2 b on the opposite side of the outer ring 2. The small end portion 12b of the boot 12 is attached to the stub shaft 8 and fastened by the boot band 14, and the large end portion 12a of the boot 12 is held by crimping the end portion of the boot adapter 13.

  Such a Lebro type constant velocity universal joint includes an end plate 10. That is, the end plate 10 bulges toward the hollow portion side of the flange portion 16 and the cylindrical portion 10a that is externally fitted to the outer ring end portion on the opposite shaft protruding side, the radial wall portion 10b that extends from the cylindrical portion 10a in the inner diameter direction. A deep dish body 10c. The radial wall portion 10b is provided with a through hole through which the bolt member 18 is inserted, and the bolt member 18 is screwed into the screw hole 19 of the flange 16 through the through hole. For this reason, the radial wall portion 10 b is sandwiched between the end surface 2 a of the outer ring 2 and the outer ring corresponding surface 11 of the flange 16.

  In the constant velocity universal joint as shown in FIG. 8, the inner ring 1 can move to the flange inner side until it contacts the cage 4, but the outer ring 2 is received by the outer ring corresponding surface 11 of the flange 16. Cannot move to. For this reason, when the joint assembly body (inner ring, outer ring, ball, cage, etc.) is subjected to an impact (shock in the compression direction) with a large pressing force acting on the inner side of the flange, the impact must be absorbed. I can't.

For this reason, conventionally, when an impact force in the compression direction is applied, the inner ring presses the end plate (seal plate) and enters the hollow chamber side of the flange 16 to absorb the impact. Yes (Patent Document 2). That is, in the device described in Patent Document 2, the seal plate 10 is not sandwiched between the end surface 2a of the outer ring 2 and the outer ring corresponding surface 11 of the flange 1 as shown in FIG. It is installed in.
Japanese Utility Model Publication No. 1-168019 (FIGS. 1 and 4) JP 2001-347845 A

  In the thing of patent document 2, since the seal plate 10 is mounted in the hollow chamber of the flange 16, this seal plate 10 is constructed by assembling the inner ring 1, the outer ring 2, the ball 3, the cage 4, and the like. Cannot function as an end stopper. For this reason, when the joint assembly body is attached to the vehicle, it must be handled so that the inner ring or the like does not come off from the joint assembly body (so as not to exceed the slide range).

  Moreover, in the thing of the said patent document 1 and the patent document 2, since the bolt for fastening is used, rotational torque is transmitted by the frictional force which acts on the mating surface of an outer ring | wheel and a flange by tightening a bolt member. . However, in order to smoothly transmit this rotational torque, it is necessary to tighten the bolt member with a specified tightening torque. For this reason, it is necessary to adjust the tightening torque with high accuracy, and the assembly workability is poor.

  In view of the above-described problems, the present invention provides a constant velocity universal joint that can be attached with an end plate (seal plate) that also functions as a slide stopper and can be improved in assembling to a vehicle.

  In the constant velocity universal joint of the present invention, linear track grooves are formed in each of the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring in the axial direction in a state where they are inclined in directions opposite to each other in the axial direction. A joint assembly including an inner ring, an outer ring, a ball, and a cage is formed by incorporating balls into the intersections of the grooves and holding the balls by a cage disposed between the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring. In the constant velocity universal joint that is configured and fitted into the hollow member, the axially inward direction in the hollow member of the joint assembly body in which the end plate is mounted on the outer ring end on the inner side of the hollow member A compression-direction shock absorbing mechanism that allows movement toward the outer ring is provided between the outer diameter surface of the outer ring and the inner diameter surface of the hollow member.

  In the constant velocity universal joint of the present invention, the joint assembly is allowed to move inward in the axial direction within the hollow member, and therefore when subjected to an impact force in the compression direction (the shaft attached to the inner ring is the hollow member). The joint assembly can be slid into the hollow member. In addition, even if the end plate is attached to the joint assembly body, axial movement in the hollow member is allowed, so the end plate is attached to the joint assembly body before assembly to the vehicle. I can leave.

  Further, the axial shock absorbing mechanism is fitted into the axial guide groove formed on the inner diameter surface of the hollow member, the fitting recess formed on the outer diameter surface of the outer ring, and the fitting recess. The sliding member slides along the axial guide groove when the compression direction impact is applied, and the sliding member functions as a torque transmission means between the hollow member and the outer ring.

  As a result, the sliding member slides along the axial guide groove when the compression direction impact acts, so that the outer ring into which the sliding member is fitted, and thus the entire joint assembly body, is hollow along the axial guide groove. Slide inside. In addition, the sliding member can function as a torque transmission means between the hollow member and the outer ring, and a fastening operation using a bolt member is not necessary, and a reliable torque transmission can be performed with a reduced number of parts.

  When the sliding resistance to the hollow member of the joint assembly body is made larger than the sliding resistance in the joint assembly body, when the impact force in the compression direction is applied (the shaft attached to the inner ring is pressed toward the inner side against the hollow member. First, the ball held by the cage window in the joint assembly and the inner ring slide relative to the outer ring until the inner ring outer diameter surface and the cage inner diameter surface interfere with each other, that is, until the slide is restricted. Thereafter, the joint assembly can slide in the hollow member to absorb the impact.

  The hollow member and the joint assembly body can be fastened by providing a screw portion on the outer peripheral surface of the hollow member, and screwing an assembly tightening member into the screw portion. That is, it is possible to easily assemble a joint assembly composed of an inner ring, a cage, a ball and the like to the hollow member only by screwing the assembly fastening member into the threaded portion of the vehicle mounting flange (hollow member). it can.

  According to the constant velocity universal joint of the present invention, since the joint assembly body is allowed to move inward in the axial direction within the hollow member, the impact generated in the vehicle is absorbed when subjected to an impact force in the compression direction. can do. In addition, since the end plate can be attached to the joint assembly body before assembly to the vehicle, the end plate is a companion flange side seal member and a non-float type rebro type constant velocity universal joint. It can also function as a slide stopper, can prevent the inner ring from coming off from the joint assembly body during handling, etc., and can improve the ease of assembly of the joint assembly body to the vehicle.

When the axial impact absorbing mechanism receives an impact force in the compression direction because the outer ring with which the sliding member is fitted, and the joint assembly as a whole, slides along the axial guide groove to the inside of the hollow member. The joint assembly can be stably moved toward the inside of the hollow member, and the impact absorbing function can be effectively exhibited. In addition, since the torque transmission means between the hollow member and the outer ring can be constituted by a sliding member, the fastening work by the bolt member is not required, and the complicated phase alignment is not required by reducing the number of parts. As a result, the assembly workability can be improved. Moreover, reliable torque transmission is possible, and an excellent function as a constant velocity universal joint can be exhibited.

  By screwing the assembly fastening member, the joint assembly body can be reliably assembled to the vehicle mounting flange (hollow member) in a short time.

  An embodiment of a constant velocity universal joint according to the present invention will be described with reference to FIGS.

  As an embodiment of the present invention, a float type Lebro type (or cross groove type) in which the minimum inner diameter of the cage is set smaller than the maximum outer diameter of the inner ring, that is, the inner ring incorporated in the cage does not come out in the axial direction. ) Constant velocity universal joint is shown in FIG. It can be applied to a non-float type. In this case, the fastening force between the end plate and the outer ring is set to be larger than the sliding resistance of the shock absorbing portion.

  The constant velocity universal joint in this embodiment includes an inner ring 21, an outer ring 22, a ball 23, and a cage 24 as main components.

  The inner ring 21 has a plurality of track grooves 26 formed on the outer peripheral surface thereof. A stub shaft 28 is inserted into the center hole 25 of the inner ring 21 and is spline-fitted, and the torque can be transmitted between the two by the spline fitting. The stub shaft 28 is prevented from coming off from the inner ring 21 by the snap ring 20.

  The outer ring 22 is located on the outer periphery of the inner ring 21, and the same number of track grooves 27 as the track grooves 26 of the inner ring 21 are formed on the inner peripheral surface thereof. As shown in FIG. 2, the track groove 26 of the inner ring 21 and the track groove 27 of the outer ring 22 form an angle inclined in the opposite direction to the axis (track crossing angle α), and the track groove 26 of the inner ring 21 that forms a pair. A ball 23 is incorporated at the intersection of the outer ring 22 and the track groove 27. A cage 24 is disposed between the inner ring 21 and the outer ring 22, and the ball 23 is held in a pocket 29 of the cage 24.

  And the joint assembly body 30 comprised by the inner ring | wheel 21, the outer ring | wheel 22, the ball | bowl 23, the cage 24 grade | etc., Is mounted | worn with the hollow member 31 (a companion flange or a hollow shaft). When the outer diameter of the outer ring 22 is set smaller than the inner diameter of the hollow member 31 and the joint assembly 30 is attached to the hollow member 31, the outer diameter surface 51 of the outer ring 22 and the inner diameter surface 52 of the hollow member 31 A gap S is formed between the two.

  An end plate 37 is attached to the outer ring end portion on the opposite shaft protruding side (the outer ring end portion on the inner side of the hollow member). The end plate 37 closes the joint opening on the anti-shaft projecting side, and prevents leakage of grease filled in the joint and prevents foreign matter from entering. The end plate 37 bulges to the inner side of the hollow member 31, a cylindrical portion 37 a that is fitted (press-fitted) to the outer ring end portion on the opposite shaft protruding side, a radial wall portion 37 b that extends from the cylindrical portion 37 a in the inner diameter direction. A deep dish-shaped main body part 37c, and a tapered wall part 37d connecting the deep dish-shaped main body part 37c and the radial wall part 37b. When the end plate 37 is mounted, the radial wall portion 37b is in contact with the end surface 22a of the outer ring 22 on the side opposite to the shaft protruding side.

  A sealing device 40 is attached to the shaft protruding side of the joint assembly body 30. The sealing device 40 includes a boot 42 and a metal boot adapter 43 in order to suppress the rotational expansion of the boot during high-speed rotation. The boot 42 has a large end portion 42a and a small end portion 42b, and is shaped like a V-shape in the middle. The boot adapter 43 includes a large-diameter cylindrical portion 43a that is press-fitted into the outer ring end portion on the shaft protruding side, a small-diameter cylindrical main body portion 43b, a radial wall portion 43c that extends in an inner diameter direction from the cylindrical portion 43a, and a diameter thereof. A tapered wall portion 43d that connects the directional wall portion 43c and the cylindrical main body portion 43b is provided. A small end portion 42 b of the boot 42 is attached to the stub shaft 28 and fastened with a boot band 44. The large end 42 a of the boot 42 is held by crimping the end of the boot adapter 43.

  The axial shock absorbing mechanism 50 that allows the joint assembly 30 to move inward in the axial direction within the hollow member 31 is divided into an outer diameter surface (outer peripheral surface) 51 of the outer ring 22 and an inner diameter surface (inner side) of the hollow member 31. (Circumferential surface) 52. As shown in FIG. 1 and the like, when the joint assembly 30 is fitted in and attached to the hollow member 31, the cylindrical portion 37 a of the end plate 37 and the cylindrical portion 43 a of the boot adapter 43 are connected to the hollow member 31. The inner surface 52 is not contacted.

  The axial shock absorbing mechanism 50 includes an axial guide groove 49 formed on the inner diameter surface 52 of the hollow member 31, a fitting recess 53 formed on the outer diameter surface 51 of the outer ring 22, and the fitting recess 53. The sliding member 54 is fitted into the axial guide groove 49. That is, as shown in FIG. 3 and FIG. 4, fitting recesses 53 are provided on the outer diameter surface 51 of the outer ring 22 at a predetermined pitch (60 ° pitch in the example) along the circumferential direction. A sliding member 54 made of a solid pin member 54a is fitted. Further, axial guide grooves 49 are formed on the inner diameter surface 52 of the hollow member 31 at a predetermined pitch (60 ° pitch) along the circumferential direction corresponding to the fitting recesses 53 of the outer ring 22. The axial groove 49 of the hollow member 31 opens at the opening end of the joint assembly body 30 on the mounting side. This makes it easy to mold the hollow member 31 by cold molding or machining.

  The sliding member 54 fitted in the fitting recess 53 is fitted in the axial guide groove 49. Therefore, the sliding member 54 is pressed into the fitting recess 53 on the outer ring 22 side and the axial guide groove 49 on the hollow member 31 side, and constitutes a torque transmission means between the hollow member 31 and the outer ring 22. It will be.

  At this time, the sliding resistance of the joint assembly body 30 with respect to the hollow member 31 is set larger than the sliding resistance in the joint assembly body 30. Here, the sliding resistance of the joint assembly body 30 with respect to the hollow member 31 means that the sliding member 54 fitted in the fitting recess 53 of the outer ring 22 moves along the arrow Z along the axial guide groove 49 of the hollow member 31. It is the resistance when sliding in the direction. The slide resistance of the joint assembly body 30 is resistance when the inner ring 21 slides in the direction of arrow Z with respect to the outer ring 22.

  1, 3, and 5, a screw portion 59 is formed on the outer diameter surface 47 on the opening side of the hollow member 31, and an assembly fastening member 55 is screwed to the screw portion 59. ing. As shown in FIGS. 1 and 6, the assembly fastening member 55 includes a short cylindrical main body portion 57 having a screw portion 56 on its inner surface, and an inner flange portion 58 of the main body portion 57 on the sealing device side. Consists of. Then, the screw portion 56 of the tightening member 55 is screwed into the screw portion 59 of the hollow member 31 from the sealing device side. The inner flange 58 is formed of a ring body having an axial hole 61, and the inner diameter thereof is larger than the outer diameter of the cylindrical main body 43 b of the boot adapter 43, and the inner diameter end of the radial wall 43 c of the boot adapter 43. The diameter is about. Further, on the outer peripheral surface (outer diameter surface) 62 of the main body 57 of the tightening member 55, fitting planes 63 are formed at a predetermined pitch along the circumferential direction. The fitting plane 63 is for engaging (fitting) a jig (not shown) for fastening the fastening member 55. In addition, although the fitting plane 63 is provided at six places in the illustrated example, it is sufficient that at least two places are provided in consideration of the fastening property of the fastening member 55.

  Next, a method for assembling the constant velocity universal joint configured as described above to the hollow member 31 will be described. First, the sliding member 54 is fitted into the fitting recess 53 of the outer ring 22 of the joint assembly 30, and the joint assembly 30 is inserted (inserted) into the hollow member 31 along the axial direction. At this time, the phase of the sliding member 54 fitted in the fitting recess 53 of the outer ring 22 is matched with the phase of the axial guide groove 49 of the hollow member 31, so that the threaded portion 56 of the assembly tightening member 55. Is screwed into the threaded portion 59 of the hollow member 31.

  That is, if the assembly fastening member 55 is screwed into the threaded portion 59 of the hollow member 31, the inner flange portion 58 of the assembly fastening member 55 presses the radial wall portion 43 c of the boot adapter 43. Thus, the joint assembly 30 is fitted into the hollow member 31. When this screwing is completed, the sliding member 54 fitted in the fitting concave portion 53 of the outer ring 22 is pressed into the axial concave groove 49 of the hollow member 31, and the joint assembly body 30 is hollow. It is assembled to the member 31. In this assembled state, the radial wall 43 c of the boot adapter 43 is sandwiched between the end surface 22 b of the outer ring 22 and the inner surface of the inner collar portion 58 of the assembly fastening member 55.

  In the constant velocity universal joint assembled to the hollow member 31 as described above, the slide resistance of the joint assembly body 30 with respect to the hollow member 31 is larger than the slide resistance within the joint assembly body 30 as described above. Therefore, when the constant velocity universal joint receives an impact force in the compression direction (when the shaft 28 receives a pressing force in the arrow Z direction shown in FIG. 1 with respect to the hollow member 31), first, the joint assembly body The ball 23 held by the cage window 29 and the inner ring 21 slide within 30. At this time, it slides until the inner ring outer diameter interferes with the cage inner diameter (relative displacement with respect to the outer ring 22). Thereafter, the joint assembly 30 slides in the hollow member 31 as indicated by phantom lines in FIG.

  In the constant velocity universal joint configured as described above, the joint assembly 30 moves inward in the axial direction within the hollow member 31 when it receives an impact force in the compression direction in a state where it is mounted on the hollow member 31. Therefore, the joint assembly 30 can escape to the inside of the hollow member 31 and can absorb the impact generated in the vehicle. Moreover, since the end plate 37 can be attached to the joint assembly 30 before being assembled to the vehicle, the end plate 37 functions as a sealing member on the hollow member 31 side. The press-fitting allowance of the sliding member 54 to the axial concave groove 49 can be adjusted according to the magnitude of the axial force input when receiving an impact force in the compression direction. That is, by adjusting the press-fitting allowance, it is possible to absorb the impact corresponding to the impact force received.

  In addition, since the outer ring 22 into which the sliding member 54 is fitted and the joint assembly 30 as a whole slides along the axial guide groove 49 to the inside of the hollow member, the axial shock absorbing mechanism 50 slides in the compression direction. When receiving an impact force, the joint assembly 30 can be stably moved to the inside of the hollow member, and the impact absorbing function can be effectively exhibited. Further, since the torque transmission means between the hollow member 31 and the outer ring 22 can be constituted by the sliding member 54, the fastening work by the bolt member is not required, and the complicated phase alignment is not required by reducing the number of parts. Thus, the assembly workability can be improved. Moreover, reliable torque transmission is possible, and an excellent function as a constant velocity universal joint can be exhibited.

  By screwing the assembly fastening member 55, the joint assembly 30 can be reliably assembled to the hollow member 31 in a short time. The tightening direction of the assembly fastening member 55 may be arbitrarily set according to the entire rotation direction.

  Next, FIG. 7 shows another embodiment. In this case, a ball (sphere) 54 b is used as the sliding member 54 of the axial direction impact absorbing mechanism 50. That is, two balls 54 b are fitted in each fitting recess 53. Further, the cylindrical portion 43 a of the boot adapter 43 of the sealing device 40 is externally fitted to the opening of the hollow member 31. That is, the circumferential groove 45 is formed in the outer diameter surface 47 of the hollow member 31, and the cylindrical portion (cylindrical outer fitting portion) 43 a of the adapter 43 is press-fitted (outer fitting) into the hollow member 31. The distal end portion 46 is caulked and fitted into the circumferential groove 45. The circumferential groove 45 is formed with an inclined portion 45a in which the end surface 31a side of the hollow member 31 becomes shallow toward the end surface 31a. The other configuration of the constant velocity universal joint shown in FIG. 7 is the same as that of the constant velocity universal joint shown in FIG. 1. In FIG. 7, the same members as those in FIG. The description thereof is omitted.

  Also in the constant velocity universal joint shown in FIG. 7, the slide resistance of the joint assembly body 30 with respect to the hollow member 31 is made larger than the slide resistance in the joint assembly body 30.

  Next, a method for assembling the joint assembly 30 of the constant velocity universal joint shown in FIG. 7 to the hollow member 31 will be described. In this case, the joint assembly body 30 is press-fitted into the hollow member 31 with the pair of balls 54 b and 54 b fitted in the fitting recess 53 of the outer ring 22 of the joint assembly body 30. In the press-fitted state, the radial wall portion 43 c of the boot adapter 43 is brought into contact with the end surface 31 a of the hollow member 31 and is brought into contact with the end surface 22 b on the end plate side of the outer ring 22.

  Therefore, even in the constant velocity universal joint shown in FIG. 7, when the impact force in the compression direction is applied, the joint assembly body 30 can escape to the inside of the hollow member 31 and absorb the impact generated in the vehicle. Can do. In addition, the end plate 37 can be attached to the joint assembly 30 before being assembled to the vehicle. For this reason, also in the constant velocity universal joint shown in FIG. 7, the same effect as the constant velocity universal joint shown in the said FIG. 1 can be show | played. Moreover, the assembly fastening member is not required, the number of parts can be reduced, and the cost can be reduced.

  Although the embodiments of the present invention have been described above, the number of sliding members 54 can be increased or decreased arbitrarily. In this case, the outer diameter of the pin member 54a, the length of the pin member 54a, and the thickness of the cylindrical member 54 are different depending on the thickness of the pin member 54a. Any device can be used as long as it can be moved to the side, can exhibit an impact absorbing function, and can transmit torque. In this way, the outer diameter dimension, the length dimension of the sliding member 54, and the wall thickness dimension of the cylindrical body can be variously changed as long as the shock absorbing function can be exhibited and torque transmission is possible. Furthermore, various materials can be used as the material of the sliding member 54.

  Even when the ball 54b is used for the sliding member 54, the outer diameter of the ball 54b, the number to be fitted in one fitting recess 53, the material of each ball 54b, etc. can exhibit the shock absorbing function. Moreover, various changes can be made as long as torque transmission is possible.

It is sectional drawing of the constant velocity universal joint which shows embodiment of this invention. It is a partial front view for demonstrating the track crossing angle in the inner ring | wheel and outer ring | wheel of the said constant velocity universal joint. It is the sectional view on the AA line in the state where the fastening member of Drawing 1 was omitted. It is a rear view of a joint assembly body. It is a rear view of a hollow member. It is a rear view of the fastening member for assembly. It is sectional drawing of other embodiment of this invention. It is sectional drawing of the conventional constant velocity universal joint. It is sectional drawing of the other conventional constant velocity universal joint.

Explanation of symbols

21 Inner ring 22 Outer ring 23 Ball 24 Cage 26, 27 Track groove 30 Joint assembly 31 Hollow member 37 End plate 49 Axial guide groove 50 Axial shock absorbing mechanism 51 Outer diameter surface 52 Inner diameter surface 53 Fitting recess 54 Sliding member 55 Assembly Tightening member 59 Threaded part

Claims (4)

A straight track groove is formed on each of the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring in the axial direction in a state of being inclined in opposite directions with respect to the axial direction, and balls are incorporated at the intersections of both track grooves, The balls are held by a cage disposed between the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring to form a joint assembly body including the inner ring, the outer ring, the ball, and the cage. The joint assembly body is hollow. In the constant velocity universal joint inserted in the member,
A compression-direction shock absorbing mechanism that allows an axially inward movement of the joint assembly body, in which the end plate is mounted on the outer ring end on the inner side of the hollow member, in the hollow member, the outer diameter surface of the outer ring and the hollow member A constant velocity universal joint characterized in that it is provided between the inner diameter surface of the joint.   The axial shock absorbing mechanism is compressed by being fitted in the axial guide groove formed in the inner diameter surface of the hollow member, the fitting recess formed in the outer diameter surface of the outer ring, and the fitting recess. 2. A sliding member that slides along an axial guide groove when a direction impact is applied, and the sliding member functions as a torque transmission means between the hollow member and the outer ring. Fast universal joint.   The constant velocity universal joint according to claim 2, wherein a sliding resistance of the joint assembly body with respect to the hollow member is larger than a sliding resistance in the joint assembly body.   A screw part is provided in the outer peripheral surface of the said hollow member, the fastening member for assembly is screwed together in this screw part, and the said hollow member and a joint assembly body are fastened. One of the constant velocity universal joints.

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