JP2022091582A - Clutch device - Google Patents

Abstract

To surely prevent the contact of a disc spring even if vibration is imparted to a clutch device.SOLUTION: In a clutch device 10, a plurality of first and second friction plates 18, 20 which are slidably fit to each other in an axial direction are accommodated in an outer member 12, and a circular disc spring 22 for energizing the first friction plate 18 in the axial direction is arranged between a pressurization part 56 of a piston 16 for pressing the first and second friction plates 18, 20 in the axial direction and the first friction plate 18. Then, a first step 62 at which the disc spring 22 is engaged with an end face facing the first friction plate 18, and which regulates movement in a radial direction is arranged at the pressurization part 56 of the piston 16.SELECTED DRAWING: Figure 2

Description

The present invention relates to a multi-plate clutch device used for a vehicle transmission or the like.

The present applicant has proposed a transmission provided with a multi-plate clutch device for switching a transmission state of a driving force from an internal combustion engine to an axle in a vehicle (see Patent Document 1).

This transmission includes an input shaft into which a driving force from an internal combustion engine is input, an output shaft for outputting the driving force to the axle side, and a drive pulley supported by the input shaft, and an end of the input shaft. The portion is provided with a clutch that transmits the rotation of the input shaft to the drive pulley.

This clutch includes a clutch outer, a clutch inner rotatably housed inside the clutch outer, and a plurality of clutch inners whose relative rotation is restricted inside the clutch outer and which is slidably housed in the axial direction. A plurality of clutch discs that are alternately superposed on the clutch plate in the axial direction, relative rotation is restricted on the outer peripheral side of the clutch inner, and are provided so as to be slidable in the axial direction, and the clutch outer. It is provided with a clutch piston housed inside the clutch plate and urging the clutch disk in the axial direction, and a return spring provided between the clutch piston and the clutch plate and urging the clutch plate and the clutch disk in a direction away from each other. ..

Then, the clutch piston is urged toward the clutch disc side by the hydraulic oil supplied to the clutch oil chamber between the clutch outer and the clutch piston, and the return spring is compressed in the axial direction to form the clutch disc and the clutch plate. Are in axial contact with each other. As a result, the frictional force between the clutch disc and the clutch plate increases, and the driving force transmitted from the input shaft to the clutch outer is transferred to the clutch inner under the contact action with the clutch disc and the clutch plate. Is transmitted and rotates integrally.

Japanese Patent No. 3509441

The present invention has been made in connection with the above proposal, and an object of the present invention is to provide a clutch device capable of reliably preventing contact with a case even when vibration is applied.

In order to achieve the above object, the embodiment of the present invention is slidable in the axial direction with respect to the case, the inner member rotatably housed inside the case, and the inner peripheral surface of the case facing the inner member. A plurality of first friction plates to be spline-fitted to the first friction plate, and a plurality of second friction plates to be spline-fitted to the outer peripheral surface of the inner member so as to be slidably overlapped with respect to the first friction plate. The friction plate comes into contact with the friction plate, the piston housed inside the case and pressing the first and second friction plates in the axial direction, and the pressure portion and the first friction plate of the piston that presses the first and second friction plates. In a clutch device having an annular countersunk spring urging in the axial direction and capable of transmitting the driving force input to the case to the inner member via the first and second friction plates.
The pressurizing portion is provided with a first engaging portion in which a disc spring is engaged with an end surface facing the first friction plate to restrict movement in the radial direction.

According to the present invention, in a clutch device in which a plurality of first and second friction plates are housed inside a case so as to be movable in the axial direction, pressure is applied to a piston that presses the first and second friction plates in the axial direction. An annular flat spring that abuts on the portion and the first friction plate and is urged in the axial direction is provided. A first engaging portion is provided in which the movement of the piston is restricted.

Therefore, even when vibration from an internal combustion engine or the like that generates a driving force is applied to the clutch device, the disc spring provided between the piston and the first friction plate is the first engaging portion. Engages with and restricts radial movement.

As a result, even when vibration is applied to the clutch device mounted on the vehicle so that the input direction of the driving force is horizontal, the disc spring is held against the piston and is radially outward under the action of gravity. It is possible to reliably prevent the case from moving downward and coming into contact with the inner peripheral surface of the case arranged on the outer peripheral side, and it is possible to avoid wear of the case due to this contact.

According to the present invention, the following effects can be obtained.

That is, for example, even when vibration from an internal combustion engine that generates a driving force is applied to the clutch device, a disc spring provided between the piston and the first friction plate is a pressure portion of the piston. Since it is always engaged with the first engaging portion formed on the surface, it is possible to reliably prevent the movement in the radial direction.

As a result, it is surely prevented that the disc spring is held by the piston and moves radially outward under the action of gravity and comes into contact with the inner peripheral surface of the case arranged on the outer peripheral side, and this contact is achieved. The resulting wear of the case can be avoided.

It is a partially omitted sectional view of the clutch device which concerns on embodiment of this invention. It is an enlarged sectional view which shows the vicinity of the outer peripheral side in the clutch device of FIG. It is a front view of the piston constituting the clutch device shown in FIG. 1 as seen from the pressurizing unit side. FIG. 3 is a cross-sectional view showing a state in which a piston in the clutch device of FIG. 1 is urged and the first and second friction plates are pressed by the piston and are in contact with each other. FIG. 3 is an enlarged cross-sectional view showing the vicinity of the outer peripheral side of the clutch device of FIG.

A preferred embodiment of the clutch device according to the present invention will be described in detail below with reference to the accompanying drawings.

The clutch device 10 is, for example, a multi-plate wear type clutch used in a vehicle such as an automobile and for transmitting a driving force generated by an internal combustion engine to a transmission or the like, as shown in FIGS. 1 and 2. The outer member (case) 12 formed in a bottomed tubular shape, the inner member 14 rotatably provided inside the outer member 12, and the inner member 14 rotatably accommodated inside the outer member 12 so as to be movable in the axial direction. A plurality of first and second friction plates 18 and 20 provided between the outer member 12 and the inner member 14 and movable in the axial direction (arrows A and B), and the piston 16. Includes a countersunk spring 22 disposed between the first friction plate 18 and the first friction plate 18.

An input shaft 24 is integrally connected to the center of the outer member 12, and an output shaft 26 is integrally formed at the other end of the inner member 14 in the axial direction. The clutch device 10 described above is used, for example, arranged sideways so that the input shaft 24 and the output shaft 26 are in the horizontal direction (arrows A and B directions).

The outer member 12 has a circular end wall portion 28 formed at one end in the axial direction, and a cylindrical portion 30 extending from the outer edge of the end wall portion 28 to the other end side in the axial direction (arrow B direction). A cylindrical hub 34 is continuously provided in the hole 32 opened at the center of the end wall 28. That is, the outer member 12 opens in the other side in the axial direction (direction of arrow B) and is formed in a cylindrical shape.

The cylindrical portion 30 is formed, for example, having substantially the same diameter and having a predetermined length along the axial direction (arrows A and B directions), and a plurality of first spline grooves along the circumferential direction on the inner peripheral surface 30a thereof. 36 is formed, and the outer peripheral edges of a plurality of first friction plates 18 described later are spline-fitted in the first spline groove 36 so as to be slidable in the axial direction (arrows A and B directions). In other words, the plurality of first friction plates 18 are accommodated in a state where the outer member 12 is allowed to move in the axial direction (arrows A and B directions) and the relative rotation in the circumferential direction is restricted. There is.

The hub 34 is provided so as to extend toward the other end side in the axial direction (direction of arrow B) with respect to the end wall portion 28 of the outer member 12, and a spline groove 38 is provided on the inner peripheral surface of the other end in the axial direction. The spline portion 24a of the input shaft 24 formed and inserted into the inner circumference of the hub 34 is fitted to the spline groove 38. As a result, the relative rotation between the hub 34 constituting the outer member 12 and the input shaft 24 is restricted, and the outer member 12 is integrally rotated together with the input shaft 24 by the driving force input from the input shaft 24.

Further, a spring receiving member 40 is mounted on the other end side of the hub 34 in the axial direction (in the direction of arrow B) so as to project radially outward with respect to the outer peripheral surface, and a return spring is provided between the hub 34 and the piston 16 described later. 42 is intervened. The return spring 42 is, for example, formed of a coil spring, is provided on the outer peripheral side of the hub 34, and has a hub 34 (outer member 12) having a spring receiving member 40 and a piston 16 described later in the axial direction (arrow A,). It is urged in the direction away from (B direction).

The inner member 14 has a large diameter portion 44 formed on one end side in the axial direction (direction of arrow A) and provided on the inner peripheral side of the first and second friction plates 18 and 20, and a diameter from the end portion of the large diameter portion 44. It has an output shaft 26 that is bent inward multiple times in the direction to form a small diameter, and the large diameter portion 44 and the output shaft 26 have a cylindrical shape extending along the axial direction (arrows A and B directions). Is formed in each.

The large diameter portion 44 has the same diameter and is formed with a predetermined length along the axial direction (arrows A and B directions), and a plurality of second spline grooves 46 are formed along the circumferential direction on the outer peripheral surface thereof. The inner peripheral edges of the plurality of second friction plates 20, which will be described later, are spline-fitted so as to be slidable in the axial direction (arrows A and B). Further, a drive gear 48 having a plurality of gear teeth is mounted on the outer peripheral surface at the other end of the output shaft 26 in the axial direction, and rotates integrally with the output shaft 26.

That is, the plurality of second friction plates 20 are accommodated in a state where the inner member 14 is allowed to move in the axial direction (arrows A and B) and the relative rotation in the circumferential direction is restricted.

As shown in FIGS. 1 to 3, the piston 16 has a circular cross-sectional shape corresponding to the shape of the outer member 12, and has a main body portion 50 provided in parallel with the end wall portion 28 of the outer member 12, and the piston 16. The outer edge portion 52 formed on the outer peripheral side of the main body portion 50, the inner edge portion 54 formed on the inner peripheral side of the main body portion 50, and the first and second friction plates 18 and 20 sides with respect to the main body portion 50. It has a pressurizing portion 56 protruding in the direction of (arrow B direction).

The main body portion 50 is formed to have a substantially constant thickness, and a hydraulic chamber 58 (not shown) to which hydraulic oil is supplied is formed between the main body portion 50 and the end wall portion 28 of the outer member 12. Further, one end of the return spring 42 held by the spring receiving member 40 is interposed in the main body portion 50 at a position near the boundary portion with the inner edge portion 54. As a result, the piston 16 is urged in a direction away from the first and second friction plates 18 and 20 under the elastic action of the return spring 42.

The outer edge portion 52 is formed so as to be wide in the axial direction with respect to the main body portion 50, is provided so as to face the cylindrical portion 30 of the outer member 12 and slide in contact with the inner peripheral surface 30a, and an annular groove is formed on the outer peripheral surface thereof. The first seal member 60 is mounted via the passage. Then, the first seal member 60 comes into contact with the inner peripheral surface 30a of the cylindrical portion 30, and when the piston 16 slides in the axial direction (arrows A and B directions) with respect to the outer member 12, the first seal member 60 comes into contact with the inner peripheral surface 30a. The member 60 seals between the outer edge portion 52 and the outer member 12.

The pressurizing portion 56 faces the first friction plate 18 arranged on one side in the axial direction (arrow A direction), and is formed at a position on the inner peripheral side with respect to the outer edge portion 52, and the outer edge portion 52 is formed. It is formed so as to protrude in the other side in the axial direction (direction of arrow B). Further, for example, the pressurizing portions 56 are formed in an arc shape in cross section when viewed from the moving direction of the piston 16 shown in FIG. 3, and are provided in plurality so as to be equidistant from each other along the circumferential direction of the piston 16. (See Fig. 3).

Further, the end surface of the pressurizing portion 56, which is the other end in the axial direction, is formed in a flat shape perpendicular to the moving direction of the piston 16, that is, orthogonal to the axial direction and parallel to the first friction plate 18, and the countersunk spring 22 described later. It has a first step (first engaging portion) 62 to which the inner peripheral portion (inner peripheral end) 22a is engaged.

The first step 62 has, for example, a rectangular cross section when viewed from the circumferential direction of the piston 16 shown in FIG. 2, and is recessed by a predetermined depth in one axial direction (arrow A direction) with respect to the end face of the pressurizing portion 56. At the same time, it is formed in the vicinity of the outer peripheral side in the pressurizing portion 56. Further, the first step 62 is formed in an arc shape with a radius corresponding to the inner peripheral portion 22a of the disc spring 22 described later. That is, the plurality of first steps 62 are provided so as to be on the same circumference with respect to the center of the piston 16, and are provided in the same number as the pressurizing portions 56.

The inner edge portion 54 is formed so as to project toward the other side in the axial direction (arrow B direction) with respect to the main body portion 50, is provided so as to face the outer peripheral surface of the hub 34 and is in sliding contact with the inner peripheral surface thereof, and is provided on the inner peripheral surface thereof. The second seal member 64 is mounted via the annular groove. Then, the second seal member 64 comes into contact with the outer peripheral surface of the hub 34, and when the piston 16 slides in the axial direction (arrows A and B directions) with respect to the hub 34, the inner edge is formed by the second seal member 64. A seal is made between the portion 54 and the hub 34.

For example, the first friction plate 18 is formed in a hollow disk shape from a metal plate having an integral thickness, and a plurality of first friction plates 18 are provided so as to be separated from each other in the axial direction (arrows A and B directions) of the outer member 12 at predetermined intervals. A second friction plate 20 is arranged between two adjacent first friction plates 18. A plurality of spline teeth 18a are provided on the outer peripheral edge of each first friction plate 18 along the circumferential direction, and the spline teeth 18a are fitted into the first spline groove 36 with respect to the outer member 12. Rotation is regulated.

Further, among the plurality of first friction plates 18, the first friction plate 18 arranged on one side in the axial direction (arrow A direction) has an outer peripheral portion of a disc spring 22 (described later) on the end surface facing the piston 16. It has a second step (second engaging portion) 66 with which the outer peripheral end) 22b is engaged.

The second step 66 has, for example, a rectangular cross section when viewed from the circumferential direction of the first friction plate 18 shown in FIG. 2, and is axially opposite to the end surface of the first friction plate 18 (arrow B direction). It is recessed by a predetermined depth and is formed in an annular shape along the circumferential direction of the first friction plate 18 and has a diameter corresponding to the outer peripheral portion 22b of the countersunk spring 22 described later. In other words, the second step 66 is formed in a groove shape along the circumferential direction of the first friction plate 18.

The second friction plate 20 is composed of, for example, a base plate 68 formed in an annular shape from a metal plate having a constant thickness, and a set of annular friction linings 70 bonded to both sides of the base plate 68 in the axial direction. It is composed. The friction lining 70 is formed of a friction material having a higher coefficient of friction than a metal material. A plurality of the second friction plates 20 are provided so as to be separated from each other by predetermined intervals in the axial direction (arrows A and B directions) of the inner member 14, and an outer member is provided between the two adjacent second friction plates 20. A plurality of first friction plates 18 spline-fitted to the 12 are arranged respectively. A plurality of spline teeth 20a are provided at the inner peripheral end of each second friction plate 20 along the circumferential direction, and the spline teeth 20a are fitted into the second spline groove 46 to form an inner member 14. Rotation against is regulated.

Further, there is a slight gap in the axial direction (arrows A and B) between the plurality of first and second friction plates 18 and 20, respectively. That is, the first friction plate 18 and the second friction plate 20 are provided so as to overlap each other in the radial direction and to alternate in the axial direction.

Further, a stopper plate 72 is provided on the other side in the axial direction so as to face the second friction plate 20 arranged on the other end side in the axial direction (direction of arrow B), and the stopper plate 72 has the first friction. Similar to the plate 18, the outer member 12 is slidably spline-fitted into the first spline groove 36, and is brought into contact with the locking ring 74 mounted on the inner peripheral surface 30a of the cylindrical portion 30 in the axial direction. Movement to the other side (direction of arrow B) is restricted.

The countersunk spring 22 is formed, for example, from a metal material into an annular shape having a hole in the center and a conical shape having a predetermined height in the axial direction (arrows A and B), and the inner peripheral portion 22a thereof. And the outer peripheral portion 22b are separated by a predetermined distance in the axial direction (arrows A and B directions). The disc spring 22 is provided for the purpose of cushioning the impact when the piston 16 moves and comes into contact with the first friction plate 18 and presses it in the axial direction.

Then, as shown in FIGS. 1 and 2, the countersunk spring 22 is arranged coaxially with the piston 16 and the first friction plate 18, and its inner peripheral portion 22a is on the outer edge portion 52 side (one in the axial direction) of the piston 16. The side is engaged with the first step 62 (in the direction of arrow A), and the outer peripheral portion 22b becomes the side of the first friction plate 18 (the other side in the axial direction, in the direction of arrow B) adjacent to the outer edge portion 52. Engage in step 66. As a result, the countersunk spring 22 is arranged so as to be inclined toward the other side in the axial direction (arrow B direction) from the inner peripheral portion 22a to the outer peripheral portion 22b when viewed from the direction orthogonal to the axial direction shown in FIG. The piston 16 and the first friction plate 18 are urged so as to be separated from each other in the axial direction (arrows A and B directions). In other words, the disc spring 22 is arranged so as to be inclined with respect to the first friction plate 18.

Further, the disc spring 22 has an outer peripheral portion 22b facing the inner peripheral surface 30a of the cylindrical portion 30 of the outer member 12, and is arranged radially inward with respect to the inner peripheral surface 30a at a predetermined interval (distanced from the inner peripheral surface 30a). See Figure 2).

The clutch device 10 according to the embodiment of the present invention is basically configured as described above, and its operation and action / effect will be described next. As shown in FIG. 1, the first and second friction plates 18 and 20 have a gap in the axial direction from each other, and the driving force input to the input shaft 24 is an inner member having the output shaft 26. The non-transmission state that is not transmitted to 14 will be described as the initial state.

First, in the non-transmission state of the driving force shown in FIG. 1, the outer member 12 rotates together with the input shaft 24 to which the driving force from the internal combustion engine of a vehicle (not shown) is input, and the hydraulic chamber is passed through a supply port (not shown). By supplying the hydraulic oil to 58, the piston 16 is pressed toward the other side in the axial direction (direction of arrow B) by the hydraulic pressure of the hydraulic oil, and the countersunk spring 22 is compressed against the elastic force of the return spring 42. While advancing toward the first and second friction plates 18 and 20 (in the direction of arrow B).

Then, the pressurizing portion 56 of the piston 16 compresses the countersunk spring 22 with the end surface of the first friction plate 18 in the other axial direction (direction of arrow B), so that the countersunk spring 22 is gradually applied. While deforming so as to be substantially parallel to the compression portion 56 and the end face, the plurality of first and second friction plates 18 and 20 are pressed by the piston 16 and the countersunk spring 22 toward the other side in the axial direction (arrow B direction). It is moved to the stopper plate 72 side. At this time, since the inner peripheral portion 22a of the disc spring 22 remains engaged with the first step 62, the disc spring 22 is always held coaxially with the piston 16 and does not move relative to the radial direction.

As a result, the gaps between the plurality of adjacent first and second friction plates 18 and 20 are reduced, and the first friction plate 18 and the friction lining 70 of the second friction plate 20 gradually come into contact with each other. As it goes on, the frictional force between the two gradually increases. As a result, the driving force input to the input shaft 24 begins to be gradually transmitted from the first friction plate 18 which is spline-fitted to the outer member 12 and rotates integrally to the second friction plate 20, and the second friction The output shaft 26 gradually begins to rotate by being transmitted to the inner member 14 spline-fitted to the plate 20.

Then, as shown in FIGS. 4 and 5, the piston 16 is further advanced in the other axial direction (direction of arrow B) by the hydraulic pressure of the hydraulic oil, and the outer peripheral portion 22b of the countersunk spring 22 is separated from the second step 66. Then, it becomes substantially parallel to the end surface of the pressurizing portion 56, and the first friction plate 18 is further pressed by the pressurizing portion 56, so that the first and second friction plates 18 and 20 are further moved to the other side in the axial direction. The second friction plate 20 on the other side in the axial direction (direction of arrow B) comes into contact with the stopper plate 72, and the stopper plate 72 is locked to the locking ring 74.

As a result, the advance of the first and second friction plates 18 and 20 in the other axial direction (in the direction of arrow B) due to the pressing of the piston 16 is restricted and stopped. Also in this case, since the inner peripheral portion 22a of the disc spring 22 is engaged with the first step 62 of the piston 16, it is held coaxially with the piston 16.

In this way, the gap between the plurality of first and second friction plates 18 and 20 disappears and they come into contact with each other, so that the frictional force between them further increases and becomes maximum, and the driving force from the input shaft 24 becomes the first and second. All of them are transmitted to the inner member 14 via the second friction plates 18 and 20, and are output to the drive gear 48 via the output shaft 26 with the same torque as the driving force input to the input shaft 24. That is, it is in a driving force transmission state in which all the driving force input to the input shaft 24 is transmitted to the output shaft 26.

On the other hand, in the driving force transmission state of the clutch device 10 described above, by stopping the supply of the hydraulic oil to the hydraulic chamber 58, the hydraulic pressure in the hydraulic chamber 58 is destroyed and the piston 16 is caused by the elastic force of the return spring 42. It moves backward by being pressed to one side in the axial direction (direction of arrow A). At the same time, the compression state of the countersunk spring 22 in the other axial direction (arrow B direction) by the pressurizing portion 56 of the piston 16 is also released, so that the plurality of first and second friction plates 18 and 20 are axially oriented. It becomes movable in the (arrows A and B directions), and a gap is formed again between the adjacent first friction plate 18 and the second friction plate 20.

As a result, the contact pressure between the first friction plate 18 and the second friction plate 20 is reduced, so that the frictional force generated between the two is reduced, and accordingly, the first and second friction plates 18 and 20 are interposed. The transmission of the driving force from the input shaft 24 to the output shaft 26 is cut off, resulting in a non-transmission state.

Further, as shown in FIG. 1, in the clutch device 10 arranged sideways with respect to the vehicle so that the input shaft 24 and the output shaft 26 are in the horizontal direction, the inner peripheral portion 22a of the countersunk spring 22 is always the piston 16. Since it is engaged with the first step 62 of the above, for example, even when vibration from the internal combustion engine of the vehicle is applied to the countersunk spring 22 and the countersunk spring 22 rotates inside, the countersunk spring 22 Is held coaxially with the piston 16 to prevent it from coming into contact with the cylindrical portion 30 (inner peripheral surface 30a) of the outer member 12 provided on the outer peripheral side of the countersunk spring 22. Therefore, it is possible to prevent the outer member 12 from being worn due to contact with the disc spring 22 due to the vibration of the clutch device 10.

As described above, in the present embodiment, in the clutch device 10 used in the vehicle for transmitting the driving force from the internal combustion engine to the transmission or the like, the clutch device 10 is provided between the piston 16 and the first friction plate 18. Since the inner peripheral portion 22a of the disc spring 22 is engaged with the first step 62 formed on the end surface of the pressurizing portion 56 of the piston 16, the disc spring 22 is always held coaxially with the piston 16. Is possible.

Therefore, in the clutch device 10 arranged sideways so that the input shaft 24 and the output shaft 26 are in the horizontal direction (arrows A and B), the disc spring 22 rotates due to vibration from the internal combustion engine or the like. Even so, it is possible to prevent the outer member 12 from moving downward under the action of gravity and coming into contact with the cylindrical portion 30 of the outer member 12 arranged on the outer peripheral side.

As a result, even when vibration is applied to the clutch device 10, the contact of the disc spring 22 with the outer member 12 is surely prevented, and the wear of the outer member 12 due to the contact is suitably avoided. Is possible.

Further, by providing a second step 66 to which the outer peripheral portion 22b of the disc spring 22 can engage with the end surface of the first friction plate 18 facing the pressurizing portion 56 of the piston 16, the disc spring 22 is provided with the first step 62. The inner peripheral portion 22a can be held, and the outer peripheral portion 22b can be held by the second step 66. Therefore, for example, even when vibration generated by an internal combustion engine or the like is applied, the disc spring 22 can be more reliably held coaxially with the piston 16 and the first friction plate 18. Therefore, it is possible to more reliably prevent the disc spring 22 from coming into contact with the outer member 12 and avoid wear.

Further, by forming the first and second steps 62 and 66 so as to be recessed in the moving direction of the piston 16 (directions of arrows A and B), the pressure portion 56 of the piston 16 and the end faces of the first friction plate 18 are formed. The inner peripheral portion 22a and the outer peripheral portion 22b of the disc spring 22 can be easily and surely engaged with each other to regulate the movement in the radial direction (outer peripheral side).

It should be noted that the clutch device according to the present invention is not limited to the above-described embodiment, and of course, various configurations can be adopted without departing from the gist of the present invention.

10 ... Clutch device 12 ... Outer member 14 ... Inner member 16 ... Piston 18 ... First friction plate 20 ... Second friction plate 22 ... Belleville spring 22a ... Inner peripheral part 22b ... Outer peripheral part 42 ... Return spring 56 ... Pressurizing part 62 ... 1st step 66 ... 2nd step

Claims (5)

A case, an inner member rotatably housed inside the case, and a plurality of first friction plates spline-fitted so as to be slidable in the axial direction with respect to the inner peripheral surface of the case facing the inner member. A plurality of second friction plates, which are alternately arranged on the first friction plate and spline-fitted to the outer peripheral surface of the inner member so as to be slidable in the axial direction, and housed inside the case. The piston that presses the first and second friction plates in the axial direction, the pressure portion of the piston that presses the first and second friction plates, and the first friction plate come into contact with each other in the axial direction. In a clutch device having an annular countersunk spring urging the case and capable of transmitting the driving force input to the case to the inner member via the first and second friction plates.
The clutch device is provided with a first engaging portion in which the disc spring is engaged with an end surface facing the first friction plate to restrict movement in the radial direction. In the clutch device according to claim 1,
A clutch device provided with a second engaging portion on the end surface of the first friction plate facing the pressurized portion, to which a disc spring is engaged and restricts movement in the radial direction. In the clutch device according to claim 1 or 2.
A clutch device in which the inner peripheral end of the disc spring is engaged with the first engaging portion. In the clutch device according to claim 2,
A clutch device in which the outer peripheral end of the disc spring is engaged with the second engaging portion. In the clutch device according to any one of claims 1 to 4.
The engaging portion is a clutch device formed by being recessed in the moving direction of the piston.

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