JP2017048880A - Constant velocity universal joint - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a constant velocity universal joint which suppresses an increase of a joint dimension and weight while preventing the breakage of a joint itself and a peripheral member while being brought into a torque-released state when excessively-large torque is generated, and can improve maintenance and restoration work.SOLUTION: An outside joint member has a cylindrical external peripheral side member which is attached to a flange member connected to a device-side member, and an internal peripheral side member in which a track groove is formed at an inside diameter face, and which is continuously arranged at the external peripheral side member. A torque limiter which releases torque by idling states of rolling bodies between the outside joint member and the flange member, a cage, and an inside joint member at the generation of excessively-large torque is arranged at an external peripheral side of the external peripheral side member. The torque limiter has a plunger whose tip part can be inserted into and released from a recess which is formed at the flange member, and a spring member for push-pressing the plunger, fitting its tip part into the recess, and making the plunger engaged with the recess.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a constant velocity universal joint, and more particularly, to a constant velocity universal joint used for a power transmission mechanism (rotation transmission unit) in a drive device of an industrial machine (steel, paper, or construction machine).

  14 and 15 show an example of a constant velocity universal joint used for a power transmission mechanism in a drive device of an industrial machine. This constant velocity universal joint includes an outer joint member 3 having a track groove 2 on an inner diameter surface 1, an outer joint member 3, and an outer joint member 3. An inner joint member 6 having a track groove 5 on the radial surface 4; a plurality of balls 7 interposed between the track groove 2 of the outer joint member 3 and the track groove 5 of the inner joint member 6; A cage 9 is provided between the inner diameter surface 1 of the joint member 3 and the outer diameter surface 4 of the inner joint member 6 to hold the balls 7. The center of curvature O1 of the outer peripheral surface 9a of the cage 9 and the center of curvature O2 of the inner peripheral surface 9b are offset in the axial direction opposite to the angle center O of the joint.

  The outer joint member 3 is fixed to the flange member 10. That is, the flange member 10 includes a short cylindrical portion 10a and an outer flange portion 10b provided continuously with one opening of the short cylindrical portion 10a. Further, a notch 3a for fitting is provided at an end of the outer joint member 3 on the flange member side, and an outer diameter side end of the short cylindrical portion 10a of the flange member 10 on the opposite outer flange side is provided on the notch 3a for fitting. In this state, the flange member 10 and the outer joint member 3 are integrated by welding. In addition, in FIG. 14, S has shown the welding part.

  FIG. 16 shows a state in which the constant velocity universal joint shown in FIGS. 14 and 15 is connected to the shaft 20. The shaft 20 has a large-diameter main body 20a and a small-diameter end 20b, and a male spline 21 is formed at the end of the small-diameter end 20b. Further, a female spline 22 is formed on the inner diameter surface of the axial hole of the inner joint member 6, and the male spline 21 is fitted into the axial hole of the inner joint member 6 so that the male spline 21 and the female spline 22 are fitted.

  Further, a stopper 23 that is in contact with the end surface of the inner joint member 6 on the inner side of the joint is attached to the end surface of the shaft 20 via a bolt member 24 that is screwed to the end surface of the shaft 20. Further, a circumferential groove is formed on the proximal end side of the female spline 22, and a retaining ring 25 is attached to the circumferential groove.

  The opening of the outer joint member 3 is closed with a sealing device 30. The sealing device 30 includes a boot 31 made of a flexible material such as a rubber material or a resin material, and a metal adapter 32. The boot 31 includes a large-diameter portion 31a, a small-diameter portion 31b, and a bent portion 31c having a substantially U-shaped cross section that connects the large-diameter portion 31a and the small-diameter portion 31b.

  The adapter 32 includes a mounting portion 32a mounted on the opening end of the outer joint member 3, and a short cylindrical portion 32b extending from the mounting portion 32a to the other joint side. The mounting portion 32 a is provided with a fitting recess 33, and the opening of the outer joint member 3 is fitted into the fitting recess 33. The adapter 32 is attached to the outer joint member 3 via a bolt member 34 that is screwed to the outer joint member 3. The large diameter portion 31a of the boot 31 is fitted on the short cylindrical portion 32b, and the boot band 35 is fastened to the large diameter portion 31a. Thereby, the adapter 32 and the boot 31 are fixed. Further, the small diameter portion 31b of the boot 31 is externally fitted to the boot mounting portion 36 of the shaft 20, and the boot band 35 is fastened to the small diameter portion 31b. Thereby, the shaft 20 and the boot 31 are fixed.

  The flange member 10 is connected to a device fixing shaft member (not shown). That is, the flange portion of the device fixing shaft member and the flange member 10 are connected to each other via the fastener (bolt / nut connection) 36.

  When a constant velocity universal joint (sliding type constant velocity universal joint) as shown in FIG. 14 is applied to a rotation transmission part as a drive device for an industrial machine, excessive torque is generated due to overloading of equipment peripheral members during driving. In addition, the joints and peripheral members may be damaged.

  That is, as shown in FIG. 17, the constant velocity universal joint for an industrial machine rotates with a substantially constant torque for many hours during operation (A to D in FIG. 17). Excessive torque is generated due to overloading of the member, and the joint and peripheral members may be damaged. In FIG. 17, excessive torque is generated in front of the A part, between the A part and the B part, between the B part and the C part, and between the C part and the D part.

  Therefore, conventionally, as described in Non-Patent Document 1, in a constant velocity universal joint for roll driving used in a rolling mill, when momentary excessive torque is generated, torque transmission acting on the constant velocity universal joint is instantaneously transmitted. In some cases, a torque limiter is used to open the door. Non-Patent Document 1 discloses a shear pin type torque limiter and a hydraulic expansion type torque limiter.

  The shear pin type torque limiter performs torque release by shearing a pin (metal material). The hydraulic expansion type torque limiter combines a cylindrical hole flange provided with a hydraulic expansion chamber and a cylindrical shaft flange, and supports both ends thereof with bearings. That is, by enclosing and releasing oil in the hydraulic expansion chamber, the transmission torque is controlled by changing the static frictional force of the contact surface between the cylindrical hole flange and the cylindrical shaft flange.

  Another example of the torque limiter is a ball clutch type torque limiter. This ball clutch type torque limiter is pushed into a hole by a spring force, and torque is transmitted to the ball. When a torque exceeding the set value (excessive torque) is applied, the ball escapes from the hole against the spring force and enters a free rotation state.

JTEKT Engineering Journal No.1004 (2007) P78-P81

  In a shear pin type torque limiter, since shear fracture is governed by material strength, there is a large variation in shear torque during operation. In terms of maintenance, metal fatigue accumulates in the stress concentration part of the round bar, so periodic shear pin replacement is necessary. In addition, when the machine is restored after operation, it is necessary to take care of the shear pin built-in portion, etc., which requires a lot of time for maintenance.

  The hydraulic expansion type torque limiter is more maintainable than the shear pin type torque limiter, but the structure becomes complicated due to the need for a control device that manages the hydraulic pressure by providing a cylindrical hole flange and a cylindrical shaft flange in a member other than the joint. In addition, the weight is increased and the cost is significantly increased.

  In the ball clutch type torque releaser, the value for releasing the torque varies greatly depending on the contact position between the ball, which is the torque transmission part, and the recess, and thus it is difficult to manage the set value for releasing the torque when overloaded. Further, like the shear pin type torque limiter, when the excessive torque is generated, the rotating member idles, so that the rotating member needs to be supported by the bearing, and the joint size and weight increase.

  Therefore, the present invention enters a torque release state when excessive torque is generated, and prevents damage to the joint itself and peripheral members, while suppressing increase in joint dimensions and weight, and improving maintenance and recovery work. Provided is a constant velocity universal joint that can be used.

  The constant velocity universal joint of the present invention includes an outer joint member having a track groove on the inner diameter surface, an inner joint member having a track groove on the outer diameter surface, and a track groove of the outer joint member and a track groove of the inner joint member. Constant velocity freely including a plurality of balls as rolling elements that transmit torque by being interposed between them and a cage that holds the balls interposed between the inner diameter surface of the outer joint member and the outer diameter surface of the inner joint member A joint, wherein the outer joint member is attached to a flange member connected to the apparatus side member, and has a torque limiter that releases torque between the outer joint member and the flange member when excessive torque is generated, The torque limiter includes a plunger in which a tip portion can be inserted into and removed from a recess provided in the flange member, and a spring portion that presses the plunger to engage the tip portion with the recess. And it has a door.

  In the constant velocity universal joint of the present invention, the torque transmission path is performed by the ball as the rolling element → the inner peripheral member →→ the outer peripheral member → the torque limiter → the flange member. At this time, if excessive torque (a preset value and torque that may damage the constant velocity universal joint itself or its peripheral members) is generated, the plunger is resisted against the reaction force of the spring member. Escapes from the recess, causing the outer joint member, rolling element (ball), cage, and inner joint member to idle and release torque.

  It is preferable that the torque release value is controlled based on the pressing force of the spring member, the shape of the tip of the plunger, and the number of torque limiters provided.

  It is preferable that the spring member of the torque limiter has a pressing force that automatically returns to a state in which the distal end portion of the plunger is engaged with the concave portion in an unloaded state of excessive torque.

  The tip of the plunger of the torque limiter may have any shape selected from a cylindrical shape, a tapered shape, or an arc shape. Moreover, it is preferable that a plunger is comprised with the carbon steel for machine structure, or chromium molybdenum steel materials, and the hardening process of induction hardening tempering or carburizing hardening tempering is performed. Further, the inner surface of the concave portion provided in the short cylindrical portion of the flange member can be set so as to have a tapered surface shape or an arc shape.

  At least the inner surface of the recess provided in the short cylindrical portion of the flange member is made of mechanical structural carbon steel or chromium molybdenum steel material, and is subjected to induction hardening tempering or carburizing quenching tempering hardening treatment. Preferably it is.

  The outer joint member includes a cylindrical outer peripheral member, and an inner peripheral member that is formed with a track groove on an inner diameter surface and is connected to the outer peripheral member, and the outer joint member is disposed on the outer peripheral side of the outer peripheral member. A torque limiter may be provided.

  In the present invention, since the torque limiter is disposed on the outer peripheral side of the outer peripheral side member, an increase in the size and weight of the constant velocity universal joint itself can be suppressed, and the constant velocity universal joint itself and the peripheral member are caused by excessive torque generation. Damage can be prevented.

  In the case of controlling the torque release value, stable torque release can be performed, damage to the constant velocity universal joint itself and peripheral members can be effectively prevented, and the durability is excellent.

  The spring member of the torque limiter preferably has a pressing force that automatically returns to a state in which the distal end portion of the plunger is engaged with the concave portion in an unloaded state of excessive torque. As described above, in the case of automatic return, it is possible to shorten the time for maintenance and recovery work, and it is possible to improve workability and cost.

It is sectional drawing of the constant velocity universal joint of this invention. It is a front view which shows a part at the time of torque load of the constant velocity universal joint of FIG. It is a side view of the constant velocity universal joint of FIG. It is a front view which shows a part at the time of torque release of the constant velocity universal joint of FIG. It is sectional drawing of a 1st torque limiter. It is an enlarged front view of the plunger of the 1st torque limiter. FIG. 7 is an X1 arrow diagram of FIG. 6. FIG. 7 is an X2 arrow diagram of FIG. 6. The first torque limiter is shown, (a) is a sectional view at the time of torque load, (b) is a sectional view at the time of torque release, and (c) is a sectional view at the time of automatic return. The 2nd torque limiter is shown, (a) is a sectional view at the time of torque load, (b) is a sectional view at the time of torque release, and (c) is a sectional view at the time of automatic return. It is sectional drawing of a 3rd torque limiter. It is sectional drawing of a 4th torque limiter. It is sectional drawing of a 5th torque limiter. It is sectional drawing of the conventional constant velocity universal joint. It is a front view of the constant velocity universal joint of FIG. It is sectional drawing of the state which integrated the constant velocity universal joint of FIG. 14 in the industrial machine. It is a graph which shows the torque pattern loaded on a constant velocity universal joint.

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

  1 to 4 show a constant velocity universal joint according to the present invention. The constant velocity universal joint includes an outer joint member 53 having a track groove 52 on an inner diameter surface 51 and an inner side having a track groove 55 on an outer diameter surface 54. A joint member 56, a plurality of balls 57 that are interposed between the track groove 52 of the outer joint member 53 and the track groove 55 of the inner joint member 56, and transmit torque, the inner diameter surface 51 of the outer joint member 53, and the inner joint A cage 59 that is interposed between the outer diameter surface 54 of the member 56 and holds the ball 57.

  The center of curvature O1 of the outer peripheral surface 59a of the cage 59 and the center of curvature O2 of the inner peripheral surface 59b are offset in the axial direction opposite to the angle center O of the joint. That is, this constant velocity universal joint is a so-called double offset type sliding constant velocity universal joint.

  The outer joint member 53 includes a cylindrical outer peripheral member 60 and an inner peripheral member 61 having a track groove 52 formed on the inner diameter surface 51. In this case, a circumferential notch 62 is provided on the inner diameter side of the end surface of the outer peripheral member 60 on the inner peripheral member 61 side, and the outer diameter of the inner peripheral member 61 on the outer peripheral member 60 side is provided in the circumferential notch 62. The side end 63 is fitted, and in this state, the outer peripheral member 60 and the inner peripheral member 61 are joined and integrated by a joining means such as welding. In FIG. 1, S indicates a welded portion.

  The outer peripheral side member 60 of the outer joint member 53 is attached to the flange member 65. That is, the flange member 65 includes a short cylindrical portion 65a and an outer flange portion 65b provided continuously to one opening of the short cylindrical portion 65a. The outer peripheral member 60 is fitted on the short cylindrical portion 65a. The flange member 65 is connected to a device side member (not shown). That is, the flange portion of the apparatus side member and the flange member 65 are connected via the fixing tool (bolt / nut connection) 64.

  Further, torque limiters 66 are arranged on the outer peripheral side of the outer peripheral member 60 at a predetermined pitch (90 ° pitch in the illustrated example) along the same circumferential direction. As shown in FIG. 5, the torque limiter 66 includes a plunger 67 and a spring member 68 that elastically presses the plunger 67 toward the distal end side thereof. The spring member 68 is accommodated in the casing 69. The casing 69 includes a main body 69a formed of a cylindrical body having an upper wall 69c in which a through hole 70 is formed, and an outer flange 69b that protrudes from the lower outer peripheral portion of the main body 69a to the outer diameter side.

  The plunger 67 includes a first shaft portion 67a and a second shaft portion 67c connected to the first shaft portion 67a via an outer flange portion 67b. As shown in FIGS. 6 and 7, the first shaft portion 67a is made of a columnar body, the outer flange portion 67b is made of a disk shape body, and the second shaft portion 67c is made of a disk shape body, as shown in FIGS. And a prismatic body (a quadrangular prism-shaped body). Further, the second shaft portion 67c has a notch formed in the tip surface thereof, and the tip portion is tapered. That is, a tapered portion 71 having a tapered surface 71a at the tip is formed. As the taper angle θ of the taper surface 71a, for example, an acute angle, that is, an angle smaller than 0 ° and smaller than 90 ° can be set.

  And the outer peripheral side member 60 of the outer joint member 53 is provided with a hole portion 72 through which the second shaft portion 67c of the plunger 67 passes, as shown in FIG. For this reason, the plunger 67 has its outer flange portion 67 b accommodated in the main body portion 69 a of the casing 69, and the spring member 68 is externally fitted to the first shaft portion 67 a of the plunger 67. It is interposed between the upper wall 69 c of 69 a and the outer flange portion 67 b of the plunger 67. Therefore, the outer flange 67b of the plunger 67 is pressed toward the inner diameter side and comes into contact with the outer diameter surface of the outer peripheral member 60 of the outer joint member 53, and the tapered portion 71 at the tip of the second shaft portion 67c It protrudes to the inner diameter side from the inner diameter surface of the outer peripheral side member 60.

  A through hole 73 is provided in the outer flange portion 69 b of the casing 69, and a screw hole 74 is provided in the outer peripheral side member 60 corresponding to the through hole 73. For this reason, the casing 69 can be attached to the outer peripheral side member 60 by inserting the bolt member 75 into the through hole 73 in the outer flange portion 69 b of the casing 69 and screwing it into the screw hole 74.

  Further, as shown in FIGS. 1 and 2, the short cylindrical portion 65a of the flange member 65 is provided with a concave portion 77 into which the distal end portion of the plunger 67, that is, the tapered portion 71 can be inserted and removed. In this case, as shown in FIG. 9A and the like, in a state where the outer flange portion 67b of the plunger 67 is in contact with the outer diameter surface of the outer peripheral side member 60 and the distal end portion of the plunger 67 is fitted, The tip surface 71b of the plunger 67 does not come into contact with the bottom surface 77a of the recess 77, and as shown in FIG. 9C, at the time of automatic return (in the initial state where no excessive torque is applied, the taper portion 71 of the plunger 67 The end surface 71 d on the side opposite to the taper surface comes into contact with the side surface 77 c of the recess 77.

  A circumferential groove 80 is formed on the outer circumferential surface of the outer circumferential member 60, and the recess 77 is formed in the circumferential groove 80. In this case, as shown in FIG. 5, when the width dimension of the circumferential concave groove 80 is H and the width dimension of the tapered portion 71 of the plunger 67 is h, H> h. 9A, 9B, and 9C, the rounded portion 78 is provided at the open end of the side surface 77b corresponding to the tapered surface 71c of the plunger 67 of the concave portion 77 and the side surface 77c corresponding to the anti-tapered surface. , 79 are formed.

  In this constant velocity universal joint, when the torque is applied, the short cylindrical portion 65a of the flange member 65 is displaced in the arrow direction with respect to the outer peripheral side member 60 as shown in FIG. For this reason, the taper portion 71 of the plunger 67 abuts on the rounded portion 78 of the side surface 77 b of the recess 77.

  Therefore, in the constant velocity universal joint configured as described above, the torque transmission path is the ball 57 as the rolling element → the inner peripheral member 61 → the outer peripheral member 60 → the plunger 67 of the torque limiter 66 → the flange member 65. Done. For this reason, in the state where the excessive torque is not generated as shown in FIG. 17, the taper portion 71 of the plunger 67 contacts the rounded portion 78 of the side surface 77 c of the recess 77 as shown in FIG. The state can be maintained.

  However, as shown in FIG. 17, when an excessive torque is generated, the taper surface 71a of the plunger 67 slides on the rounded portion 78, and the plunger 67 is pushed up against the elastic force of the spring member 68. As shown in FIG. 9B, the distal end surface 71 b of the plunger 67 rides on the circumferential groove 80 of the outer member 60. In this state, the outer joint member 53, the rolling element (ball) 57, the cage 59, and the inner joint member 56 are in a torque release state in which they idle.

  After the torque is released, the plunger 67 is restrained from operating in the axial direction by the circumferential concave groove 80 and prevents the outer peripheral side member 60 from falling off the flange member 65 during operation. Then, when the recess 77 and the plunger 67 are in the same phase in the circumference, as shown in FIG. 9C, the taper portion 71 at the tip of the plunger 67 returns to the initial state where it is fitted into the recess 77. That is, when the excessive torque load is released, the torque transmission is resumed automatically.

  Next, FIG. 10 has two tapered surfaces 71 a and 71 c as the tapered portion 71 at the distal end portion of the plunger 67. For this reason, as shown in FIG. 10A, in a torque load state that is not excessive, the tapered portion 71 at the tip of the plunger 67 is fitted into the recessed portion 77, and one tapered surface 71a is formed on the side surface 77b of the recessed portion 77. While being in contact with the rounded portion 78, the other tapered surface 71 c is in contact with the rounded portion 79 of the side surface 77 c of the recess 77. In this state, the tip surface 71 b of the plunger 67 does not contact the bottom surface 77 a of the recess 77.

  When an excessive torque is generated, the tapered surface 71a (71c) of the plunger 67 slides on the rounded portion 78 (79), and the plunger 67 is pushed up against the elastic force of the spring member 68. Finally, as shown in FIG. 10B, the tip surface 71b of the plunger 67 rides on the circumferential groove 80 formed on the outer peripheral surface of the short cylindrical portion 65a of the flange member 65, and torque It becomes an open state.

  When the recess 77 and the plunger 67 are in the same phase around the circumference, the taper portion 71 at the tip of the plunger 67 returns to the initial state where it is fitted into the recess 77 as shown in FIG. That is, when the excessive torque load is released, the torque transmission is resumed automatically.

  As a distal end portion of the plunger 67 in FIG. 11, a tapered portion 81 having a pair of opposed convex curved surfaces 81a and 81c is formed. Also in this case, in a torque load state that is not excessive, the tapered portion 81 at the tip of the plunger 67 is fitted into the recess 77, and one convex curved surface 81a abuts against the round portion 78 of the side surface 77b of the recess 77, The other convex curved surface 81 c comes into contact with the rounded portion 79 of the side surface 77 c of the concave portion 77. In this state, the tip surface 81 b of the plunger 67 does not contact the bottom surface 77 a of the recess 77.

  Even in this case, when excessive torque is generated, the convex curved surface 81a (81c) of the plunger 67 slides on the rounded portion 78 (79), and the plunger 67 resists the elastic force of the spring member 68. As a result, the tip end surface 81b of the plunger 67 rides on the circumferential groove 80 formed on the outer peripheral surface of the outer peripheral member 60, and the torque is released.

  When the concave portion 77 and the plunger 67 are in the same phase in the circumference, the taper-shaped portion 81 of the plunger 67 returns to the initial state where it is fitted into the concave portion 77. That is, when the excessive torque load is released, the torque transmission is resumed automatically.

  12 and 13, the tip portion of the second shaft portion 67 c of the plunger 67 is not formed with the taper portion 71 or the tapered portion 81, but simply with a chamfered portion 82 formed at the tip corner portion. is there. In FIG. 12, the side surfaces 77b and 77c of the recess 77 are inclined surfaces, and the cross-sectional shape of the recess 77 is a trapezoidal shape in which the outer diameter side is larger than the inner diameter side. In FIG. 13, the side surfaces 77b and 77c of the recess 77 are concave curved surfaces, and the end surfaces are not provided at the tips.

  For this reason, even in the case shown in FIGS. 12 and 13, the chamfered portion 82 at the tip of the second shaft portion 67c comes into contact with the side surfaces 77b and 77c, and the torque can be transmitted, resulting in excessive torque. In this case, the chamfered portion 82 of the plunger 67 slides on the side surfaces 77b and 77c, pushes up the plunger 67 against the elastic force of the spring member 68, and finally the distal end surface of the plunger 67. 71b rides on the circumferential groove 80 formed on the outer peripheral surface of the outer peripheral member 60, and the torque is released.

  By the way, if the torque load direction shown in FIG. 9 is assumed to be normal rotation, the one shown in FIGS. 10 to 13 can cope with a torque load direction opposite to the torque load direction shown in FIG. . That is, the one shown in FIGS. 10 to 13 can cope with forward and reverse rotation.

  In the present invention, since the torque limiter 66 is disposed on the outer peripheral side of the outer peripheral member 60, an increase in the size and weight of the constant velocity universal joint itself can be suppressed, and excessive torque of the constant velocity universal joint itself and the peripheral members can be suppressed. Damage due to occurrence can be prevented.

  In this constant velocity universal joint, the value for releasing the torque is controlled based on the pressing force of the spring member 68, the shape of the tip of the plunger 67, and the number of torque limiters 66 provided. In the case of controlling the torque release value, stable torque release can be performed, damage to the constant velocity universal joint itself and peripheral members can be effectively prevented, and the durability is excellent.

  The spring member 68 of the torque limiter 66 is set so as to have a pressing force that automatically returns to a state in which the distal end portion of the plunger 67 engages with the concave portion 77 in an unloaded state of excessive torque. As described above, in the case of automatic return, it is possible to shorten the time for maintenance and recovery work, and it is possible to improve workability and cost.

  In this constant velocity universal joint, the inner joint member 56 and the cage 59 are well known in terms of materials, manufacturing methods, dimensional shapes, hardness, surface roughness, etc., and can be applied as existing technology, resulting in cost reduction. Can be planned.

  The plunger 72 and the hole 72 and the recess 77 of the outer peripheral member 53 are torque transmitting portions, and the plunger 67 needs to be smoothly slid in the circumferential direction or the radial direction. For this reason, materials with excellent dimensional accuracy, surface roughness, hardness, workability, and strength, such as carbon steel for mechanical structure and chromium molybdenum steel, are selected, and induction hardening tempering and carburizing and quenching are used as heat treatment. It is desirable to temper.

  Further, by providing the rounded portions 78 and 79 at the open ends of the side surfaces 77b and 77c of the concave portion 77, it is possible to avoid the occurrence of breakage or cracks due to the contact stress from the plunger 67. In addition, although a chamfer part may be provided instead of the round parts 78 and 79, the effect of avoiding the occurrence of breakage, cracks, and the like is small compared to the round parts 78 and 79.

  The tip of the plunger 67 of the torque limiter 66 can be any shape selected from a cylindrical shape, a tapered shape, or an arc shape, and is excellent in design.

  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 can be made. As described above, the number of torque limiters 66 is a value for releasing torque. Since it is one parameter for control, it can be increased or decreased. Moreover, as the spring member 68 of the torque limiter 66, the disc spring is used in the above embodiment, but another coil spring or the like may be used. As shown in FIG. 6, when the plunger 67 has one tapered surface 71a, the arrangement position of the tapered surface 71a can be adjusted by the torque load direction. Further, in the embodiment, the outer joint member 53 has been described as a type having the cylindrical outer peripheral side member 60 and the inner peripheral side member 61 in which the track groove 52 is formed on the inner diameter surface 51, but is not limited thereto. In this outer joint member, the outer peripheral member and the inner peripheral member may be integrated.

  As the constant velocity universal joint, the double offset type (DOJ) sliding type constant velocity universal joint is shown in the above embodiment, but it is a fixed type such as a barfield type (BJ) or an undercut free type (UJ). May be.

51 inner diameter surface 52 track groove 53 outer joint member 54 outer diameter surface 55 track groove 56 inner joint member 57 ball 59 cage 60 outer peripheral side member 61 inner peripheral side member 65 flange member 65a short cylindrical part 65b outer flange part 66 torque limiter 67 plan Jar 68 Spring member

Claims (8)

A plurality of outer joint members having track grooves on the inner diameter surface, inner joint members having track grooves on the outer diameter surface, and a torque groove interposed between the track grooves of the outer joint member and the track grooves of the inner joint member. A constant velocity universal joint comprising a ball as a rolling element and a cage for holding the ball interposed between the inner diameter surface of the outer joint member and the outer diameter surface of the inner joint member,
The outer joint member has a torque limiter that is attached to a flange member that is connected to the apparatus side member and that releases torque between the outer joint member and the flange member when an excessive torque is generated. The concave portion provided in the flange member has a plunger whose tip can be inserted and removed, and a spring member that presses the plunger and engages the tip by fitting the tip into the concave portion. Constant velocity universal joint.   A constant velocity universal joint comprising control means for controlling a value for releasing torque based on the pressing force of the spring member, the shape of the tip of the plunger, and the number of torque limiters provided.   The spring member of the torque limiter has a pressing force that automatically returns to a state in which the tip end portion of the plunger is engaged with the concave portion in an unloaded state of excessive torque. Constant velocity universal joint.   The tip portion of the plunger of the torque limiter has any one shape selected from a cylindrical shape, a taper shape, and an arc shape. The constant velocity universal joint described.   5. The plunger according to claim 1, wherein the plunger is made of carbon steel for machine structure or chromium molybdenum steel, and is subjected to induction hardening tempering or carburizing quenching tempering. The constant velocity universal joint according to any one of claims.   The constant velocity universal joint according to any one of claims 1 to 5, wherein an inner surface of the concave portion provided in the short cylindrical portion of the flange member has a tapered surface shape or an arc shape.   At least the inner surface of the recess provided in the short cylindrical portion of the flange member is made of mechanical structural carbon steel or chromium molybdenum steel material, and is subjected to induction hardening tempering or carburizing quenching tempering hardening treatment. The constant velocity universal joint according to any one of claims 1 to 6, wherein:   The outer joint member includes a cylindrical outer peripheral member, and an inner peripheral member that is formed with a track groove on an inner diameter surface and is connected to the outer peripheral member, and the outer joint member is disposed on the outer peripheral side of the outer peripheral member. The constant velocity universal joint according to any one of claims 1 to 7, wherein a torque limiter is provided.

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