JP3241152B2 - 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 using a sprag for an engaging element.

[0002]

2. Description of the Related Art As a device for transmitting power to an automobile,
A device for transmitting engine torque to wheels using a two-way differential clutch is disclosed in Japanese Patent Laid-Open No. 3-19972.
No. 2 proposes this.

This device, as shown in FIGS. 4 and 5,
The opposing surfaces of the input gear 1 and the rotating shaft 2 penetrating the input gear are formed by coaxial cylindrical surfaces 3 and 4, and the outer retainer 6 is fixed to the cylindrical surface 3 of the input gear 1 by a knock pin 5 and rotated. An inner retainer 7 is rotatably mounted on the outer periphery of the shaft 2 via a bearing 8.

A plurality of pockets 9 and 10 are formed in the outer cage 6 and the inner cage 7 so as to face each other in the radial direction, and both ends of the sprag 11 are inserted into the pockets 9 and 10, respectively. A spring member 12 for holding the sprag 11 in a neutral state is attached to both sides. As shown in FIG. 6, each of the sprags 11 has arcuate surfaces 15, 1 at its both ends.
6 are formed, and when the sprags are tilted in either direction, the cam surfaces 13 and 14 come into contact with both cylindrical surfaces 3 and 4 to connect the input gear 1 and the rotating shaft 2. .

The inner retainer 7 is pressed against a sub-gear 18 by a disc spring 17 and the sub-gear 18 and the input gear 1 are pressed.
Are engaged with a gear (not shown) on the engine side. In this case, the number of teeth of the sub gear 18 is set to be larger than the number of teeth of the input gear 1, and the rotational force of the engine is reduced to the gears 1, 1
8, the inner cage 7 pressed against the sub gear 18 is slightly delayed by the rotation of the input gear 1, and the sprag 11 is moved by the relative rotation of the inner cage 7 and the outer cage 6 as shown in FIG.
And the clutch becomes operable.

When the input gear 1 rotates counterclockwise relative to the rotary shaft 2 from the above-mentioned clutch operable state, the sprags 11 are engaged and the input gear 1 and the rotary shaft 2 are connected.
It becomes the torque load state. When the input gear 1 rotates in the direction opposite to the above, the sprag 11 tilts in the direction opposite to that in FIG.

[0007]

In the above-described two-way differential clutch, when shifting from the clutch operable state to the torque load state, the cylindrical surface 3 of the input gear 1 and the outer diameter side cam surface 13 of the sprag 11 are required. , And the cylindrical surface 4 of the rotating shaft 2 and the inner diameter side cam surface 14 of the sprag 11 make rolling contact with each other without causing slip on their respective contact surfaces.

In this rolling contact, the outer cage 6
Is fixed to the input gear 1 by the knock pin 5, the side surface 9a of the pocket 9 rotates similarly to the rotation of the input gear 1 due to the torque load, and moves to the position indicated by the solid line in FIG. On the other hand, the sprag 11 is tilted by rolling on the cam surface, and the corner 11a of the sprag shows a locus as shown by a solid line from a chain line in FIG.

When the movement trajectories of the pocket 9 and the sprag 11 are overlapped, the corner 11a of the sprag 11 and the pocket side surface 9a of the outer retainer 6 overlap each other as shown in FIG. . However, since the outer retainer 6 is integrally fixed to the input gear 1 with the knock pin 5, the above-described interference acts to hinder the tilting of the sprag 11 during torque load. As a result, the sprags 11 whose inclination is suppressed may cause sliding wear on the cam surfaces 13 and 14, which may adversely affect the load durability of the clutch.

On the other hand, the outer cage 6 is connected to the input gear 1.
When the outer retainer 6 is fixed to the inside by press-fitting, the outer retainer 6 is displaced in the circumferential direction due to the above-described interference, and an effect of relieving the interference to some extent can be expected. Since this does not occur unless a force acts, a sufficient mitigation effect against interference cannot be obtained. Further, there is a problem that it is difficult to set a press-fit or the like in order to cause a displacement required for relaxation with respect to a predetermined interference force.

SUMMARY OF THE INVENTION An object of the present invention is to solve the above-mentioned problem, and it is possible to effectively reduce interference between a sprag and a retainer at the time of torque load, and to suppress occurrence of abrasion on a cam surface. It is intended to provide a dynamic clutch.

[0012]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention forms a coaxial cylindrical surface on each of opposing surfaces of an input gear and a rotary shaft passing through the input gear. A cage fixed to the input gear and a cage rotatably supported are provided between them, and a plurality of pockets are formed in each of the cages in the radial direction. A sprag that engages between the two cylindrical surfaces by the relative rotation of the input gear and the rotating shaft in two directions is incorporated .
A spring member for holding the sprag in a neutral state on the reversing side retainer
In the attached two-way differential clutch, elastically deformable sprag receivers are formed on both sides of the pocket of the fixed-side cage.

[0013]

In the above structure, the rotary holder is attached to the rotating side retainer.
Girder spring member and sprag receptacle in pocket of fixed side cage
The two elastic members maintain the position of the sprag, and if interference occurs between the sprag and the retainer during torque load, the sprag receiver is elastically deformed to reduce the interference.

[0014]

FIG. 1 shows a two-way differential clutch according to an embodiment. The basic structure of the clutch of this embodiment is the same as that of the conventional structure shown in FIGS. 5 and 6, and the same parts are denoted by the same reference numerals and description thereof will be omitted. Will be described.

In FIG. 1, reference numeral 21 denotes an outer retainer fixed to the cylindrical surface 3 on the inner diameter side of the input gear 1. The outer retainer 21 faces the inner retainer 7 having the same structure as the conventional one. Provided.

As shown in FIGS. 1 and 2, the outer retainer 21 is formed of a band-shaped spring plate 22 having a length surrounding the cylindrical surface 3. The spring plate 22 is formed by punching a press. A plurality of pockets 23 at predetermined intervals in the length direction
Are formed. Each pocket 23 is provided corresponding to each pocket 10 of the inner retainer 7.

On both sides of each pocket 23, spring pieces 24, 24 are punched integrally by press working, and after each spring piece rises to the inner diameter side, it is bent in a U shape to receive sprags. 25 and 26 are formed. On the opposing surfaces of the sprag receivers 25 and 26, contact surfaces 27 and 28 that contact the sprags are formed.

As shown in FIG. 1, the outer retainer 21 is wound around the cylindrical surface 3 of the input gear 1 in a state where both ends of the band-shaped spring plate 22 are overlapped with each other. And is fixed to the input gear 1.

When a speed difference occurs between the outer cage 21 and the inner cage 7 from the standing state of the sprags, the sprags 11 are tilted by the spring force of the spring member 12, and the clutch can be operated as shown by a chain line in FIG. When the input gear 1 rotates relative to the rotating shaft 2 in the direction of the arrow from this state, the sprag 11 further tilts as shown by the solid line in FIG.

In this case, if the sprag receiver 25 of the outer retainer 21 tries to interfere with the corner 11a of the sprag 11, the sprag receiver 25 deflects and escapes in the circumferential direction to reduce the interference. For this reason, the cam surfaces 13, 1,
No excessive twisting or slippage occurs in 4, and the occurrence of wear is suppressed.

In the structure of the above embodiment, the outer retainer 21 is formed of a band-shaped spring plate, and the pockets and sprag receivers can be integrally formed by punching and bending of a press. Compared to the case where the cage is formed by machining from the ring, it can be formed at a lower manufacturing cost. Further, since the outer retainer 21 is formed of a thin spring plate, the space volume for retaining the lubricating oil inside the clutch can be increased, so that the lubricating performance can be improved.

In the above example, the outer retainer 21
The sprag receivers 25 and 26 may be formed by rolling a spring piece into a circular shape, and may have any shape as long as it can be elastically deformed by interference with the sprag 11.

[0023]

As described above, according to the present invention, the fixed-side cage is provided with the sprag receiver which is elastically deformed to reduce the interference between the cage and the sprag when the torque is applied. , And the load durability performance of the clutch can be improved.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a two-way differential clutch according to an embodiment.

FIG. 2 is a perspective view showing the outer retainer according to the first embodiment;

FIG. 3 is a sectional view showing an operation state of the sprag according to the first embodiment;

FIG. 4 is a sectional view showing a power transmission device using a two-way differential clutch.

FIG. 5 is a view showing a longitudinal section of the clutch according to the first embodiment;

FIG. 6 is a diagram showing an operable state of a conventional clutch.

FIG. 7 is a sectional view showing a torque load state according to the first embodiment;

FIG. 8 is an enlarged view showing an interference part according to the embodiment.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 input gear 2 rotating shaft 3, 4 cylindrical surface 7 inner retainer 10 pocket 11 sprag 12 spring member 13, 14 cam surface 21 outer retainer 22 spring plate 23 pocket 24 spring piece 25, 26 sprag receiver 27, 28 contact surface 29 pin

Continuation of the front page (72) Inventor Koji Sato 2-10-10 Imanoura, Iwata-shi 7 (72) Inventor Masahiro Kawai 548, Toyonishicho, Hamamatsu-shi (56) References JP-A-4-366036 (JP, A) Kaihei 2-145328 (JP, U) (58) Fields investigated (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 input gear and a rotating shaft penetrating the input gear, and a retainer fixed to the input gear is provided between the cylindrical surfaces. And a plurality of pockets radially opposed to each other are formed in each of the cages, and each of the pockets is formed in each of the pockets by the relative rotation of the input gear and the rotating shaft in two directions. incorporate sprags which engage between, the rotation
The side retainer has a spring member that holds the sprags in a neutral state.
The two-way differential clutch according to claim 1, wherein sprag receivers that can be elastically deformed are formed on both side surfaces of the pocket of the fixed retainer.