JP2002195284A - Constant velocity universal joint - Google Patents

Abstract

PROBLEM TO BE SOLVED: To further reduce the induced thrust and slide resistance of a tripod constant velocity universal joint. SOLUTION: This constant velocity universal joint is provided with an outer joint member in which three track grooves having roller guide faces facing each other in the circumferential direction thereof are formed, a tripod member having three leg shafts protruded in the radial direction, the rollers inserted in the track grooves, and the rings which are externally fitted to the leg shafts to rotatably support the rollers. Each roller is movable in the axial direction of the outer joint member along the roller guide face, and the ring has free relations, to the leg shaft in axial movement and swiveling. Further, a grinding process is performed only on the region of the outer peripheral face of the leg shaft contacting the inner peripheral face of the ring.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a sliding tripod type constant velocity universal joint. In general, a constant velocity universal joint is a type of universal joint that connects two shafts on a driving side and a driven side and can transmit rotational force at a constant speed even when there is an angle between the two shafts. In this type, the relative axial displacement between two axes is made possible by plunging a joint, and the tripod type uses a tripod member having three radially protruding leg shafts on one axis. A hollow cylindrical outer joint member having three track grooves extending in the axial direction is connected to the other shaft, and the tripod member shaft is accommodated in the track groove of the outer joint member to transmit torque. It is something to do.

[0002]

2. Description of the Related Art An example of a sliding tripod type constant velocity universal joint will be described with reference to FIG. 10. Three cylindrical track grooves 2 are formed in the inner peripheral surface of an outer joint member 1 in the axial direction. An annular roller rotatably fitted via a plurality of needle rollers 6 to a cylindrical outer peripheral surface of three leg shafts 5 protruding in the radial direction of a tripod member 4 inserted into the outer joint member 1. 7 is inserted into the track groove 2. A pair of roller guide surfaces 3 facing each other in the circumferential direction of each track groove 2 are concave curved surfaces parallel to the axial direction, and the outer peripheral surface of each roller 7 of the three leg shafts 5 is a convex conforming to the roller guide surface 3. It is a curved surface. Each roller 7
Can move along the track groove 2 while rotating around the leg shaft 5 while engaging with the roller guide surface 3 of the corresponding track groove 2.

As shown in FIG. 10 (B), when the joint transmits the rotational force with the operating angle θ, the roller 7 and the roller guide surface 3 are inclined relative to each other as shown in FIG. 10 (C). It becomes an intersecting relationship. In this case, while the roller 7 tends to roll in the direction indicated by the arrow t in FIG. 10B, the track groove 2 is a part of a cylindrical surface parallel to the axis of the outer joint member. 7 moves while being restrained by the track groove 2. As a result, the roller guide surface 3
A slip occurs between the roller and the roller 7 to generate a slide resistance, and the slip generates an induced thrust in the axial direction. Such slide resistance and induced thrust are:
It is desirable to reduce as much as possible in order to cause vibration and noise of the vehicle body, affect the NVH performance of the vehicle, and reduce the degree of freedom in designing the underbody of the vehicle.

As a sliding tripod type constant velocity universal joint designed to reduce such slide resistance and induced thrust, for example, a structure shown in FIG. 11 is known. That is, as shown in the drawing, the outer peripheral surface of the leg shaft 5 of the tripod member 4 is formed into a true spherical surface, and the cylindrical inner peripheral surface of the cylindrical ring 8 is slidably fitted on the true spherical surface. The ring 8 and the roller 7 form a roller assembly that is relatively rotatable via rolling elements. The needle rollers 6 are arranged in a so-called full roller state between the cylindrical outer peripheral surface of the ring 8 and the cylindrical inner peripheral surface of the roller 7, and are prevented from falling off by an annular washer 9. The roller 7 is accommodated in the track groove 2 of the outer joint member 1 and is movable in the axial direction of the outer joint member 1 while rolling on the roller guide surface 3 of the track groove 2.

[0005] The outer peripheral surface of the leg shaft 5 is a true spherical surface having a center of curvature on the axis of the leg shaft 5, and the roller assemblies (7, 8) swing around the center of curvature. Since the roller assembly is swingable, the roller 7 keeps a posture parallel to the axis of the outer joint member 1 when transmitting torque when the outer joint member 1 and the tripod member 4 are at an operating angle. As described above, the roller is guided by the roller guide surface 3 of the outer joint member 1, and rolls correctly on the roller guide surface 3 in the same posture. Therefore, the sliding resistance during the operation angle operation is reduced, and the generation of the sliding resistance and the induced thrust is suppressed.

[0006]

It is known to use a sliding tripod type constant velocity universal joint for transmitting a rotational force from an automobile engine to wheels at a constant speed. The sliding tripod type constant velocity universal joint has a spherical roller attached to the leg shaft of a tripod member, and a full-roller type without a needle roller as a rolling element between the outer peripheral surface of the leg shaft and the inner peripheral surface of the spherical roller. Used in When torque is transmitted in an angled state, induced thrust is generated during rotation due to mutual friction between internal components, and slide resistance is generated when the shaft is forcibly expanded and contracted in the axial direction even in a stopped state. . As typical NVH phenomena of an automobile involving the induced thrust and slide resistance, there is a lateral vibration of a running vehicle in relation to the former, and an idling vibration phenomenon in a D range at a stop of an AT car in relation to the latter.

The point of solving the problem of NVH in automobiles is to reduce the magnitude of induced thrust and slide resistance of the joint. Generally, the induced thrust and slide resistance of a joint tend to depend on the magnitude of the operating angle. For this reason, when applied to a drive shaft of an automobile, it leads to design restrictions that the operating angle cannot be increased. Therefore, in order to increase the degree of freedom in designing a vehicle underbody, there has been a problem of stabilizing induced thrust and slide resistance at a low level.

Therefore, an object of the present invention is to further reduce and stabilize the induced thrust and slide resistance.

[0009]

SUMMARY OF THE INVENTION The present invention comprises an outer joint member having three track grooves formed with circumferentially opposed roller guide surfaces, and three radially projecting leg shafts. A tripod member, a roller inserted into the track groove, and a ring externally fitted to the leg shaft and rotatably supporting the roller, wherein the roller is an outer joint member along the roller guide surface. In the constant velocity universal joint that can move in the axial direction, the ring is in a relationship in which the ring can freely move in the axial direction and swing with respect to the leg shaft, and the ring inner peripheral surface of the outer peripheral surface of the leg shaft Characterized in that only a predetermined range including the contact area is ground. The predetermined range is preferably set to be somewhat wider than the contact area in consideration of a processing error or the like. Then, the portion other than the predetermined range may be left as forged without being subjected to grinding, whereby the processing time and cost can be reduced.

The relationship in which the ring can freely move in the axial direction and swing with respect to the leg shaft is, for example, that the inner peripheral surface of the ring is formed in an arc-shaped convex cross section, and the outer peripheral surface of the leg shaft is formed in a vertical cross section. A straight shape, and in a cross section, a shape that makes contact with the inner peripheral surface of the ring in a direction orthogonal to the axis of the joint and forms a clearance between the inner peripheral surface of the ring and the axial direction of the joint. It is established by doing.

[0011] With the above-described shape of the leg shaft, the leg shaft can be inclined with respect to the outer joint member without changing the attitude of the roller assembly when the joint takes an operation angle. Moreover, as is clear from comparison between FIG. 1 (C) and FIG. 11 (C), since the contact ellipse between the outer peripheral surface of the leg shaft and the ring approaches the point from the lateral length, the friction moment for tilting the roller assembly is increased. Reduce. Therefore, the attitude of the roller assembly is always stable, and the roller can be smoothly rolled because the roller is held parallel to the roller guide surface. This contributes to a reduction in slide resistance and a reduction in induced thrust.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS First, an embodiment shown in FIGS. 1 and 2 will be described. Here, FIG. 1 (A) shows a cross section of the joint, FIG. 1 (B) shows a cross section perpendicular to the leg axis, and FIG. 2 shows a vertical cross section of the joint with an operating angle θ. As shown in FIG. 1, the constant velocity universal joint includes an outer joint member 10 and a tripod member 20. One of two shafts to be connected is connected to the outer joint member 10, and the other is connected to the tripod member 20.

The outer joint member 10 has three track grooves 12 extending in the axial direction on the inner peripheral surface. Roller guide surfaces 14 are formed on circumferentially opposite side walls of each track groove 12. The tripod member 20 has three radially protruding leg shafts 22, and a roller 34 is mounted on each leg shaft 22, and the rollers 34 are housed in the track grooves 12 of the outer joint member 10. . The outer peripheral surface of the roller 34 is a convex curved surface that conforms to the roller guide surface 14.

The outer peripheral surface of the roller 34 is a convex curved surface having an arc having a center of curvature at a position radially away from the axis of the leg shaft 22 as a generating line, and the cross-sectional shape of the roller guide surface 14 is a Gothic arch shape. Thus, the roller 34 and the roller guide surface 14 make an angular contact. FIG.
In (A), the action lines at the two contact positions are indicated by alternate long and short dash lines. Roller guide surface 1 against the outer peripheral surface of the spherical roller
Even if the cross-sectional shape of No. 4 is tapered, angular contact between them can be realized. By employing a configuration in which the roller 34 and the roller guide surface 14 make an angular contact in this manner, the roller is less likely to oscillate, and the posture is stabilized. In the case where the angular contact is not adopted, for example, the roller guide surface 14 is constituted by a part of a cylindrical surface whose axis is parallel to the axis of the outer joint member 10, and its cross-sectional shape is formed by a bus of the outer peripheral surface of the roller 34. It can also be a corresponding arc.

A ring 32 is fitted on the outer peripheral surface of the leg shaft 22. The ring 32 and the roller 34 are unitized via a plurality of needle rollers 36, and constitute a roller assembly that can be relatively rotated. That is, with the cylindrical outer peripheral surface of the ring 32 as the inner raceway surface and the cylindrical inner peripheral surface of the roller 34 as the outer raceway surface, the needle rollers 36 are rollably interposed between the inner and outer raceway surfaces. As shown in FIG. 1 (B), the needle rollers 36 have as many rollers as possible.
It is installed in a so-called full roller state without a retainer. Reference numerals 33 and 35 denote a pair of washers mounted in an annular groove formed on the inner peripheral surface of the roller 34 for preventing the needle rollers 36 from falling off. These washers 33, 35 have a cut at one location in the circumferential direction (FIG. 6).
(See (B)), the roller 34 is mounted in an annular groove on the inner peripheral surface of the roller 34 with its diameter reduced elastically.

The outer peripheral surface of the leg shaft 22 has a longitudinal section (FIG. 2).
(A)) has a straight shape parallel to the axis of the leg shaft 22, and a cross section (FIG. 1 (B)) has an elliptical shape whose major axis is orthogonal to the axis of the joint. The cross-sectional shape of the leg shaft is
The thickness of the tripod member 20 as viewed in the axial direction is reduced, and the tripod member 20 has a substantially elliptical shape. In other words, the cross-sectional shape of the leg shaft is
The surfaces of the tripod member facing each other in the axial direction are retracted in the mutual direction, that is, on the smaller diameter side than the virtual cylindrical surface.

The inner peripheral surface of the ring 32 has an arc-shaped convex cross section. That is, the generatrix of the inner peripheral surface is a convex arc having a radius r (FIG. 1C). Because of this, the cross section of the leg shaft 22 is substantially elliptical as described above, and a predetermined clearance is provided between the leg shaft 22 and the ring 32.
Is not only capable of moving the leg shaft 22 in the axial direction, but also is swingable about the leg shaft 22. Since the ring 32 and the roller 34 are unitarily rotatable via the needle rollers 36 as described above, the leg shaft 2
In relation to 2, the ring 32 and the roller 34 are swingable as a unit. Here, the swing means that the axes of the ring 32 and the roller 34 are inclined with respect to the axis of the leg shaft 22 in a plane including the axis of the leg shaft 22 (see FIG. 2A).

In the case of the conventional joint shown in FIG.
11C is in contact with the inner circumferential surface of the ring 8 over the entire circumference, so that the contact ellipse has a horizontally elongated shape extending in the circumferential direction as shown by a broken line in FIG. 11C. Therefore, when the leg shaft 5 is tilted with respect to the outer joint member 1, a frictional moment is generated which acts to tilt the ring 8 and thus the roller 7 with the movement of the leg shaft 5. On the other hand, in the embodiment shown in FIG. 1, the cross section of the leg shaft 22 is substantially elliptical, and the cross section of the inner peripheral surface of the ring 32 is cylindrical.
As shown by the dashed line in (C), the contact ellipse of the two becomes close to a point, and the area decreases at the same time. Therefore, the force for inclining the roller assembly (32, 34) is greatly reduced as compared with the conventional one, and the posture stability of the roller 34 is further improved. In the case of the conventional joint shown in FIG. 11, when the operating angle is 0, the contact portion between the leg shaft 5 and the ring 8 is at the center in the width direction of the ring 8 as shown in FIG. When the torque is transmitted in the state of taking the operating angle, the leg shaft 4 swings toward the near side and the back side of the sheet of FIG. 11A, so that the contact between the leg shaft 5 and the ring 8 is Is shifted downward from the center in the width direction. As a result, the behavior of the needle rollers 6 becomes unstable, and stable rolling may not be performed. In contrast, FIG.
In this embodiment, the contact portion between the leg shaft 22 and the inner peripheral surface of the ring 32 is always located at the center in the width direction of the ring 32, so that the needle rollers 36 roll stably.

Next, the embodiment shown in FIGS. 3 and 4 will be described. In this embodiment, while the generatrix of the inner peripheral surface of the ring 32 is formed by a single arc in the above-described embodiment, the center arc portion 32a and the escape portions 32b on both sides thereof are formed. They differ only in that they are formed in combination. The escape portion 32b is a portion for avoiding interference with the leg shaft 22 when the operating angle θ is set as shown in FIG. 3C, and gradually from the end of the arc portion 32a toward the end of the ring 32. It is composed of a straight line or a curve whose diameter is enlarged. here,
The case where the relief portion 32b is a part of a conical surface with a cone angle α = 50 ° is illustrated. The arc portion 32a has a large radius of curvature r of, for example, about 30 mm to allow the inclination of the leg shaft 22 with respect to the ring 32 by about 2 to 3 °.

In the tripod type constant velocity universal joint, mechanically,
When the outer joint member 10 makes one rotation, the tripod member 20
Swings about the center of the outer joint member 10 three times. At this time, the amount of eccentricity represented by the symbol e (FIG. 2A) increases in proportion to the operating angle θ. And the three leg shafts 22 are 12
Although they are separated by 0 °, when the operating angle θ is taken, FIG.
As shown in (B), considering the vertical leg shaft 22 shown on the upper side of the figure as a basis, the other two leg shafts 22
They are slightly inclined from their axes at the operating angle 0 shown by the dashed line. The inclination is about 2 to 3 ° when the operating angle θ is about 23 °, for example. Since this inclination is naturally allowed by the curvature of the arc portion 32a on the inner peripheral surface of the ring 32, it is possible to prevent the contact pressure between the leg shaft 22 and the ring 32 from becoming excessively high. Note that FIG.
FIG. 2B schematically shows three leg shafts 22 of the tripod member 20 as viewed from the left side surface of FIG. 2A, and a solid line represents the leg shaft. Further, a clearance is provided between the major axis diameter 2a of the leg shaft 22 and the inner diameter of the ring 32, which can absorb the inclination of the leg shaft 22 caused by the whirling of the trunnion center peculiar to the tripod type constant velocity universal joint. Specific numerical values of this clearance will be described in detail in the section of Examples.

In the above-described embodiment, as shown in FIGS. 1A and 3A, the inner side of the track groove 12, that is, the outer joint member 10 is formed for the purpose of restricting the inclination of the roller 34. A flange facing the end face of the roller 34 is formed on the large-diameter side when viewed in the cross section. However, in each of the above-described embodiments and the examples described below, a factor for inclining the roller 34 has been removed, so that it is not always necessary to provide the track groove 12 with a flange. Thus, the collar can be omitted. As a result, the roller 34
However, even if it temporarily oscillates for some reason, there is no fear that it will come into contact with the collar and generate sliding friction.

[0022]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS In carrying out the present invention, as shown in FIG. 6, since a leg shaft 22 having a substantially elliptical cross section and a circular ring 32 come into contact with each other to transmit torque, the surface pressure is reduced. It is necessary to relax. Hereinafter, specific examples for that purpose will be described. In FIG. 6B, the vertical direction on the paper is the load side, and the horizontal direction on the paper is the non-load side.

When the joint transmits the torque with the operating angle θ, the leg shaft 22 reciprocates within a range of the operating angle θ with respect to the ring 32 as shown by a broken line in FIG. At this time, on the non-load side, since a relatively large gap exists between the leg shaft 22 and the ring 32, the leg shaft 22 can swing without interfering with the ring 32. However, on the load side, as the operating angle θ increases and the inclination of the leg shaft 22 increases, the apparent curvature of the leg shaft 22 increases as indicated by the broken line in FIG. When the curvature becomes larger than the inner diameter of the leg shaft 22, the leg shaft 22 and the ring 32 come to two points. Then, thereafter, only the leg shaft 22 cannot be freely tilted, and the ring 32 is extended to extend the roller assembly (32, 32).
34). Therefore, within a predetermined angle range, the cross-sectional shape of the leg shaft 22 is set so that only the leg shaft 22 can be tilted without interfering with the ring 32.
In particular, the shape on the load side is determined.

Specifically, the maximum operating angle θmax is set to 25 °
7, as shown in FIG. 7, the major axis radius a and the minor axis radius b of the substantially elliptical cross section of the leg shaft 22 and the radius of curvature r of the inner peripheral surface of the ring (see FIGS. 1C and 4) ) Is set as follows, even if the joint has the maximum operating angle, the ring 3
2 to prevent the leg shaft 22 and the ring 3 from tilting.
2 can be minimized. r = 1.369a b / a = 0.759 The recommended range of the radius of curvature r of the inner peripheral surface of the ring is 0.5r-1.
5r, that is, 0.684a to 2.053a, the ellipticity b / a at that time is 0.836 to 0.647.
Becomes

The above setting, however, is possible in terms of shape, but there is a concern that the actual surface pressure between the leg shaft 22 and the ring 32 is too high when the vehicle is actually used. Therefore, if low vibration is required in a normal operating angle range for automotive applications, if the operating angle is reduced to such an extent that the roller assembly (32, 34) does not tilt, the surface pressure is reduced, and actual use is possible. For example, if the normal operating angle θ is in the range of more than 10 ° and less than 20 °, the optimum value and the recommended range of the radius of curvature r and the ellipticity b / a of the ring inner peripheral surface are as shown in Table 1.

[0026]

[Table 1]

As described above, as the ellipticity b / a of the substantially elliptical cross section of the leg shaft 22 is smaller, the leg shaft 22 tilts without tilting the roller assembly (32, 34) even at a larger operating angle. However, the surface pressure at the contact portion increases, and the strength of the leg shaft 22 also decreases. Therefore, FIG.
In the embodiment shown in FIG.
The ellipticity b1 / a1 is increased only for a region that contacts with the contact, i.e., the contact region β, and the other non-contact region has a composite elliptical shape with an ellipticity b2 / a2 that does not interfere with the maximum operating angle. For example, the normal operating angle θm
When ax is 15 ° and the radius of curvature r of the inner peripheral surface of the ring 32 is 2.898a, the ellipticity b1 / a1 of the contact area is obtained.
Is set to 0.859, and the ellipticity b2 / a2 of the non-contact area is set to 0.635. In FIG. 8, the contact area β is displayed only on the lower side of the figure, but it goes without saying that the contact area also exists on the upper side of the figure because the cross section of the leg shaft 22 is symmetrical.

In the embodiment shown in FIG. 9, the contact area β is not constituted by a single ellipse, but the ellipticity (b / a) is continuously changed. For example, in the same manner as described above, when the normal working angle θmax is set to 15 ° and the radius of curvature r of the inner peripheral surface of the ring 32 is set to 2.898a, the ellipticity at the position intersecting with the long axis is set to 1.0 in the contact area. The ellipticity is gradually reduced as the distance from the position increases, and the ellipticity is set to 0.635 in the non-contact area. Alternatively, the shape may be such that the ellipticity is gradually reduced from 1.0 to 0.635 from the long axis side to the short axis side regardless of the contact area and the non-contact area. FIG. 9 illustrates a case where the ellipticity is set to 1.0 at a position intersecting with the long axis of the contact area, and the radius of curvature is gradually decreased at predetermined angles as away from the position, for example, as illustrated.

As described above, since the cross-sectional shape of the leg shaft 22 is substantially elliptical, the grinding range is limited to the load-side contact region (β) where accuracy is required, and the other non-contact regions are regular. It is also possible to form a shape retreated to the inner diameter side from the ellipse (indicated by the two-dot chain line in FIG. 9) to make it a grinding relief. It is not always necessary to form this relief portion by actively performing cutting or other processing, and it may be formed in the shape at the time of forging the leg shaft and leave the forged finish. It also leads to shortening and cost reduction.

The value of the clearance provided between the long axis diameter 2a of the leg shaft 22 and the inner diameter of the ring 32 in order to absorb the inclination of the leg shaft 22 caused by the whirling of the trunnion center peculiar to the tripod type constant velocity universal joint. Is as shown in Table 2 below.

[0031]

[Table 2]

[0032]

The present invention relates to an outer joint member having three track grooves formed with circumferentially opposed roller guide surfaces, and a tripod member having three radially projecting leg shafts. And a roller inserted into the track groove, and a ring that is externally fitted to the leg shaft and rotatably supports the roller, wherein the roller extends in the axial direction of the outer joint member along the roller guide surface. In the movable constant velocity universal joint, the ring is in a relationship in which the ring can freely move in the axial direction and swing with respect to the leg shaft, and a contact area of the outer peripheral surface of the leg shaft with the inner peripheral surface of the ring. Since only a predetermined range including the grinding process is performed, the leg shaft can be inclined with respect to the outer joint member without changing the attitude of the roller assembly when the joint takes an operating angle. Therefore, the attitude of the roller assembly is always stable, and the roller can be smoothly rolled because the roller is held parallel to the roller guide surface. This further reduces slide resistance and induced thrust.

Also, since only a predetermined range of the outer peripheral surface of the leg shaft including the contact area with the inner peripheral surface of the ring is ground, a portion other than the predetermined range is forged without grinding. The finish may be left as it is, thereby shortening the processing time and reducing the cost.

The constant velocity universal joint of the present invention can contribute to the improvement of the NVH performance of an automobile, especially when applied to a drive shaft of an automobile, in which the magnitude of the slide resistance and the induced thrust is involved, and the design of the vehicle underbody can be freely designed. The degree increases.

[Brief description of the drawings]

1A is a cross-sectional view of a constant velocity universal joint according to an embodiment of the present invention, FIG. 1B is a cross-sectional view perpendicular to a leg axis and a leg axis of a roller assembly, and FIG. FIG.

2 (A) is a longitudinal sectional view of the constant velocity universal joint shown in FIG. 1, showing a state where an operating angle is set, and FIG. 2 (B) is a schematic side view of the tripod member in FIG. 2 (A).

3 (A) is an end view of a constant velocity universal joint with a partial cross section, showing another embodiment of the present invention, and FIG. 3 (B) is a view perpendicular to a leg axis and a leg axis of a roller assembly. FIG. 2C is a longitudinal sectional view of the constant velocity universal joint, showing a state where an operating angle is taken.

FIG. 4 is an enlarged sectional view of the ring in FIG. 3;

FIG. 5 is an end view of the constant velocity universal joint with a partial cross section, showing another embodiment of the outer joint member.

6A is a longitudinal sectional view of a constant velocity universal joint, and FIG. 6B is a plan view of a leg shaft and a roller assembly.

FIG. 7 is a transverse sectional view of a leg shaft.

FIG. 8 is a transverse sectional view of a leg shaft.

FIG. 9 is a transverse sectional view of a leg shaft.

10A is a cross-sectional view of a conventional constant velocity universal joint, FIG.
(B) is a longitudinal sectional view of the constant velocity universal joint of (A), (C) is a schematic perspective view showing the interrelationship between the roller, the roller guide surface, and the roller in (B).

11A is a cross-sectional view of another conventional tripod type constant velocity universal joint, FIG. 11B is a cross-sectional view perpendicular to a leg axis, and FIG. 11C is a cross-sectional view of a ring for explaining a contact ellipse. It is.

[Explanation of symbols]

 Reference Signs List 10 outer joint member 12 track groove 14 roller guide surface 20 tripod member 22 leg axis a long axis radius b short axis radius 32 ring 32a arc portion r radius of curvature 32b relief portion 34 roller 36 needle roller

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Kenji Terada 1578 Higashikaizuka, Iwata-shi, Shizuoka Pref. Inside (72) Inventor Masayuki Kuroda 1-317 Kyomachibori, Nishi-ku, Osaka-shi, Osaka Pref.

Claims (1)

[Claims] 1. An outer joint member having three track grooves formed with circumferentially opposed roller guide surfaces, a tripod member having three radially protruding legs, and the track. A roller inserted into the groove, and a ring externally fitted to the leg shaft and rotatably supporting the roller, wherein the roller is movable in the axial direction of the outer joint member along the roller guide surface. In the speed universal joint, a predetermined range including a region in which the ring can freely move in the axial direction and swing with respect to the leg shaft, and includes a contact region with a ring inner peripheral surface of an outer peripheral surface of the leg shaft. A constant velocity universal joint characterized by being ground only.