JP3354982B2 - Two-way differential clutch - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a two-way differential clutch in which a sprag is engaged by relative rotation of an inner member and an outer member in two directions. The present invention relates to a structure that prevents assembly errors.

[0002]

2. Description of the Related Art As shown in FIG. 4, a two-way differential clutch using a sprag for an engaging element has a coaxial cylindrical surface 3, 4 in which opposing surfaces of an inner member 1 and an outer member 2 which are fitted to each other. , And a plurality of sprags 7 are held by inner and outer retainers 5 and 6 having different diameters, which are incorporated between the cylindrical surfaces 3 and 4.

The inner and outer cages 5 and 6 have an outer cage 6 fixed to a cylindrical surface 4 of an outer member 2 and an inner cage 5 rotatable with respect to the cylindrical surface 3 of the inner member 1. Both ends of the sprag 7 are inserted into pockets 8, 9 which are supported and are provided radially opposite to the inner and outer retainers 5, 6.

In the pocket 8 of the retainer 5 on the rotating side,
Attach spring members 10 to be in contact with both side surfaces of sprags 7,
The sprag 7 is held in a neutral state by the elastic force.

In the clutch having the above-described structure, when the outer member 2 is relatively rotated with respect to the inner member 1 in a direction indicated by an arrow in a state in which the sprag 7 is inclined and stands by at the operating position as shown in FIG. The cam surfaces 11 and 12 of the portions engage with the cylindrical surfaces 3 and 4, and the torque of the outer member 2 is transmitted to the inner member 1 via the sprags 7. Conversely, when the rotation speed of the inner member 1 becomes faster than that of the outer member 2, the sprag 8 overruns on the cylindrical surface 3, and the outer member 2 idles.

On the other hand, when the outer member 2 rotates in the direction opposite to the above, the sprags 7 are inclined in the direction opposite to that of FIG. The same clutch operation as that described above is performed.

[0007] In the above-mentioned clutch, in order for the sprag 7 to engage with the two cylindrical surfaces 3 and 4 to transmit torque reliably,
In the engaged state as shown in FIG. 5, a line A connecting the contact points a and b at both ends of the sprag 7 is inclined with respect to a line B extending from the center of rotation O and passing through one contact point a, and is fixed. Wedge angle α
Need to be formed.

For this reason, in the conventional sprag 7, as shown in FIG. 6, the cam surfaces 11 and 12 at both ends are formed by arc surfaces 15 and 16 having different centers of curvature, respectively. The curvature radii R ₃ , R ₄ and their center positions are different from each other, so that the cylindrical surfaces 3, 4 and the arc surface 15,
A predetermined wedge angle α is formed at the time of contact with the reference numeral 16. Also, a sprag 7 to be inserted into each of the pockets 8 and 9 is provided.
Of the width t _1, t ₂ of the both end portions are formed primarily from the top of the quality control in the same dimension t ₁ = t _2.

[0009]

However, in the conventional sprag 7 having the same width at both ends as described above,
Arc surfaces 15, 16 forming cam surfaces 11, 12 at both ends
Although the radius of curvature is different, the difference is small,
Since both ends are substantially symmetrical, and it is difficult to easily distinguish the difference in the shape of the two ends, each retainer 5,
When the sprags 7 are inserted into the pockets 8 and 9 of the cartridge 6, there is a possibility that the ends of the sprags 7 are assembled in the wrong direction.

However, if the sprags 7 are assembled in a wrong direction, not only the set transmission torque cannot be obtained but also the durability of the clutch is adversely affected. For example,
If the wedge angle of one sprag becomes smaller than that of the other sprag due to an erroneous assembly, the sprag may cause abnormal wear and shorten the life of the clutch.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems, and it is an object of the present invention to provide a structure capable of reliably preventing an error in assembling a sprag by modifying the shape of the sprag.

[0012]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention is to change the width of the sprags at both ends in the circumferential direction from each other, and to insert these both ends.
The circumferential width of each cage pocket
The width of the sprag is made different depending on the width of the end, and the width of the end of the sprag on the larger side is set larger than the width of the smaller side of the pocket .

[0013]

In the above structure, the sprag is inserted into the pocket of the other retainer for holding the sprag, and if the sprag is set so as to be properly assembled in the inserted state, the sprag of the sprag is set. Even when assembling with both ends reversed, the sprags are wider than the pocket width of one of the retainers, so that they cannot interfere with each other to assemble, thereby preventing errors.

[0014]

FIG. 1 shows a two-way differential clutch according to an embodiment.
FIG. 2 shows a cross-sectional shape of a sprag used in the two-way differential clutch.

The basic structure of the clutch of this embodiment is the same as that of the conventional structure shown in FIG. 4, and the same parts are denoted by the same reference numerals and description thereof will be omitted. Will be described.

As shown in FIGS. 1 and 2, the sprags 7 inserted into the pockets 8, 9 of the inner and outer retainers 5, 6 have a width t ₁ at the inner end and a width t at the outer end. It is formed larger than ₂ (t ₁ > t ₂ ).

The width t ₃ of the pocket 8 of the inner retainer 5 is larger than the width t ₁ of the inner end of the sprag 7 (t ₃ > t ₁ ), and the pocket 9 of the outer retainer 6 is formed.
Width t ₄ of greater than the width t ₂ of the outer ends of the sprag 7 (t _4> t ₂₎ are formed.

Further, the width t ₁ of the inner end, which is the larger side of the sprag 7, is formed larger than the width t ₄ of the pocket 9 of the outer retainer 6 (t ₁ > t ₄ ). That is, the above width dimensions are set so as to have a relationship of t ₃ > t ₁ > t ₄ > t ₂ .

In the above structure, when the sprags 7 are assembled in the inner and outer retainers 5 and 6 in the orientation shown in FIG. 1, both ends of the sprags 7 are inserted into the respective pockets 8 and 9 to assemble them securely. Can be.

On the other hand, if the sprags 7 are to be assembled with their both ends upside down as shown in FIG. 1, the inner ends of the sprags 7 will interfere with the pockets 8 of the outer retainer 6, and the sprags will be inserted. I can't. For this reason, an error in the assembling direction becomes apparent, and it is possible to start over in the correct assembling direction.

Incidentally, contrary to the example shown in FIG.
Even if the width dimension of the outer end portion is set larger than the inner end portion and larger than the pocket width of the inner retainer 5, the same effect as described above can be obtained. For example, in the above structure, t ₂ > t ₁ , t ₂ > t _3, and t ₄ > t ₂ > t ₃ >
Setting the respective widths so that t _1, can only be incorporated only in the same direction the sprag can be prevented errors of assembly.

In the structure shown in FIG. 1, since the width of the inner end of the sprag 7 is widened, the cam surface 11 on the inner diameter side can be formed with a plurality of radii of curvature. In this case, as shown in FIG. 2, both sides of the cam surface 11 are formed by arc surfaces (curvature radii R ₁ ) 13, 13 in which the wedge angles increase sharply. When formed with the arc surface 14 (curvature radius R ₂ ) in which the wedge angle gradually increases, the following operation is obtained. That is, when torque is applied from the clutch operable state, the arcuate surface 14 is
When the excessive torque is applied, the sprags tilt, and when the arc surface 13 tries to contact the cylinder surface 3, the wedge angle of the arc surface 13 suddenly increases. As a result, slippage occurs at the contact portion without biting into the cylindrical surface 3, and it is possible to prevent the occurrence of indentations due to biting and a sprag breakage accident. That is, by increasing the width of the end of the sprag, the degree of freedom for ensuring the limiter function can be increased.

On the other hand, FIG. 3 shows a power transmission device for transmitting the engine power of an automobile to each wheel using the two-way differential clutch of the above embodiment.

In this rotation transmission device, an input gear 22 as an outer member is rotatably supported via bearings 23 and 24 on the outer side of a rotation shaft 21 as an inner member. A plurality of sprags 27 are incorporated between the cylindrical surface 25 and the cylindrical surface 26 having the inner diameter of the input gear 22.

An outer retainer 28 is fixed to the input gear 22. An inner retainer 29 is rotatably provided on the outer diameter of the rotating shaft 21 via a bearing 26.
Is pressed against the sub gear 31 via the disc spring 30.
Also, the stopper pin 32 fixed to the inner retainer 29 is
A pin hole 33 provided in the outer retainer 28 is fitted with a gap in the circumferential direction.

The input gear 22 and the sub gear 31
Is meshed with a gear (not shown) on the engine side, and the rotation of the engine is input to both gears 22 and 31. In this case, the number of teeth of the sub gear 31
And the rotation of the sub gear 31 is slightly delayed from the rotation of the input gear 22 when the torque of the engine is transmitted.

In the above structure, the two gears 2 are driven by the engine.
When the gears 2 and 31 are turned, the inner cage 29 pressed against the sub gear 31 generates a differential speed with respect to the rotation of the input gear 22, and the inner cage 29 and the outer cage 22 are connected to the stopper pin 32 and the pin 32. The sprags 27 are relatively rotated until the holes 33 come into contact with each other, and each sprag 27 is tilted to be in a standby state.

In the above-described rotation transmission device, when the input gear 22 rotates forward or backward, the sprag 27 is engaged only when the rotation of the input gear 22 becomes faster than the rotation shaft 21, and the input gear 22 is rotated. The rotation can be transmitted to the rotation shaft 21. In this case, if the clutch of the above-described embodiment is used for the two-way differential clutch that performs the above-described operation, the assembly error of the sprag 27 is eliminated, and the clutch can be assembled accurately. Can be formed.

[0029]

As described above, according to the present invention, the sprags interfere with the widths of the pockets of the retainer so that the sprags can be mounted only in a fixed direction, so that there is no mistake in assembling the sprags and stable quality. This has the effect that the clutch can be provided with a function that satisfies the transmission torque as designed.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a clutch according to an embodiment.

FIG. 2 is an enlarged view showing the sprag according to the first embodiment;

FIG. 3 is a sectional view showing a rotation transmission device.

FIG. 4 is a sectional view showing a conventional two-way differential clutch.

FIG. 5 is a sectional view showing a standby state of the sprag according to the first embodiment;

FIG. 6 is an enlarged view of a conventional sprag.

[Explanation of symbols]

 Reference Signs List 1 inner member 2 outer member 3, 4 cylindrical surface 5 inner retainer 6 outer retainer 7 sprag 8, 9 pocket 11, 12 cam surface

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int.Cl. ⁷ , DB name) F16D 41/00-41/36

Claims (1)

(57) [Claims] 1. A coaxial cylindrical surface is formed on each of opposing surfaces of an inner member and an outer member which are rotatably fitted to each other. Form radially opposed pockets, with cams at each end in each pocket
Surface with a substantially symmetrical shape at both ends.
Both ends of the lug are inserted, and the cam surfaces at both ends are engaged with both cylindrical surfaces by the relative rotation of the inner member and the outer member in two directions.
In the two- way differential clutch, the circumferential widths at both ends of the sprags are made different from each other, and the circumferential widths of the pockets of the cages into which these ends are inserted are also the same as those at both ends of the sprags. A two-way differential clutch, wherein the width is made different according to the width, and the width of the large end of the sprag is set larger than the width of the small side of the pocket.