WO2004097238A1

WO2004097238A1 - Constant velocty joint and rotation drive force transmission mechanism

Info

Publication number: WO2004097238A1
Application number: PCT/JP2004/003653
Authority: WO
Inventors: Toru Mabuchi
Original assignee: Honda Motor Co., Ltd.
Priority date: 2003-04-28
Filing date: 2004-03-18
Publication date: 2004-11-11

Abstract

A constant velocity joint, comprising a retainer (36) having a first spherical surface (44) formed on an outer surface side and a second spherical surface (46) formed on an inner surface side with the centers of curvatures (A, B) displaced by equal distances to both sides of the intersection (C) thereof with a ball center surface on a joint axis (48), and a slide ring (38) installed between an inner ring (30) and the retainer (36). A cylindrical surface part (56) in contact with the projected cylindrical surface part (40) of the inner ring (30) is formed on the inner peripheral surface of the slide ring (38), and a third spherical surface (54) in contact with the second spherical surface (46) of the retainer (36) is formed on the inner peripheral surface of the slide ring (38).

Description

Constant velocity joints and rotational driving force transmission mechanism

The present invention provides, for example, arbitrarily selecting a constant velocity joint for connecting one transmission shaft and the other transmission shaft and a structure of an inner joint corresponding to various vibration characteristics in a driving force transmission portion of an automobile. The present invention relates to a rotational driving force transmission mechanism capable of performing a turning operation. Background art

2. Description of the Related Art Conventionally, in a driving force transmission unit of an automobile, a constant velocity joint that connects one transmission shaft to another transmission shaft and transmits a rotational force to each axle has been used.

For example, Japanese Utility Model Publication No. 63-26665 discloses a constant velocity joint according to this type of prior art, which has a center of curvature that is offset on both sides of a pole center plane on a joint shaft. A double offset type constant velocity joint having a cage having spherical inner and outer surfaces is disclosed.

In the double offset type constant velocity joint disclosed in Japanese Utility Model Publication No. 63-26665, an axial gap is provided between the cage and the inner joint member (both sides of the cylindrical surface at the center of the cage). According to the document, the inner joint member and the cage can move relative to each other by a very small distance along the axial direction even when the axial vibration is applied, so that slide resistance can be reduced.

In Japanese Utility Model Publication No. 63-26665, the slide resistance in a use state where an angular displacement or an axial displacement is generated while transmitting the torque of the drive shaft as in idling at the time of running or stopping is described. By reducing the engine speed, it is possible to prevent the drive from the engine from being transmitted to the vehicle body to avoid discomfort to the occupants. 'Similarly, Japanese Patent Application Laid-Open No. 11-182570 discloses a double offset type constant velocity joint. In the double offset constant velocity joint disclosed in Japanese Patent Application Laid-Open No. H11-182580, the radius of curvature of the partial spherical surface on the inner peripheral surface of the cage is calculated as follows. The radius of curvature of the spherical surface that is the outer peripheral surface of the inner joint member is set to be larger than the radius of curvature of the spherical surface that is the outer peripheral surface of the inner joint member. By arranging it at an offset position, it is possible to form a larger axial gap.

In the above-mentioned Japanese Patent Application Laid-Open No. 11-182570, an axial gap is formed. Therefore, even if vibration is applied from the engine side in a state where a torque is applied, the axial gap is formed. It is described that relatively small movement in the relative axial direction by the inner joint member and the cage becomes possible, and the slide resistance can be reduced.

However, the double offset type constant velocity joint disclosed in Japanese Utility Model Publication No. 63-26565 and Japanese Patent Application Laid-Open No. 11-187570 has a structure in which a cage and an inner joint member are provided between the cage and the inner joint member. It is a technical idea to reduce the slide resistance by increasing the relative axial movement amount between the cage and the inner joint member by increasing the provided axial gap. The moving distance of the relatively moving cage and the inner joint member is limited to a small distance, and the moving distance due to the axial gap is limited. Disclosure of the invention

A general object of the present invention is to provide a constant velocity joint capable of reducing the slide resistance over a wider range by further increasing the amount of inner ring movement in a double offset type.

A main object of the present invention is to provide a constant velocity joint capable of securing an appropriate amount of movement of the inner ring while maintaining a reduction in slide resistance over a wide range of the amount of movement of the inner ring. is there.

Another object of the present invention is to provide a constant velocity joint capable of suppressing a tapping sound generated when the amount of inner ring movement is restricted.

Another object of the present invention is to appropriately select the structure of an inner joint connected to a rotary drive source (differential gear) side in accordance with vibration characteristics such as tertiary vibration and Z or idling vibration. Times that can obtain good vibration characteristics An object of the present invention is to provide a rolling drive force transmission mechanism.

According to the present invention, when the two axes intersect and a relative displacement occurs in the axial direction, and the inner ring and the outer member relatively move in the axial direction, the protrusion formed on the outer peripheral surface of the inner ring. When the cylindrical surface slides along the cylindrical surface formed on the inner peripheral surface of the intermediate member, the pole held by the holding window of the retainer can be rolled. Therefore, the pawl held by the holding window of the retainer is smoothly guided by the first guide groove and the second guide groove. As a result, in a state where the constant velocity of the two axes is secured, the amount of movement of the inner ring is further increased, and the slide resistance is reduced over a wider range.

Further, according to the present invention, when the two axes intersect and a relative displacement occurs in the axial direction, and when the inner ring and the outer member relatively move in the axial direction, the intermediate member moves inside the retainer. In addition to being displaced in the axial direction along the axial gap formed between the inner ring and the surface, the convex cylindrical surface formed on the outer peripheral surface of the inner ring is replaced with the cylindrical surface formed on the inner peripheral surface of the intermediate member. By sliding along, the ball held by the holding window of the retainer is in a state where it can roll. BRIEF DESCRIPTION OF THE FIGURES

FIG. 1 is a longitudinal sectional view along the axial direction of a constant velocity joint according to a first embodiment of the present invention.

FIG. 2 is a perspective view of the constant velocity joint shown in FIG.

FIG. 3 is an exploded perspective view of the constant velocity joint shown in FIG.

FIG. 4 is a longitudinal sectional view of the constant velocity joint shown in FIG. 1 in a state where the second axis is tilted by a predetermined angle.

FIG. 5 is a partially enlarged longitudinal sectional view for explaining the operation of the constant velocity joint shown in FIG. FIG. 6 is an explanatory diagram that simplifies the relationship between the movement amount of the pole and the inner ring shown in FIG.

FIG. 7 is an explanatory diagram of constant velocity of the constant velocity joint shown in FIG.

FIG. 8 is a partial enlarged longitudinal view of a constant velocity joint according to a modification of the first embodiment. FIG.

FIG. 9 is a longitudinal sectional view of a constant velocity joint according to a comparative example.

FIG. 10 is a longitudinal sectional view along the axial direction of a constant velocity joint according to the second embodiment of the present invention.

FIG. 11 is a perspective view of the constant velocity joint shown in FIG. 10 cut away in the axial direction. FIG. 12 is an exploded perspective view of the constant velocity joint shown in FIG.

FIG. 13 is a longitudinal sectional view of the constant velocity joint shown in FIG. 10 in a state where the second axis is tilted by a predetermined angle.

FIG. 14 is a partially enlarged longitudinal sectional view for explaining the operation of the constant velocity joint shown in FIG.

FIG. 15 is a partially enlarged longitudinal sectional view of a constant velocity joint according to a modification of the second embodiment.

FIG. 16 is a longitudinal sectional view along the axial direction of a constant velocity joint according to the third embodiment of the present invention.

FIG. 17 is a perspective view of the constant velocity joint shown in FIG. 16 cut away in the axial direction. FIG. 18 is an exploded perspective view of the constant velocity joint shown in FIG.

FIG. 19 is a longitudinal sectional view of the constant velocity joint shown in FIG. 16 in a state where the second axis is tilted by a predetermined angle.

FIG. 20 is a partially enlarged longitudinal sectional view for explaining the operation of the constant velocity joint shown in FIG. _

FIG. 21 is a partially enlarged sectional view showing the shape of another notch.

FIG. 22 is a longitudinal sectional view showing a state in which the displacement of the pole is restricted by the stop portion formed on the inner ring when the inner ring moves integrally with the second shaft.

FIG. 23 is a longitudinal sectional view along the axial direction of a constant velocity joint according to a fourth embodiment of the present invention.

FIG. 24 is a longitudinal sectional view of the constant velocity joint shown in FIG. 23 in a state where the second axis is tilted by a predetermined angle. FIG. 25 is a partially enlarged longitudinal sectional view for explaining the operation of the constant velocity joint shown in FIG.

FIG. 26 is a longitudinal sectional view along the axial direction of a constant velocity joint according to a fifth embodiment of the present invention.

FIG. 27 is a longitudinal sectional view showing a state in which the ring member provided on the constant velocity joint shown in FIG. 26 abuts on the annular flange portion of the slide ring to restrict the displacement of the inner ring.

FIG. 28 is a longitudinal sectional view along the axial direction of a constant velocity joint according to a sixth embodiment of the present invention.

FIG. 29 is a partially enlarged longitudinal sectional view along the axial direction of a constant velocity joint according to a seventh embodiment of the present invention.

FIG. 30 is a partially enlarged longitudinal sectional view showing a single cushioning member integrally formed so as to cover the end face of the inner ring and the stopper portion, respectively.

FIG. 31 is a longitudinal sectional view along the axial direction of a constant velocity joint according to an eighth embodiment of the present invention.

FIG. 32 is a longitudinal sectional view along the axial direction of a constant velocity joint according to a ninth embodiment of the present invention.

FIG. 33 is a longitudinal sectional view showing a modification of the constant velocity joint shown in FIG. FIG. 34 is a longitudinal sectional view showing a modification of the constant velocity joint shown in FIG. FIG. 35 is a vertical cross-sectional view showing a state in which a buffer member is provided on the side peripheral surface of the inner ring.

FIG. 36 is a longitudinal sectional view showing a state in which a buffer member is provided only on the inner wall of the annular flange portion of the slide ring.

FIG. 37 is a longitudinal sectional view showing a state where a cushioning member is provided on a side peripheral surface of the inner ring in a constant velocity joint having an axial gap.

FIG. 38 is a longitudinal sectional view showing a state in which a cushioning member is provided only on the inner wall of the annular flange portion of the slide ring in a constant velocity joint having an axial gap. FIG. 39 is a view showing an axial direction of a constant velocity joint according to the tenth embodiment of the present invention. FIG.

FIG. 40 is a longitudinal sectional view showing a state where an annular protrusion of a cylindrical body provided on the constant velocity joint shown in FIG. 39 is in contact with an annular flange.

FIG. 41 is a partially omitted perspective view of a front-wheel drive vehicle to which the rotational driving force transmission mechanism according to the embodiment of the present invention is applied.

FIG. 42 is a partial cross-sectional configuration diagram showing a first type of rotational driving force transmission mechanism in which a first constant velocity joint is connected to both sides as an inner joint.

FIG. 43 is a partial cross-sectional configuration diagram showing a second type of rotational driving force transmission mechanism in which a first constant velocity joint and a second constant velocity joint are combined as an inner joint.

FIG. 44 is a partial cross-sectional configuration diagram showing a third type of rotational driving force transmission mechanism in which a first constant velocity joint and a third constant velocity joint are combined as an inner joint.

FIG. 45 is a longitudinal sectional view along the axial direction of the second constant velocity joint shown in FIG.

FIG. 46 is a longitudinal sectional view along the axial direction of the third constant velocity joint shown in FIG. 44.

FIG. 47 is an explanatory diagram showing characteristics of the first to third constant velocity joints with respect to tertiary vibration and idling vibration. BEST MODE FOR CARRYING OUT THE INVENTION

In FIG. 1, reference numeral 10 denotes a constant velocity joint according to the first embodiment of the present invention. The constant velocity joint 10 is integrally connected to one end of a first shaft 12. A cylindrical cup with a bottom (opening member) 16 having an opening 14, and fixed to one end of a second shaft 18 and housed in a hole 20 of the cup 16. It is basically composed of the inner member 22.

As shown in FIGS. 2 and 3, the inner wall surface of the iron cup 16 is formed of a cylindrical surface 24. The cylindrical surface 24 extends in the axial direction and extends around the axis. Each The six first guide grooves 26 a to 26 f are formed at intervals of 60 degrees. Each of the first guide grooves 26a to 26f is formed in an arc-shaped cross section or a compound curved cross-section in which a pair of arcs intersect in a V-shape.

The inner member 22 includes an inner ring 30 having a plurality of second guide grooves 28 a to 28 f having an arc-shaped cross section corresponding to the first guide grooves 26 a to 26 f on the outer peripheral surface. Between the first guide grooves 26 a to 26 f formed on the inner wall surface of the outer cup 16 and the second guide grooves 28 a to 28 f formed on the outer peripheral surface of the inner ring 30. And a plurality of poles 32 that are arranged to be able to roll with and perform a rotational torque transmitting function.

In the first embodiment, as shown in FIG. 3, an explanation is given using six poles 32. However, the present invention is not limited to this. For example, three to ten poles are used. It is also possible to use poles such as.

The inner member 22 has a plurality of holding windows 34 for holding the pawls 32 formed in a circumferential direction, and a retainer 3 interposed between the outer cup 16 and the inner ring 30. 6 and a slide ring 38 interposed between the retainer 36 and the inner ring 30.

The inner ring 30 is spline-fitted to the end of the second shaft 18, or is connected to the end of the second shaft 18 via a ring-shaped locking member attached to the annular groove of the second shaft 18. It is integrally fixed to the part. On the outer peripheral surface of the inner ring 30, a plurality of second guide grooves 2 which are arranged corresponding to the first guide grooves 26 a to 26 f of the outer cup 16 and are separated by an equal angle along the circumferential direction. 8a to 28f are formed. A convex cylindrical surface portion (convex cylindrical surface) 40 extending substantially parallel to the axis of the second shaft 18 is formed between the adjacent second guide grooves 28 a to 28 f.

In addition, a chamfered portion 42 subjected to chamfering processing is provided at a ridge portion forming a boundary between the convex cylindrical surface portion 40 and one end surface or the other end surface along the axial direction of the inner ring 30. (See Figure 1).

The pole 32 is formed, for example, by a steel ball, and is formed between the first guide grooves 26 a to 26 f of the auta cup 16 and the second guide grooves 28 a to 28 f of the inner ring 30. One is provided so that it can roll along the circumferential direction. This pole 3 2 The rotation torque of the first shaft 12 is transmitted to the second shaft 18 via the inner ring 30, and the first guide grooves 26a to 26f and the second guide grooves 28a to 28 By rolling along ί, the axial relative displacement between the second shaft 18 (the inner ring 30) and the first shaft 12 (the outer cup 16) and the relative It enables displacement.

The retainer 36 is formed in a substantially cylindrical shape, and a first spherical surface 44 having a point 点 as a center of curvature is provided on an outer peripheral surface that slides on an inner wall surface (cylindrical surface 24) of the outer cup 16. A second spherical surface 46 having a center of curvature at point B is provided on the inner peripheral surface (see FIG. 5). The points A and B are disposed on the joint shaft 48, respectively, and a virtual plane (pole center plane) connecting the center point O of the pole 32 and the joint shaft 48 are orthogonal to each other. Are placed at equal offsets from the intersection C (line segment AC-line segment BC).

The retainer 36 has a plurality of holding windows 34 each having a substantially rectangular cross section and corresponding to the number of the poles 32 and spaced apart by an equal angle along the circumferential direction. The pole 32 provided between the first guide grooves 26a to 26f and the second guide grooves 28a to 28f is held. In this case, the inner diameter (inner diameter width) of the holding window 34 is set slightly smaller than the diameter of the pole 32 (see FIG. 1).

The slide ring 38 is provided so as to surround the outer peripheral surface of the second shaft 18, and has an annular flange portion 50 formed along the radial direction of the second shaft 18, and the annular flange portion. Fold from 50 and go to the first axis 12 side:? And a plurality of claw portions 52 formed at an equal angle along the circumferential direction of the annular flange portion 50 while projecting in a substantially horizontal direction by a predetermined length. The claws 52 are integrally formed (see FIG. 3).

The outer peripheral surface of the claw portion 52 of the slide ring 38 is slidably provided in contact with the second spherical surface 46 of the inner peripheral surface of the retainer 36, and corresponds to the second spherical surface 46. A third spherical surface 54 having a radius of curvature is formed. The third spherical surface 54 of the claw portion 52 is formed including the thickness of the annular flange portion 50 (see FIG. 1). Further, the inner peripheral surface of the claw portion 52 comes into contact with the convex cylindrical surface portion 40 of the outer peripheral surface of the inner ring 30 so as to contact the inner surface. A cylindrical surface portion (cylindrical surface) 56 that enables relative axial displacement with the nulling 30 is formed.

In this case, the claw portion 52 of the slide ring 38 is externally fitted to the inner ring 30 along the convex cylindrical surface portion 40, and through a space formed between the adjacent claw portions 52. Pole 32 is installed.

The constant velocity joint 10 according to the first embodiment is basically configured as described above. Next, its operation and effect will be described.

When the first shaft 12 rotates, the rotation torque is transmitted from the outer cup 16 to the inner ring 30 via each pole 32, and the second shaft 18 maintains the same speed as the first shaft 12 While rotating in a predetermined direction.

In this case, for example, when the front side of the car rises and the rear side sinks, such as when the car suddenly starts, the relative displacement in the axial direction between the first axis 12 and the second axis 18 Occurs, and the inner ring 30 and the outer cup 16 move relatively in the axial direction. At this time, the convex cylindrical surface portion 40 formed on the outer peripheral surface of the inner ring 30 slides along the cylindrical surface portion 56 formed on the inner peripheral surface of the slide ring 38, thereby retaining the retainer. The pole 32 held by the holding window 34 of 36 is in a state capable of rolling movement. Therefore, the pole 32 held by the holding window 34 of the retainer 36 is guided by the first plan inner grooves 26a to 26f and the second guide grooves 28a to 28mm to smoothly roll. Move. '

On the other hand, when the intersection angle between the first axis 12 and the second axis 18 changes, the distance between the first guide grooves 26 a to 26 f and the second guide grooves 28 a to 28: f The retainer 36 is tilted by a predetermined angle under the action of the pawl 32 that rolls at the predetermined angle to allow the angular displacement, and the second spherical surface 46 formed on the inner peripheral surface of the retainer 36 and the slide ring 3 When the third spherical surface 54 formed on the outer peripheral surface of the slide 8 slides, and the slide ring 38 is tilted by a predetermined angle with respect to the retainer 36, the angular displacement is allowed (FIG. See). Thus, while maintaining the constant velocity of the first shaft 12 and the second shaft 18, their angular displacement and relative displacement in the axial direction are suitably allowed.

Here, the constant velocity joint 10 according to the first embodiment absorbs displacement in the axial direction. This case will be described with reference to FIG.

When a relative displacement in the axial direction occurs between the first axis 12 and the second axis 18, for example, when the inner ring 30 attempts to move in the direction of the arrow XI, the radial cup 16 Assuming that the contact point D between the first guide grooves 26a to 26f and the pole 32 is 100% rolling contact, the pole 32 moves in the direction of arrow E with the center point 0 as the center of rotation. The contact point D is moved along the direction of the arrow X2 by 1Z2, which is the distance moved by the arrow X1, with the rotation of. FIG. 6 shows the relationship between the inner ring 30 and the pole 32 when the first guide grooves 26 a to 26 f of the auta cup 16 are fixed and the inner ring 30 is movable. This is a simplified explanation of the relationship between the movement amounts.

In this case, the second spherical surface 46 on the inner peripheral surface of the retainer 36 and the third spherical surface 54 on the outer peripheral surface of the slide ring 38 come into spherical contact, so that displacement in the direction of the slide ring 38 is restricted. However, the convex cylindrical surface portion 40 of the outer peripheral surface of the inner ring 30 swings along the cylindrical surface portion 56 of the inner peripheral surface of the slide ring 38, thereby causing the inner ring 30 to move in the axial direction. Displacement is allowed.

Therefore, as shown in FIG. 5, the contact point F between the pole 32 and the inner groove 28 a to 28 f of the second plan of the inner ring 30 becomes movable along the axial direction. 0% rolling contact. As a result, even when a large relative axial displacement occurs between the first shaft 12 and the second shaft 18, the cylindrical surface 56 of the inner peripheral surface of the slide ring 38 and the inner Under the sliding action of the outer peripheral surface of the ring 30 with the convex cylindrical surface portion 40, the amount of displacement of the inner ring 30 in the axial direction can be further increased, and the slide resistance can be reduced over a wide range. be able to.

Next, the constant velocity joint 10 according to the first embodiment and the constant velocity joint 10 according to the comparative example (see Japanese Patent Application Laid-Open No. 3-277822) are compared in detail below. And explain.

As shown in FIG. 9, the constant velocity joint 101 according to this comparative example includes an outer joint member 103 in which a first guide groove 101 is formed, and a second guide groove 104. An inner joint member 105 formed, a pole 106 rotatably disposed between the first guide groove 102 and the second guide groove 104, and an outer Joint member 103 and inner joint member 105 And a cage 108 in which a pole holding window 107 for holding the ball 106 is formed.

The constant velocity joint 101 according to the comparative example includes a sliding ring 109 interposed between the inner joint member 105 and the cage 108, It has a pair of elastically deformable elastic members 110a and 110b disposed between 9 and the axial end of the cage 108.

The sliding ring 109 has a straight cylindrical outer peripheral surface 1111 in contact with the inner peripheral surface of the cage 108, and a concave spherical inner surface in contact with the outer peripheral surface of the inner joint member 105. A peripheral surface 112 and a receiving window provided at a position corresponding to the pole holding window 107 are slightly larger than the pole holding window 107 are formed. '

In the constant velocity joint 101 according to the comparative example, relative displacement occurs in the axial direction between the drive shaft 114 and the driven shaft 115, and the inner joint member 105 and the outer joint When the joint member 103 moves relatively along the axial direction, the sliding ring 109 moves together with the inner joint member 105, and moves in the axial direction with respect to the cage 108. To slide. The displacement of the sliding ring 109 is absorbed by a pair of elastic members 110a and 110b disposed at both ends thereof.

When the large axial relative movement between the inner joint member 105 and the outer joint member 103 is stopped, the pair of elastic members 110a and 110b elastically return to a sliding state. The cage 108 is returned to the initial setting position with respect to the inner joint member 105 via the bush 109 and is centered. One

For this reason, in the constant velocity joint 101 according to the comparative example, the pole 106 is always kept in a state capable of rolling motion, and a large axial dimension is provided between the drive shaft 114 and the driven shaft 115. It is stated that the slide resistance can be kept small even if a relative displacement occurs.

Next, the configuration, operation and effect of the constant velocity joint 10 according to the first embodiment and the constant velocity joint 101 according to the comparative example will be compared and studied.

In the constant velocity joint 10 according to the first embodiment, the third spherical surface 54 on the outer peripheral surface of the slide ring 38 contacts the second spherical surface 46 on the inner peripheral surface of the retainer 36, While the cylindrical surface portion 56 of the inner peripheral surface of the slide ring 38 is formed so as to contact the convex cylindrical surface portion 40 of the inner ring 30, the constant velocity joint 101 according to the comparative example has: The right cylindrical outer peripheral surface 1 1 1 of the sliding ring 1 09 contacts the inner peripheral surface of the cage 1 08, and the concave spherical inner peripheral surface 1 1 2 of the sliding ring 1 09 is inward. The configuration is different in that it is formed so as to be in contact with the outer peripheral surface of the joint member 105.

In other words, the slide ring 38 of the constant velocity joint 10 according to the first embodiment and the slide ring 109 of the constant velocity joint 101 according to the comparative example have an outer peripheral surface and an inner peripheral surface. Are different in that the relationship between the spherical surface and the cylindrical surface is reversed.

Regarding the operation, in the constant velocity joint 10 according to the first embodiment, the inner ring 30 is provided so as to be independently displaced in the axial direction along the slide ring 38. The constant velocity joint 101 according to the comparative example is different in that the inner joint member 105 is displaced in the axial direction integrally with the sliding ring 109.

Regarding the effect, in the constant velocity joint 10 according to the first embodiment, the cylindrical surface portion 56 on the inner peripheral surface of the slide ring 38 and the convex cylindrical surface portion 40 on the outer peripheral surface of the inner ring 30 While the displacement of the inner ring 30 in the axial direction can be set to be large under the sliding action of, the constant velocity joint 101 according to the comparative example has a sliding ring 10. Because a pair of elastic members 110a and 110b that absorb the displacement of 9 are disposed between the sliding ring 109 and the axial end of the cage 108, The joint member 105 can move by a very small distance.

In this case, in the constant velocity joint 101 according to the comparative example, when the movement amount of the inner joint member 105 is increased, the cage 108 and the pole 106 deviate from the bisector. Therefore, it may be difficult to ensure uniform speed between the drive shaft 114 and the driven shaft 115.

On the other hand, in the constant velocity joint 10 according to the first embodiment, the structure of the double offset type constant velocity joint 10 that secures constant velocity between the first shaft 12 and the second shaft 18 is provided. A significant effect different from the constant velocity joint 101 according to the comparative example in that the amount of displacement of the inner ring 30 in the axial direction is further increased while maintaining the Having.

Here, the constant velocity of the double offset type constant velocity joint 10 according to the first embodiment will be described with reference to FIG.

In FIG. 7, the pawl 32 is disposed so as to roll freely between the first guide grooves 26 a to 26 f of the auta cup 16 and the second guide grooves 28 a to 28 f of the inner ring 30. The first guide grooves 26 a to 26 f are provided so as to be parallel to the axis G of the first shaft 12 which is the input shaft, and the second guide grooves 28 a to 28 f and the second shaft which is the output shaft. The shaft 18 is provided so that the axis H is parallel to the axis H. The axis I indicates the axis of the retainer 36.

Also, the input shaft angular velocity is ω 、, the output shaft angular velocity is ω2, and the contact point when the perpendicular is lowered from the center point の of the pole 32 to the first guide grooves 26 a to 26 f of the auta cup 16 is a. The point of contact when the perpendicular is lowered from the center point の of the pole 32 to the second guide grooves 28 a to 28 f of the inner ring 30 is denoted by b.

In this case, the tangential velocity V 1 of the pole 32 viewed from the first axis 12 which is the input axis becomes V 1 = vector ao 'cl (! ■), while the output axis 2 The tangential speed V 2 of the pole 32 seen is

V 2 = vector b o · ω 2… (2) Where V1 = V2

The vector a o · ω 1 = vector b o · ω 2-(3) holds. _

In this case, since vector aο = vector bο, ω1 = ω2, and the constant velocity between the first shaft 12 as the input shaft and the second shaft 1.8 as the output shaft is secured.

As described above, in the first embodiment, the axial direction of the inner ring 30 is controlled by the sliding action of the cylindrical surface portion 56 on the inner peripheral surface of the slide ring 38 and the convex cylindrical surface portion 40 on the outer peripheral surface of the inner ring 30. Even if the displacement amount is set large, the intersection angle between the first axis 12 and the second axis 18 can be bisected by the pole 32 (the pole center plane connecting the centers of multiple poles) that performs the torque transmission function. Since it is configured to be held on a bisecting surface, constant velocity is ensured. Next, a constant velocity joint 10a according to a modification of the first embodiment is shown in FIG. In the constant velocity joint 10a according to the modification shown in FIG. 8, the inner diameter (inner diameter width) of the retaining window 34 of the retainer 36 is set to be larger than the diameter of the pole 32, By forming the axial gap 62 between the inner wall surface of the pole 4 and the pole 32, the axial displacement of the inner ring 30 can be further increased.

Next, FIGS. 10 to 15 show constant velocity joints 120 according to the second embodiment. In the following embodiments, the same components as those of the constant velocity joint 10 according to the first embodiment are denoted by the same reference numerals, and detailed description thereof will be omitted. The constant velocity joint 120 according to the second embodiment includes a pair of second spherical surfaces 1 46 a and 1 46 b of a retainer 1 36 and a third spherical surface 1 5 4 of a slide ring 1 3 8. This is different from the constant velocity joint 10 according to the first embodiment in that an axial gap 155 is formed between them.

As shown in FIGS. 10 to 13, the constant velocity joint 120 has a plurality of holding windows 34 for holding the pole 32 along the circumferential direction, and includes an outer cup 16 and an inner ring 3. 0, and a slide ring 138 interposed between the retainer 136 and the inner ring 30.

The retainer 1336 has a substantially cylindrical shape. As shown in FIG. 14, the outer surface of the retainer 13 that slides on the inner wall surface (cylindrical surface 24) of the auta cup 16 has a point A as a center of curvature. A first spherical surface 44 is provided.

Further, the retainer 1336 has an inner surface having an axial center formed by a point B, and the inner surface has a cylindrical surface (a first cylindrical surface) extending a predetermined length in the axial center. Surface) and a pair of first and second pairs which are formed continuously on both sides of the cylindrical surface and which are spaced apart from the joint shaft by a distance K in the radial direction by a point M and a point N, respectively. Two spherical surfaces 1 4 6 a and 1 4 6 b are provided.

The point A and the point B are disposed on the joint shaft 48, respectively, and the imaginary plane (pole center plane) connecting the center point O of the pole 32 and the joint shaft 48 are orthogonal to each other. They are located at equal offsets from intersection C (line segment AC-line segment BC). The slide ring 13 is provided so as to surround the outer peripheral surface of the second shaft 18, and has an annular flange portion 50 formed along the radial direction of the second shaft 18; Bending from the portion 50 and protruding toward the first shaft 12 side in a substantially horizontal direction by a predetermined length, and formed at equal angles along the circumferential direction of the annular flange portion 50. The annular flange portion 50 and the claw portion 52 are integrally formed (see FIG. 12). .

The outer peripheral surface of the claw portion 52 of the slide ring 13 is provided so as to be able to contact the second spherical surfaces 1 46 a and 1 46 b of the inner surface of the retainer 1 36, and the center of curvature is a point B. A third spherical surface 154 is formed. In this case, the radius of curvature of the third spherical surface 154 is set to be smaller than the pair of second spherical surfaces 144a and 146b formed on the inner surface of the retainer 135. An axial gap 1555 is formed between a set of second spherical surfaces 1346a, 146b and a third spherical surface 154 of the sliding ring 1338. The third spherical surface 154 of the claw portion 52 is formed including the thickness of the annular flange portion 50 (see FIG. 10). In addition, the inner peripheral surface of the claw portion 52 comes into contact with the convex cylindrical surface portion 40 of the outer peripheral surface of the inner ring 30 to enable relative displacement in the axial direction with the inner ring 30. A cylindrical surface portion (second cylindrical surface) 56 is formed.

Hereinafter, an operation and an effect of the constant velocity joint 120 according to the second embodiment will be described.

In this case, for example, when the front side of the car rises and the rear side sinks, such as when the car suddenly starts, the relative displacement in the axial direction between the first axis 12 and the second axis 18 Occurs, and the inner ring 30 and the outer cup 16 relatively move in the axial direction. At that time, the slide ring 38 is displaced in the axial direction along the axial gap 15 5 formed between the second spherical surface 1 46 a, 1 46 b and the third spherical surface 1 54, Further, the convex cylindrical surface portion 40 formed on the outer peripheral surface of the inner ring 30 slides along the cylindrical surface portion 56 formed on the inner peripheral surface of the slide ring 138, thereby reducing The pole 32 held by the holding window 34 of the tena 13 36 is in a state where it can roll. Accordingly, the pawl 32 held by the holding window 34 of the retainer 36 is guided by the first guide grooves 26a to 26f and the second guide grooves 28a to 28f to smoothly roll. I do. On the other hand, when the intersection angle between the first axis 12 and the second axis 18 changes, the distance between the first guide groove 26 a to 26 f and the second guide groove 28 a to 28 f Under the action of the pole 3 2 that rolls, the retainer 1 36 tilts by a predetermined angle to allow the angular displacement, and the second spherical surface 1 46 a formed on the inner surface of the retainer 1 36 1 4 6 b and the third spherical surface 1 5 4 formed on the outer surface of the slide ring 1 3 8 contact through the axial gap 1 5 5, and slide ring 1 3 against retainer 1 3 6 By tilting 8 by a predetermined angle, the angular displacement is allowed (see FIG. 13).

Thus, while maintaining the constant velocity of the first shaft 12 and the second shaft 18, their angular displacement and relative displacement in the axial direction are suitably allowed.

Here, a case where the constant velocity joint 120 according to the second embodiment absorbs axial displacement will be described with reference to FIG.

When a relative displacement in the axial direction occurs between the first axis 12 and the second axis 18, for example, when the inner ring 30 attempts to move in the direction of the arrow X 1, the (1) Assuming that the contact point D between the guide grooves 26a to 26f and the pole 32 is 1'00% rolling contact, the pole 32 will rotate in the direction of the arrow E with the center point 〇 as the center of rotation. While rotating, the contact point D is moved along the direction of the arrow X2 by 移動 of the distance moved by the arrow X1.

In this case, the axial gap 1 formed between the second spherical surface 1 46 a, 1 4 6 b on the inner surface of the retainer 1 3 6 and the third spherical surface 1 5 4 on the outer surface of the slide ring 1 3 8 The slide ring 13 8 moves in the axial direction along 5 5, and the convex cylindrical surface on the outer peripheral surface of the inner ring 30 along the inner peripheral surface 5 6 of the slide ring 13 8. The sliding of 40 allows the inner ring 30 to be displaced in the axial direction. .

Accordingly, as shown in FIG. 14, the contact point F between the pole 32 and the second guide groove 28 a to 28 の of the inner ring 30 becomes movable along the axial direction. 0 0% rolling contact. As a result, even if a large relative axial displacement occurs between the first axis 12 and the second axis 18, the second spheres 144 a and b b and the second spherical 3 The slide ring 1 3 8 is displaced in the axial direction along the axial gap 1 5 5 formed between the spherical surface 1 5 4 and the cylindrical surface 5 6 on the inner peripheral surface of the slide ring 1 3 8. Under the sliding action of the outer peripheral surface of the inner ring 30 with the convex cylindrical surface portion 40, the amount of displacement of the inner ring 30 in the axial direction can be further increased, and the slide resistance can be reduced over a wide range. Can be reduced.

Next, the configuration, operation and effect of the constant velocity joint 120 according to the second embodiment and the constant velocity joint 101 according to the comparative example (see FIG. 9) will be compared and studied.

In the constant velocity joint 120 according to the second embodiment, the third spherical surface 154 on the outer surface of the slide ring 13 8 and the second spherical surface 1 4 6 a on the inner surface of the retainer 13 6 An axial gap 1 5 5 is formed between 1 4 6 b and the cylindrical surface 5 6 of the inner peripheral surface of the slide rings 1, 3 8 contacts the convex cylindrical surface 40 of the inner ring 30. On the other hand, in the constant velocity joint 101 according to the comparative example, a straight cylindrical outer peripheral surface of the sliding ring 109 is formed. The configuration is different in that a concave spherical inner peripheral surface 112 of the sliding ring 109 is formed so as to be in contact with an outer peripheral surface of the inner joint member 105 as well as the sliding ring 109. ′ Regarding the operation, in the constant velocity joint 120 according to the second embodiment, the inner ring 30 is provided so as to be displaced in the axial direction alone along the slide ring 13. On the other hand, the constant velocity joint 101 according to the comparative example is different in that the inner joint member 105 is displaced in the axial direction integrally with the sliding ring 109. Regarding the effect, in the constant velocity joint 120 according to the second embodiment, the axial direction formed between the second spherical surface 1 46 a, 1 4 6 b and the third spherical surface 1 5 4 A slide ring 13 8 is provided along the gap 15 5 so that it can be displaced in the axial direction, and the cylindrical surface 56 on the inner peripheral surface of the slide ring 1 38 and the convex circle on the outer peripheral surface of the inner ring 30. While the amount of displacement of the inner ring 30 in the axial direction can be set to be larger by two layers under the sliding action with the cylinder surface portion 40, the constant velocity joint 10 according to the comparative example can be set. In Fig. 1, a pair of elastic members 110 a, 1 Since 1 Ob is disposed between the sliding ring 109 and the axial end of the cage 108, the inner joint member 105 can move a minute distance. .

In this case, in the constant velocity joint 101 according to the comparative example, when the moving amount of the inner joint member 105 is increased, the cage 108 and the ball 106 deviate from the bisector. Therefore, it may be difficult to ensure uniform speed between the drive shaft 114 and the driven shaft 115.

On the other hand, in the constant velocity joint 120 according to the second embodiment, a double offset type constant velocity joint 120 that secures constant velocity between the first shaft 12 and the second shaft 18 is used. In the state where the configuration is maintained, there is a remarkable effect different from the constant velocity joint 101 according to the comparative example in that the amount of displacement of the inner ring 30 in the axial direction is further increased.

The constant velocity joint of the constant velocity joint 120 according to the second embodiment is the same as the constant velocity joint 10 according to the first embodiment, and a detailed description thereof will be omitted.

Next, a constant velocity joint 120a according to a modified example of the second embodiment is shown in FIG.

In the constant velocity joint 120 a according to the modified example, the inner diameter (inner diameter width) of the retaining window 34 of the retainer 13 36 is set to be larger than the diameter of the ball 32, and the inner wall surface of the retaining window 34 is set. By forming a clearance 162 between the inner pole 30 and the pole 32, the axial displacement of the inner ring 30 can be further increased;

Next, FIGS. 16 to 22 show a constant velocity joint 210 according to a third embodiment.

The constant velocity joint 210 according to the third embodiment is different from the first and second embodiments in that a stopper mechanism that appropriately holds the displacement of the pole 32 (the inner ring 30) is provided. This is different from the constant velocity joints 10 and 120 according to the embodiment.

'' A stopper (stopper mechanism) 41 that regulates the amount of displacement of the pole 32 (the inner ring 30 ') is provided in the second guide groove 28 a to 28 f of the inner ring 30 on the slide ring 38 side. The stopper portion 41 is formed to bulge toward the opening of the outer cup 16. It is formed only at one end of the second guide grooves 28a to 28f close to the mouth 14 side.

In this case, the stopper portion 41 is formed continuously with the bottom wall 43 having a linear cross section of the second guide grooves 28 a to 28 f, and a bulging dimension t based on the bottom wall 43. Is set to about 0.5 mm to 2 mm (see Figure 16).

The shape of the stopper portion 41 is, as shown in FIGS. 16 and 18, the bottom of the second guide groove 28 a to 28 f toward the opening portion 14 side of the aperture 16. It is formed so as to gradually bulge from the wall 43, or, as shown in FIG. 21, rises slightly upward from the bottom wall 43 of the second guide groove 28a to 28〜, Further, the protrusions may be formed as protrusions 41a that are continuous in an arc shape in cross section.

Hereinafter, an operation and an effect of the constant velocity joint 210 according to the third embodiment will be described.

A relative displacement occurs in the axial direction between the first axis 12 and the second axis 18. For example, the inner ring 30 moves in the direction opposite to the arrow XI direction (the back side of the auta cup 16). When moving, the pole 32 held by the holding window 34 of the retainer 36 rolls along the bottom wall 43 of the second guide groove 28a to 28f of the inner ring 30. Line la.

At this time, the pawl 32 comes into contact with a stopper portion 41 formed at a terminal portion of the second guide groove 28 a to 28 f close to the annular flange portion 50 of the slide ring 38, and the rolling occurs. Movement is blocked. Therefore, when the inner ring 30 moves to the inner side of the outer cup 16, the pole 32 comes into contact with the stopper 41 formed at the end of the second guide groove 28 a to 28 f. By regulating the displacement, an appropriate amount of displacement of the inner ring 30 is secured (see Fig. 22).

The stopper portion 41 is not formed so as to protrude from the other end portion of the second guide grooves 28 a to 28 f, which is the back side of the outer cup 16. This is because, when the inner ring 30 is displaced in the direction of the arrow X1, the inner ring 30 comes into contact with the annular flange portion 50 of the slide ring 38 and the displacement of the inner ring 30 in the direction of the arrow X1 is reduced. Because of the restriction, the second guide groove 28 a to 28 の It is not necessary to form the stopper portion 41 at the end portion.

Next, FIGS. 23 to 25 show a constant velocity joint 300 according to a fourth embodiment. Note that, in the following embodiments, the same components as those of the constant velocity joint 210 according to the third embodiment will be denoted by the same reference numerals, and detailed description thereof will be omitted.

In the constant velocity joint 300 according to the fourth embodiment, the axial gap 150 is formed between the inner wall of the retainer 136 and the outer wall of the slide ring 138. This is different from the constant velocity joint 210 according to the third embodiment. Since the function of the axial gap 155 is the same as that of the constant velocity joint according to the second embodiment, a detailed description thereof will be omitted.

Next, FIGS. 26 and 27 show a constant velocity joint 400 according to a fifth embodiment.

In the constant velocity joint 400 according to the fifth embodiment, a ring member 202 functioning as a stop ring mechanism is mounted at a predetermined position of the second shaft 18 via an annular groove 204. This is different from the constant velocity joints 210 and 300 according to the third and fourth embodiments.

The outer diameter of the ring member 202 is set to be larger than the inner diameter of the hole 38 a of the slide ring 38, and the second shaft 18 is integrally formed with the inner ring 30 on the inner side of the outer cup 16. When the ring member 202 is moved toward the second shaft 1.8, the displacement of the inner ring 30 is restricted by the ring member 202 mounted on the second shaft 1.8 abutting against the annular flange portion 50 of the slide ring 38 (see FIG. 27), the appropriate amount of displacement of the inner ring 30 is ensured.

Next, a constant velocity joint 500 according to a sixth embodiment is shown in FIG.

In the constant velocity joint 500 according to the sixth embodiment, a ring member 200 shown in FIG. 26 is provided with respect to the second shaft 18 of the constant velocity joint 300 according to the fourth embodiment. 2 is common to the constant velocity joint 300 according to the fifth embodiment in that it is mounted.

Note that the configuration, operation, and effects of the ring member 202 are the same as those of the fifth embodiment. Therefore, the detailed description is omitted.

Next, a constant velocity joint 600 according to a seventh embodiment is shown in FIG.

When the pole 32 rolls along the second guide groove 28 a to 28 f of the inner ring 30, the pole 32 is terminated at the end of the second guide groove 28 a to 28 f. There is a possibility that hitting sound (interference sound) may be generated by contacting the stopper portion 41 provided on the horn. When the inner ring 30 and the slide ring 38 are relatively displaced along the axial direction, the inner wall of the annular flange portion 50 of the slide ring 38 comes into contact with the end face of the inner ring 30. As a result, a tapping sound (interference sound) may be generated.

Therefore, in the constant velocity joint 600 according to the seventh embodiment, in order to prevent the hitting sound from being generated, the constant velocity joint 600 is made of, for example, a resin material or a rubber material. A first cushioning member that covers the contact surface between the inner ring 30 and the end surface of the inner ring 30 and a second cushioning member 4 that covers the contact surface between the inner wall of the annular flange 50 of the slide ring 38 and the end surface of the inner ring 30 0 and 4 are provided.

The first cushioning member 402 is fixed to an upper surface of a stopper portion 41 which is one end portion of the inner ring 30, and the second cushioning member 400 is an annular flange portion of a slide ring 38. It is fixed to the 50 inner wall. By providing the first and second cushioning members 402, 404, the impact when the stopper portion 41 and the pole 32 or the inner ring 30 and the slide ring 38 abut is absorbed. The occurrence of rearing is prevented.

The first cushioning member 402 and the second cushioning member 404 are not formed separately from each other. Instead, as shown in FIG. 30, the end face of the inner ring 30 and the stopper portion 41 are formed. And a single cushioning member 406 may be provided which is integrally formed so as to respectively cover the above.

By providing the cushioning members 402, 404, and 406 in this manner, generation of a tapping sound is prevented, and a smooth relative displacement of the slide ring 38 and the inner ring 30 along the axial direction is achieved. Is made.

Next, the constant velocity joints 700 and 800 according to the eighth and ninth embodiments are shown in FIG. 1 and Fig. 32.

In the constant velocity joint 700 according to the eighth embodiment, as shown in FIG. 31, the ring member 202 mounted on the second shaft 18 comes into contact with the annular ring of the slide ring 38. This is different from the constant velocity joint 600 according to the seventh embodiment in that the cushioning member 502 is fixed to the outer peripheral surface of the flange portion 50.

Further, in the constant velocity joint 800 according to the ninth embodiment, as shown in FIG. 32, not the outer surface of the annular flange portion 50 of the slide ring 38 but the ring member 20. The second embodiment is different from the constant velocity joint 700 according to the eighth embodiment in that a ring-shaped cushioning member 600 is attached to the second embodiment. In this case, the buffer member 62 and the ring member 202 may be formed integrally, or may be formed separately.

That is, when the second shaft 18 moves in the axial direction integrally with the inner ring 30, the cushioning member 62 attached to a predetermined portion of the second shaft 18 is attached to the outer surface of the slide ring 38. The contact makes it possible to prevent the occurrence of a tapping sound, and also ensures that the amount of movement of the inner ring 30 is properly maintained.

As shown in FIGS. 33 and 34, a constant velocity joint 700 a having an axial gap 150 formed between the inner wall of the retainer 1 36 and the outer wall of the slide ring 1 38. , 800a may be provided with the same impact members 502, 602 as described above.

Alternatively, as shown in FIG. 35 and FIG. 37, a buffer member is provided on the side peripheral surface of the inner ring 30 which is close to the inner wall of the annular flange portion 50 of the slide rings 38, 1 38. Alternatively, as shown in FIGS. 36 and 38, the cushioning member 502 may be mounted only on the inner wall of the annular flange 50 of the slide rings 38, 138. Good. The constant velocity joints shown in FIGS. 37 and 38 differ from those of FIGS. 35 and 36 in that an axial gap 150 is formed.

Next, a constant velocity joint 900 according to the tenth embodiment is shown in FIGS. '

In the constant velocity joint 900 according to the tenth embodiment, the end of the second shaft 18 (A back side of the cup cup 16) and has a cylindrical body 702 which is press-fitted from the inner side of the second shaft 18 and is fixed to a predetermined portion of the second shaft 18; An annular projection 704 that can be engaged with the annular flange 50 of the slide ring 38 is formed.

The annular protrusion 704 of the cylindrical body 702 functions as a stopper mechanism, and when the inner ring 30 is displaced in the axial direction toward the back side of the auta cup 16, the second shaft 18 The annular protrusion 704 of the cylindrical body 702 locked to the inner ring is displaced integrally with the inner ring 30, and as shown in FIG. 40, the annular protrusion 704 becomes the annular flange 5. The displacement of the inner ring 30 is regulated by abutting on 0. Next, FIG. 41 shows a state in which the rotary driving force transmission mechanism 100 according to the present embodiment is applied to a front wheel drive vehicle. This rotational driving force transmission mechanism 100 is composed of a set of drive shafts 2 16 a, 2 1 arranged coaxially with an engine (rotary driving source) 2 1 2 and a differential gear device 2 1 4 therebetween. Has 6b.

A first outer joint 218a on the wheel side is connected to one end of one long drive shaft 216a, and a first inner joint 220a on the engine side is connected to the other end. Are linked. A second outer joint 218b on the wheel side is connected to one end of the other short drive shaft 216b, and a second inner joint 220b on the engine side is connected to the other end. Is done.

The first and second inner joints 220a and 220b are composed of different types or the same type of constant velocity joints respectively connected to a rotary drive shaft (not shown) of the differential gear device 214. The vibration of the engine 211 is transmitted via the rotary drive shaft. Further, as the first and second outer joints 218a and 218b, known bar-field type constant velocity joints (not shown) having the same configuration are used. ,

The first and second inner joints 220a and 22ob connected to the differential gear device 214 side include a first constant velocity joint 10 (see FIGS. 1 to 5). It includes three types consisting of a second constant velocity joint 200 and a third constant velocity joint 301.

As a combination of the first to third constant velocity joints 10, 200, 301, As shown in FIG. 42, the first and second inner joints 20a and 20b have the same structure and are respectively constituted by the first constant velocity joints 10 shown in FIGS. 1 to 5. One type of rotational driving force transmission mechanism 100a, and as shown in FIG. 43, one of the first and second inner joints 220a and 220b is a first constant velocity joint. A second type of rotational driving force transmission mechanism 100b composed of a second constant velocity joint 200 and the other, as shown in FIG. A third type of rotational driving force transmission mechanism in which one of the joints 220 a and 220 b is constituted by a first constant velocity joint 10 and the other is constituted by a third constant velocity joint 301. 100 c.

In the second and third types of rotational driving force transmission mechanisms 100b and 100c, the first constant velocity joint 10 includes left and right first and second inner joints 20a, It may be located on either side of 20b.

The first to third types of rotational driving force transmission mechanisms 100a to 100c are appropriately selected according to the vibration characteristics of the tertiary vibration and Z or idling vibration, as described later. is there.

Next, the first to third constant velocity joints 100, 200, and 310 constituting the first to third types of rotational driving force transmission mechanisms 100a to 100c are sequentially described. explain.

First, the first constant velocity joint 10 is the same as the constant velocity joint 10 according to the first embodiment shown in FIGS. 1 to 5, and thus a detailed description thereof is omitted. Note that, instead of the constant velocity joint 10, the constant velocity joint 120 according to the second embodiment in which the axial gaps 150 shown in FIG. 10 to FIG. It may be used as a constant velocity joint.

In the first constant velocity joint 10, by providing a slide ring 38 between the retainer 36 and the inner ring 30, the amount of displacement of the inner ring 30 in the axial direction is further increased to cover a wide area. As a result, idling vibration is absorbed and good vibration characteristics can be obtained.

In addition, in the first constant velocity joint 10, six poles 3 Since the configuration in which 2 is held is adopted, the tertiary vibration caused by the induced tertiary thrust force of rotation is reduced, and good vibration characteristics are obtained.

Next, the second constant velocity joint 200 is shown in FIG.

The second constant velocity joint 200 is a double offset type having a retainer having a partially spherical inner and outer surface having a center of curvature and offset on both sides of the ball center plane on the joint axis. The points are common to the first constant velocity joint 10 described above, but a slide ring 38 is provided between a retainer 203 disposed inside the outer cup 201 and an inner ring 205. The first constant velocity joint 10 differs from the first constant velocity joint 10 in that the inner surface of the retainer 203 and the outer surface of the inner ring 205 are in direct contact with each other.

In the second constant velocity joint 200 shown in FIG. 45, the same components as those of the first constant velocity joint 10 are denoted by the same reference numerals, and detailed description thereof will be omitted. You.

In the second constant velocity joint 200, the number of parts is small and the cost can be reduced because the slide ring 38 is not provided as compared with the first constant velocity joint 10; The slide resistance is increased in that the rolling range is limited. Therefore, the second constant velocity joint 200 provides good vibration characteristics for the tertiary vibration caused by the induced tertiary thrust force of the rotation, similar to the first constant velocity joint 10, but the idling vibration The vibration characteristics are inferior to the first constant velocity joint 10. _

Subsequently, the third constant velocity joint 301 is shown in FIG.

The third constant velocity joint 301 is formed of a known tri-board type constant velocity joint, and extends along the axial direction on the inner wall surface of the bottomed tubular auta cup 302 so as to extend around the axis. Three guide grooves 304a to 304c are formed at intervals of 120 degrees, respectively (however, the guide grooves 304b and 304c are omitted from the drawing). ing) . In the space of the auta cup 302, three trunnions 30 are provided at intervals of 120 degrees around the bulging axis toward the guide grooves 304a to 304c, respectively. 6 a to 30 c are formed physically (However, trunnions 300 b and 300 c are (Not shown).

The trunnion 300a (306b306c) having a partial spherical surface along the outer periphery is fitted with a cylindrical roller support member 108 having an L-shaped cross section. A ring-shaped roller 312 is mounted on the outer peripheral surface of the roller support 3108 via a plurality of rolling elements 310. The rolling element 310 may be a rolling bearing including a needle, a roller, and the like, for example.

The first to third types of rotational driving force transmission mechanisms 100 a to 100 c are based on the first constant velocity joint 10, and a double offset type second constant velocity joint 200. It is composed of a combination with a tri-board type third constant velocity joint 301.

Next, FIG. 47 shows the vibration characteristics of the first to third constant velocity joints 100, 200, and 301 with respect to the tertiary vibration and the idling vibration. In FIG. 47, the symbol 〇 indicates that the characteristics for various vibrations are good, and the symbol △ indicates that the characteristics for various vibrations are normal.

The tertiary vibration (vibration during acceleration) refers to the rotation when two axes (first axis 12 and second axis 18) have an operating angle, starting and accelerating due to the tertiary induced thrust force. Idling vibration is caused by axial sliding resistance, and is applied to the floor, steering wheel, etc. when the vehicle stops when rotational torque is applied. Vibration.

As can be understood from FIG. 47, the first constant velocity joint 10 has good vibration characteristics by suppressing both the tertiary vibration and the idling vibration, and has the second constant velocity joint 20. 0 indicates that the tertiary vibration is suppressed and good vibration characteristics are obtained, but has normal vibration characteristics with respect to idling vibration, and the third constant velocity joint 301 is good because the idling vibration is suppressed Although it has excellent vibration characteristics, it has ordinary vibration characteristics for tertiary vibration.

Combining the first to third constant velocity joints 10, 200, and 301 having different vibration characteristics with respect to such various vibrations, the first to third constant velocity joints shown in FIGS. 42 to 44 are combined. The type of rotational driving force transmission mechanism 100a to 100c is constructed. For example, depending on the type, size, drive system, etc. of the vehicle body, if there is a condition that both the tertiary vibration and the idling vibration deteriorate, the left and right vibrations as shown in Fig. 42 Select the first type of rotational driving force transmission mechanism 100a, in which the first constant velocity joints 10 and 10 are respectively disposed in both the 1st and 2nd inner joints 220a and 220b. I do. The conditions under which the vibration characteristics of both the tertiary vibration and the idling vibration are degraded include, for example, a vehicle in which the operating angle of the two axes is large, and the front nose of the vehicle body is large when the vehicle suddenly starts, and is independent. This refers to cases where the vehicle is used for vehicles with large driving torque, such as four-wheel drive vehicles.

For example, if the vibration characteristics of idling vibration are good but the vibration characteristics of tertiary vibration are deteriorated due to differences in the type, size, and drive system of the vehicle body, etc. The first and second inner joints 220a and 220b are provided with a first constant velocity joint 10 on one side and a second constant velocity joint 200 on the other side. Select the two types of rotational driving force transmission mechanism 100b. The conditions under which the vibration characteristics of the idling vibration are good but the vibration characteristics of the tertiary vibration deteriorate are, for example, a case where the vehicle is used in a vehicle having a large operating angle of two axes.

Furthermore, for example, if the vibration characteristics of the tertiary vibration are good but the vibration characteristics of the idling vibration are deteriorated due to differences in the type, size, drive method, etc. of the vehicle body, as shown in FIG. 44, 3rd type in which the first constant velocity joint 10 is disposed on one of the first and second inner joints 220a and 220b and the third constant velocity joint 301 is disposed on the other Of the rotation drive force transmission mechanism 100 c of the above. The condition in which the vibration characteristic of the tertiary vibration is good but the vibration characteristic of the idling vibration is deteriorated means, for example, a case where the vibration characteristic is used for a vehicle having a large driving torque such as an independent four-wheel drive vehicle.

As described above, in the present embodiment, any one of the first to third types of rotational driving force transmission mechanisms 100 a to 100 c can be arbitrarily selected according to various vibration characteristics. Accordingly, the tertiary vibration and the idling vibration are both suppressed, and good vibration characteristics can be obtained.

Claims

The scope of the claims

1. A plurality of first guide grooves (26a to 26f), which are connected to one of the two intersecting axes (12, 18) and have an inner peripheral surface and extend in the axial direction, are formed. A mouth member to be spoken (16),

Second guide grooves (28a to 28f), which are connected to the other of the two shafts, have a convex cylindrical surface (40) on the outer periphery, extend in the axial direction, and have the same number as the first guide grooves. With inner ring (30)

A pole (32) that is arranged to be rollable between the first guide groove and the second guide groove and that transmits torque;

A holding window (34) for accommodating the pole is formed, and a first spherical surface on the outer surface side having a center of curvature (A, B) equidistantly offset on both sides of an intersection with the pole center plane on the joint axis ( 44) and a retainer (3 '6) formed with a second spherical surface (46) on the inner surface side,

In constant velocity joints with

An intermediate member is interposed between the inner ring and the retainer. The intermediate member has a cylindrical surface (56) that contacts a convex cylindrical surface of the inner ring, and a second spherical surface of the retainer. A constant velocity joint (10) characterized in that a third spherical surface (54) is formed in contact with the joint.

2. In the constant velocity join described in claim 1,

The constant velocity joint according to claim 1, wherein an axial width of the holding window formed in the retainer is set to be larger than a diameter of the pole.

3. In the constant velocity joint according to claim 1,

The intermediate member comprises a slide ring (38), the slide ring being bent from the annular flange portion (50) and projecting a predetermined length from the annular flange portion, and extending in a circumferential direction of the annular flange portion. Formed at equal angles along the Constant velocity characterized by having a number of claws (52):

4. In the constant velocity joint according to claim 3,

A constant velocity joint, wherein a third spherical surface slidably provided in contact with the second spherical surface of the retainer is formed on an outer peripheral surface of the claw portion.

5. In the constant velocity joint according to claim 3,

The inner peripheral surface of the claw portion is formed with a cylindrical surface which is in contact with the convex cylindrical surface of the inner ring and enables relative displacement in the axial direction with the inner ring. .

6. a plurality of first guide grooves connected to one of the two intersecting shafts and having an inner peripheral surface and extending in the axial direction, and an outer member having an open end;

An inner ring connected to the other of the two shafts, having a convex cylindrical surface on the outer periphery and extending in the axial direction and having the same number of second guide grooves as the first guide grooves;

A pole that is arranged to be rollable between the first guide groove and the second guide groove and that transmits torque;

A holding window for accommodating the pole is formed, an outer surface formed of a first spherical surface, a first cylindrical surface (145) at a central portion in the axial direction, and a pair of second spherical surfaces (146) formed continuously on both sides thereof. a, 146 b), wherein the center of curvature of the outer surface and the axial center of the inner surface are equidistantly offset on both sides of the intersection with the pole center plane on the joint axis. And a retainer located at

In constant velocity joints with

An intermediate member is interposed between the inner ring (30) and the retainer (136), and the intermediate member has a second cylindrical surface (56) in contact with the convex cylindrical surface of the inner ring. ) And a third spherical surface (154) capable of contacting the second spherical surface of the retainer,

An axial gap is provided between the second spherical surface of the retainer and the third spherical surface of the intermediate member. (125) The constant velocity joint (120), which is provided with (155).

7. The constant velocity joint according to claim 6,

8. The constant velocity joint according to claim 6,

The intermediate member includes a slide ring (138), and the slide ring is bent from the annular flange and protrudes by a predetermined length, and extends along a circumferential direction of the annular flange. And a plurality of claw portions formed at an equal angle apart from each other.

9. The constant velocity joint according to claim 8,

A constant velocity joint, wherein a third spherical surface is provided on the outer peripheral surface of the claw portion so as to be movable in contact with the second spherical surface of the retainer.

10. The constant velocity joint according to claim 8,

The inner peripheral surface of the claw portion is formed with a cylindrical surface which is in contact with the convex cylindrical surface of the inner ring and enables relative displacement in the axial direction with the inner ring. Speed joint.

1 1. A plurality of first shafts connected to the first shaft and having an inner peripheral surface and extending in the axial direction.

_ A guide member formed with a guide groove, one end of which is open;

An inner ring that is connected to a second shaft that intersects the first shaft, has a convex cylindrical surface on the outer periphery, extends in the axial direction, and has the same number of second guide grooves as the first guide grooves; A pole that is arranged to be rollable between the first guide groove and the second guide groove and that transmits torque;

A holding window for accommodating the pole is formed, an outer surface formed of a first spherical surface, and an axial direction A central cylindrical first surface and an inner surface formed of a pair of second spherical surfaces formed continuously on both sides thereof, wherein a center of curvature of the outer surface and an axial center of the inner surface are aligned with each other. A retainer arranged at a position equidistantly offset on both sides of the intersection with the pole center plane on the joint axis,

An intermediate member interposed between the inner ring and the retainer, the intermediate member having a second cylindrical surface that contacts a convex cylindrical surface of the inner ring, and a third spherical surface that can contact a second spherical surface of the retainer; ,

A stopper mechanism for restricting movement of the inner ring in a direction from the opening of the outer member toward the back side;

A constant velocity joint (210), comprising:

12. In the constant velocity joint according to claim 11,

The constant velocity joint according to claim 1, wherein the stopper mechanism comprises a stopper portion (41) bulged at an end of the second guide groove of the inner ring.

13. In the constant velocity joint according to claim 11,

The constant velocity joint according to claim 1, wherein the stop mechanism comprises a ring member (202) locked to a predetermined portion of the second shaft (18).

14. In the constant velocity joint according to claim 11,

The constant velocity joint is characterized in that the stoma mechanism is constituted by a cylindrical body (702) having an annular projection (704), which is locked to a predetermined portion of the second shaft.

15 In the constant velocity joint according to claim 12,

A constant velocity joint having a buffer member (402, 404, 406) covering the stopper portion.

16. In the constant velocity joint according to claim 11, The constant velocity joint, wherein the intermediate member comprises a slide ring having an annular flange portion, and a cushioning member (502) is provided between the annular flange portion of the slide ring and the inner ring.

5 17. In the constant velocity joint according to claim 13,

The constant velocity joint, wherein the intermediate member comprises a slide ring having an annular flange portion, and a cushioning member (602) is provided between the annular flange portion of the slide ring and the ring member.

Ten .

18. It has first and second drive shafts (216a, 216b) arranged coaxially with a rotary drive source (212) therebetween, and connected to the wheel side of the first drive shaft. And the first inner joint (220a) connected to the rotary drive source side and the second outer joint (220a) connected to the wheel side of the second drive shaft. 218b) and a second inner joint (220b) connected to the rotary drive source 5 in a rotary drive transmission mechanism for a vehicle,

The first and second inner joints are

A plurality of poles are held by a retainer having inner and outer surfaces having a center of curvature equidistantly offset on both sides of the intersection with the pole center plane on the joint axis, and a slide ring (20) is provided between the retainer and the inner ring. 38) a double offset first constant velocity joint (10) with

A second constant velocity joint (200) of a double offset type in which the inner surface of the retainer and the outer surface of the inner ring are in direct contact without the slide ring (38) being interposed;

25 It is configured by a combination with a tri-board type third constant velocity joint (301) having three trunnions' bulging toward a guide groove formed in the inner wall of the outer cup,

The first and second inner joints are connected to the first constant velocity joint (10). The first type (100a),

A second type (100b) in which the first and second inner joints are respectively constituted by the first constant velocity joint (10) and the second constant velocity joint (200);

A third type (100c) in which the first and second inner joints are respectively constituted by the first constant velocity joint (10) and the third constant velocity joint (301);

The first to third types (100a to 100c) are selected according to various vibration characteristics.

19. The mechanism according to claim 18, wherein

The first type (100a) is selected when both of the tertiary vibration and the idling vibration have a condition of deteriorating the vibration characteristics,

The second type (100b) is selected when there is a condition that the vibration characteristics of the third vibration deteriorate.

The third type (100c) is a rotary driving force transmission mechanism that is selected when there is a condition under which the vibration characteristics of idling vibration deteriorate.