JPH09133147A - Constant velocity joint - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve plunging performance and a vibration cut-off characteristic and make a manufacturing cost low through simple structure. SOLUTION: Track grooves 26a-26c are formed of plane parts 34 and pairs of nearly flat opposed roller guide grooves 30a, 30b where roller outer members 28 roll. The roller outer members 28 have the substantially flat peripheral surface corresponding to the roller guide grooves 30a, 30b, and are extended along the axial direction of the track grooves 26a-26c and held by protruding parts 54a, 54b formed at the internal wall of an outer cup 22.

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 portion 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. Here, a constant velocity joint according to the related art devised by the present applicant is shown in FIG. The constant velocity joint 1 includes three roller guide grooves 3 extending in the axial direction on the inner wall surface of the outer cup 2.
A (3b, 3c) is defined, and a spider 4 is disposed inside the outer cup 2.

The spider 4 has a roller guide groove 3a.
Spider shaft 5a (5b) bulging toward (3b, 3c)
b, 5c) are respectively formed on the spider shaft 5a.
A ring-shaped inner roller 6 is fitted onto the outer peripheral surfaces of (5b, 5c), and a holder 9 for holding a needle 7 and an outer roller 8 is further provided on the outer peripheral portion of the inner roller 6.
Is provided. The outer roller 8 is formed on the curved surface of the roller guide groove 3a (3b, 3c) with which the outer roller 8 slides.
The end face restricting portion 10 that restricts the inclination of is bulged. A flange 11 is provided on the bottom surface of the holder 9 so as to project toward the roller guide groove 3a.

In this case, the spider 4 connected to the driven shaft
A driving force acts on the spider 4 and a large operating angle is given to the spider 4, so that the outer roller 8 slides along the curved roller guide groove 3a. Therefore, by bringing the upper end 12 of the holder 9 into contact with the upper surface 13 of the outer cup 2 or bringing the flange 11 of the holder 9 into contact with the end face restricting portion 10, the outer roller 8 is moved relative to the roller guide groove 3a. The sliding displacement is regulated within a predetermined range.

[0005]

However, in the constant velocity joint 1 according to the above-mentioned prior art, the holder 9 is mounted on the upper surface portion 13 or the end surface regulating portion 10 of the outer cup 2 in order to regulate the sliding displacement of the outer roller 8. When they are brought into contact with each other, sliding friction is generated, which may impair plunge performance.

Further, in the constant velocity joint 1 described above, the holder 9 has the upper surface portion 13 of the outer cup 2 or the end surface regulating portion 1.
When it comes into contact with 0, the vibration from the outer cup 2 passes through the holder 9 and the inner roller 6 and the spider shaft 5a.
Therefore, the vibration isolation characteristic may deteriorate. The present invention has been made to improve the above-mentioned points, and an object thereof is to provide a constant velocity joint that can be manufactured inexpensively with a simple structure while improving plunge performance and vibration isolation characteristics. And

[0007]

In order to achieve the above-mentioned object, the present invention provides a plurality of track grooves, which are spaced apart by a predetermined distance and extend along the axial direction, on the inner peripheral surface, and one of the conductive shafts is provided. A cylindrical outer member connected to the roller member, a roller member that is displaced along the track groove, and a holder that holds the roller member, and the other outer conductive member is inserted into the inner space that opens in the outer member. In a constant velocity joint including an inner member connected to a shaft, the roller member is in rolling contact and a set of substantially flat first surfaces facing each other;
The track groove is formed by a second surface that is substantially orthogonal to the surface of the roller member, and the roller member has a substantially flat outer peripheral surface corresponding to the first surface and extends along the axial direction of the track groove. It is characterized in that it is extended and held by a ridge formed on the inner wall surface of the outer member.

According to the present invention, the sliding direction of the roller member is limited only to the direction along the axial direction of the track groove by the ridge portion having the function of restricting the displacement of the roller member along the axial direction. . As a result, it is possible to prevent the holder from generating sliding resistance and improve plunge performance. In addition, the transmission of vibration from one transmission shaft to the other transmission shaft is blocked by the needle bearing interposed between the roller member and the holder.

[0009]

BEST MODE FOR CARRYING OUT THE INVENTION Next, preferred embodiments of a constant velocity joint according to the present invention will be described in detail below with reference to the accompanying drawings. Reference numeral 2 in FIG.
Reference numeral 0 denotes a constant velocity joint according to the first embodiment of the present invention, and this constant velocity joint 20 is a tubular outer cup (which is integrally connected to one end of a drive shaft (not shown) and has an opening ( The outer member 22 and an inner member 25 fixed to one end of the driven shaft 24 and housed in the hole of the outer cup 22 are basically configured.

On the inner peripheral surface of the outer cup 22, three track grooves 26a to 26c are formed which extend along the axial direction and are spaced 120 degrees around the axial center. Each of the track grooves 26a to 26c is a roller guide groove (first surface) 30a, 3a formed by a flat surface that is in sliding contact with a roller outer (roller member) 28 described later and faces each other.
0b and a flat surface portion (second surface) 34 formed of a flat surface substantially orthogonal to the roller guide grooves 30a and 30b. The opening of the outer cup 22 is closed by a flexible boot (not shown).

A spider 36 is fitted onto the driven shaft 24,
The track groove 2 is formed on the outer peripheral surface of the spider 36.
The three spider shafts 38a to 38c are integrally formed with each other at intervals of 120 degrees around the bulging shafts 6a to 26c. Each of the spider shafts 38a to 38c has a substantially columnar shape and is formed to bulge in a direction substantially orthogonal to the axis of the driven shaft 24. The components attached to each of the spider shafts 38a to 38c have the same shape and have the same reference numerals, and one of them will be referred to as the spider shaft 38 hereinafter.
A description will be given based on a.

A row liner 40 having a curved outer peripheral surface is externally fitted to the spider shaft 38a, and a holder 42 having a concave portion corresponding to the curved surface is externally fitted to the row liner 40. In this case, the row liner 40
Is formed so as to be slidable along the axial direction of the spider shaft 38a.
The holder 42 is formed so as to be tiltable at a predetermined angle via a curved surface that contacts the holder 42.

The roller outer 28 is fitted onto the outer peripheral portion of the holder 42 via a plurality of needle bearings 44. The needle bearing 44 includes a ring-shaped washer 46 and a circlip 4 mounted on the holder 42.
Held by 8. The roller outer 28 and the holder 42 are formed in a non-contact state with a needle bearing 44 interposed. In addition, the top 50 of the roller outer 28
Is formed so as to project from the top portion 52 of the holder toward the plane portion 34 side of the track groove 26a by a predetermined length.

The roller outer 28 is formed in a substantially cylindrical shape having a flat outer peripheral surface corresponding to the rolling roller guide grooves 30a and 30b, and the top 50 of the roller outer 28 contacts the flat surface 34 of the track groove 26a. Is formed. The top portion 50 of the roller outer 28 and the flat surface portion 3
A predetermined clearance (not shown) may be defined between the first and second parts.

On the inner wall surface of the outer cup 22 adjacent to the roller guide grooves 30a and 30b, a set of ridges 54a projecting toward the spider shaft 38a and extending along the axial direction of the track groove 26a. , 54b are formed. In this case, the bottom surface of the roller outer 28 is held by the protrusions 54a and 54b, so that the roller outer 28 rolls and displaces only along the axial direction of the track groove 26a, and the axial direction of the spider shaft 38a (see FIG. 1
Displacement in the vertical direction) is prevented. Therefore, the protrusions 54a and 54b function as stoppers when the roller outer 28 is inclined.

The constant velocity joint 20 according to the first embodiment of the present invention is basically constructed as described above. Next, its operation and action and effect will be explained. When a drive shaft (not shown) rotates, its rotational force is transmitted to the inner member 25 via the outer cup 22, and the driven shaft 24 rotates via the spider shaft 38a. That is, the rotational force of the outer cup 22 is
The driven shaft 2 that is sequentially transmitted to the spider shafts 38a to 38c via the needle bearing 44, the holder 42 and the row liner 40 and engages with the spider shafts 38a to 38c.
4 rotates in a predetermined direction.

In this case, when the drive shaft or the driven shaft 24 is tilted, the roller outer 28 causes the track grooves 26a-26.
Roll along the axial direction of c. Therefore, the rotation speed of the drive shaft is always transmitted to the driven shaft 24 at a constant rotation speed without being influenced by the inclination angle of the driven shaft 24 with respect to the outer cup 22. Here, when the roller outer 28 is tilted at a predetermined angle from the track grooves 26a to 26c, the roller outer 28 is held by the protrusions 54a and 54b, and along the axial direction of the track grooves 26a to 26c, the roller guide grooves 30a and 30b. And the top portion 50 of the roller outer 28 is displaced by the track grooves 26a-2.
Since it is in sliding contact with the flat portion 34 of 6c, the spider shaft 38
Sliding displacements along the axial direction of a to 38c are prevented.

Therefore, even if the roller outer 28 is tilted, the holder 42 does not come into contact with the flat portions 34 of the track grooves 26a to 26c, so that sliding friction is not generated and the plunge performance is prevented from being impaired. It In addition,
Plunge performance means that the roller outer 28 is guided by the track grooves 26a to 26c under the guiding action of the roller guide grooves 30a and 30b.
The reciprocating motion is smooth along the axial direction of.

Further, since the rolling displacement direction of the roller outer 28 is limited to the axial direction of the track grooves 26a to 26c, the top clearance and the radial clearance of the roller outer 28 with respect to the track grooves 26a to 26c can be easily controlled. It will be possible. Furthermore, even if the operating angle of the driven shaft 24 is large, the outer cup 2
Only the roller outer 28 is in contact with 2 and the holder 42 is not in contact with 2, and the vibration is blocked by the needle bearing 44 interposed between the holder 42 and the roller outer 28.
It is possible to prevent the vibration from being transmitted to the 8a to 38c sides. As a result, good vibration isolation characteristics can be obtained.

Furthermore, as compared with the constant velocity joint 1 according to the prior art, in this embodiment, the roller outer 28 is used.
The outer cup 2 is formed while the shape of the
Since the second roller guide grooves 30a and 30b only have to be formed flat, the manufacturing process is simplified and the manufacturing cost can be reduced. Next, FIG. 2 shows a constant velocity joint 60 according to a second embodiment of the present invention. In the following embodiments, substantially the same components as those of the constant velocity joint 20 shown in FIG. 1 are designated by the same reference numerals, and only different points will be described.

In the constant velocity joint 60 according to the present embodiment, an annular step portion 62 for holding the row liner 40 is formed at the root of the spider shafts 38a to 38c, and a circlip 64 fitted in the annular groove is used. The row liner 40 is locked. Further, it is different from the constant velocity joint 20 shown in FIG. 1 in that the inner peripheral surface of the holder 66 that contacts the outer peripheral surface of the curved liner 40 is formed flat.

Next, FIG. 3 shows a constant velocity joint 70 according to a third embodiment of the present invention. In the constant velocity joint 70 according to this embodiment, the spider shafts 72a to 72a are provided without providing the row liner 40 having a curved outer peripheral portion.
The constant velocity joint 60 shown in FIG. 2 is formed in that the outer peripheral surface of 2c is formed as a spherical surface portion 74, and the spherical surface portion 74 is formed so as to make point contact with the inner wall surface of the flat holder 66.
And different.

Since other operational effects are substantially the same as those of the first embodiment, detailed description thereof will be omitted.

[0024]

According to the constant velocity joint of the present invention,
The following effects can be obtained. That is, it is possible to prevent the occurrence of sliding resistance by the holder and improve plunge performance. In addition, the transmission of vibration from one of the transmission shafts to the other transmission shaft is blocked by the needle bearing interposed between the roller member and the holder, and good vibration blocking characteristics can be obtained.

Furthermore, the first and second track grooves are formed.
Since it suffices to form the respective surfaces substantially flat and the outer peripheral surface of the roller member substantially flat, the manufacturing process can be simplified and the manufacturing cost can be reduced.

[Brief description of the drawings]

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

FIG. 2 is a sectional view of a constant velocity joint according to a second embodiment of the present invention in a direction orthogonal to the axial direction.

FIG. 3 is a sectional view of a constant velocity joint according to a third embodiment of the present invention in a direction orthogonal to the axial direction.

FIG. 4 is a cross-sectional view of a constant velocity joint according to the related art devised by the present applicant in a direction orthogonal to the axial direction.

[Explanation of symbols]

20, 60, 70 ... Constant velocity joint 22 ... Outer cup 24 ... Driven shaft 26a-2
6c ... Track groove 28 ... Roller outer 30a, 3
0b ... Roller guide groove 34 ... Plane part 36 ... Spider 38a-38c, 72a-72c ... Spider shaft 40 ... Row liner 42, 66
... Holder 44 ... Needle bearing 50, 52
... Tops 54a, 54b ... Ridges 62 ... Steps

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Ken Chino 19 Tochigi Works, Honda Motor Co., Ltd. Matsuyama-cho, Moka City, Tochigi Prefecture (72) Inventor Atsushi Nagaoka 19 Matsuyama Town, Moka-shi, Tochigi Honda Motor Co., Ltd. Tochigi Works Within

Claims (3)

[Claims] 1. A cylindrical outer member having a plurality of track grooves which are spaced apart from each other by a predetermined distance and extend along the axial direction, and which is connected to one of the conductive shafts. An inner member that has a roller member that displaces and a holder that holds the roller member, and that is inserted into the inner space of the outer member that is open and that is connected to the other conduction shaft; The track groove is formed by a pair of substantially flat first surfaces that are in rolling contact with each other and are opposed to each other, and a second surface that is substantially orthogonal to the first surface, and the roller member is the first 1 has a substantially flat outer peripheral surface corresponding to the first surface, and is held by a ridge portion extending along the axial direction of the track groove and formed on the inner wall surface of the outer member. Constant velocity joint. 2. The constant velocity joint according to claim 1,
The constant velocity joint characterized in that the ridge portion restricts the displacement of the roller member along the axial direction by holding the ridge portion in contact with the bottom surface portion of the roller member. 3. The constant velocity joint according to claim 1 or 2, wherein a needle bearing is interposed between the roller member and the holder, and the roller member and the holder are formed in a non-contact state. Constant velocity joint.