JPH0781599B2 - 2-way differential clutch - Google Patents

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a two-way differential clutch that enables transmission or interruption of rotation in both left and right directions on an input side.

(Prior Art) In a part-time four-wheel drive vehicle (hereinafter also referred to as a 4WD vehicle), a differential clutch that automatically transmits driving force to the front wheels at the moment when the rear wheels slip and the speed decreases Running clutches have come into use.

In such a differential clutch, the front wheel hub is set to rotate faster than the drive shaft, and rotation of the drive shaft is not transmitted to the front wheel hub during two-wheel drive. When the rear wheels slip and the rotation of the drive shaft increases, the wedge action of the rollers or balls inserted in the gap between the drive shaft and the front wheel hub causes the drive shaft and the front wheel hub to mesh, and the rotation is transmitted to the front wheel hub. It

However, in order to cause a wedge action in this differential clutch, a saw-shaped cam is provided on the surface of the drive shaft,
Since it operates only in one direction of rotation, there is a problem that the front wheels cannot be driven when moving backward. Further, even in the differential clutch using the sprags instead of the rollers or the balls, the action of the sprags is limited to one direction, and the above problems are involved.

(Problems to be Solved by the Invention) The present invention has been made in view of such conventional problems, and is a two-way differential clutch that enables transmission or interruption of rotation in both left and right directions on the input side. For the purpose of providing.

(Means for Solving the Problems) The present invention has been devised in view of the above-mentioned problems of the related art, and relatively rotates the input gear side cylindrical surface and the output gear side cylindrical surface with a gap. In a two-way differential clutch that is movably arranged and has a plurality of sprags interposed in the gap, the sprags include a pocket of a first holding member fixed to a cylindrical surface on the input gear side, The input gear side cylindrical surface and the output gear side cylindrical surface are housed in a pocket of a second holding member which is arranged so as to be slidable in the circumferential direction adjacent to the output gear side cylindrical surface. Is disposed so as to be tiltable from a neutral position where it is not engaged with a clutch operating position where it engages with both of the cylindrical surfaces, and the second holding member generates a differential speed corresponding to the rotation of the input gear. With sub gear It is mobile, the second holding member slides in the circumferential direction by the difference speed, is that constituted so as to tilt the sprags to a clutch actuating position.

(Function) If the number of teeth of the sub gear is greater than the number of teeth of the input gear, the same rotation input causes the sub gear to rotate later than the input gear, causing a differential speed between both gears, and this differential speed causes the input gear to rotate counterclockwise. In either case of right or left rotation, the rotation of the input gear to the left and right can be transmitted to or blocked from the output gear because the sprag can be tilted to bring the output shaft into mesh with the rotation shaft. You can

Embodiment An embodiment of the present invention will be described below with reference to the drawings.

FIG. 1 is a longitudinal sectional view of the two-way differential clutch of the first embodiment, FIG. 2 is a sectional view taken along the line AA of FIG. 1, and FIGS. FIG. 5 and FIG. 6 show enlarged views of essential parts.

In FIG. 1, reference numeral 1 denotes a rotary shaft, which has various stepped portions on its outer peripheral surface. Reference numeral 2 is an input gear, which is connected to one step portion of the rotary shaft 1 by a spline 2a. Reference numeral 2b is a tooth formed on the outer periphery of the input gear 2 and meshes with a gear on the drive shaft side (not shown). Reference numeral 17 denotes an outer peripheral cylindrical surface, which is formed in parallel with the input gear 2 at another step portion on the outer periphery of the rotary shaft 1. An output gear 4 has an inner peripheral cylindrical surface 18 and is externally fitted to the outer peripheral cylindrical surface 17 with a gap. 4a is a tooth provided on the outer periphery of the output gear 4,
It meshes with a gear on the driven shaft side (not shown).

As seen in the enlarged view of the main part of FIG. 6, between the inner peripheral cylindrical surface 18 of the output gear 4 and the outer peripheral cylindrical surface 17 of the rotary shaft 1,
A plurality of sprags 6 are arranged at predetermined intervals in the circumferential direction.

The outer diameter side arcuate surface 6a and the inner diameter side arcuate surface 6b of the sprag 6 are arcuate surfaces of radius value r, and are the inner peripheral cylindrical surface 18 of the output gear 4.
Is set to be larger than 1/2 of the interval δ between the outer peripheral cylindrical surface 17 of the rotary shaft 1. The length l in the direction connecting the centers of the radius values r of the arcuate surfaces 6a, 6b is slightly smaller than the interval δ. Therefore, in the neutral state in which the sprag 6 stands between the opposing cylindrical surfaces 17 and 18, the arc surfaces 6a and 6a of the sprag 6 are formed.
A radial skimmer is formed between b and the cylindrical surfaces 17 and 18.
Further, when tilted in the circumferential direction of the cylindrical surfaces 17, 18 from the neutral state, the cylindrical surface 17, 1 where the outer diameter side arc surface 6a and the inner diameter side arc surface 6b face each other.
Engage against 8.

The inner diameter side end portions 6c, 6f of the sprag 6 are fitted into the pocket 10a of the inner holding member 10 fixed to the outer peripheral cylindrical surface 17 of the rotary shaft 1 by a method such as press fitting, and the outer diameter side end portions 6d, 6e are The outer holding member 9 is slidably inserted into the pocket 9a of the outer holding member 9 between the inner holding member 10 and the output gear 4. The dimension A between the side surfaces of the outer holding member 9 facing each other in the circumferential direction of the pocket 9a is larger than the dimension B of the inner holding member 10 between the side surfaces facing each other in the circumferential direction. Also, the pocket in the outer holding member 9
A recess 9b is formed in the center of the side surfaces of the 9a that face each other in the circumferential direction, and the pair of elastic bodies 7 incorporated in the recess 9b press the outer diameter side ends 6d, 6e of the sprag 6 from both sides. As shown in FIG. 6, the sprag 6 is held in a neutral state. Here, a leaf spring, a coil spring, or the like can be used as the elastic body 7. In this embodiment, as shown in FIG.
Although an example in which a metallic leaf spring is attached as the elastic body 7 from the outer diameter portion 9c of the outer holding member 9 is shown, the outer holding member 9 may be attached from the inner diameter portion 9d.

Returning to FIG. 1, reference numeral 8 denotes a sub gear, which is the input gear 2
Is inserted between the output gear 4 and the output gear 4. Reference numeral 8a is a tooth provided on the outer periphery of the sub gear 8 and meshes with a gear (not shown) on the drive shaft side like the input gear 2. An outer holding member 9 is slidably inserted into the outer circumference of the rotary shaft 1 on the inner circumference side of the sub gear 8. The sub gear 8 is pressed by a disc spring 19 between the retaining ring 20 attached to the outer holding member 9 and the side surface of the step portion of the outer holding member 9. The inner peripheral side of the outer holding member 9 is partially notched to provide a notch 11, while
The rotary shaft 1 is provided with a stopper 1a at a position facing the cutout 11. 12, 14 are bearings that support the rotary shaft 1, and 13 and 15 are bearings that support the output gear 4.

The operation of the two-way differential clutch configured as described above will be described.

This two-way differential clutch is, for example, a part-time type 4WD
When provided in a vehicle power transmission device, the rotation on the drive shaft side is transmitted to the input gear 2 and the sub gear 8 meshing with the rotation. However, while the teeth 2b of the input gear 2 have, for example, 53 teeth, the teeth 8a of the sub gear 8 are set to have, for example, 54 teeth, and the rotation of the same drive shaft causes the rotation of the sub gear 8 to be input. It will be later than the rotation of the gear 2. Therefore, as shown in FIG. 4, the outer holding member 9 pressed against the sub gear 8 has a differential speed with respect to the rotation of the rotary shaft 1 and the left side surface of the notch 11 of the outer holding member 9 is It rotates relative to the right until it contacts the stopper 1a. Then, the sprags 6 housed in the pockets 9 a of the outer holding member 9 fall in the rotation direction of the outer holding member 9. Therefore, as shown in FIG. 4, the cylindrical surfaces 17, 18 of the sprag 6 on which the outer diameter side arc surface 6a and the inner diameter side arc surface 6b face each other.
To engage the clutch in the direction of the arrow.

Here, when the 4WD is in the two-wheel drive state, the output gear 4 is set to rotate faster than the input gear 2, that is, the rotation shaft 1, so the sprag 6
Receives a frictional force in the standing direction, spins, and does not get caught in the cylindrical surfaces 17 and 18. On the other hand, if there is slip on the rear wheels, the rotational speed of the drive shaft will increase, so the input gear 2,
That is, the rotation of the rotary shaft 1 becomes faster than the rotation of the output gear 4, the clutch in the arrow direction operates, and the rotational force of the rotary shaft 1 is transmitted to the output gear 4. After the stopper 1a comes into contact with the wall surface of the notch 11, the outer holding member 9 idles with respect to the sub gear 8, so that the sub gear 8 is not damaged.

As described above, the clutch operating principle of the sprag 6 due to the differential speed of the sub gear 8 is not related to the direction of rotation of the input gear 2, and thus even when the part-time four-wheel drive vehicle is in reverse, this two-way differential clutch It works effectively.

FIG. 7 shows a second embodiment of the present invention, in which the bear links 13 and 15 for supporting the output gear 4 are replaced with bearings 13 '.

(Effect of the Invention) In the two-way differential clutch of the present invention, a cylindrical surface on the input gear side and a cylindrical surface on the output gear side are arranged so as to be relatively rotatable with a gap, and a plurality of sprags are provided in the gap. In the two-way differential clutch, the sprag includes a pocket of the first holding member fixed to the cylindrical surface on the input gear side and a circle adjacent to the cylindrical surface on the output gear side. From the neutral position, which is housed in the pocket of the second holding member that is slidably arranged in the circumferential direction and does not engage with the cylindrical surface on the input gear side and the cylindrical surface on the output gear side, both cylindrical surfaces The second holding member is arranged so as to be tiltable over a clutch differential position that engages with, and the second holding member is associated with a sub gear that generates a differential speed in response to rotation of the input gear, and the second differential member causes 2nd holding part Since the material slides in the circumferential direction and the sprag can be tilted to the clutch operating position, the rotation of the input gear is transmitted to the output gear regardless of whether the input gear rotates leftward or rightward. Or can be blocked.

[Brief description of drawings]

FIG. 1 is a longitudinal sectional view of a first embodiment of the present invention, FIG. 2 is a sectional view taken along the line AA of FIG. 1, FIGS. 3 and 4 are operational explanatory views, and FIGS. Is an enlarged view of a main part, and FIG. 7 is a longitudinal sectional view of the second embodiment. 1 ... Rotary shaft, 2 ... Input gear, 4 ... Output gear, 6 ... Sprag, 7 ... Elastic body, 8 ... Sub gear, 9 ... Outer holding member, 10 ... Inner holding member, 17 Outer peripheral cylinder Surface, 18 …… Inner cylindrical surface

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Hiromi Nojiri 1019-68 Akigashima, Iwata-shi, Shizuoka

Claims (1)

[Claims] 1. A two-way differential in which a cylindrical surface on the input gear side and a cylindrical surface on the output gear side are disposed so as to be relatively rotatable with a gap therebetween, and a plurality of sprags are interposed in the gap. In the clutch, the sprag includes a pocket of a first holding member fixed to the cylindrical surface on the input gear side,
A cylindrical surface on the input gear side and a cylinder on the output gear side, which are housed in a pocket of a second holding member which is disposed so as to be slidable in the circumferential direction adjacent to the cylindrical surface on the output gear side. The second holding member is arranged so as to be tiltable from a neutral position where it does not engage with the surface to a clutch operating position where it engages with both of the cylindrical surfaces, and the second holding member provides a differential speed corresponding to the rotation of the input gear. A two-way differential clutch, characterized in that, in cooperation with a sub gear that is generated, the second holding member slides in the circumferential direction due to the differential speed, and the sprag can be tilted to a clutch operating position.