JP2005308132A - Constant velocity universal joint - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a constant velocity universal joint of the large turning angle with balls interposed between rotating bodies. <P>SOLUTION: The constant velocity universal joint 1 comprises a inner race 80 having an inner race groove 81 in contact with balls 60 formed in an outer surface, a sliding groove 50 having an outer race groove 51 in contact with the balls 60 formed in an inner surface, and balls 30 for slide to hold the sliding groove 50 slidably in the extending direction of the outer race groove 51. An inner race groove center 82 and an outer race groove center 52 extending on the arc around a turning center 2 have the torsional angle so as to be symmetric to each other with respect to the bisecting plane 100, and the balls 60 are held at the position at which the inner race groove center 82 is intersected with the outer race groove center 52. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a constant velocity universal joint, and more particularly to a constant velocity universal joint in which a ball is interposed between rotating bodies.

Conventionally, constant velocity universal joints are disclosed in, for example, JP-A-8-156618 (Patent Document 1), JP-A-2002-147482 (Patent Document 2) and JP-A-2003-278875 (Patent Document 3). ing.
JP-A-8-156618 Japanese Patent Laid-Open No. 2002-147481 JP 2003-278875 A

  Patent Document 1 discloses a structure in which a refraction angle is increased by using three constant velocity joints.

  Patent Document 2 discloses a constant velocity joint having a structure in which a ball can be assembled in a ball groove so as not to be caught.

  Patent Document 3 discloses a rocking and rotating speed reducer in which the crossing angle between an input shaft and an output shaft is increased.

  However, any of the above-described techniques has a problem that the swing angle (rotation angle) cannot be increased in one constant velocity universal joint.

  Accordingly, the present invention has been made to solve the above-described problems, and an object thereof is to provide a constant velocity universal joint capable of increasing a rotation angle.

  In the constant velocity universal joint according to the present invention, a ball is interposed between the first rotating body and the second rotating body, and the first rotating body is centered on the rotation center with respect to the second rotating body. As the rotation axis of the first rotation body can be inclined with respect to the rotation axis of the second rotation body, and the rotation axis of the first rotation body and the rotation of the second rotation body A constant velocity universal joint that transmits a rotational force via a ball between a first rotating body and a second rotating body by placing the ball on a surface that bisects the angle formed by the shaft. A first groove member that rotates with the first rotating body and has an inner race groove that contacts the ball formed on the surface, and an outer race groove that rotates with the second rotating body and contacts the ball on the surface. A second groove member formed and a slide that holds the second groove member slidably in the direction in which the outer race groove extends. And an id part. The centers of the inner race groove and the outer race groove extend on an arc centered on the rotation center. The centers of the inner race groove and the outer race groove have a twist angle so as to be symmetrical with respect to the bisecting plane. The ball is held at a position where the centers of the inner race groove and the outer race groove intersect.

  In the constant velocity universal joint configured as described above, the outer race groove is slidable, so that a larger rotation angle than the conventional structure in which the outer race groove does not slide can be obtained. That is, it is possible to increase the angle formed by the first and second rotation axes.

  More preferably, the slide part has a rolling element and a holder that holds the rolling element. A rolling element is interposed between the second rotating body and the second groove member.

  In this case, the outer race groove can be smoothly slid by the rolling element being interposed between the second rotating body and the second groove member.

  More preferably, the constant velocity universal joint further includes a cage for holding a ball, and the inner surface and the outer surface of the cage have a spherical shape centering on the rotation center. In this case, the cage itself can also rotate smoothly.

  According to the present invention, it is possible to provide a constant velocity universal joint that can increase the rotation angle (swing angle).

  Embodiments of the present invention will be described below with reference to the drawings. In the following embodiments, the same or corresponding parts are denoted by the same reference numerals, and description thereof will not be repeated.

(Embodiment 1)
1 is a cross-sectional view of a constant velocity universal joint according to Embodiment 1 of the present invention. With reference to FIG. 1, the overall structure and each partial structure of the constant velocity universal joint according to the first embodiment of the present invention will be described.

  First, with respect to the overall structure, the constant velocity universal joint 1 is a mechanism for transmitting power between the plurality of shafts 10 and 90, and the shafts 10 and 90 are arranged even when the shafts 10 and 90 are angled. One rotation of 90 can be transmitted to the other side of shafts 10 and 90 without changing the angular velocity. An outer race 20, a sliding ball 30, a sliding groove 50, a ball 60, and an inner race 80 are provided between the shafts 10 and 90, and rotational torque is transmitted between the shafts 10 and 90 via these members. . The rotation axis 11 of the shaft 10 and the rotation axis 91 of the shaft 90 intersect each other at the rotation center 2, and the rotation axis 11 makes an angle with respect to the rotation axis 91 while maintaining the state intersected at the rotation center 2. Can be made. Even in the state where the rotation shaft 11 is inclined with respect to the rotation shaft 91, the angular velocity of rotation of the shaft 10 becomes equal to the angular velocity of rotation of the shaft 90. For this purpose, a ball 60 for transmitting power is always arranged on the bisector 100. The bisecting surface 100 is provided on a surface that bisects the angle formed by the rotation shafts 11 and 91 and always passes through the rotation center 2.

  Next, regarding the description of each element, the shaft 10 is, for example, a drive shaft or a propeller shaft of an automobile, and can rotate around the rotation axis 11. In the constant velocity universal joint 1 according to the present invention, since a large rotation angle can be obtained, the shaft 10 is preferably used as a drive shaft of an automobile. That is, the rotational force output from the differential gear is transmitted to the shaft 90 via the shaft 10 and further transmitted to the wheels. By using the constant velocity universal joint 1 according to the present invention in the vicinity of the steering wheel, the steering angle (the steering angle of the steering wheel) can be increased.

  The material of the shaft 10 is not particularly limited. For example, a steel material having excellent durability can be used for an automobile. Moreover, when using for a propeller shaft etc., it is also possible to employ | adopt a resin member. Moreover, although the shaft 10 has a solid shape (a shape in which the contents are packed) in the cross section of FIG. 1, a hollow shaft 10 may be employed. In addition, when the hollow shaft 10 is employed, lubricating oil or the like may flow through the hollow space. Furthermore, the shaft 10 may be made of a light metal alloy such as aluminum in a field where strength is not so required and weight reduction is required.

  The outer race 20 is connected to the shaft 10 and has a substantially spherical inner surface 25. The inner surface 25 of the outer race 20 surrounds a predetermined space, and the components of the constant velocity universal joint 1 such as the ball 60 are accommodated in the enclosed space. The inner surface 25 of the outer race 20 has a spherical shape larger than the hemisphere. Specifically, the spherical surface extends beyond the bisecting surface 100 to the shaft 90 side. A spherical surface of the inner surface 25 is a spherical surface centered on the rotation center 2 and is formed so as to surround the rotation center 2.

  A slide ball groove 21 is provided on the inner surface 25. In the cross section shown in FIG. 1, two slide ball grooves 21 are shown, but FIG. 1 is a virtual cross section, and the slide ball grooves 21 are arranged at positions twisted with respect to each other. The slide ball groove 21 has a groove center 22, and the groove center 22 is arranged on an arc centered on the rotation center 2. That is, the groove center 22 extends in a curved shape, and when the curve is further extended, the groove center 22 has a shape that draws a circle around the rotation center 2. The upper groove center 22 and the lower groove center 22 in FIG. 1 actually only intersect at two points and are not in the same plane. The groove center 22 and the inner surface 25 are arranged concentrically around the rotation center 2. The material of the outer race 20 is not particularly limited, and the same material as the shaft 10 or a different material may be used. Further, since the wear resistance is required in the vicinity of the slide ball groove 21 in the outer race 20, this portion may be hardened such as quenching.

  The slide balls 30 are arranged on the slide ball groove 21. A plurality of slide balls 30 are arranged in the direction in which the slide ball groove 21 extends, and rolls on the slide ball groove 21. The slide balls 30 as rolling elements are held in a slide ball cage 40 as a cage, and the intervals between the slide balls 30 are kept substantially constant. In this embodiment, the slide ball 30 is used as the rolling element, but the present invention is not limited to this, and a needle bearing may be used when a larger load is expected to be applied. Furthermore, the number of slide balls 30 is not limited to that shown in FIG. 1, and more slide balls 30 and fewer slide balls 30 may be used.

  The slide ball 30 is made of, for example, a steel ball. The slide ball 30 rolls on the slide ball groove 21 along the groove center 22. The sliding ball 30 uses the sliding ball groove 21 formed in the outer race 20 as an outer race, and the sliding ball groove 55 of the sliding groove 50 as an inner race, thereby reducing the frictional resistance between the outer race and the inner race. .

  The sliding groove 50 is provided inside the outer race 20, and an outer race groove 51 for holding the ball 60 is formed on the inner surface side thereof. A sliding ball groove 55 that contacts the sliding ball 30 is provided on the outer surface side of the sliding groove 50, and the sliding ball groove 55 is disposed so as to face the sliding ball groove 21. The sliding groove 50 has an arc shape centered on the rotation center 2 and can freely move on the arc centered on the rotation center 2. The outer race groove center 52, which is the center of the outer race groove 51, extends on an arc centered on the rotation center 2, and the ball 60 moves so as to substantially coincide with the outer race groove center 52. An incomplete groove 57 is provided at the tip of the outer race groove 51, and the ball 60 is held by the incomplete groove 57.

  That is, if the outer race groove 51 extends on the arc centering around the rotation center 2 even in the vicinity of the sliding groove end face 53, there arises a problem that the ball 60 is released to the outside. In order to solve this problem, the incomplete groove 57 is provided, and the outer race groove 51 is formed so as to be wound around the sliding groove end surface 53 in the vicinity of the rotation center 2 side, thereby preventing the ball 60 from jumping out. Yes.

  The sliding groove 50 requires high durability because the inner surface side contacts the ball 60 and the outer surface side contacts the sliding ball 30. Since the sliding groove 50 is in contact with the sliding ball 30, the outer race groove 51 provided in the sliding groove 50 also slides on the arc together with the sliding groove 50. Even if the sliding groove 50 slides, the position of the outer race groove center 52 does not change.

  That is, in the sliding groove 50, the sliding ball 30 and the sliding ball groove 21 that are in contact with each other, the groove center 22 and the outer race groove center 52 are on the same plane centering on the rotation center 2 and concentrically. Provided. Therefore, even if the sliding groove 50 slides, the sliding direction is the direction in which the outer race groove center 52 extends, and the position of the outer race groove center 52 does not change.

  The ball 60 and the cage 70 are members for transmitting power, and the cage 70 holds the position of the ball 60. The ball 60 is always arranged on the bisector 100. The ball 60 is always disposed on the intersection of the outer race groove center 52 and the inner race groove center 82. Since the outer race groove center 52 and the inner race groove center 82 intersect each other, the constant velocity universal joint 1 according to the present invention is a so-called cross groove type constant velocity universal joint. Since the ball 60 rolls in the outer race groove 51, a predetermined lubricant such as lubricating oil or grease may be applied to the outer surface of the ball 60 in order to reduce friction at the same time. Similarly, it is preferable to apply a lubricant such as grease for reducing friction to the outer surface of the slide ball 30.

  As a method of lubricating the ball 60 and the slide ball 30, for example, a gel-like lubricant is disposed in the vicinity of the ball 60 and the slide ball 30 so that lubrication is possible. Furthermore, the constant velocity universal joint 1 itself may be immersed in an oil sump. Further, lubricating oil may be sprayed on the constant velocity universal joint 1. The entire constant velocity universal joint 1 may be covered with boots or the like in order to prevent the lubricant from scattering.

  The cage 70 has a role as a cage for holding the ball 60, and plays a role in smoothly positioning the ball 60 at a predetermined position. The cage 70 is provided with a ball hole 71 which is a through hole, and the ball 60 is positioned by fitting the ball 60 into the ball hole 71. The cage 70 has a cage inner surface 72 and a cage outer surface 73, and both surfaces of the cage inner surface 72 and the cage outer surface 73 are arranged on a spherical surface with the rotation center 2 as the center. The cage inner surface 72 slides with the inner race 80, and the cage outer surface 73 slides with the sliding groove 50. The cage inner surface 72 and the cage outer surface 73 are preferably lubricated with a lubricant such as grease so as not to prevent this sliding. The cage 70 has a dome shape and has a shape surrounding the inner race 80.

  The inner race 80 is provided in the vicinity of the rotation center 2 and supports the ball 60 from the inside. An inner race groove 81 is provided on the outer surface of the inner race 80, and the ball 60 is held in the inner race groove 81. The inner race groove 81 is provided so as to be inclined with respect to the rotation shaft 91, and specifically, the outer race groove 51 and the inner race groove 81 are positioned symmetrically with respect to the bisector 100. Provided. The point where the inner race groove center 82 and the outer race groove center 52 intersect is provided on the bisector 100, and the ball 60 is held at the intersecting point.

  The inner race groove center 82 and the outer race groove center 52 are arranged on a spherical surface with the rotation center 2 as the center, and intersect at two symmetrical points with the rotation center 2 as the center. The inner race 80 can be rotated around the rotation center 2 and is rotated with a certain distance from the outer race 20. In FIG. 1, the inner race 80 has a solid shape (a shape in which the contents are packed), but may have a hollow shape. The inner race 80 is provided with a plurality of inner race grooves 81.

  The shaft 90 is a member for outputting or inputting rotational force, and is integrally attached to the inner race 80. The shaft 90 may be constituted by a member separate from the inner race 80 or may be constituted integrally. At the tip of the shaft 90, for example, a hub for mounting a wheel of an automobile may be provided. Moreover, you may use the shaft 90 as an input shaft which inputs the output from an engine. Further, the shaft 90 may be connected to the propeller shaft. Further, the shaft 90 may be used as a power input and output portion of a constant velocity universal joint used in a machine tool, a generator, etc. without being limited to a constant velocity universal joint for an automobile. The rotating shaft 91 of the shaft 90 can have various angles with respect to the rotating shaft 11 of the shaft 10.

  A constant velocity universal joint 1 according to Embodiment 1 of the present invention includes a ball 60 as an intermediate member between a shaft 90 as a first rotating body and a shaft 10 and an outer race 20 as a second rotating body. The shaft 90 can be tilted with respect to the rotation shaft 91 by rotating the shaft 90 about the rotation center 2 with respect to the shaft 10. By disposing the ball 60 on the bisecting surface 100 that bisects the angle formed by the rotating shaft 11 and the rotating shaft 91, the rotational force can be transmitted between the shafts 10 and 90 via the ball 60. it can. The constant velocity universal joint 1 rotates together with the shaft 90 and rotates together with the inner race 80 as the first groove member in which the inner race groove 81 contacting the ball 60 is formed on the outer surface, the shaft 10 and the outer race 20. A sliding groove 50 as a second groove member in which an outer race groove 51 that contacts the ball 60 is formed on the inner surface, and a slide portion that holds the sliding groove 50 so as to be slidable in the direction in which the outer race groove 51 extends. A slide ball 30 and a slide ball cage 40 are provided. The inner race groove center 82 and the outer race groove center 52, which are the groove centers of the inner race groove 81 and the outer race groove 51, extend on an arc centered on the rotation center 2, and the inner race groove center 82 and the outer race groove center The groove center 52 has a twist angle so as to be symmetric with respect to the bisector 100, and the ball 60 is held at a position where the inner race groove center 82 and the outer race groove center 52 intersect.

  FIG. 2 is a cross-sectional view of the constant velocity universal joint in a state where the shaft 90 is inclined with respect to the shaft 10. With reference to FIG. 2, the rotation operation of the constant velocity universal joint 1 will be described. The shaft 90 can make an angle θ <b> 1 with respect to the shaft 10. For example, the angle θ1 is 120 °. At this time, the inner race groove 81 and the outer race groove 51 are positioned so that the ball 60 is disposed on the bisecting surface 100 that bisects the angle θ1.

  On the upper side of FIG. 2, as the ball 60 rotates from the state shown in FIG. 1, the sliding groove 50 and the sliding ball 30 also rotate clockwise about the rotation center 2. At this time, the ball 60 receives a force in the direction of jumping out from the outer race groove 51, but the presence of the incomplete groove 57 causes the ball 60 to be caught in the incomplete groove 57 and the ball 60 to jump out. Absent. Similarly, the slide ball 30 also protrudes from the outer race 20 and jumps to the outside. However, since the slide ball 30 is held by the slide ball cage 40, the slide ball 30 jumps to the outside. Can be prevented.

  In the lower side of FIG. 2, the shaft 90 is in contact with the outer race end surface 23 and the sliding groove end surface 53. In preparation for such contact, the outer race end surface 23 and the sliding groove end surface 53 are tapered surfaces and come into surface contact with the shaft 90. Therefore, wear with the shaft 90 can be reduced, and damage to the shaft 90 can be prevented.

  As shown in FIG. 2, even when the shaft 90 is inclined with respect to the shaft 10, the intersection of the rotating shaft 11 and the rotating shaft 91 is the rotation center 2. In this state, the shaft 90 can rotate around the rotation shaft 91 in a state where the shaft 90 is rotated (oscillated). Even if the shaft 90 rotates, the plurality of balls 60 are arranged on the bisector 100, so that the rotation of the shaft 90 is transmitted to the shaft 10 without converting the angular velocity.

  As shown in FIG. 2, since the sliding groove 50 slides along the extending direction of the outer race groove 51, it can be considered that the outer race groove 51 is formed long in the present invention. The ball 60 rotates about the center of rotation 2 along 51. In the conventional constant velocity universal joint, if the outer race groove 51 is extended, the shaft 90 and the outer race groove 51 come into contact with each other, and a sufficiently large rotation angle cannot be obtained. In the present invention, in a constant velocity universal joint that is mounted on the front wheel side of an automobile and transmits a driving force at a large angle, by sliding the outer race groove 51, a larger angle (swinging) than the conventional product is obtained. It is possible to provide the structure of the constant velocity universal joint 1 that transmits the driving force at a dynamic angle.

  The outer race groove 51 slides with respect to the outer race 20 in the direction in which the outer race groove 51 extends. The outer race groove center 52 and the inner race groove center 82 are provided on a two-dimensional arc centered on the rotation center (swing center) 1 of the constant velocity universal joint 1. The outer race groove 51 and the inner race groove 81 have a twist angle with respect to the bisector 100 so that they are symmetric with each other. The cage inner surface 72 and the cage outer surface 73 of the cage 70 are arranged on a spherical surface centered on the rotation center 2.

  In FIG. 1 and FIG. 2, a plurality of inner race grooves 81 and outer race grooves 51 appear in the same cross section, but in reality, a twist angle is given to these inner race grooves 81 and outer race grooves 51. Therefore, the inner race groove 81 and the outer race groove 51 do not appear to extend long in the same cross section.

  By adopting such a configuration, it is possible to transmit the driving force at a large angle, for example, a rotation angle (sliding angle) of 60 °.

  FIG. 3 is a schematic view of the center of the inner race groove and the center of the outer race groove. Referring to FIG. 3, inner race groove center 82 and outer race groove center 52 extend three-dimensionally and intersect on bisector 100. The ball 60 is held at the crossed position. In actual design, it is not necessary that the center of the ball 60 exactly coincides with the intersection of the inner race groove center 82 and the outer race groove center 52, and a slight deviation may occur. Further, in order to make the movement of the ball 60 smooth, some play may be provided. The rotation center 2 is located on the bisector 100, and the two rotation axes 11 and 91 intersect at the rotation center 2.

  FIG. 4 is a schematic view of the inner race groove center and the outer race groove center as seen from the direction indicated by the arrow IV in FIG. Referring to FIG. 4, inner race groove center 82 and outer race groove center 52 have a twist angle θ2. The twist angle θ2 indicates the inclination of the outer race groove center 52 and the inner race groove center 82 with respect to the rotating shafts 11 and 91, and the inclination of the inner race groove center 82 and the inclination of the outer race groove center 52 are substantially equal. Become. The inner race groove center 82 and the outer race groove center 52 are inclined to each other and intersect at one point, so that the ball 60 can be held at this intersection. As the twist angle θ2, various angles exceeding 0 ° can be adopted.

  FIG. 5 is a schematic view of the center of the inner race groove and the center of the outer race groove of the constant velocity universal joint shown in FIG. Referring to FIG. 5, the inner race groove center 82 and the outer race groove center 52 intersect on the bisecting plane 100 even when the two rotation shafts 11 and 91 are not provided with an angle. The ball 60 is held at the crossing point. That is, even if the rotating shaft 91 is inclined with respect to the rotating shaft 11, the inner race groove center 82 and the outer race groove center 52 are provided on a spherical surface centered on the rotation center 2. The center 82 and the outer race groove center 52 always meet at one point. Further, since the inner race groove center 82 and the outer race groove center 52 are symmetrical, the inner race groove center 82 and the outer race groove center 52 always intersect on the bisector 100. That is, the inner race groove center 82 and the outer race groove center 52 are provided symmetrically with respect to the bisector 100.

  Next, a structure for preventing the balls and slide balls from coming off will be described. FIG. 6 is a cross-sectional view of the constant velocity universal joint according to the first embodiment. Note that the cross section shown in FIG. 6 is different from the cross section shown in FIG. Referring to FIG. 6, first, the outer race 20 is provided with a holding angle θ3 in order to prevent the sliding ball 30 and the sliding groove 50 from falling off. By providing the embracing angle θ3, there is a function of preventing the sliding ball 30 and the sliding groove 50 from coming out to the outside. Further, the incomplete groove 57 is configured to go to the rotation center 2 side, and the distance from the rotation center 2 is small in the incomplete groove 57. As a result, it is possible to prevent the ball 60 from falling off. Since the sliding ball grooves 21 and 55 shown in FIGS. 1 and 2 have a twist angle, they do not come out even when the embedding angle θ3 is shallow.

  FIG. 7 is a cross-sectional view of the constant velocity universal joint in which the shaft 90 is inclined with respect to the shaft 10. Note that the cross section shown in FIG. 7 is different from the cross section shown in FIG. With reference to FIG. 7, the sliding ball 30 is positioned outside the outer race 20 during rotation (when swinging). At this time, since the slide ball 30 rotates about the rotation shaft 11, a centrifugal force acts on the slide ball 30. However, since the sliding ball 30 is press-fitted into the sliding ball cage 40, even if centrifugal force is applied, it does not fly outward.

  The sliding groove 50 is provided with a claw-shaped stopper 54, and the stopper 54 is fitted in the stopper groove 24. It is possible to prevent the sliding groove 50 from coming off by catching the stopper 54 on the end face of the stopper groove 24. The positions of the stopper 54 and the stopper groove 24 can be appropriately changed according to the rotation angle (oscillation angle). When it is desired to make a large oscillation, the stopper groove 24 is lengthened and the sliding groove 50 is What is necessary is just to enlarge a slide angle (slide amount). On the upper side of FIG. 7, the ball 60 is in contact with the incomplete groove 57 to prevent the ball 60 from being released to the outside. Thus, by providing the incomplete groove 57 in the sliding groove 50, the ball 60 slides the outer race groove 51 when an angle is given.

  6 and 7, the inner race groove 81 and the outer race groove 51 are drawn so as to extend on the same plane, but this is different from the actual cross section. Actually, since the inner race groove 81 and the outer race groove 51 are given a twist angle, the inner race groove 81 and the outer race groove 51 do not appear to extend long in the same plane.

  FIG. 8 is a perspective view including a partial cross section of the outer race. Referring to FIG. 8, inner surface 25 of outer race 20 has a spherical shape (dome shape), and slide ball groove 21 and stopper groove 24 are provided in the spherical surface. The two slide ball grooves 21 are formed as a set, and the two adjacent slide ball grooves 21 extend in parallel to each other. The slide ball groove 21 does not penetrate the outer race 20 and has a concave shape having a bottom. A stopper groove 24 is arranged between the two slide ball grooves 21. The stopper groove 24 extends along and parallel to the slide ball groove 21.

  In FIG. 8, the stopper groove 24 is sandwiched between the two slide ball grooves 21. However, the present invention is not limited to this, and the slide ball groove 21 is formed on both sides of the slide ball groove 21. A stopper groove 24 may be provided so as to surround it. Further, the number and length of the stopper groove 24 and the sliding ball groove 21 can be variously modified according to the requirements of the constant velocity universal joint 1. Each slide ball groove 21 is arranged on the same spherical surface and arranged on an arc centered on the rotation center 2. Therefore, if one slide ball groove 21 is extended, if the slide ball groove 21 is extended so as to return to the original position, the slide ball groove 21 extends so as to return to the original position. The circular shape in which the slide ball groove 21 is formed is a circular shape with the rotation center 2 as the center. In other words, the sliding ball groove 21 is arranged on the spherical great circle constituting the inner surface 25. In order to stabilize the movement of the sliding groove, two slide ball grooves 21 are provided.

  FIG. 9 is a front view of the outer race viewed from the direction indicated by IX in FIG. Referring to FIG. 9, the slide ball grooves 21 provided on the inner surface 25 of the outer race 20 are symmetrical to each other and extend on a spherical surface with the rotation center 2 as the center. That is, the distance between each point of the slide ball groove 21 and the rotation center 2 is equal. Further, in order to limit the sliding amount, the length of the sliding ball groove 21 is limited, and sliding of the sliding groove is allowed only within a certain range.

  FIG. 10 is a perspective view of the inner race. Referring to FIG. 10, inner race 80 is connected to shaft 90 and has a plurality of inner race grooves 81. The inner race groove 81 is inclined with respect to the shaft 90 and is twisted at a certain angle. The inner race groove center 82 has a circular shape centering on the rotation center 2 and extends non-parallel to the rotation shaft 91. The number of inner race grooves 81 is not limited to that shown in FIG. 10, and more inner race grooves 81 may be provided. The outer surface of the inner race 80 has an arc shape, and makes sliding with other members smooth.

  FIG. 11 is a plan view in which a part of the constant velocity universal joint according to the first embodiment of the present invention is cut away. FIG. 12 is a side view including a partial cross section of the constant velocity universal joint as viewed from the direction indicated by XII in FIG. FIG. 13 is a front view of the constant velocity universal joint as viewed from the direction indicated by XIII in FIG. Referring to FIG. 11, a slide ball 30 is disposed in the outer race 20 so as to be inclined with respect to the shaft 10. One slide ball cage 40 holds two rows of slide balls 30, and the slide balls 30 are fitted in slide ball grooves 55 as inner races provided in the sliding groove 50. That is, between the outer race 20 and the sliding groove 50, slide balls 30 as rolling elements inclined with respect to the shaft 10 are arranged. The arrangement direction of the slide balls 30 is the same as the arrangement direction of the outer race grooves. A cage 70 is provided inside the sliding groove 50, and a shaft 90 is disposed further inside the cage 70. The shaft 90 is inclined with respect to the shaft 10 and is given a predetermined swing angle.

  Referring to FIG. 12, when viewed from the side, shaft 90 is greatly inclined with respect to shaft 10, and a part of shaft 90 is in contact with outer race 20. The shaft 90 is connected to the inner race 80, and a part of the inner race 80 protrudes from the outer race 20. The inner race 80 is provided with an inner race groove 81 inclined, and the cage 70 is provided so as to be rotatable with respect to the inner race 80. A ball hole 71 for holding a ball is formed in the cage 70, and the sliding groove 50 is in contact with the outer surface of the cage 70. The sliding groove 50 can be slid in a certain direction by the sliding ball 30, and a stopper 54 for preventing the sliding groove 50 from sliding excessively is formed integrally with the sliding groove 50. The stopper 54 meshes with the stopper groove 24, and the stopper groove 24 and the stopper 54 come into contact with each other in the maximum inclined state.

  Referring to FIG. 13, as shown in the front view, an inner race 80 is attached to the shaft 90, and the inner race 80 is formed with a plurality of inner race grooves 81 that are inclined with respect to the extending direction of the shaft 90. Is done. The inner race groove 81 holds the ball 60 that is a rolling element. A cage 70 having a shape in which a sphere is partially cut out is disposed so as to contact the outer surface of the inner race 80. The inner surface of the cage 70 contacts the inner race 80. The cage 70 has a plurality of ball holes 71. The ball 60 is held in the ball hole 71. Since the inner race groove 81 is inclined with respect to the rotation shaft 91, the ball 60 moves in the rotation direction within the inner race groove 81. That is, the ball 60 moves in the circumferential direction of the cage 70 along the inclination direction of the inner race groove 81. In order to absorb this movement, the ball hole 71 of the cage 70 is a long hole, and is formed so that a long axis exists in the rotation direction. By adopting such a shape, it is possible to absorb the movement of the ball 60 in the rotation direction.

  The sliding groove 50 is disposed so as to contact the ball 60. As shown in FIG. 13, the sliding groove 50 is provided so as to be inclined in a direction different from the inner race groove 81. The inner race groove 81 and the outer race groove 51 are symmetrical, and the ball 60 is held at the point where the inner race groove 81 and the outer race groove 51 intersect. An outer race groove 51 is disposed on the inner surface side of the sliding groove 50, and the outer race groove 51 receives the ball 60. Two sliding ball grooves 55 are arranged on the outer surface of the sliding groove 50 in parallel with the direction in which the outer race groove 51 extends. The slide ball 30 moves on the slide ball groove 55. The slide ball 30 is held in the slide ball groove 21 of the outer race 20.

  FIG. 14 is a perspective view of the sliding groove. FIG. 15 is a perspective view of the sliding groove as seen from the direction indicated by XV in FIG. Referring to FIG. 14, the sliding groove 50 has an arc shape, and the inner surface thereof has an outer race groove 51 for contacting the ball and an imperfection for holding the ball to prevent the ball from jumping out. A groove 57 is formed. Each of the incomplete groove 57 and the outer race groove 51 is a recess, and the ball rolls in the recess. A slide ball groove 55 for holding the slide ball is provided on the outer surface side.

  Referring to FIG. 15, slide ball groove 55 extends along outer race groove 51 in FIG. 14 and is arranged concentrically with outer race groove 51. That is, the outer race groove 51 and the slide ball groove 55 are arranged on a concentric circle with the rotation center as the center. A claw-shaped stopper 54 is disposed between the two slide ball grooves 55 to prevent the projection from jumping out.

  Next, a method for assembling the constant velocity universal joint according to the first embodiment of the present invention will be described. 16 to 19 are cross-sectional views for illustrating the method of assembling the constant velocity universal joint according to the first embodiment of the present invention shown in FIG. First, referring to FIG. 16, a cage 70, an inner race 80, and a shaft 90 are prepared. The cage 70 has an internal space for accommodating the inner race, and the internal space is surrounded by a spherical inner surface 72 of the cage. A cage outer surface 73 is provided so as to face the cage inner surface 72, and the cage outer surface 73 is also provided on a spherical surface centering on the rotation center, similarly to the cage inner surface 72. The inner race 80 is inserted from the largest opening portion of the cage 70.

  Referring to FIG. 17, when the inner race 80 is inserted into the cage 70, the outer surface of the inner race 80 contacts the cage inner surface 72. In this state, the ball 60 is inserted from the ball hole 71 into the inner race groove 81 side. Then, the sliding groove 50 is attached so as to contact the ball 60 and the cage 70. At this time, the outer race groove 51 of the sliding groove 50 is brought into contact with the ball 60.

  With reference to FIG. 18, the sliding groove 50 is assembled to the outer race 20 in a state where the sliding groove 50 is in contact with the ball 60. Specifically, the sliding groove 50, the ball 60, and the inner race 80 are inserted into a space surrounded by the inner surface 25 of the outer race 20.

  Referring to FIG. 19, the sliding ball 30 is fitted into the sliding ball hole 41 while sliding the sliding ball cage 40. At this time, the ball is fitted from the inner side (the shaft 10 side), the ball is fitted, and the sliding ball cage 40 is pushed toward the shaft 10 side. Thereby, the constant velocity universal joint shown in FIG. 11 is completed.

  In the constant velocity universal joint 1 according to the present invention, the slide portion includes a slide ball as a rolling element and a slide ball cage 40 as a holder for holding the slide ball 30. It is interposed between the sliding groove 50 and the outer race 20.

  The constant velocity universal joint 1 further includes a cage 70 that holds the ball 60, and the cage inner surface 72 and the cage outer surface 73 have a spherical shape with the rotation center 2 as the center.

  In the constant velocity universal joint 1 according to the first embodiment configured as described above, the outer race groove 51 slides in a predetermined direction as shown in FIG. As a result, a larger rotation angle (swinging angle) can be obtained as compared with the conventional product in which the outer race groove does not slide, and a large rotation angle can be realized with one constant velocity universal joint.

(Embodiment 2)
FIG. 20 is a schematic diagram of an automobile according to the second embodiment of the present invention. Referring to FIG. 20, in automobile 400 according to the second embodiment of the present invention, constant velocity universal joint 1 according to the first embodiment is used between differential device 202 and tire 200. Specifically, the constant velocity universal joint 1 according to the present invention may be used as the constant velocity universal joint on the tire 200 side. Further, the constant velocity universal joint 1 according to the present invention may be used as a constant velocity universal joint on the side close to the differential device 202. A drive shaft 201 is interposed between the differential device 202 and the tire 200. The automobile 400 travels in the direction of the arrow 203, and the direction indicated by the arrow 203 is the vehicle front direction.

  In general, in a front drive vehicle, the constant velocity joint on the front wheel side needs to transmit a driving force to the tire side at a large angle. In order to reduce the turning radius of the vehicle, it is necessary to increase the cutting angle of the tire 200. However, in the conventional constant velocity universal joint, since the rotation angle is limited, the automobile 400 having a large cutting angle is manufactured. I couldn't. According to the present invention, by using the constant velocity universal joint of the present invention as the constant velocity universal joint on the tire 200 side, the automobile 400 in which the cutting angle of the tire 200 is dramatically improved can be provided.

(Embodiment 3)
FIG. 21 is a sectional view of a constant velocity universal joint according to the third embodiment of the present invention. The cross section shown in FIG. 21 corresponds to the cross section shown in FIG. Referring to FIG. 21, in constant velocity universal joint 1 according to the third embodiment of the present invention, the first embodiment is different in that no sliding ball is provided between sliding groove 50 and outer race 20. Different from the constant velocity universal joint 1 according to the above. The sliding groove 50 is in direct contact with the inner surface 25 of the outer race 20. It is possible to slide in the direction in which the outer race groove 51 extends with respect to the inner surface 25 of the outer race 20. Since the sliding groove 50 slides with respect to the outer race 20, a lubricant such as oil or grease may be interposed between the sliding groove 50 and the outer race 20 in order to suppress frictional resistance during sliding. .

  The constant velocity universal joint 1 according to the third embodiment configured as described above has the same effect as the constant velocity universal joint 1 according to the first embodiment.

  Although the embodiment of the present invention has been described above, the embodiment shown here can be variously modified. First, in each embodiment, a plurality of slide ball grooves 21, slide balls 30, outer race grooves 51, and inner race grooves 81 are provided, but the number of these is not particularly limited. Furthermore, the dimensions and materials of each element can be changed as appropriate.

  The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

  The present invention can be used in the field of constant velocity universal joints.

It is sectional drawing of the constant velocity universal joint according to Embodiment 1 of this invention. 2 is a cross-sectional view of a constant velocity universal joint in a state where a shaft 90 is inclined with respect to the shaft 10. FIG. It is a schematic diagram of the inner race groove center and the outer race groove center. FIG. 4 is a schematic diagram of an inner race groove center and an outer race groove center as viewed from the direction indicated by an arrow IV in FIG. 3. It is a schematic diagram of the inner race groove center and outer race groove center of the constant velocity universal joint shown in FIG. 2 is a cross-sectional view of a constant velocity universal joint according to Embodiment 1. FIG. 3 is a cross-sectional view of a constant velocity universal joint in which a shaft 90 is inclined with respect to the shaft 10. It is a perspective view containing the partial cross section of an outer race. It is a front view of the outer race seen from the direction shown by IX in FIG. It is a perspective view of an inner race. It is the top view which notched a part of constant velocity universal joint according to Embodiment 1 of this invention. It is a side view including the partial cross section of the constant velocity universal joint seen from the direction shown by XII in FIG. It is a front view of the constant velocity universal joint seen from the direction shown by XIII in FIG. It is a perspective view of a sliding groove. It is a perspective view of the sliding groove seen from the direction shown by XV in FIG. It is sectional drawing which shows the 1st process of the assembly method of the constant velocity universal joint according to Embodiment 1 of this invention shown in FIG. It is sectional drawing which shows the 2nd process of the assembly method of the constant velocity universal joint according to Embodiment 1 of this invention shown in FIG. It is sectional drawing which shows the 3rd process of the assembly method of the constant velocity universal joint according to Embodiment 1 of this invention shown in FIG. It is sectional drawing which shows the 4th process of the assembly method of the constant velocity universal joint according to Embodiment 1 of this invention shown in FIG. It is a schematic diagram of the motor vehicle according to Embodiment 2 of this invention. It is sectional drawing of the constant velocity universal joint according to Embodiment 3 of this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Constant velocity universal joint, 2 Center of rotation, 10,90 shaft, 11,91 Rotating shaft, 20 Outer race, 21 Slide ball groove, 22 Groove center, 23 Outer race end face, 24 Stopper groove, 25 Inner surface, 30 Slide ball, 40 Slide ball cage, 41 Slide ball hole, 50 Sliding groove, 51 Outer race groove, 52 Outer race groove center, 53 Sliding groove end face, 54 Stopper, 55 Slide ball groove, 57 Incomplete groove, 60 balls, 70 cage, 71 ball holes, 72 cage inner surface, 73 cage outer surface, 80 inner race, 81 inner race groove, 82 inner race groove center, 100 bisection surface.

Claims (3)

A ball is interposed between the first rotating body and the second rotating body, and the first rotating body rotates about the rotation center with respect to the second rotating body. It is possible to incline the rotating shaft of the rotating body of the second rotating body with respect to the rotating shaft of the second rotating body, and the angle formed by the rotating shaft of the first rotating body and the rotating shaft of the second rotating body. A constant velocity universal joint that transmits a rotational force via the ball between the first rotating body and the second rotating body by arranging the ball on a surface that bisects ,
A first groove member that rotates together with the first rotating body and has an inner race groove formed on a surface that contacts the ball;
A second groove member that rotates with the second rotating body and has an outer race groove formed on a surface thereof that contacts the ball;
A slide portion that holds the second groove member slidably in a direction in which the outer race groove extends,
The center of the inner race groove and the outer race groove extends on an arc centered on the rotation center,
The center of the inner race groove and the outer race groove have a twist angle so as to be symmetrical with respect to the bisecting surface, and at the position where the centers of the inner race groove and the outer race groove intersect. A constant velocity universal joint in which the ball is held.   The said slide part has a rolling element and the holder | retainer which hold | maintains the said rolling element, The said rolling element interposes between the said 2nd rotary body and the said 2nd groove member. Constant velocity universal joint. A cage for holding the ball;
3. The constant velocity universal joint according to claim 1, wherein an inner surface and an outer surface of the cage have a spherical shape with the rotation center as a center.

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