JP2016176568A - Slide type constant velocity universal joint - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a slide type constant velocity universal joint which can sharply enlarge an actuation angle, increases a usable area of an angle of a drive shaft and improves degree of freedom of layout of driving system components.SOLUTION: A stationary constant velocity universal joint part 2 includes: an outer coupling member 6 formed of a plurality of truck grooves 11 on a spherical inner circumferential surface 10; an inner coupling member 7 formed of a plurality of truck grooves 13 facing the truck grooves 11 of the outer coupling member 6 on a spherical outer circumferential surface 12; a plurality of torque transmission balls 8 incorporated between truck grooves of the outer coupling member and the inner coupling member; and a retainer 9 which is arranged between the outer coupling member and the inner coupling member and retains the torque transmission ball. The stationary constant velocity universal joint part is inserted to an outer cylindrical member 3 and a ball spline part 4 is formed between an inner circumferential surface 24 of the outer cylindrical member and an outer circumferential surface 25 of the stationary constant velocity universal joint part. The number of the torque transmission balls of the stationary constant velocity universal joint part is eight.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a sliding type constant velocity universal joint used for automobiles and various industrial machines.

  Today's automobiles are becoming more and more diversified due to major trends such as global environmental conservation and globalization. Along with this, with respect to drive shafts, there is an increasing need for new functions and expanded use areas.

  The drive shaft for automobiles usually uses a fixed type constant velocity universal joint on the drive wheel side (also called outboard side), and a sliding type constant velocity universal joint on the differential side (also called inboard side). These two constant velocity universal joints are connected by an intermediate shaft. The fixed type constant velocity universal joint can take a large operating angle but does not slide in the axial direction. On the other hand, the sliding type constant velocity universal joint is slidable in the axial direction, but cannot take a large operating angle.

  Specifically, the maximum allowable angle of the joint of the fixed type constant velocity universal joint used on the drive wheel side is set to 46 ° to 50 ° so that the angle at the time of full steering can be dealt with. On the other hand, in the sliding type constant velocity universal joint used on the differential side, the maximum allowable angle of the joint is set to 23 ° to 30 ° so that the movement of the suspension can be absorbed. In the sliding type constant velocity universal joint, the maximum operating angle is obtained in the full bound state where the suspension sinks most and the full rebound state where the suspension is fully extended.

  In general, an SUV vehicle (sports utility vehicle) having a vehicle height higher than that of a passenger vehicle has a large drive shaft angle (hereinafter referred to as a normal use angle) in a flat running state, and further has a tendency to increase a suspension movement.

  As a drive shaft for an automobile, a shaft that can slide in the axial direction by a ball spline using a fixed constant velocity universal joint has already been proposed (Patent Document 1, Non-Patent Document 1).

Japanese Patent No. 4316289

SAE Universal Joint and Diversheft DESIGN MANUAL Section 2.2 Weiss and Rzeppa Ball Joints, FIG. 2.11

  Future automobiles are not limited to the diversification of these suspensions, and the layout of the entire drive system components including the engine may change significantly. Assuming these, the maximum allowable angle of sliding constant velocity universal joints is 40 It is expected that the angle needs to be enlarged to about 45 ° to 45 °. As a sliding type constant velocity universal joint, a double offset type constant velocity universal joint (DOJ) composed of an outer joint member, an inner joint member, a cage and 6 to 8 balls, an outer joint member, a trunnion, 3 A tripod type constant velocity universal joint (TJ) composed of individual rollers and needle rollers as a number of rolling elements is often used. However, it is structurally difficult to greatly increase the maximum operating angle by improving the conventional sliding constant velocity universal joint, and it has not been put into practical use so far.

  Patent Document 1 proposes a drive shaft that uses two fixed constant velocity universal joints and is connected by a shaft having a ball spline. This drive shaft uses a fixed type constant velocity universal joint with a large operating angle on the differential side, but the ball spline provided on the shaft incurs a significant cost increase and the axial length of the ball spline. Therefore, the drive shaft is also limited in dimension. For this reason, the drive shaft of patent document 1 has remained for the application for some special vehicles.

  Non-Patent Document 1 describes a drive shaft having a structure in which ball splines are arranged on the outer periphery of a fixed type constant velocity universal joint. It was put into practical use for some luxury vehicles in the early 1960s, before the rise of front-wheel drive vehicles (FF vehicles). This was a structure before the practical use of DOJ as a standard for sliding constant velocity universal joints, and this structure was very expensive. As a result, it was deceived by currently used DOJ and TJ. As described above, Non-Patent Document 1 is a structure before DOJ as a sliding type constant velocity universal joint is put into practical use, and is not intended to increase the angle of the sliding type constant velocity universal joint.

  In view of the above problems, the present invention can greatly increase the operating angle of the sliding type constant velocity universal joint, thereby expanding the usable range of the angle of the drive shaft and the layout of the drive system components. The purpose of the present invention is to provide a sliding constant velocity universal joint that can greatly contribute to diversifying automobile designs.

  The inventors of the present invention have made various studies to achieve the above-described object, and efficiently arrange a ball spline on the outer periphery of a compact fixed type constant velocity universal joint to reduce torque loss and reduce cost and weight. The idea has led to the present invention.

  As technical means for achieving the above-mentioned object, the present invention includes an outer joint member in which a plurality of track grooves are formed on a spherical inner peripheral surface, and a plurality of tracks facing the track grooves of the outer joint member on a spherical outer peripheral surface. An inner joint member in which a groove is formed, a plurality of torque transmission balls incorporated between track grooves of the outer joint member and the inner joint member, and the inner joint member disposed between the outer joint member and the inner joint member. A fixed type constant velocity universal joint portion is constituted by a cage for holding a torque transmission ball, and the fixed type constant velocity universal joint portion is inserted into an outer cylinder member, and the inner peripheral surface of the outer cylinder member and the fixed type In the sliding type constant velocity universal joint in which a ball spline portion is formed between the outer peripheral surface of the outer joint member of the speed universal joint portion, the ball of the ball spline portion is connected to the inner peripheral surface of the outer cylindrical member and the outer joint. With the outer peripheral surface of the member Held by arranged retainer, and wherein the number of the torque transmitting balls of the fixed type constant velocity universal joint is eight.

  With the above configuration, the operating angle of the sliding constant velocity universal joint is greatly expanded, so the usable range of the drive shaft angle is expanded, the degree of freedom in the layout of drive system parts is improved, and the automobile is diversified It is possible to realize a sliding type constant velocity universal joint that can greatly contribute to the design. Moreover, a ball spline part having a cage can be arranged on the outer periphery of a compact fixed type constant velocity universal joint part to reduce a torque loss and realize a sliding type constant velocity universal joint with reduced cost and weight. .

  It is preferable to arrange the ball spline grooves of the ball spline part in a phase between adjacent track grooves of the outer joint member of the fixed type constant velocity universal joint part. Thereby, a ball spline part can be efficiently arrange | positioned on the outer periphery of a fixed type constant velocity universal joint part, and cost and weight can be suppressed.

  By setting the number of balls in the above-mentioned ball spline part to 2 or more per ball spline groove, smooth sliding is possible even when bending moment is applied to the ball spline part 4 when the operating angle is taken. Become.

  By making the cage of the ball spline part made of resin, light weight and low friction can be achieved.

  The above-mentioned ball spline part slides smoothly due to the rolling of the ball.

  Since the stem shaft portion is formed integrally with the outer cylinder member, the connection with the differential gear is easy.

  The fixed constant velocity universal joint is preferably composed of a Rzeppa constant velocity universal joint or a constant velocity universal joint having a cross track groove. Thereby, torque loss can be reduced and it can be set as the sliding type constant velocity universal joint which suppressed cost and weight.

  According to the sliding type constant velocity universal joint of the present invention, since the operating angle is greatly expanded, the usable range of the angle of the drive shaft is expanded, the degree of freedom of layout of the drive system parts is improved, and various It is possible to realize a sliding type constant velocity universal joint that can greatly contribute to the design of automobiles.

  Moreover, a ball spline part having a cage can be arranged on the outer periphery of a compact fixed type constant velocity universal joint part to reduce a torque loss and realize a sliding type constant velocity universal joint with reduced cost and weight. . As an advantageous configuration, the ball spline portion can be efficiently arranged in the phase between adjacent track grooves of the outer joint member, and the cost and weight can be further suppressed.

FIG. 3 is a longitudinal sectional view taken along GN-G in FIG. 2, showing the sliding type constant velocity universal joint according to the first embodiment of the present invention. It is the side view seen from the HH line of FIG. FIG. 2 is an enlarged cross-sectional view of one ball and a track groove along the line P-P in FIG. 1. It is a longitudinal cross-sectional view which shows the state which the sliding type constant velocity universal joint of FIG. 1 slid in and took the operating angle. It is a longitudinal cross-sectional view which shows the state which the sliding type constant velocity universal joint of FIG. 1 slid out and took the operating angle. FIG. 2 is a longitudinal sectional view showing a state in which the sliding type constant velocity universal joint of FIG. 1 is slid from the center position, where (a) is a slide-in state, (b) is a center position, and (c) is a slide. Indicates the state of being out. It is a longitudinal cross-sectional view which shows the drive shaft to which the sliding type constant velocity universal joint of FIG. 1 is applied. FIG. 10 shows a sliding constant velocity universal joint according to a second embodiment of the present invention, and is a longitudinal sectional view taken along GN-G in FIG. 9. FIG. 9 is a side view taken along the line HH in FIG. 8. It is a longitudinal cross-sectional view of the outer joint member of FIG. It is a figure which shows the outer peripheral surface of the inner side coupling member of FIG. It is sectional drawing of the outer joint member seen in the plane M containing the ball track centerline of the track groove of FIG. 10, and a joint center. It is sectional drawing of the inner side coupling member seen in the plane Q containing the ball | bowl track center line of the track groove | channel of FIG. 11, and a joint center.

  A first embodiment of the present invention will be described with reference to FIGS.

  As shown in FIGS. 1 and 2, a sliding type constant velocity universal joint 1 according to a first embodiment of the present invention includes a fixed type constant velocity universal joint portion 2, an outer cylinder member 3, and an outer cylinder member 3. And a ball spline part 4 formed between the fixed type constant velocity universal joint part 2.

  The fixed type constant velocity universal joint portion 2 is constituted by a Rzeppa type constant velocity universal joint having eight torque transmission balls (hereinafter, also simply referred to as balls), and includes an outer joint member 6, an inner joint member 7, a ball 8 and The cage 9 is a main component. Eight curved track grooves 11 are formed on the spherical inner peripheral surface 10 of the outer joint member 6 at equal intervals in the circumferential direction and along the axial direction. Eight curved track grooves 13 facing the track grooves 11 of the outer joint member 6 are formed on the spherical outer peripheral surface 12 of the inner joint member 7 at equal intervals in the circumferential direction and along the axial direction. . Eight balls 8 for transmitting torque are incorporated one by one between the track groove 11 of the outer joint member 6 and the track groove 13 of the inner joint member 7. A cage 9 that holds the ball 8 is disposed between the spherical inner peripheral surface 10 of the outer joint member 6 and the spherical outer peripheral surface 12 of the inner joint member 7. The ball 8 is accommodated in the pocket portion 9 a of the cage 9. The spherical outer circumferential surface 14 of the cage 9 is fitted with the spherical inner circumferential surface 10 of the outer joint member 6, and the spherical inner circumferential surface 15 of the cage 9 is fitted with the spherical outer circumferential surface 12 of the inner joint member 7.

  The centers of curvature of the spherical inner peripheral surface 10 of the outer joint member 6 and the spherical outer peripheral surface 12 of the inner joint member 7 are formed at the joint center O, respectively. In contrast, the center of curvature Oo of the curved track groove 11 of the outer joint member 6 and the center of curvature Oi of the curved track groove 13 of the inner joint member 7 are opposite to the center O of the joint in the axial direction. Is offset by the same distance f1. As a result, when the joint takes an operating angle, the ball 8 is always guided on a plane that bisects the angle formed by the axes of the outer joint member 6 and the inner joint member 7, and rotates at a constant speed between the two axes. Communicated.

  A female spline (spline includes serration; the same applies hereinafter) 17 is formed in the inner diameter hole 16 of the inner joint member 7, and the male spline 20 formed at the end of the intermediate shaft 19 is fitted to the female spline 17. , And are connected so that torque can be transmitted. The inner joint member 7 and the intermediate shaft 19 are positioned in the axial direction by a retaining ring 21.

  FIG. 3 is an enlarged cross-sectional view of one ball and a track groove along the line P-P in FIG. The cross-sectional shape of the track grooves 11 and 13 is formed in an elliptical shape or a Gothic arch shape. As shown in FIG. 3, the ball 8 is in angular contact with the track groove 11 of the outer joint member 6 at two points C12 and C13, and is in angular contact with the track groove 13 of the inner joint member 7 at two points C15 and C16. . The angle (contact angle α) formed by the straight line passing through the ball center O2 and the contact points C12, C13, C15, C16 and the straight line passing through the ball center O2 and the joint center O is preferably set to about 30 ° to 45 °. .

  As shown in FIGS. 1 and 2, the fixed type constant velocity universal joint portion 2 is fitted and inserted into the outer cylindrical member 3, and the outer peripheral surface 24 of the outer cylindrical member 3 and the outer side of the fixed type constant velocity universal joint portion 2. A ball spline portion 4 is formed between the outer peripheral surface 25 of the joint member 6. Specifically, eight ball spline grooves 26 having a circular arc cross section are formed on the inner peripheral surface 24 of the outer cylinder member 3 in a straight line in the axial direction. On the outer peripheral surface 25 of the outer joint member 6, eight ball spline grooves 27 having a circular arc cross section are formed linearly in the axial direction corresponding to the ball spline grooves 26 of the outer cylinder member 3.

  Two balls 28 are incorporated in each groove of each pair of ball spline grooves 26 and 27. Between the outer peripheral surface 25 of the outer joint member 6 and the inner peripheral surface 24 of the outer cylinder member 3, a cage 29 for holding the ball 28 is disposed. Two pocket portions 29 a of the cage 29 are provided for each ball spline groove 26, 27, that is, a pocket portion 29 a for each ball 28 is provided. Each ball 28 is accommodated and held in the pocket portion 29 a of the cage 29, and the cage 29 slides while holding the ball 28. The inner and outer peripheral surfaces of the cage 29 are respectively guided by the outer peripheral surface 25 of the outer joint member 6 and the inner peripheral surface 24 of the outer cylinder member 3. The fixed type constant velocity universal joint portion 2 slides with respect to the outer cylindrical member 3 as each ball 28 of the ball spline portion 4 rolls on the ball spline grooves 26 and 27. By arranging two balls 28 per one of the ball spline grooves 26 and 27, smooth sliding is possible even if a bending moment is applied to the ball spline portion 4 when the operating angle is taken.

  The cage 29 of the ball spline portion 4 is made of resin in consideration of weight reduction and low friction because it does not receive a large load. The cage 29 is preferably a commonly used resin having excellent wear resistance, seizure resistance, and the like. Examples of the thermoplastic resin include polyethylene, polyamide, polyacetal, polyethylene terephthalate, polybutylene terephthalate, polycarbonate, Examples include polyphenylene sulfide, polyether sulfone, polyether imide, polyamide imide, polyether ether ketone, and thermoplastic polyimide. Thermosetting resins include synthesis of thermosetting polyimide, epoxy resin, and phenol resin. Resin. In order to improve the strength and dimensional stability, it is preferable to add glass fibers or carbon fibers based on a thermoplastic resin such as polyamide, polyphenylene sulfide, or polyether ether ketone.

  As a material for the cage 29, it is preferable to use a polyamide resin excellent in tensile elongation, tensile strength, impact resistance, wear resistance, lubricity and the like. Examples of the polyamide resin include PA66 (polyamide 66), PA46 (polyamide 46), PA9T (polyamide 9T), PA11 (polyamide 11), and PA6 (polyamide 6). Since it is excellent in tensile elongation, tensile strength, impact resistance, wear resistance, lubricity, etc., a high-quality cage can be obtained.

  By using a thermosetting resin such as a thermosetting polyimide, an epoxy resin, or a phenol resin as the material of the cage 29, a cage suitable for use at a high temperature can be obtained. In the present embodiment, the cage 29 of the ball spline portion 4 is illustrated as being made of resin, but is not limited thereto, and may be made of metal such as a steel pipe.

  In this embodiment, the ball spline grooves 26 and 27 are arranged with two balls 28 per groove for reducing the number of parts. The number is not limited to this, and an appropriate number can be set as long as it is two or more. Moreover, although the thing provided with the pocket part 29a for every ball | bowl 28 was illustrated in the holder | retainer 29, it is not restricted to this, You may make it the structure which hold | maintains a several ball | bowl in one pocket part.

  A stem 3b connected to a differential gear (not shown) is integrally formed on the bottom 3a of the outer cylinder member 3. The stem portion 3b is formed with a spline 3c at the shaft end and a sliding bearing portion 3d having an oil groove at the center. The spline 3c is fitted into the spline hole of the differential gear and connected so as to be able to transmit torque. Since the stem shaft portion 3b is integrally formed with the outer cylinder member 3, the connection with the differential gear is easy.

  As shown in FIG. 1, a retaining ring 30 is provided at the groove bottom of the ball spline groove 26 at the opening side end of the inner peripheral surface 24 of the outer cylinder member 3. Retaining rings 31 and 32 are provided at the groove bottoms at both ends of the ball spline groove 27 on the outer peripheral surface 25 of the outer joint member 6. Since each retaining ring 30, 31, 32 protrudes from the groove bottom of the ball spline groove 26, 27, the fixed constant velocity is freely fixed to the outer cylinder member 3 at a position where the ball 28 interferes with the retaining ring 30, 31, 32. The axial movement of the joint portion 2 is prevented.

  A bellows-like boot 22 is attached to the outer peripheral surface of the outer cylinder member 3 and the outer peripheral surface of the intermediate shaft 19 connected to the inner joint member 7. Specifically, one end of the boot 22 is attached to a seal adapter 23, and the seal adapter 23 is fixed by caulking in an attachment groove 18 provided on the outer peripheral surface of the outer cylinder member 3. The other end of the boot 22 is fastened and fixed to the outer peripheral surface of the intermediate shaft 19 by a boot band 33. As a result, leakage of grease as a lubricant sealed inside the joint is prevented and entry of foreign matter from the outside is prevented.

  As shown in FIG. 2, in order to arrange the ball spline portions 4 efficiently, the ball spline grooves 27 formed on the outer peripheral surface 25 of the outer joint member 6 are formed on the spherical inner peripheral surface 10 of the outer joint member 6. It is arranged in the surplus portion of the phase between the adjacent track grooves 11. The sliding type constant velocity universal joint 1 according to the present embodiment will be described later in detail with respect to a configuration in which the ball spline portion 4 is efficiently arranged on the outer periphery of the compact fixed type constant velocity universal joint portion 2 to reduce cost and weight.

  Next, the operation of the sliding type constant velocity universal joint 1 according to the present embodiment will be described with reference to FIGS. FIG. 4 is a longitudinal sectional view showing a state where the sliding type constant velocity universal joint 1 is slid in and has an operating angle. The fixed type constant velocity universal joint portion 2 slides to the back side (bottom portion 3a side) of the outer cylinder member 3 by rolling of the ball spline portion 4. Specifically, since the inner and outer peripheral surfaces of the retainer 29 are guided by the outer peripheral surface 25 of the outer joint member 6 and the inner peripheral surface 24 of the outer cylindrical member 3, the posture of the retainer 29 is stabilized. The balls 28 accommodated in the 29 pocket portions 29a roll smoothly on the ball spline grooves 26 and 27 in the axial direction.

  In the sliding type constant velocity universal joint 1 of this embodiment, the operating angle is taken by the inner fixed type constant velocity universal joint portion 2 and the axial slide is taken by the ball spline portion 4. Thus, the function of taking the operating angle and the function of taking the slide in the axial direction are divided into the fixed type constant velocity universal joint portion 2 and the ball spline portion 4. Therefore, the sliding type constant velocity universal joint 1 of the present embodiment has an axial force problem due to the operating angle generated in the currently used sliding type constant velocity universal joint that simultaneously performs the function of taking the operating angle and the function of sliding. The NVH (Noise, Vibration, Harshness) characteristics are good.

  The final position of the slide-in of the sliding type constant velocity universal joint 1 is regulated by interference between the retaining ring 31 provided at the opening side end portion of the outer peripheral surface 25 of the outer joint member 6 and the ball 28. In the slide-in state, the operating angle is restricted due to interference between the intermediate shaft 19 and the boot 22, but in this state, the vehicle is not in a full bound or full rebound state. A very large operating angle is not required, and there is no practical problem.

  FIG. 5 is a longitudinal sectional view showing a state in which the sliding type constant velocity universal joint 1 is slid out. Contrary to the slide-in state, the fixed type constant velocity universal joint portion 2 slides to the opening side of the outer cylindrical member 3 by rolling of the ball spline portion 4. The final slide-out position of the sliding type constant velocity universal joint 1 is provided at the retaining ring 30 provided at the opening end of the inner peripheral surface 24 of the outer cylinder member 3 and the inner end of the outer joint member 6. It is regulated when the ball 28 interferes with the retaining ring 32.

  In the slide-out state, the fixed type constant velocity universal joint portion 2 overhangs with respect to the outer cylinder member 3 to take an operating angle, and a bending moment is applied to the ball spline portion 4, but the ball spline groove 26, The load can be supported by two balls 28 arranged per one groove 27. In the slide-out state, there are few problems such as interference between the intermediate shaft 19 and the boot 22 and a large operating angle can be obtained, so that it is possible to cope with a full bound or full rebound state of the vehicle. Thereby, since the operating angle of the sliding type constant velocity universal joint 1 of the present embodiment is greatly expanded to about 40 ° to 45 °, the usable range of the angle of the drive shaft is expanded, and the layout of the drive system components is increased. The degree of freedom increases, and it can greatly contribute to the design of a diverse car.

  The setting of the slide amount of the sliding type constant velocity universal joint 1 of the present embodiment will be described with reference to FIG. 6A and 6B are longitudinal sectional views showing a state where the sliding type constant velocity universal joint is slid from the center position. FIG. 6A is a slide-in state, FIG. 6B is a center position state, and FIG. c) shows the slid out state.

  From the center position shown in FIG. 6B, the slide amount L can be secured on the back side of the outer cylinder member 3 shown in FIG. 6A, and the slide amount L can be secured on the opening side shown in FIG. The diameter D4 of the balls 28 (see FIG. 2) and the number of balls 28 per one of the ball spline grooves 26 and 27 were set. The slide amount L varies depending on the joint size and the mounted vehicle type, but is about 20 to 30 mm. In the present embodiment, the slide is limited by the interference between the ball 28 and the retaining rings 30, 31, 32, but is not limited thereto, and may be limited by the interference between the cage 29 and the retaining ring. .

  Next, the ball spline part 4 is efficiently arranged on the outer periphery of the compact fixed type constant velocity universal joint part 2 to reduce torque loss and reduce the cost and weight. The structure of will be described.

First, a fixed type constant velocity universal joint using eight balls constituting the fixed type constant velocity universal joint portion 2 according to the present embodiment will be described with reference to FIGS. 1 and 2. In this fixed type constant velocity universal joint, the ratio r1 (= PCD _BALL / D _BALL ) between the pitch circle diameter (PCD _BALL ) and the ball diameter (D _BALL ) of the ball 8 is 3.3 ≦ r1 ≦ 5.0, preferably Is set in the range of 3.5 ≦ r1 ≦ 5.0. Here, the pitch circle diameter (PCD _BALL ) of the ball 8 is twice the size of the PCR (PCD _BALL = 2 × PCR). The length of the line segment connecting the center of curvature Oo of the track groove 11 of the outer joint member 6 and the center O2 of the ball 8, and the length of the line segment connecting the center of curvature Oi of the track groove 13 of the inner joint member 7 and the center O2 of the ball 8 Are respectively PCR, and both are equal. The ratio r2 (= D _OUTER / PCD _SERR ) between the outer diameter (D _OUTER ) of the outer joint member 6 and the pitch circle diameter (PCD _SERR ) of the female spline 17 of the inner diameter hole 16 of the inner joint member 7 is 2.5. It is set to a value within the range of ≦ r2 ≦ 3.5. Therefore, the conventional joint (fixed constant velocity universal joint using six balls) has strength, load capacity and durability equal to or higher than those of a conventional joint, and the outer diameter is compact.

Next, the ball spline portion 4 disposed on the outer periphery of the fixed type constant velocity universal joint portion 2 using the above-described compact eight balls will be described. In order to arrange the ball spline portion 4 efficiently, the following items were noted and studied.
(1) Ratio of PCD (PCD _BS ) of ball spline grooves 26 and 27 and outer diameter (D _OUTER ) of fixed type constant velocity universal joint 2 As shown in FIG. In order to secure the necessary strength of the fixed type constant velocity universal joint portion 2 by arranging the ball spline groove 27 in the middle surplus portion of the adjacent track groove 11 of the two outer joint members 6, the PCD ( It has been found that it is necessary to set PCD _BS ) to a necessary and sufficient size.
(2) Ratio of the ball diameter of the ball spline section to the ball diameter of the fixed type constant velocity universal joint section If the ball diameter of the ball spline section 4 is larger than necessary, the outer diameter of the sliding type constant velocity universal joint 1 or the ball spline It has been found that the diameter D4 of the ball 28 of the ball spline portion 4 needs to be set to a necessary and sufficient size because the lengths of the grooves 26 and 27 are increased, which causes an increase in cost and weight. However, if the diameter D4 of the ball 28 is small with respect to the input torque, the ball spline grooves 26 and 27 may be prematurely peeled or broken due to stress deformation of the ball spline grooves 26 and 27. It has been found.

From the above examination results, it was found that the following ratio is preferable in order to arrange the ball spline portions 4 efficiently.
(1) The ratio of PCD _BS / D _OUTER between the PCD (PCD _BS ) of the ball spline grooves 26 and 27 and the outer diameter (D _OUTER ) of the fixed type constant velocity universal joint portion 2 is set to PCD _BS / D _OUTER = 0.96 to Set to 1.00.
(2) The ratio D4 / D _BALL between the ball diameter (D4) of the ball spline part 4 and the ball diameter (D _BALL ) of the fixed type constant velocity universal joint part 2 is D4 / D _BALL = 0.57 to 0.64. To do.

  As described above, the sliding type constant velocity universal joint 1 of the present embodiment has an efficient arrangement of the fixed type constant velocity universal joint portion 2 and the ball spline portion 4 using the eight compact balls 8 described above. Together, it reduces torque loss, is lightweight and compact, and can reduce costs.

  FIG. 7 shows a front wheel drive shaft 40 of an automobile to which the sliding type constant velocity universal joint 1 of the present embodiment is applied. In the drive shaft 40, a fixed type constant velocity universal joint 41 is connected to one end of the intermediate shaft 19, and the sliding type constant velocity universal joint 1 of the present embodiment is connected to the other end. The fixed type constant velocity universal joint 41 is a Rzeppa type constant velocity universal joint using eight balls, and has the same internal configuration as the fixed type constant velocity universal joint portion 2 of the sliding type constant velocity universal joint 1. The fixed type constant velocity universal joint 41 is connected to a hub wheel (not shown) on which driving wheels are mounted, and the sliding type constant velocity universal joint 1 is connected to a differential gear (not shown). Between the outer peripheral surface of the fixed type constant velocity universal joint 41 and the outer peripheral surface of the intermediate shaft 19, and between the outer peripheral surface of the sliding type constant velocity universal joint 1 and the outer peripheral surface of the intermediate shaft 19, respectively. , 34 are fastened and fixed by the boot bands 33, 35a, and 35b, and the end of the seal adapter 23 of the boot 22 is fixed by crimping.

  Since the sliding type constant velocity universal joint 1 of the present embodiment is used, the operating angle is greatly expanded, the usable area of the angle of the drive shaft 40 is expanded, and the degree of freedom of layout of the drive system parts is improved. It can greatly contribute to the design of diversifying automobiles. Moreover, since the ball spline part 4 which has a holder | retainer is formed in the overlapping state between the fixed type constant velocity universal joint part 2 and the outer cylinder member 3, the dimension of an axial direction can be suppressed. Furthermore, the sliding type constant velocity universal joint 1 combines the efficient arrangement of the fixed type constant velocity universal joint portion 2 using eight compact balls 8 and the ball spline portion 4 to reduce torque loss. It can be reduced and light and compact, and the cost can be suppressed. As a result, the drive shaft 40 is highly efficient and light and compact, which leads to cost reduction.

  Next, a sliding type constant velocity universal joint according to a second embodiment of the present invention will be described with reference to FIGS. The sliding type constant velocity universal joint 51 of this embodiment is different from the first embodiment in the fixed type constant velocity universal joint portion 52. Since other configurations are the same as those in the first embodiment, portions having the same functions are denoted by the same reference numerals and description thereof is omitted.

  As shown in FIGS. 8 and 9, the fixed type constant velocity universal joint 52 mainly includes an outer joint member 56, an inner joint member 57, a ball 58, and a cage 59. As shown in FIGS. 8 to 11, each of the eight track grooves 61 and 63 of the outer joint member 56 and the inner joint member 57 is inclined in the circumferential direction with respect to the joint axis NN, and the inclined direction is the circumferential direction. The track grooves 61A, 61B and 63A, 63B adjacent to each other are formed in opposite directions. In addition, eight balls 58 are arranged at the intersections of the track grooves 61A, 63A and 61B, 63B that form pairs of the outer joint member 56 and the inner joint member 57. As described above, the fixed type constant velocity universal joint portion 52 is formed of a constant velocity universal joint having the tolerance track grooves 61 and 63. Details of the track grooves 61 and 63 will be described later.

  As shown in FIG. 9, also in this embodiment, the ball spline groove 27 formed in the outer peripheral surface 75 of the outer joint member 56 is formed in the spherical inner periphery of the outer joint member 56 in order to efficiently arrange the ball spline portion 4. Arranged in the surplus portion of the phase between adjacent track grooves 61 formed in the surface 60. Also in the sliding type constant velocity universal joint 51 of the present embodiment, the ball spline portion 4 is efficiently arranged on the outer periphery of the compact and highly efficient fixed type constant velocity universal joint portion 52 to reduce cost and weight.

  A longitudinal section of the joint is shown in FIG. In the present embodiment, the term “ball trajectory centerline” will be used to describe the shape and shape of the track groove extending substantially in the axial direction, such as an inclined state and a curved state. Here, the ball trajectory center line means a locus drawn by the center of the ball when the ball arranged in the track groove moves along the track groove. Therefore, the inclination state of the track groove is the same as the inclination state of the ball track center line, and the arc shape or the straight state of the track groove is the arc shape or straight state of the ball track center line. The same.

  As shown in FIG. 8, the track groove 61 of the outer joint member 56 has a ball track center line X, and the track groove 61 has a first ball track center line Xa having an arc-shaped ball track center line Xa with the joint center O as the center of curvature. Track groove portion 61a and a second track groove portion 61b having a linear ball track center line Xb. The ball track center line Xa of the second track groove portion 61b extends to the ball track center line Xa of the first track groove portion 61a. Xb is smoothly connected as a tangent. On the other hand, the track groove 63 of the inner joint member 57 has a ball track center line Y, and the track groove 63 includes a first track groove portion 63a having an arc-shaped ball track center line Ya with the joint center O as the center of curvature. And a second track groove portion 63b having a straight ball track center line Yb, and the ball track center line Yb of the second track groove portion 63b is smoothly tangent to the ball track center line Ya of the first track groove portion 63a. It is connected to the. By arranging the centers of curvature of the ball track center lines Xa and Ya of the first track groove portions 61a and 63a on the joint center O, that is, the joint axis NN, the track groove depth can be made uniform. And processing can be facilitated.

  The cross-sectional shape of the track grooves 61 and 63 is formed in an elliptical shape or a Gothic arch shape as in FIG. 3 described above, and the track grooves 61 and 63 and the ball 58 have a contact angle (about 30 ° to 45 °). So-called angular contact. Therefore, the ball 58 is in contact with the side surfaces of the track grooves 61 and 63 that are slightly apart from the groove bottoms of the track grooves 61 and 63.

  A state in which the track groove 61 of the outer joint member 56 is inclined in the circumferential direction with respect to the joint axis NN will be described with reference to FIG. FIG. 10 shows a partial longitudinal section of the outer joint member 56. The track grooves 61 of the outer joint member 56 are denoted by the reference numerals of the track grooves 61A and 61B because of the difference in inclination direction. As shown in FIG. 10, the plane M including the ball track center line X and the joint center O of the track groove 61A is inclined by an angle γ with respect to the joint axis NN. The track groove 61B adjacent to the track groove 61A in the circumferential direction is not shown, but the plane M including the ball track center line X and the joint center O of the track groove 61B is in relation to the joint axis NN. The track groove 61A is inclined by an angle γ in a direction opposite to the inclination direction of the track groove 61A.

  In the present embodiment, the entire area of the ball track center line X of the track groove 61A, that is, both the ball track center line Xa of the first track groove portion 61a and the ball track center line Xb of the second track groove portion 61b are on the plane M. Is formed. However, the present invention is not limited to this, and a mode in which only the ball trajectory center line Xa of the first track groove 61a is included in the plane M can also be implemented. Therefore, at least the first track groove portion 61a of the first track groove portion 61a including the ball trajectory center line Xa and the plane M including the joint center O is inclined with respect to the joint axis NN and the inclination direction is adjacent in the circumferential direction. What is necessary is just to be formed in the mutually opposite direction by 61a.

  Here, the reference numerals of the track grooves will be supplemented. When referring to the entire track groove of the outer joint member 56, reference numeral 61 is given, and the first track groove part is given reference numeral 61a, and the second track groove part is given reference numeral 61b. Further, when differentiating track grooves having different inclination directions, reference numerals 61A and 61B are assigned, reference numerals 61Aa and 61Ba are assigned to the first track groove parts, and reference signs 61Ab and 61Bb are assigned to the second track groove parts. The track grooves of the inner joint member 57 to be described later are also given the same reference numerals.

  Next, a state in which the track groove 63 of the inner joint member 57 is inclined in the circumferential direction with respect to the joint axis NN will be described with reference to FIG. FIG. 11 shows the outer peripheral surface of the inner joint member 57. The track grooves 63 of the inner joint member 57 are given the reference numerals of the track grooves 63A and 63B because of the difference in the inclination direction. As shown in FIG. 11, the plane Q including the ball track center line Y and the joint center O of the track groove 63A is inclined by an angle γ with respect to the joint axis NN. The track groove 63B adjacent to the track groove 63A in the circumferential direction is not shown, but the plane Q including the ball track center line Y and the joint center O of the track groove 63B is in relation to the joint axis NN. The track groove 63A is inclined by an angle γ in a direction opposite to the inclination direction of the track groove 63A. The inclination angle γ is set to 4 ° to 12 ° in consideration of the operability of the fixed type constant velocity universal joint portion 52 and the spherical surface width F (see FIG. 9) on the closest side of the track groove of the inner joint member 57. Is preferred.

  Similar to the outer joint member 56 described above, in the inner joint member 57 of the present embodiment, the entire area of the ball track center line Y of the track groove 63A, that is, the ball track center line Ya of the first track groove portion 63a and the second track. Both the ball trajectory center lines Yb of the grooves 63b are formed on the plane Q. However, the present invention is not limited to this, and a mode in which only the ball trajectory center line Ya of the first track groove 63a is included in the plane Q can also be implemented. Therefore, the plane Q including at least the ball track center line Ya of the first track groove 63a and the joint center O is inclined in the circumferential direction with respect to the joint axis NN, and the inclined direction is adjacent to the circumferential direction in the first direction. The track grooves 63a may be formed in opposite directions. The ball trajectory center line Y of the track groove 63 of the inner joint member 57 is based on the plane P including the joint center O in the state where the operating angle is 0 °, and the ball trajectory center line of the track groove 61 that forms a pair with the outer joint member 56. X and mirror image symmetry.

  Based on FIG. 12, the detail of the track groove seen from the longitudinal cross-section of the outer joint member 56 is demonstrated. The partial vertical cross section of FIG. 12 is a cross sectional view seen from a plane M including the ball track center line X and the joint center O of the track groove 61A of FIG. Therefore, strictly speaking, it is not a longitudinal sectional view in a plane including the joint axis NN, but shows a section inclined by an angle γ. FIG. 12 shows the track groove 61A of the outer joint member 56. The track groove 61B has the same configuration as the track groove 61A except that the inclination direction is opposite to the track groove 61A. Since there is, explanation is omitted. A track groove 61A is formed in the spherical inner peripheral surface 60 of the outer joint member 56 along the axial direction. The track groove 61A has a ball track center line X, and the track groove 61A has a first track groove portion 61Aa having an arc-shaped ball track center line Xa with the joint center O as the center of curvature (no axial offset). And a second track groove 61Ab having a linear ball trajectory center line Xb. Then, at the end A on the opening side of the ball track center line Xa of the first track groove portion 61Aa, the linear ball track center line Xb of the second track groove portion 61Ab is smoothly connected as a tangent line. That is, the end A is a connection point between the first track groove 61Aa and the second track groove 61Ab. Since the end portion A is located on the opening side of the joint center O, the linear shape of the second track groove portion 61Ab connected as a tangent at the end portion A on the opening side of the ball track center line Xa of the first track groove portion 61Aa. The ball trajectory center line Xb is formed so as to approach the joint axis NN (see FIG. 8) as it goes to the opening side. Thereby, it is possible to secure the effective track length at the maximum operating angle and to suppress the wedge angle from becoming excessive.

  As shown in FIG. 12, let L be a straight line connecting the end A and the joint center O. The joint axis N′-N ′ projected onto the plane M (see FIG. 10) including the ball trajectory center line X and the joint center O of the track groove 61A is inclined by γ with respect to the joint axis NN. Let β ′ be the angle formed by the perpendicular line K and the straight line L at the joint center O of N′−N ′. The perpendicular K is on the plane P including the joint center O in the state where the operating angle is 0 °. Therefore, the angle β formed with respect to the plane P including the joint center O in the state where the straight line L has an operating angle of 0 ° has a relationship of sin β = sin β ′ × cos γ.

  Similarly, details of the track groove will be described based on a longitudinal section of the inner joint member 57 based on FIG. 13 is a cross-sectional view of the track groove 63A of FIG. 11 described above as seen from the plane Q including the ball trajectory center line Y and the joint center O. Therefore, exactly like FIG. 12, it is not a longitudinal sectional view in a plane including the axis NN of the joint, but shows a section inclined by an angle γ. FIG. 13 shows the track groove 63A of the inner joint member 57. The track groove 63B is the same as the track groove 63A except that the inclination direction is opposite to the track groove 63A. Since there is, explanation is omitted. A track groove 63A is formed in the spherical outer peripheral surface 62 of the inner joint member 57 along the axial direction. The track groove 63A has a ball track center line Y, and the track groove 63A has a first track groove portion 63Aa having an arc-shaped ball track center line Ya with the joint center O as the center of curvature (no axial offset). And a second track groove 63Ab having a linear ball trajectory center line Yb. The ball track center line Yb of the second track groove portion 63Ab is smoothly connected as a tangent at the end B on the back side of the ball track center line Ya of the first track groove portion 63Aa. That is, the end B is a connection point between the first track groove 63Aa and the second track groove 63Ab. Since the end portion B is located on the back side from the joint center O, the linear shape of the second track groove portion 63Ab connected as a tangent at the end portion B on the back side of the ball track center line Ya of the first track groove portion 63Aa. The ball trajectory center line Yb is formed so as to approach the joint axis NN (see FIG. 8) as it goes back. Thereby, it is possible to secure the effective track length at the maximum operating angle and to suppress the wedge angle from becoming excessive.

  As shown in FIG. 13, let R be the straight line connecting the end B and the joint center O. The joint axis N′-N ′ projected on the plane Q (see FIG. 11) including the ball trajectory center line Y and the joint center O of the track groove 63A is inclined by γ with respect to the joint axis NN. Let β ′ be the angle formed by the perpendicular line K and the straight line R at the joint center O of N′−N ′. The perpendicular K is on the plane P including the joint center O in the state where the operating angle is 0 °. Accordingly, the angle β formed with respect to the plane P including the joint center O in the state where the straight line R has an operating angle of 0 ° has a relationship of sin β = sin β ′ × cos γ.

  Next, an angle β formed by the straight lines L and R with respect to the plane P including the joint center O in a state where the operating angle is 0 ° will be described. When the operating angle θ is taken, the ball 58 moves by θ / 2 with respect to the plane P including the joint center O of the outer joint member 56 and the inner joint member 57. The angle β is determined from ½ of the frequently used operating angle, and the range of the track groove with which the ball 58 contacts is determined within the frequently used operating angle range. Here, the operating angle that is frequently used is defined. First, the common angle of the joint refers to the operating angle generated in the fixed constant velocity universal joint of the front drive shaft when the vehicle is traveling straight on a horizontal and flat road surface when the vehicle is in a straight traveling state. The service angle is usually selected and determined between 2 ° and 15 ° according to the design conditions for each vehicle type. The frequently used operating angle is not the high operating angle that occurs when the above-mentioned automobile is turned right or left at an intersection, for example, but the operating angle that occurs in a fixed constant velocity universal joint on a curved road that runs continuously This is also determined according to the design conditions for each vehicle type. The operating angle that is frequently used is targeted at a maximum of 20 °. As a result, the angle β formed by the straight lines L and R with respect to the plane P including the joint center O in a state where the operating angle is 0 ° is set to 3 ° to 10 °. However, the angle β is not limited to 3 ° to 10 °, and can be appropriately set according to the design conditions of the vehicle type. By setting the angle β to 3 ° to 10 °, it can be used for various types of vehicles.

  12, the end A of the ball trajectory center line Xa of the first track groove 61Aa in FIG. 12 is the ball of the ball when moving most toward the opening along the axial direction at the operating angle where the frequency of use is high. It becomes the center position. Similarly, in FIG. 13, in the inner joint member 57, when the end B of the ball track center line Ya of the first track groove portion 63Aa moves to the farthest side along the axial direction at the operating angle where the frequency of use is high. The center position of the ball. Since it is set in this way, in the range of the operating angle where the usage frequency is high, the ball 58 has the first track groove portions 61Aa and 63Aa of the outer joint member 56 and the inner joint member 57, and 61Ba, whose inclination direction is opposite, Since it is located at 63Ba (see FIGS. 10 and 11), a force in the opposite direction from the ball 58 acts on the pocket 59a adjacent to the circumferential direction of the cage 59, and the cage 59 is stable at the position of the joint center O. (See FIG. 8). Therefore, the contact force between the spherical outer peripheral surface 64 of the cage 59 and the spherical inner peripheral surface 60 of the outer joint member 56 and the contact between the spherical inner peripheral surface 65 of the cage 59 and the spherical outer peripheral surface 62 of the inner joint member 57. The force is suppressed, the joint operates smoothly at high loads and at high speeds, torque loss and heat generation are suppressed, and durability is improved.

  In the track groove 61A of the outer joint member 56 of the fixed type constant velocity universal joint portion 52 of the present embodiment, a second track groove portion 61Ab having a linear ball track center line Xb is formed on the opening side. In the compact design, the presence of the second track groove portion 61Ab can secure an effective track length at the maximum operating angle and suppress an excessive wedge angle. Therefore, even if the maximum operating angle is set to a high angle of about 47 °, the ball 58 can be in contact with the track groove 61Ab with the necessary and sufficient entrance chamfer 70 provided, and the wedge angle is not increased. Can be suppressed.

  Note that, in the range of the high operating angle, the balls 58 arranged in the circumferential direction have the first track groove portions 61Aa, 63Aa (61Ba, 63Ba, see FIGS. 10 and 11) and the second track groove portions 61Ab, 63Ab (61Bb, 63Bb, see FIGS. 10 and 11). Accordingly, the force acting from the ball 58 on each pocket portion 59a of the retainer 59 is not balanced as a whole of the joint, and the spherical contact portions 64 and 60 between the retainer 59 and the outer joint member 56, and the retainer 59 and the inner joint member. Although the contact force of the spherical contact portions 65 and 62 with the 57 is generated, the fixed type constant velocity universal applied to the sliding type constant velocity universal joint 51 of the present embodiment is not used in the range of the high operating angle. The joint portion 52 can suppress torque loss and heat generation when viewed comprehensively. Therefore, the compact fixed type constant velocity universal joint portion 52 is capable of taking a high operating angle with little torque loss and heat generation, having a high operating angle, and having excellent strength and durability at a high operating angle.

  As shown in FIG. 8, the fixed type constant velocity universal joint 52 having the cross track grooves 61 and 63 of the present embodiment described above is inserted into the outer cylinder member 3 as in the first embodiment. A ball spline portion 4 is formed between the inner peripheral surface 24 of the outer cylindrical member 3 and the outer peripheral surface 75 of the outer joint member 56 of the fixed type constant velocity universal joint portion 52. Also in the sliding type constant velocity universal joint 51, the operating angle is taken by the inner fixed type constant velocity universal joint portion 52 and the axial slide is taken by the ball spline portion 4 as in the first embodiment. The function of taking the operating angle and the function of taking the slide in the axial direction are divided into the fixed type constant velocity universal joint portion 52 and the ball spline portion 4, and the fixed type having the high-efficiency cross track grooves 61 and 63, etc. Combined with the quick universal joint 56, the NVH characteristics are very good.

The configuration of the outer cylindrical member 3 in the sliding type constant velocity universal joint 51 of the present embodiment, the configuration and operation of the ball spline portion 4, the slide-in / slide-out state and the regulation method, the setting of the slide amount L and the drive shaft Since application and the like are the same as those in the first embodiment described above, the description of the first embodiment is applied mutatis mutandis, and redundant description is omitted. In the sliding constant velocity universal joint 51 of the present embodiment, as in the first embodiment, (1) the outer diameter of the PCD (PCD _BS ) of the ball spline grooves 26 and 27 and the fixed constant velocity universal joint portion 52. The ratio PCD _BS / D _OUTER of (D _OUTER ) is set to PCD _BS / D _OUTER = 0.96 to 1.00, and (2) the ball diameter (D4) of the ball spline portion 4 and the fixed constant velocity universal joint portion 52 The ball diameter (D _BALL ) ratio D4 / D _BALL was set to D4 / D _BALL = 0.57 to 0.64.

  In the sliding type constant velocity universal joint 51 of the present embodiment, the intersecting track grooves have arc-shaped first track groove portions 61a and 63a having a center of curvature with no offset in the axial direction and linear second track groove portions 61b. However, the present invention is not limited to this, and the cross track groove is formed only by the arc-shaped track groove having the center of curvature with no offset in the axial direction. It may be a fixed type constant velocity universal joint.

  The present invention is not limited to the above-described embodiments, and can of course be implemented in various forms without departing from the scope of the present invention. The scope of the present invention is not limited to patents. It includes the equivalent meanings recited in the claims and the equivalents recited in the claims, and all modifications within the scope.

DESCRIPTION OF SYMBOLS 1,51 Sliding type constant velocity universal joint 2,52 Fixed type constant velocity universal joint part 3 Outer cylinder member 3b Stem part 4 Ball spline part Spherical roller 6,56 Outer joint member 7,57 Inner joint member 8,58 Torque transmission Ball 9, 59 Cage 10, 60 Spherical inner peripheral surface 11, 61 Track groove 12, 62 Spherical outer peripheral surface 13, 63 Track groove 14, 64 Spherical outer peripheral surface 15, 65 Spherical inner peripheral surface 26 Ball spline groove 27 Ball spline groove 28 Ball 29 Cage O Joint center Oi Center of curvature Oo Center of curvature P Joint center plane

Claims (8)

An outer joint member in which a plurality of track grooves are formed on a spherical inner peripheral surface, an inner joint member in which a plurality of track grooves facing the track grooves of the outer joint member are formed on a spherical outer peripheral surface, and the outer joint member; Fixed constant velocity from a plurality of torque transmission balls assembled between the track grooves of the inner joint member, and a cage that is disposed between the outer joint member and the inner joint member and holds the torque transmission ball. A universal joint portion is configured, and the fixed type constant velocity universal joint portion is fitted and inserted into the outer cylinder member. Between the inner peripheral surface of the outer cylindrical member and the outer peripheral surface of the outer joint member of the fixed type constant velocity universal joint portion In the sliding type constant velocity universal joint with the ball spline part formed in
The balls of the ball spline portion are held by a cage disposed between the inner peripheral surface of the outer cylinder member and the outer peripheral surface of the outer joint member,
A sliding type constant velocity universal joint, wherein the number of torque transmitting balls in the fixed type constant velocity universal joint portion is eight.   2. The sliding type according to claim 1, wherein the ball spline groove of the ball spline part is arranged in a phase between adjacent track grooves of an outer joint member of the fixed type constant velocity universal joint part. Fast universal joint.   The sliding type constant velocity universal joint according to claim 2, wherein the number of balls in the ball spline portion is two or more per one ball spline groove.   The sliding constant velocity universal joint according to claim 1, wherein the cage of the ball spline part is made of resin.   The sliding type constant velocity universal joint according to any one of claims 1 to 4, wherein the ball spline portion slides by rolling of the ball.   The sliding type constant velocity universal joint according to claim 1, wherein a stem shaft portion is formed integrally with the outer cylinder member.   The sliding type constant velocity universal joint according to claim 1, wherein the fixed type constant velocity universal joint portion is constituted by a Rzeppa type constant velocity universal joint.   2. The sliding type constant velocity universal joint according to claim 1, wherein the fixed type constant velocity universal joint portion is constituted by a constant velocity universal joint having a cross track groove.

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