JPH10238549A - Constant velocity universal joint - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent the occurrence of a vibration in a rotating direction or a hammering sound due to a backlash, even when a spider part smoothly tilts for an outer member and an operation angle between one transmission shaft and another transmission shaft becomes large, by applying the constitution that a spider shaft elastically tilts via a spring member, upon the tilt of an inner member relative to the outer member. SOLUTION: When spider shafts 26a to 26c tilt about a point C as a center, a holder 34 in contact with the external surfaces thereof tilts and ball members 46a to 46d roll on lateral curved parts 22a and 22b, thereby enabling the spider shafts 27a to 26c to smoothly tilt. According to this construction, action vectors for the spider shaft 26a to 26c from the ball members 46a to 46d are always on the same straight line, and a distance between the centers of the ball members 46a to 46d and the axes of the spider shafts 26a to 26c is always set at a constant value, thereby eliminating the occurrence of a play due to a backlash under no-load and ensuring the smooth transmission of a force.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a constant velocity joint for connecting a drive shaft and a driven shaft in, for example, a driving force transmitting section of an automobile.

[0002]

2. Description of the Related Art Conventionally, in a driving force transmitting section of an automobile,
A constant velocity joint is used to transmit the torque of the drive shaft to each axle via a driven shaft.

As a constant velocity joint according to the prior art, for example, as shown in FIG. 13, three cylindrical track grooves 2 are formed on an inner surface of an outer race 1 along an axial direction.
Radial leg shafts 4 protrude from a tripod member 3 disposed inside the outer ring 1, and a spherical roller 6 is rotatable on a peripheral surface of each leg shaft 4 via a plurality of needle bearings 5. 1 so as to be slidable in the axial direction, and the spherical roller 6 is provided with roller guide surfaces 7 on both sides of the track groove 2.
Is known.

[0004]

However, in the above-described constant velocity joint according to the prior art, when the tripod member 3 is inclined at a predetermined angle with respect to the axis of the outer ring 1, each spherical roller 6 and the cylindrical track groove 2 are inclined. As shown in FIGS. 13 and 14, the roller guide surface 7 is oblique to each other, and the spherical roller 6 cannot perform a correct rolling motion.

That is, the spherical roller 6 rolls in the direction of arrow A or arrow B in FIG. 13, while the track groove 2 is cylindrical and substantially parallel to the axis of the outer ring 1. The spherical roller 6 moves while being restrained by the track groove 2. As a result, the slip generated between the roller guide surface 7 of the track groove 2 and the spherical roller 6 induces an axial thrust force, and the induced thrust force increases the inclination angle of the tripod member 3 with respect to the outer ring 1. Therefore, there is a concern that it becomes difficult to smoothly transmit the rotational force of the drive shaft to the driven shaft. The induced thrust force refers to a load generated by frictional resistance caused by reciprocating movement of the spherical roller 6 along the roller guide surface 7 and resulting from the frictional resistance.

In order to solve such a problem, for example, a constant velocity joint disclosed in Japanese Patent Application Laid-Open No. 3-168416 is known. In this constant velocity joint, three ball grooves are formed in the axial direction on the inner side of the outer ring, and three sets of ball pairs are held in the respective ball grooves by retainers. A tripod member is incorporated inside the outer race, and the tripod member is provided with three radial leg shafts disposed between the adjacent ball pairs. Each leg has a spherical surface formed thereon and a ball guide having a spherical recess formed between the spherical surface and the ball for engaging the spherical surface.

However, in the constant velocity joint disclosed in Japanese Patent Application Laid-Open No. 3-168416, when the operating angle between the first shaft provided at the closed end of the outer ring and the second shaft provided at the tripod member increases, There is a possibility that vibration in the rotational direction or so-called rattling sound due to backlash may occur. The tapping sound refers to a sound generated by the play in the rotation direction. In addition, the balls are likely to fall out of the retainer during assembly, making it difficult to hold the balls in the ball guides, requiring advanced techniques for assembly, increasing the assembly time, and reducing work efficiency. I am concerned.

On the other hand, Japanese Unexamined Patent Publication No. Hei 6-74243 discloses a three-plane constant velocity joint. In this three-plane constant velocity joint, an inner joint member is inserted into an outer joint member, and a trunnion is provided in the inner joint member. The trunnion is provided with a plurality of spherical balls, and the spherical balls are configured to roll freely on side walls forming a longitudinal chamber formed in the external joint member. The spherical ball is held on the trunnion by a positioning spring mounted on the trunnion.

However, also in this three-plane constant velocity joint, when the operating angle between the outer joint member and the inner joint member is increased, there is a possibility that vibration in the rotating direction due to backlash and so-called tapping sound may be generated. . In addition, when assembling, it is difficult to hold the spherical ball in the trunnion, and there is a concern that the efficiency of the assembling operation is reduced.

The present invention has been made in order to eliminate such a concern, and reduces the induced thrust force so that the driving force can be more smoothly transmitted from one transmission shaft to the other transmission shaft. In addition, when assembling, the ball member is securely held without falling off, thereby shortening the assembling time and improving work efficiency, and increasing the operating angle between one transmission shaft and the other transmission shaft. It is another object of the present invention to provide a constant velocity joint capable of preventing the occurrence of vibration in the rotational direction and knocking noise caused by backlash.

[0011]

In order to achieve the above-mentioned object, the present invention has a cylindrical shape, and a plurality of guide grooves extending along an axial direction are provided on an inner peripheral surface thereof. In a constant velocity joint having an outer member connected to the transmission shaft of the above, and an inner member inserted into the outer member and connected to the other transmission shaft, the constant velocity joint is provided on the inner member and faces the guide groove. A spider portion having a plurality of spider shafts formed therein, a holder provided on the inner member and having a hole portion through which the spider shaft is inserted, and a roller rotatable between an outer wall of the holder and the guide groove. The rolling member interposed in the spider shaft is inserted into a gap between a wall surface forming a hole of the holder and an outer periphery of the spider shaft, and urges the wall surface and the spider shaft in a direction away from each other. On the outer periphery of the spider shaft Characterized in that it comprises a sliding freely spring member, a and.

According to the present invention, when the inner member tilts with respect to the outer member, the spider shaft is elastically tilted by the spring member, and the spider portion tilts smoothly with respect to the outer member. For this reason, even if the other transmission shaft is inclined with respect to one transmission shaft, the rotation transmission force is smoothly transmitted.

[0013]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A constant velocity joint according to the present invention will be described in detail below with reference to preferred embodiments and preferred embodiments.

In FIG. 1, reference numeral 10 denotes a constant velocity joint according to the first embodiment. The constant velocity joint 10 is integrally connected to one end of a first shaft (not shown) and has a cylindrical outer cup (outer member) 12 having an opening, and is fixed to one end of a second shaft 14 and is fixed to the outer cup. And an inner member 16 housed in the twelve holes. The inner wall surface of the outer cup 12 extends along the axial direction, and each extends 120 ° around the axis.
The three guide grooves 18a to 18c are formed at intervals of. The guide grooves 18a to 18c are, as shown in FIG.
The ceiling portion 2 curved along the outer periphery of the outer cup 12
0 and side curved portions 22a and 22b formed on both sides of the ceiling portion 20 so as to face each other and centered on a point C in each of the guide grooves 18a to 18c. The ceiling 20 may be formed in a flat shape.

As shown in FIG. 1, the second shaft 14
The spider 30 is fitted around the outer periphery of the spider 30 at intervals of about 120 ° around the axis of the second shaft 14 toward the guide grooves 18a to 18c.
The spider shafts 26a to 26c are formed to protrude in a columnar shape.

As shown in FIGS. 3 and 4, a holder 34 having an outer shape of a square is provided on the outer periphery of the spider shafts 26a to 26c, and is formed at the center of the holder 34. The spider shafts 26a to 26c are provided so as to be freely inserted through a hole 32 having a rectangular cross section.

The hole 32 has a spider shaft 26a-26.
It is constituted by a pair of contact surfaces 36a and 36b that slide in a state of being in line contact with the outer peripheral surface of c, and a pair of wall surfaces 38a and 38b orthogonal to the corresponding contact surfaces 36a and 36b. The pair of contact surfaces 36a, 36b and the wall surfaces 38a, 38
b are formed to face each other.

The holder 34 has a pair of outer walls 40a, 4
0b, and one outer wall portion 40a has the contact surface 36
Grooves 42a and 42b are formed in parallel with a and 36b, and grooves 42c and 42d are formed in the other outer wall 40b in parallel with the contact surfaces 36a and 36b. The grooves 42a-
The cross section of 42d is formed in a V-shape, and its groove surface is formed slightly curved to reduce surface pressure on a ball member described later (see FIG. 2). In addition, the said groove part 42a-
The cross-sectional shape of 42d is not limited to the V-shape, and may be formed as a compound curve or an elliptical shape constituted by a plurality of curves having different radii of curvature.

At substantially the center of the outer wall portions 40a and 40b, stoppers 44a and 44b for isolating between the groove portions 42a and 42b and between the groove portions 42c and 42d are formed. The groove 4
Ball members (rolling members) 46a and 46b are interposed between the groove portions 42c and 42d and the other side curved portion 22b so as to be freely rotatable. The ball members 46c and 46d are interposed so as to roll freely.

The ball members 46a to 46d are supported at two points on the curved groove surfaces of the groove portions 42a to 42d formed in the holder 34. The ball members 46a to 46d are rotatable along the longitudinal direction of the groove portions 42a to 42d of the holder 34, and the displacement range thereof is regulated by the stoppers 44a and 44b.

As shown in FIG. 5, a frame (spring member) 48 is formed between the spider shafts 26a to 26c and the ceiling 20 in a substantially U-shape with a material such as an elastic metal plate. Are provided, and leg portions 50 of the frame 48 are provided.
a and 50b are inserted into gaps formed between the outer peripheral surfaces of the spider shafts 26a to 26c and the wall surfaces 38a and 38b of the holder 34. Both legs 50 of the frame 48
a, 50b are formed in a wave shape and the spider shafts 26a to 26b are formed.
26c and the wall surfaces 38a, 3
8b, and urges them in a direction away from each other.

A retainer 52 made of a material such as an elastic metal plate is provided between the frame 48 and the ceiling 20. Side portions 54a, 54 of the retainer 52 are provided.
b is bent and inserted between the outer wall portions 40a and 40b of the holder 34 and the side curved portions 22a and 22b (see FIGS. 2 and 3). A plurality of circular holes 56a and 56b are formed in the side part 54a, and a plurality of holes 56a and 56b are formed in the side part 54b.
c, 56d are formed.

By forming the diameters of the holes 56a to 56d slightly smaller than the diameters of the ball members 46a to 46d, the ball members 46a to 46d
6a to 56d so as to rollably engage with each other.
In this case, the interval between the holes 56a and 56b is selected such that when one ball member 46b contacts the stopper 44a, the other ball member 46a does not separate from the groove 42b, as can be understood from FIG. Hole 56
The same applies to c and 56d.

The ball members 46a to 46d are pressed toward the grooves 42a to 42d by the elasticity of the retainer 52. Therefore, this constant velocity joint 1
0, the ball members 46a to 46d
The ball members 46a to 46d are always held in a state of being engaged with the groove portions 42a to 42d.
The constant velocity joint 10 can be easily assembled as a whole because it does not come off.

The constant velocity joint 10 according to the embodiment of the present invention is basically configured as described above. Next, the operation thereof will be described.

When the first shaft (not shown) rotates, the rotational force is applied to the side curved portion 2 of the outer cup 12 depending on the direction of rotation.
The ball members 46a, 4b from either one of 2a, 22b
The spider 30 is rotated by being transmitted to the spider shafts 26a to 26c via the holder 6 and the spider shafts 26a to 26d, and the second shaft 14 whose one end is fitted to the spider 30 rotates. (See FIG. 1).

In this case, when the second shaft 14 is tilted by a predetermined angle with respect to the axis of the outer cup 12 having the first shaft (not shown), the spider shafts 26a to 26c tilt with the tilt of the second shaft 14.

For example, as shown in FIG.
When 6a to 26c are tilted about the point C, the holder 34 that is in line contact with the outer periphery of the spider shafts 26a to 26c is tilted, and the ball members 46a to 46d are moved to the side curved portions 22a,
Rolling on 22b, spider shafts 26a to 26c tilt smoothly. At this time, the holder 34 is provided so as to always follow the spider shafts 26a to 26c at the same inclination angle (see a two-dot chain line in FIG. 2).

That is, as shown in FIGS. 10A to 10C, the holder 34 inserted into the spider shafts 26a to 26c through the hole 32 is connected to the holder 34 and the guide grooves 18a to 1c.
In the direction of arrow A or arrow B, following the displacement of the spider shafts 26a to 26c, under the rolling operation of the ball members 46a to 46d rotatably provided between the side curved portions 22a and 22b of the spider shaft 8c. It is provided so as to be displaced integrally. Then, the ball members 46a to 46d, the holder 3
When a force is transmitted between 4 and spider shaft 26 a to 26 c, acts vector S _1, S ₂ of the force, as shown in FIG. 10B and FIG. 10C, the spider shaft 26 a to 26 c with respect to the outer cup 12 Even when the holder 34 is integrally inclined, the holder 34 is always on the same straight line and the center of the ball members 46a to 46d and the spider shafts 26a to 26d.
The clearance (clearance) from the axis of 26c is set to be always constant.

As described above, in this embodiment, the ball members 46a to 46d are connected to the spider shafts 26a to 26c (or the spider shafts 26a to 26c are connected to the ball members 46a to 46d).
There force acting vector S _1, S ₂ are always collinear relative to 46d), and such that the spaced distance between the axial center and the center of the spider shaft 26a~26c ball member 46 a to 46 d (clearance) is always constant With this setting, there is an effect that the force is smoothly transmitted without occurrence of backlash due to backlash on the no-load side.

On the other hand, in the constant velocity joint 41 according to the comparative example shown in FIGS. 11A and 11B, the ball member 43 (the ball member on the no-load side relative to the ball member 43 on the load side is denoted by reference numeral 45). ), When a force is transmitted between the holder 47 and the spider shaft 49, the action vectors S ₁ and S ₂ of the force are on the straight line T _{1 in} the state of FIG. 11A,
In the state of FIG. 11B, force action vectors S ₁ and S ₂ exist on a straight line T ₂ .

Therefore, when the spider shaft 49 is displaced from the state shown in FIG. 11A to the state shown in FIG. 11B, the force action vectors S ₁ ,
S ₂ is on different straight lines T ₁ , T ₂ , and in the state of FIG. 11B, between the non-load-side ball member 45 and the guide grooves 55, and the grooves 51, 53 formed in the holder 47, respectively. Clearance occurs. As a result, in FIG. 11B, the relationship of R ₁ + R ₁ ′ <R ₂ + R ₂ ′ holds, and on the no-load side, there is an inconvenience that play occurs due to the clearance between the ball member 45 and the grooves 51 and 53. There is. FIG. 11B corresponds to FIG.
This shows a state in which the spider shaft 49 has been displaced downward by a predetermined amount from the state of FIG. 1A.

Therefore, in the constant velocity joint 41 according to the comparative example shown in FIGS. 11A and 11B, the ball member 4
3 (45) to the spider shaft 49 (or the spider shaft 4).
9 when the force is transmitted to the ball members 43 and 45).

In FIG. 2, the spider shafts 26a to 26a
One ball member 46b (46a) and the other ball member 46d (4
6c), the side curved portions 22a and 22b are formed in an arc shape inward, so that simultaneous and horizontal rolling displacement toward the lower side in FIG. 2 is prevented.

5, the spider shafts 26a to 26c are connected to one leg 5 of the frame 48 as indicated by a two-dot chain line.
0b, the spider shafts 26a-2a
Part of the outer periphery of 6c compresses one leg 50b of the frame 48 against the elasticity of the frame 48 and approaches the wall surface 38b of the holder 34, and the other part of the outer periphery of the frame 48 And is separated from the wall surface 38a.

Further, the spider shafts 26a to 26c are in slidable line contact with the contact surfaces 36a, 36b of the holder 34 (see FIG. 2), and the leg portions 50a, 5
0b (see FIG. 5), the spider shafts 26a to 26c are provided so as to be displaceable relative to the holder 34 in the axial direction (the direction of arrow N in FIG. 5). Have been.

Further, the spider shafts 26a to 26c
However, as shown in FIG. 3, when the spider shaft 26a is rotated about its axis (point D in FIG. 3), the outer surfaces of the spider shafts 26a to 26c are in contact with the contact surfaces 36a and 36b of the holder 34 and the frame 48.
Of the spider shafts 26a to 26
6c without excessive force being applied to the spider shaft 26.
a to 26c rotate smoothly.

As described above, by providing the spider shafts 26a to 26c so as to be tiltable with respect to the outer cup 12, the clearance between the components increases even when the operating angle between the first shaft and the second shaft 14 increases. Therefore, it is possible to prevent the occurrence of vibration in the rotational direction and the occurrence of a tapping sound due to the backlash.

Further, when the spider shafts 26a to 26c are tilted, the spider shafts 26a to 26c
When the ball members 46a to 46c are displaced along
6d are the grooves 42a to 42d of the holder 34 and the guide grooves 1 while being held in the holes 56a to 56d of the retainer 52.
Rolls along both sides of the side curved portions 22a and 22b of 8a to 18c. For this reason, the induced thrust force applied to the spider shafts 26a to 26c is only the rolling resistance of the ball members 46a to 46d, and the spider shafts 26a to 26c can tilt and displace with less resistance.

At this time, as shown in FIG. 3, the ball members 46b and 46d abut against the stoppers 44a and 44b to restrict the displacement range, and the respective ball members 46a to 46d are formed in the holes 56a of the retainer 52. ５６56d and their relative positions are determined. in this case,
One side of the grooves 42a to 42d (for example, in the direction of arrow E)
Even when the ball members 46a to 46d are displaced, the force of the spider shafts 26a to 26c acting on the contact surfaces 36a and 36b of the holder 34 is always between the ball members 46a and 46b and between the ball members 46c and 46d. Because there is, holder 3
4 is well-balanced by the ball members 46a to 46d.

At this time, the ball members 46a and 46c slightly protrude from the end of the holder 34. However, since the ball members 46a and 46c are held by the retainer 52,
The ball members 46a, 46c are prevented from dropping out of the grooves 42a, 42c. Therefore, even if the length of the holder 34 is relatively short, the holder 34 is
Can have a long displacement range.

Next, a constant velocity joint 60 according to a second embodiment of the present invention is shown in FIGS. In the embodiments described below, the same components as those in the first embodiment are denoted by the same reference numerals, detailed description thereof will be omitted, and only different operation and effects will be described.

The spider shaft 62 of the constant velocity joint 60
Holes 64 orthogonal to the axial direction of the spider shafts 62a to 62c are formed in the holes a to 62c, and the pin members 66 are inserted into the holes 64. Both ends of the pin member 66 are formed as protrusions 67a, 67b protruding from the hole 64, and the protrusions 67a, 67b have spherical surfaces 68a, 68b centered on the center point F of the pin member 66. It is formed.
Flat portions 70a, 70b on which the spherical surfaces 68a, 68b of the pin member 66 are slidably contacted are formed on the wall constituting the hole 32 of the holder 34. The pin member 6
The diameter of the spherical surface 68 is selected by selecting the diameter of the spherical surface 68 to a predetermined value.
The radius of curvature of a and 68b can be set to a predetermined value.

When the spider shafts 62a to 62c are tilted at a predetermined angle with respect to the outer cup 12, the spherical surfaces 68a and 68b of the pin member 66 slide along the flat portions 70a and 70b, as shown by a two-dot chain line in FIG. By moving, the spider shafts 62a to 62c relatively rotate around the point F in the direction of arrow G or H. 7, the spherical surfaces 68a, 68b of the pin member 66 are indicated by two-dot chain lines.
Slides along the plane portions 70a, 70b,
The spider shafts 62a to 62c are formed by arrows I around the point F.
Or it turns in the direction of arrow J. As described above, the spider shafts 62a to 62c are tiltable with respect to the outer cup 12, and the degree of freedom is secured.

Next, a constant velocity joint 80 according to a third embodiment of the present invention is shown in FIG.

Grooves 83a and 83b are formed in one outer wall 40a of the holder 82 of the constant velocity joint 80.
Grooves 83c and 83d are formed in the other outer wall 40b. Both ends and the center of the outer wall portions 40a and 40b are formed as stoppers 84a to 84f. Therefore, the groove portions 83a and 83b, 83c and 83d are formed as stoppers 84b and 8d.
4e. In each of the grooves 83a to 83d,
Each of the ball members 46a to 46d is provided so as to freely roll one by one.

As can be easily understood from FIG. 8, the spider shafts 26a to 26c are attached to the outer cup 12 in the circumferential direction (FIG. 8).
When a force in the direction of arrows K and L in the middle is applied, the spider shafts 26a to 26c
Is always between the ball members 46a and 46b and between the ball members 46c and 46d.
2 is well-balanced by the ball members 46a to 46d. As a result, in FIG. 8, the axis (not shown) of the holder 82 and the side curved portions 22a and 22b are held so as to be substantially parallel at all times, and the ball members 46a to 46d
The holder 82 is prevented from inclining in the direction of the arrow K or the arrow L based on the peripheral clearance or deformation of the holder 82.

Next, a constant velocity joint 100 according to a fourth embodiment is shown in FIG.

The holder 102 of the constant velocity joint 100
The outer wall portions 40a, 40b have grooves 103a, 1
A plurality of ball members 106a to 106f are engaged with the grooves 103a and 103b, respectively, and stoppers 104a to 104d are formed at both ends of the wall constituting the grooves 103a and 103b. For this reason, the ball members 106 are formed by the stoppers 104a to 104d.
a to 106f are restricted, and the grooves 103a,
The ball members 106a to 106f do not fall off from 03b. Note that ball members 106a to 106c (106d to 106d) provided in one groove 103a (103b) are provided.
The number of 106f) is not limited to three, but is 2
At least two or more may be used.

Here, based on FIG.
The following describes an example in which the number of ball members 106a to 106f provided on 03b is set to, for example, six (three on one side in parallel). This constant velocity joint 1
00, the outer cup 1 is attached to the spider shafts 26a to 26c.
2, when the force in the circumferential direction is applied, the spider shafts 26a to 26a
26c is a point M on the contact surfaces 36a and 36b of the holder 102.
Press.

At this time, when the ball members 106a to 106f are displaced in the end portions of the grooves 103a and 103b, for example, in the direction of arrow E and the ball members 106a and 106d come into contact with one of the stoppers 104a and 104c, the ball member 1
06c and 106f are at the center of the other stopper 1 from point M.
04b and 104d.

Accordingly, even when the pressing force of the spider shafts 26a to 26c acts on the holder 102, the holder 102 can be replaced with the six ball members 106a to 106c.
It is well-balanced by f. As a result, in FIG. 9, the not-shown axis of the holder 102 and the side curved portion 2
2a and 22b are always held substantially parallel.

For example, in FIG.
2 ball members 106a, 106 on each side
b, 106d, 106e, and the holder 1
02, the load is applied from the inside of the holder 102 to the holder 102 by the reaction force of the ball member 106b (106a) disposed on one side of the holder 102.
Is applied to a ball member 106d disposed on the other side of the holder 102 on the opposite side to the above.
Since the holder 102 is canceled by the reaction force (not shown) to (106e), the holder 102 does not tilt.

In the above embodiment, the description has been made using the tripod type constant velocity joints 10, 60, 80, and 100 provided with the three spider shafts 26a to 26c and 62a to 62c. Is not
For example, two spider shafts 26 as shown in FIG.
Needless to say, the present invention can be applied to a bipot type constant velocity joint 10a provided with a and 26b.

[0055]

According to the present invention, the following effects and advantages can be obtained.

Since the other transmission shaft has a degree of freedom of inclination with respect to the one transmission shaft, and the spider shaft can be displaced with a small resistance by the ball member, the roller member can be displaced as in the prior art. No frictional resistance is generated. Therefore, even if the inclination angle of the other transmission shaft with respect to the outer member increases, the load applied to the spider does not increase, and the induced thrust force can be reduced.

Further, since the ball member is supported by the retainer, the ball member is prevented from dropping during the assembling, so that the assembling is facilitated and the working efficiency is improved.

Further, since the plurality of ball members always support the holder in a well-balanced manner, there is no concern that the holder is inclined with respect to the axial direction of the guide groove.

Further, even if the inclination angle of the other transmission shaft with respect to the outer member becomes large, the clearance between the components does not increase, and the vibration in the rotational direction due to the backlash and the so-called knocking sound are generated. Generation can be prevented.

[Brief description of the drawings]

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

FIG. 2 is a partially enlarged longitudinal sectional view of the constant velocity joint of FIG.

FIG. 3 is a sectional view taken along line III-III of the constant velocity joint of FIG. 2;

FIG. 4 is a partially enlarged exploded perspective view of the constant velocity joint of FIG. 2;

FIG. 5 is a sectional view taken along line VV of the constant velocity joint of FIG. 2;

FIG. 6 is a partially enlarged longitudinal sectional view showing a constant velocity joint according to a second embodiment of the present invention.

FIG. 7 is a sectional view taken along line VII-VII of the constant velocity joint of FIG. 6;

FIG. 8 is a partially enlarged transverse sectional view showing a constant velocity joint according to a third embodiment of the present invention.

FIG. 9 is a partially enlarged transverse sectional view showing a constant velocity joint according to a fourth embodiment of the present invention.

FIGS. 10A to 10C are operation explanatory diagrams each showing a state in which the holder is displaced by following the spider shaft in the constant velocity joint shown in FIG. 1;

FIG. 11A and FIG. 11B are operation explanatory diagrams each using a comparative example of a constant velocity joint.

FIG. 12 is a longitudinal sectional view in which the constant velocity joint according to the first embodiment of the present invention is applied to a bipot type.

FIG. 13 is a partial cross-sectional side view showing a constant velocity joint according to the related art.

14 is a partially enlarged schematic perspective view showing a state where a spherical roller used in the constant velocity joint of FIG. 13 is inclined at a predetermined angle with respect to a roller guide groove.

[Explanation of symbols]

10, 10a, 60, 80, 100: constant velocity joints 18a to 18c: guide grooves 22a, 22b: side curved portions 26a to 26c, 62a to 62c: spider shaft 30: spiders 34, 82, 102
... Holders 36a, 36b ... Contact surfaces 38a, 38b ... Wall surfaces 42a-42d ... Groove portions 44a, 44b, 84a-84f, 104a-104d
... Stoppers 46a-46d, 106a-106f Ball members 48 Frame 52 Retainers 67a, 67b Projections 68a, 68b Spherical surfaces 70a, 70b Planar portions

Claims (15)

[Claims] An outer member connected to one of the transmission shafts; and a plurality of guide grooves extending in the axial direction on an inner peripheral surface of the outer member. A constant velocity joint having an inner member inserted and connected to the other transmission shaft; a spider portion provided on the inner member and having a plurality of spider shafts formed toward the guide groove; provided on the inner member. A holder formed with a hole through which the spider shaft is inserted; a rolling member rotatably interposed between an outer wall of the holder and the guide groove; and a hole formed in the holder. A spring member that is inserted into a gap between the wall surface to be formed and the outer periphery of the spider shaft, and urges the wall surface and the spider shaft in a direction away from each other and is slidable against the outer periphery of the spider shaft. Characterized by Constant velocity joint. 2. The constant velocity joint according to claim 1, wherein the spider shaft is formed in a substantially cylindrical shape. 3. The constant velocity joint according to claim 1, wherein the hole of the holder has a rectangular cross section and slides in line with the outer peripheral surface of the spider shaft, and is substantially parallel to the guide groove. A constant velocity joint comprising: a pair of contact surfaces formed to face each other; and a pair of wall surfaces formed to be orthogonal to the contact surface and to face each other. 4. The constant velocity joint according to claim 1, wherein said rolling member comprises a plurality of ball members, said ball member rolling between a holder and a guide groove. A constant velocity joint characterized by being provided movably. 5. An outer member connected to one of transmission shafts, wherein the inner peripheral surface is provided with a plurality of guide grooves extending along an axial direction on an inner peripheral surface thereof. A constant velocity joint having an inner member inserted and connected to the other transmission shaft; a spider portion provided on the inner member, wherein a plurality of substantially cylindrical spider shafts are formed toward the guide groove; A holder provided in the inner member and having a hole through which the spider shaft is inserted; a rolling member rotatably interposed between an outer wall of the holder and the guide groove; and the spider shaft. And a protrusion formed to be orthogonal to the axis of the spider shaft. 6. The constant velocity joint according to claim 5, wherein a spherical surface is formed at an end of said projection so as to be able to slide on a hole of said holder. 7. The constant velocity joint according to claim 1, wherein a pair of curved surfaces opposing each other are formed on a wall forming the guide groove, and the curved surface and the holder are provided. A constant velocity joint characterized in that a plurality of ball members are rotatably provided between the groove and a groove formed in an outer wall of the constant velocity joint. 8. The constant velocity joint according to claim 1, wherein the holder is provided with a retainer having a hole that engages with a ball member. A constant velocity joint, wherein relative positions of a plurality of ball members provided with respect to one of the spider shafts are positioned. 9. The constant velocity joint according to claim 8, wherein the retainer has elasticity and urges the ball member toward the holder. 10. The constant velocity joint according to claim 1, wherein the holder has a pair of outer walls extending along an axial direction of the holder, and a central portion of the outer wall. A constant velocity joint provided with a stopper for restricting a displacement range of the ball member. 11. The constant velocity joint according to claim 1, wherein the holder has a pair of outer walls extending along an axial direction of the holder, and both ends of the outer wall. A constant velocity joint, wherein a stopper for regulating a displacement range of the ball member is provided. 12. The constant velocity joint according to claim 1, wherein the holder has a pair of outer walls extending along an axial direction of the holder, and both ends of the outer wall. And in the center,
A constant velocity joint, wherein a stopper for regulating a displacement range of the ball member is provided. 13. The constant velocity joint according to claim 11, wherein when a plurality of ball members are displaced toward one of the stoppers provided at both ends of the outer wall of the holder, the ball member on the other stopper side is connected to the outer wall. A constant velocity joint which is located on the other stopper side from the center of the joint. 14. A constant velocity joint according to claim 1, wherein the holder inserted through the spider shaft through the hole is rotatable between the holder and the guide groove. A constant velocity joint characterized by being integrally displaced following a displacement of the spider shaft under a rolling operation of a provided ball member. 15. A constant velocity joint according to claim 14, wherein when a force is transmitted between the ball member, the holder and the spider shaft, the action vector of the force is always on the same straight line, and A constant velocity joint wherein the distance between the center and the axis of the spider shaft is always constant.