JPH0629616B2 - Clutch device - Google Patents

Description

Description: TECHNICAL FIELD OF THE INVENTION The present invention relates to a clutch device used for two-wheel / four-wheel switching of a four-wheel drive vehicle.

[Technical Background and Problems] As a conventional clutch device of this type, for example, one described in Automotive Engineering, January 1981, page 72 (Railway Japan Co., Ltd., issued January 1, 1981). There is something.
This shows a transfer device, where spline parts are formed on both the input shaft side and the chain wheel as a rotating body on the output side, and a two-wheel / four-wheel switching sleeve is used to connect and disconnect them. Thus, the power transmission from the input shaft to the rotating body is interrupted. Therefore, in order to synchronize the input side and the rotating body side at the time of switching connection during traveling, a synchronizing mechanism is required.

However, as this type of device, an inertia lock type synchronizing mechanism which is generally used in a transmission has been applied, but as a part to be synchronized with, for example, a two-wheel / four-wheel switching of a four-wheel drive vehicle. , The differential device has a large number of propeller shafts and axle shafts, so the synchro capacity is not sufficient and there is a risk of burning.

[Object of the Invention] The present invention was devised in view of the above problems, and an object of the present invention is to provide a clutch device capable of smooth engagement during rotation without the need for a synchronizing mechanism.

[Configuration of the Invention] In order to achieve the above object, according to the present invention, a front or rear wheel connected input shaft that receives a rotational force from a drive device, and a thrust direction position of which is rotatably supported by the input shaft. The operation member can be moved from a predetermined position in the thrust direction where it is rotatable to the output shaft of the rear or front wheel connection and the input shaft and is held by the operation member to the thrust direction rotary member side by the operation member. Clutch ring, a cam ring that is movable in the thrust direction with respect to the input shaft and cannot rotate, and a clutch ring that is formed on the facing surface of the rotating body and the clutch ring moves in the thrust direction to the rotating body side to frictionally fasten both. The clutch ring is formed on the opposing surfaces of the clutch ring and the cam ring, and the clutch ring is moved toward the rotor in the thrust direction by the relative displacement between the two. Cam means composed of a concave portion and a protrusion that increases the servo at least when moved and shifts by a predetermined amount or more;
The urging means is formed between the cam ring and the input shaft side and urges and urges the cam ring to the thrust direction cam means side with the clutch ring in the predetermined position.

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

FIG. 1 shows a two-wheel / four-wheel switching portion of a transfer device used for a four-wheel drive vehicle. The input shaft 1 is rotatably supported by a transfer case (not shown) via a bearing 3, and is configured to receive a rotational force from the engine side as a drive device (not shown). This input shaft 1
A chain wheel 5 as a rotating body on the output side is rotatably supported by. The position of the chain wheel 5 on the thrust direction side is regulated by the stepped portion 1 a of the input shaft 1 and the circlip 7. A chain (not shown) is wound around the chain wheel 5 so that power can be transmitted to the front wheels.

On the other hand, on one side of the chain wheel 5 in the thrust direction, a clutch ring 9 is disposed at a predetermined position in the thrust direction and rotatably supported by the input shaft 1 in a state where the clutch is not engaged. A peripheral groove 9a is formed on the outer peripheral portion of the clutch ring 9, and a fork (not shown) is engaged therewith, and the fork can be operated from the predetermined position to the chain wheel 5 side by an operation lever. Therefore, the clutch ring 9 is configured to be movable in the thrust direction.

Clutch means 1 is provided between the chain wheel 5 and the clutch ring 9 for frictionally engaging them by moving the clutch link 9 toward the chain wheel 5 in the thrust direction.
1 is provided. The clutch means 11 includes an outer cone surface 11a provided on the surface of the clutch ring 9 facing the chain wheel 5 such that the tip side has a small diameter, and the outer cone surface 11a of the chain wheel 5 facing the clutch ring 9, The cone 11b and the inner cone surface 11b provided so as to correspond to each other.

Further, a cam ring 13 which is fitted to the input shaft 1 via a spline means 12 and is movable in the thrust direction and which cannot rotate with respect to the input shaft 1 is fitted. Cam means 15 is provided between the clutch ring 9 and the cam ring 13. This cam means 15 is the clutch ring 9
A plurality of cam recesses 15a are provided on the side surface in the circumferential direction and are recessed in the thrust direction, and a plurality of cam projections 15b formed on the cam ring 13 and fitted in the cam recesses 15a. Therefore, when the cam ring 13 is substantially integrated with the input shaft 1 side, the cam means 15 causes the clutch ring 9 to move due to the relative displacement between the clutch ring 9 and the cam ring 13.
Is configured to be moved to the chain wheel 5 side in the thrust direction. Also, the cam recess 15a and the cam protrusion 1
5b is composed of a curved surface, and the curvature of the former is formed larger than that of the latter. Therefore, the pressure angle θ of the cam means 15 is configured to be gradually reduced due to the relative displacement between the clutch ring 9 and the cam ring 13 in the rotation direction.

The cam ring 13 and the bearing 3 as the input shaft 1 side
A gap 17 is provided between the inner race and the inner race to allow the cam ring 13 to retract toward the bearing 3 side. Within this gap 17, the cam ring 13 and the bearing 3
Leaf spring 19 as a biasing means between the inner race and
Is installed. Therefore, the leaf spring 19 is the cam ring 1
3 is configured to be pressed and biased toward the thrust direction cam means side.

At this time (when the clutch is not engaged), the clutch ring 9 is held at a predetermined position in the thrust direction and has a slight clearance from the chain wheel 5.

In addition, the chain wheel 5 has a first spline portion 2
3 is formed, and the ring 25 meshed with the input shaft 1 is provided with a second spline portion 27. The second spline unit 27 includes the first spline unit 23 and the second spline unit 2
A sleeve 29 that connects the shaft 7 and the shaft 7 is meshed. The movement of the sleeve 29 is interlocked with an operation lever for operating the clutch ring 9, and the clutch ring 9 is moved by a first step operation of the operation lever, and the sleeve 29 is moved by a second step operation. ing.

Next, the operation of the above embodiment will be described.

When the clutch ring 9 is not moved and the clutch means 11 is not engaged, the driving force of the input shaft 1 is not transmitted to the chain wheel 5 but only to the rear wheel drive shaft side. Therefore, the vehicle can run in a two-wheel drive state.

When the vehicle enters a bad road and it becomes necessary to switch to four-wheel drive during traveling, the fork (not shown) is moved by an operation lever (not shown), and the clutch ring 9 is moved to the chain wheel 5 side. This movement frictionally engages the outer cone surface 11a and the inner cone surface 11b of the clutch means.
Initially, the fastening force is weak and both slip, but the clutch ring 9 receives resistance from the chain wheel 5 side and causes a relative displacement with respect to the input shaft 1 in the rotational direction. Therefore, the cam concave portion 15a receives a pressing force from the cam protrusion 15b, and the clutch ring 9 is moved to the thrust direction chain wheel 5 side. By this movement, the fastening force between the outer cone surface 11a and the inner cone surface 11b is strengthened.

At this time, when a torque more than a predetermined value for fastening the outer cone surface 11a and the inner cone surface 11b is generated due to a sudden operation or the like, a reaction force of this torque acts on the cam means 15 via the clutch ring 9. Therefore, the cam ring 13 moves backward toward the gap 17 against the biasing force of the leaf spring 19, the cam recess 15a and the cam projection 15b are further displaced in the rotational direction, and the pressure angle θ is further reduced. Therefore, the thrust force for engaging the clutch means 11 becomes small, and smooth engagement of the clutch means 11 can be expected even if a torque reaction force of a predetermined value or more occurs.

In this case, since the cam ring 13 is pushed toward the clutch ring 9 by the leaf spring 19, the cam concave portion 15a and the cam projection 15b are always in contact with each other, and the cam means 15 quickly and quickly exerts a cam pressing action based on the rotational deviation. Can be done.

Then, when the operation lever is operated to the second stage, the sleeve 29 is moved, the first spline portion 23 and the second spline portion 27 are connected, and the connection between the chain wheel 5 and the input shaft 1 is reinforced. . Therefore, it is possible to switch to four-wheel drive even while the vehicle is traveling, and traveling on a bad road is facilitated.

If the operation lever is returned to the first stage, the connection at the sleeve 29 is released, and if it is returned to the second stage, the connection at the clutch ring 9 is released.

The 2-4 wheel switching described above is possible regardless of the rotational direction of the input shaft 1, because the cam means 15 is composed of the cam projection and the cam recess protruding in the thrust direction. Therefore, the switching is achieved both when the vehicle is moving forward and when the vehicle is moving backward.

The present invention is not limited to the above embodiment. For example, the first spline portion 23, the second spline portion 27, and the sleeve 29 can be omitted. Further, the cam means 15 receives a torque reaction force of a certain level or more,
Only when the clutch ring and the cam ring deviate from each other in the rotational direction by a predetermined amount or more, the pressure angle can be gradually reduced or can be gradually reduced. Further, it is possible to provide a stopper for stopping the reduction of the thrust force.

[Effects of the Invention] As is clear from the above, according to the configuration of the present invention, the input shaft and the rotating body can be smoothly moved through the friction engagement of the clutch means by the moving operation of the clutch ring even during rotation. They can be connected, and a strong connection can be obtained by the servo action of the cam means. Therefore,
It is possible to eliminate the problems caused by the synchro mechanism without requiring the synchro mechanism. Moreover, when a torque reaction force above a certain level is applied from the rotating body side due to a sudden operation or the like, the clutch ring and the cam ring further shift in the rotation direction, and this shift causes the cam ring to move backward against the biasing means. However, the pressure angle of the cam means decreases.
Therefore, the thrust force of the cam means is reduced, and the clutch means can be engaged with less shock.

[Brief description of drawings]

FIG. 1 is a sectional view according to an embodiment of the present invention, and FIG. 2 is a sectional view of a cam means. 1 ... Input shaft, 5 ... Chain wheel (rotating body) 9 ... Clutch ring, 11 ... Clutch means 13 ... Cam ring, 15 ... Cam means 19 ... Plate spring (biasing means)

Claims (1)

[Claims] 1. An input shaft connected to front or rear wheels, which receives a rotational force from a drive device, and a rotary body on the output side connected to front or front wheels, which is rotatably supported by a position in the thrust direction of the input shaft. A clutch ring that is rotatable with respect to the input shaft and that can be moved from a predetermined position in the thrust direction where it is held by the operating member to the thrust direction rotating body side by the operating member, and in the thrust direction with respect to the input shaft. A movable and non-rotatable cam ring, clutch means formed on the facing surfaces of the rotating body and the clutch ring for frictionally engaging the clutch ring by moving the clutch ring toward the rotating direction, and the clutch ring and the cam ring facing each other. The clutch ring is formed on the surface and moves relative to the rotating body side in the thrust direction due to the relative displacement between the two Therefore, the cam ring formed between the cam ring and the input shaft side, which is composed of the concave portion and the projection for increasing the servo, presses and urges the cam ring toward the thrust direction cam means side with the clutch ring in the predetermined position. A clutch device, comprising: