CN212775251U - Friction washer - Google Patents

Abstract

The utility model relates to a friction washer. The utility model provides the high friction plate's play success rate. The friction member includes: an annular second friction member body (58) and a plurality of dividing plates (591). A plurality of dividing plates 591 are fixed on one side surface of the second friction member main body 58 in an annular arrangement.

Description

Friction washer

Technical Field

The utility model relates to a friction washer.

Background

The hysteresis torque generating mechanism used in the damper mechanism of the clutch disc assembly is composed of a friction washer, a conical spring, and the like (see, for example, patent document 1). The friction washer is disposed between the input-side member and the output-side member that are relatively rotatable, and is pressed against the input-side member by a conical spring, for example. When the input-side member and the output-side member are relatively rotated by torsional vibration, the friction washer rotates integrally with one of the input-side member and the output-side member and frictionally contacts the other, thereby generating a hysteresis torque.

Patent document 1: japanese laid-open patent publication No. 9-242823

The friction washer is annular, and is manufactured by punching a sheet-like friction material into an annular shape by press working. In this case, the portions other than the product (the inner peripheral portion and the outer peripheral portion) are discarded. Therefore, there is a problem that the yield is poor.

SUMMERY OF THE UTILITY MODEL

The technical problem of the utility model lies in improving the yield of friction packing ring.

(1) The utility model relates to a friction washer possesses: an annular holding member; and a plurality of friction members fixed to one side surface of the holding member in an annular arrangement.

Here, one friction material, which has been formed into a ring shape in the past, is divided into a plurality of pieces, and the plurality of divided friction materials are fixed to the holding member in a ring-shaped arrangement. Therefore, when the friction material is formed of a sheet-like member, the number of discarded portions is reduced, and the yield is improved. Note that although the holding member is annular, the yield is not a problem because the holding member is usually formed of a resin in many cases.

(2) Preferably, each of the plurality of friction members has a first engaging portion at one end portion in the circumferential direction and a second engaging portion at the other end portion in the circumferential direction, the second engaging portion being engaged with the first engaging portion of the adjacent friction member.

Here, the plurality of friction materials can be assembled by the first and second engagement portions. Therefore, when the plurality of friction materials are arranged on the side surface of the holding member, the work is facilitated.

(3) Preferably, the first engaging portion is a convex portion protruding in the circumferential direction, and the second engaging portion is a concave portion recessed in the circumferential direction.

(4) Preferably, the plurality of friction members are formed by punching out the sheet member.

(5) Preferably, the holding member is made of resin, and the plurality of friction materials are integrated with the holding member by insert molding.

Effect of the utility model

In the present invention as described above, the yield of the annular friction material is improved.

Drawings

Fig. 1 is a schematic longitudinal sectional view of a clutch disc assembly according to an embodiment of the present invention.

Figure 2 is a partial front view of the clutch disc assembly.

Figure 3 is a torsional characteristic diagram of the clutch disc assembly.

Fig. 4 is a partially enlarged view of fig. 1.

Fig. 5 is a front view of the output side rotating member, the high-rigidity spring, and the like.

Fig. 6 is a partially enlarged view of fig. 1.

Fig. 7 is an exploded perspective view of the low rigidity damper.

Fig. 8 is an external perspective view of the splined hub.

Fig. 9 is a partially exploded perspective view of the hysteresis mechanism.

Fig. 10 is an external perspective view of the second friction member as viewed from the holding plate side.

Fig. 11 is an external perspective view of the second friction member as viewed from the clutch plate side.

Description of the reference numerals

1: a clutch disc assembly; 3: a vibration reduction mechanism; 55: a second friction member (friction washer); 58: a second body; 59: a second friction plate; 591: a dividing plate (friction member); 591 a: a convex portion (first engaging portion); 591 b: a recess (second engaging portion).

Detailed Description

Fig. 1 is a sectional view of a clutch disc assembly having a friction member (an example of a friction washer) according to an embodiment of the present invention. The O-O line of figure 1 is the axis of rotation of the clutch disc assembly 1. The clutch disc assembly 1 transmits torque from an engine and a flywheel disposed on the left side of fig. 1 to a transmission disposed on the right side of fig. 1, and attenuates torque variation. In addition, fig. 2 is a partial front view of the clutch disc assembly 1.

[ integral Structure ]

The clutch disc assembly 1 has: a clutch disk 2 to which torque is input from the flywheel by friction fit; a damper mechanism 3 that damps and absorbs torque variation input from the clutch disk 2; and a splined hub 4.

[ Clutch disk 2]

The clutch disc 2 is pressed against the flywheel by a pressure plate, not shown. The clutch disc 2 includes a cushion plate 6 and a pair of friction linings 8 fixed to both surfaces of the cushion plate 6 by rivets 7. The damper plate 6 is fixed to an outer peripheral portion of the damper mechanism 3.

[ damping mechanism 3]

The damper mechanism 3 has a four-stage torsional characteristic on the positive side (in the rotational direction on the drive side) as shown in fig. 3 in order to damp and absorb torque variation transmitted from the engine. Note that the negative-side torsion characteristic is omitted here.

The damper mechanism 3 includes a low rigidity damper 11, a high rigidity damper 12, and a hysteresis generating mechanism 13.

As shown in fig. 3, the low rigidity damper 11 operates in the first stage torsion angle region L1. The high-rigidity damper 12 operates in a second-stage torsion angle region H2, a third-stage torsion angle region H3, and a fourth-stage torsion angle region H4 in which the torsion angle is larger in order than the first-stage torsion angle region L1.

The hysteresis generating mechanism 13 generates hysteresis torque in each stage torsion angle region.

< high rigidity damper 12 >

As shown in fig. 4, the high-stiffness damper 12 has an input-side rotating member 20, a hub flange 21, and a plurality of high-stiffness springs 22. As shown in fig. 5, the high-rigidity spring 22 includes four first coil springs 221, four second coil springs 222, and four third coil springs 223. The first coil spring 221 and the second coil spring 222 have the same length. The first coil spring 221 is accommodated in an inner peripheral portion of the second coil spring 222.

Input-side rotary member 20-

Torque is input from the engine to the input-side rotating member 20 via the clutch disc 2. The input-side rotating member 20 includes a clutch plate 24 and a holding plate 25.

The clutch plate 24 and the holding plate 25 are substantially annular and are arranged at intervals in the axial direction. The clutch plate 24 is disposed on the engine side, and the retaining plate 25 is disposed on the transmission side. The clutch plate 24 and the holding plate 25 are integrally rotated by being coupled at their outer peripheries by a stopper pin 26 (see fig. 2 and 5).

As shown in fig. 2 and 4, four first holding portions 24a and 25a and four second holding portions 24b and 25b are formed in the clutch plate 24 and the holding plate 25 at intervals in the circumferential direction. The first holding portions 24a, 25a and the second holding portions 24b, 25b are alternately arranged in the circumferential direction. Further, a plurality of notches 25c for bonding are formed in the holding plate 25.

Although fig. 2 shows only the holding plate 25, the holding portions 24a and 24b of the clutch plate 24 have the same configuration.

Hub flange 21-

The hub flange 21 is a substantially disk-shaped member (see fig. 5) and is disposed on the outer periphery of the spline hub 4. The hub flange 21 can rotate relative to the clutch plate 24 and the retaining plate 25 within a predetermined angular range. The hub flange 21 has a disc portion 211 and a plurality of teeth 21 c. The disc portion 211 is disposed between the clutch plate 24 and the retaining plate 25 in the axial direction. The plurality of teeth 21c are formed on the inner circumferential surface of the disc portion 211.

As shown in fig. 5, the hub flange 21 and the spline hub 4 are engaged with each other by a plurality of teeth 21c, 4c formed on the inner and outer peripheral portions of each other. Note that a predetermined gap G1 is set between the teeth 21c, 4c of each other. That is, the hub flange 21 and the spline hub 4 can rotate relative to each other by the angle of the gap G1 between the teeth 21c and 4c (corresponding to the first-stage torsion angle region L1).

As shown in fig. 5, the hub flange 21 is formed with first and second window holes 21a, 21b at positions facing the first and second holding portions 24a, 25a, 24b of the clutch plate 24 and the holding plate 25, respectively. Then, the first coil spring 221 and the second coil spring 222 are housed in the first window hole 21a, and the first coil spring 221 and the second coil spring 222 are held in the axial direction and the radial direction by the first holding portions 24a and 25a of the clutch plate 24 and the holding plate 25. Further, the third coil spring 223 is accommodated in the second window hole 21b, and the third coil spring 223 is held in the axial direction and the radial direction by the second holding portions 24b and 25b of the clutch plate 24 and the holding plate 25.

Note that both circumferential ends of the first holding portions 24a, 25a and the second holding portions 24b, 25b of the clutch plate 24 and the holding plate 25 can be engaged with end surfaces of the coil springs 221 to 223.

Here, as shown in fig. 5, a projection 21e projecting toward the other side is formed in a part of one end surface 21d in the circumferential direction at the first window hole 21a of the hub flange 21. The projection 21e abuts on an end surface of the first coil spring 221. On the other hand, a gap G2 (corresponding to the second-stage torsion angle region H2) is secured between the one end surface 21d of the first window hole 21a and the end surface of the second coil spring 222.

The first coil spring 221 and the second coil spring 222 are disposed in the first holding portions 24a and 25a of the clutch plate 24 and the holding plate 25 with no gap therebetween in the circumferential direction, but the third coil spring 223 is disposed in the second holding portions 24b and 25b of the clutch plate 24 and the holding plate 25 with a gap G3 (see fig. 2; corresponding to the third-stage torsion angle region H3) therebetween in the circumferential direction.

Note that engagement holes 21f penetrating in the axial direction are formed in the respective inner peripheral sides of the second window holes 21b of the hub flange 21.

According to the above configuration, in the second to fourth torsion angle regions, first, only the first coil spring 221 is compressed, and then, the second coil spring 222 is compressed in addition to the first coil spring 221, which will be described in detail later. Then, the third coil spring 223 is also compressed.

< Low rigidity damper 11 >

As shown in fig. 6 and 7, the low-rigidity damper 11 includes: a first friction member 30, and a spring holder 31, a drive plate 32, and a plurality of low stiffness springs 33.

First friction member 30

The first friction member 30 is formed in a disk shape and is disposed between the clutch plate 24 and the inner peripheral portion of the hub flange 21 in the axial direction. The first friction member 30 has a first friction member main body 35 (hereinafter described as "first body 35") and a first friction plate 36.

As shown in fig. 7, the first body 35 has a circular opening in the central portion, and has four holding portions 35a, four first engaging projections 35c, and four second engaging projections 35d having a projection length shorter than that of the first engaging projections 35 c. The holding portion 35a is formed on the inner peripheral side of each of the engaging projections 35c, 35 d. The first engagement projection 35c and the second engagement projection 35d are formed to project from the outer peripheral portion of the first body 35 toward the hub flange 21 side in the axial direction.

The first friction plate 36 is fixed integrally with the first body 35 to a side surface of the first body 35 on the clutch plate 24 side. The first friction plate 36 is formed to extend further radially inward from the inner peripheral end of the first body 35. The side surface of the first friction plate 36 on the side of the holding plate 25 forms an inner peripheral friction portion 36 a.

Spring support 31

The spring holder 31 is disposed opposite to the first body 35 with a gap therebetween in the axial direction of the hub flange 21 and the first friction member 30. The spring holder 31 has almost the same shape as the first body 35. The spring holder 31 has a circular opening in the central portion, and has four holding portions 31a, four boss portions 31b, four first cutouts 31c, and four second cutouts 31 d. The first notch 31c is formed in the boss portion 31 b.

The holding portion 31a is formed at a position opposite to the holding portion 35a of the first body 35. The first engaging projection 35c of the first body 35 is engaged with the first notch 31c of the boss portion 31b, and the boss portion 31b is engaged with the engaging hole 21f of the hub flange 21. In addition, a second cutout 31d is formed corresponding to the second engagement protrusion 35d of the first body 35, and the second engagement protrusion 35d is engaged with the second cutout 31 d.

As described above, the first friction member 30 and the spring holder 31 are integrated by the engagement of the first engagement projection 35c with the first cutout 31c and the engagement of the second engagement projection 35d with the second cutout 31 d. Next, the spring holder 31 and the hub flange 21 are integrated by the engagement of the first engaging projection 35c and the boss portion 31b with the engaging hole 21 f. Therefore, the first friction member 30 and the spring holder 31 rotate integrally with the hub flange 21.

Drive plate 32

The drive plate 32 is disposed between the first friction member 30 and the spring holder 31 in the axial direction, and is rotatable relative to the first friction member 30 and the spring holder 31 within a predetermined angular range. The drive plate 32 has an opening in the central portion, and has four window holes 32a and a plurality of engaging recessed portions 32b formed on the inner peripheral surface of the drive plate 32.

The window hole 32a is formed at a position opposing the first body 35 and the holding portions 35a, 31a of the spring holder 31. Next, the low-stiffness spring 33 is housed in each window hole 32a, and the low-stiffness spring 33 is held in the axial direction and the radial direction by the first body 35 and the holding portions 35a, 31a of the spring holder 31.

Note that both ends in the circumferential direction of the holding portions 35a, 31a of the first body 35 and the spring holder 31 can be joined to the end surface of the low stiffness spring 33.

The spring constant of the low-rigidity spring 33 is set to be significantly smaller than that of the high-rigidity spring 22. That is, the high-rigidity spring 22 has a rigidity much higher than that of the low-rigidity spring 33. Therefore, in the first-stage torsion angle region, the high-stiffness spring 22 is not compressed, and only the low-stiffness spring 33 is compressed.

[ spline hub 4]

The spline hub 4 is disposed on the inner peripheral side of the clutch plate 24 and the holding plate 25. As shown in fig. 4, 6, and 8, the spline hub 4 includes cylindrical bosses 41a and 41b extending in the axial direction, and a flange 42 extending radially outward from the bosses 41a and 41 b.

The bosses 41a, 41b extend axially through the inner peripheral portion of the clutch plate 24 and the inner peripheral portion of the holding plate 25. The clearance between the outer peripheral surface of the boss 41a on the engine side and the inner peripheral surface of the clutch plate 24 is narrower than that of the conventional structure. That is, the clutch plates 24 are positioned in the radial direction with respect to the spline hub 4 by reducing the gap between the outer peripheral surface of the boss 41a and the inner peripheral surface of the clutch plates 24. Further, spline holes 4a for engaging with an input shaft (not shown) of the transmission are formed in the inner peripheral portions of the bosses 41a and 41 b.

A plurality of engaging protrusions 4d are formed on the outer peripheral surface of the boss 41a on the engine side. The engine-side surface 4e of the engagement convex portion 4d is a part of a spherical surface (more specifically, a spherical surface bulging outward). The engaging projection 4d is engaged with the engaging recess 32b of the drive plate 32 substantially without a gap. Further, teeth 4c are formed on the outer peripheral surface of the flange 42. As described in fig. 5, the teeth 4c can mesh with the teeth 21c of the hub flange 21, and a gap G1 exists between the teeth 4c and 21c in the circumferential direction.

< delay generating means 13 >

As shown in fig. 4 and 6, the hysteresis generating mechanism 13 includes a first hysteresis generating unit 45, a second hysteresis generating unit 46, and a third hysteresis generating unit 47. The first hysteresis generating section 45 operates only in the first-stage torsion angle region L1. The second hysteresis generating section 46 operates in the second to fourth torsion angle regions H2 to H4. The third hysteresis generating section 47 operates in the entire torsion angle region.

A first hysteresis generating section 45-

The first hysteresis generating part 45 has a first bush 51 and a first conical spring 52.

The first bush 51 is an iron annular member formed by cold forging, and has a surface-treated layer of manganese phosphate or the like on the surface thereof. The first bush 51 is disposed between the side surface of the engagement convex portion 4d and the inner circumferential friction portion 36a of the first friction plate 36 on the outer circumference of the boss 41a of the spline hub 4.

As shown in detail in fig. 7, the first bush 51 has a first contact surface 51a, a second contact surface 51b, and a plurality of engagement portions 51 c.

The first contact surface 51a is a flat surface and contacts the inner circumferential friction portion 36a of the first friction plate 36. That is, the first contact surface 51a comes into contact with the inner circumferential friction portion 36a and is in frictional contact therewith, thereby generating a hysteresis torque.

The second contact surface 51b is a part of a spherical surface (more specifically, a spherical surface recessed inward), and contacts the side surface 4e of the engagement convex portion 4d of the boss 41a of the spline hub 4. As described above, the side surface 4e of the engagement convex portion 4d is a part of a spherical surface bulging outward. Therefore, misalignment of the spline hub 4 with respect to the rotation axis is absorbed by the second abutment surfaces 51b and the spherical surfaces 51b, 4e of the engagement convex portion 4d abutting each other. In addition, the side surface (spherical surface) 4e of the convex joining portion 4d has a larger radius of curvature than the second contact surface 51 b. Therefore, the side surface 4e of the engagement convex portion 4d always abuts on the outer peripheral side with the second abutment surface 51 b.

The plurality of engagement portions 51c are formed to protrude toward the engagement convex portion 4d side of the spline hub 4. Further, the engaging portion 51c is inserted between the adjacent engaging projections 4 d. That is, the engaging portion 51c engages with the engaging projection 4 d. Therefore, the first bush 51 cannot relatively rotate with respect to the spline hub 4.

Further, the radial clearance between the inner peripheral surface of the first bush 51 and the outer peripheral surface of the boss 41 of the spline hub 4 is set to be larger than the radial clearance between the inner peripheral surface of the clutch plate 24 and the outer peripheral surface of the boss 41. Therefore, the inner peripheral surface of the first bush 51 can be prevented from contacting the outer peripheral surface of the boss 41 to generate heat.

Further, the radial gap between the outer peripheral surface of the first bush 51 and the inner peripheral surface of the first main body 35 of the first friction member 30 is set to be larger than the radial gap between the inner peripheral surface of the clutch plate 24 and the outer peripheral surface of the boss 41. Therefore, the outer peripheral surface of the first bush 51 can be prevented from contacting the inner peripheral surface of the first body 35 to generate heat.

A second hysteresis generating section 46-

As shown in fig. 4, 6, and 9, the second hysteresis generating portion 46 includes a second friction member 55 (an example of a friction washer) and a second conical spring 56. Fig. 9 is an exploded view showing the components arranged between the spline hub 4 and the retainer plate 25. The second hysteresis generating portion 46 also includes the clutch plate 24-side surface of the first friction plate 36. That is, the side surface of the first friction plate 36 on the clutch plate 24 side constitutes a second friction portion 36b which is brought into frictional contact with the side surface of the clutch plate 24 to generate hysteresis torque.

The second friction member 55 includes a second friction member main body (an example of a holding member; hereinafter, described as "second main body") 58 made of resin, and a second friction plate 59.

As shown in fig. 10 and 11, the second body 58 includes an inner peripheral disk portion 60, an outer peripheral disk portion 61, a plurality of coupling portions 62, and a friction portion 63. Fig. 10 is a view of the second friction member 55 as viewed from the holding plate 25 side, and fig. 11 is a view of the second friction member 55 as viewed from the clutch plate 24 side.

The inner peripheral disk portion 60 is formed annularly, and a plurality of engaging recessed portions 60a are formed on the inner peripheral surface. The outer circumferential disc portion 61 is annular and is disposed radially outward of the inner circumferential disc portion 60 with a space in the radial direction from the inner circumferential disc portion 60. A plurality of engaging projections 61a projecting in the axial direction are formed on the side surface of the outer peripheral disk portion 61 on the holding plate 25 side. The engaging projection 61a is engaged with the cutout 25c of the holding plate 25. Therefore, the second friction member 55 cannot rotate relative to the holding plate 25. The plurality of coupling portions 62 couple the inner circumferential disk portion 60 and the outer circumferential disk portion 61 and are provided at predetermined intervals in the circumferential direction. The friction portion 63 is formed to extend further radially outward from the outer peripheral disk portion 61.

As shown in fig. 11, the second friction plate 59 is provided on the side surfaces of the outer peripheral disc portion 61 and the friction portion 63 (the side surface on the clutch plate 24 side) of the second body 58. The second friction plate 59 is formed in a ring shape by four dividing plates 591 (an example of a friction material).

The four dividing plates 591 are all in the same shape, and are formed by punching a sheet-like friction material by press working. A protruding portion 591a (an example of a first joining portion) protruding in the circumferential direction is formed at one end of each of the dividing plates 591 in the circumferential direction. Further, a recess 591b (an example of a second engaging portion) recessed in the circumferential direction is formed at the other end in the circumferential direction of each of the dividing plates 591. Then, the four dividing plates 591 are fixed to each other by fitting the convex portions 591a into the concave portions 591 b.

In forming the second friction member 55, first, a sheet-like friction material is punched to form four dividing plates 591. Then, the four dividing plates 591 are fixed in a ring shape by fitting the convex portions 591a and the concave portions 591b with each other. Thereafter, the second body 58 is set in a mold for resin molding, and the annular second friction plate 59 is insert-molded in a part of the second body 58.

The second conical spring 56 is disposed between the second friction member 55 and the holding plate 25 in the axial direction. More specifically, the second conical spring 56 is disposed between the outer peripheral disk portion 61 of the second body 58 and the inner peripheral end portion of the holding plate 25 in the axial direction. Then, the second friction member 55 is pressed against the hub flange 21.

Note that, as shown in fig. 9, a plurality of notches 56a are formed in the inner peripheral surface of the second conical spring 56. An engagement protrusion 61a formed in the outer peripheral disk portion 61 of the second body 58 penetrates the cutout 56 a. Therefore, the second conical spring 56 cannot rotate relative to the second friction member 55 and the holding plate 25.

According to the above configuration, when the second friction plate 59 of the second friction member 55 is pressed against the side surface of the hub flange 21 and the second friction member 55 and the hub flange 21 rotate relative to each other, hysteresis torque is generated. Simultaneously, the clutch plate 24 is pressed against the first friction plate 36 of the first friction member 30 via the holding plate 25 by the urging force of the second conical spring 56. Therefore, when the clutch plate 24 and the first friction member 30 rotate relatively, a hysteresis torque is generated.

A third hysteresis generating section 47-

The third hysteresis generating section 47 has a second bush 65. The second bush 65 is made of resin and is formed in a ring shape as shown in fig. 9. A plurality of engaging projections 65a projecting in the axial direction are formed on the side surface of the second bush 65 on the holding plate 25 side.

The second bushing 65 is disposed between the flange 42 of the spline hub 4 and the inner peripheral end of the second friction member 55 in the axial direction. Further, the engaging protrusions 65a are engaged with the engaging recesses 60a, and the engaging recesses 60a are formed in the inner peripheral disc portion 60 of the second friction member 55. Note that the engagement projection 65a penetrates through a cutout 52a formed in the inner peripheral surface of the first conical spring 52. Therefore, the second bush 65 and the first conical spring 52 cannot rotate relative to the second friction member 55 and the holding plate 25.

Then, the second bush 65 is pressed against the side surface of the spline hub 4 by the biasing force of the first conical spring 52. Therefore, when the retainer plate 25 and the spline hub 4 relatively rotate, a hysteresis torque is generated.

Here, the third hysteresis generating unit 47 is configured to generate a hysteresis torque smaller than the hysteresis torque generated by the first hysteresis generating unit 45.

More specifically, the pressing loads of the frictional contact portions in the first hysteresis generating unit 45 and the third hysteresis generating unit 47 are the same. However, the friction coefficient of the second bush 65 with respect to the third hysteresis generating unit 47 is about 0.1 to 0.15, and the friction coefficient of the first bush 51 of the first hysteresis generating unit 45 is about 0.4.

According to the above setting, the hysteresis torque generated by the first bush 51 is large, but the operation is performed only in the first-stage torsion angle region. On the other hand, the second bushing 65 operates in all the torsion angle regions of the first stage to the fourth stage, but the hysteresis torque generated by the second bushing 65 is small, and therefore the life can be prolonged.

[ actions ]

With respect to the torsional characteristics of the clutch disc assembly 1 of the present embodiment, only the positive side operation will be described, and the description of the negative side operation will be omitted.

< first-stage torsion Angle region L1 >

When the transmission torque and the torque fluctuation are small, the present apparatus operates in a first-stage torsion angle region (hereinafter referred to as "first stage") L1 of the torsion characteristic. In this first stage, the low-stiffness spring 33, which is less stiff, is compressed. Therefore, the first friction member 30 and the spring holder 31 rotate relative to the drive plate 32. On the other hand, the high-rigidity spring 22 is hardly compressed due to its high rigidity. Therefore, the input-side rotating member 20 (the clutch plate 24 and the retainer plate 25) rotates integrally with the hub flange 21.

According to the above, in the first stage of the torsional characteristics, { input side rotating member 20+ hub flange 21+ first friction member 30+ spring holder 31} rotates integrally, and { drive plate 32+ spline hub 4} rotates relative to these members.

In this first stage, the first bush 51 rotates integrally with the spline hub 4, and therefore rotates relative to the first friction plate 36 rotating together with the hub flange 21. That is, frictional resistance is generated between the first bush 51 and the inner circumferential friction portion 36a of the first friction plate 36, and hysteresis torque is generated therebetween.

The second bush 65 rotates integrally with the retainer plate 25 constituting the input-side rotating member 20, and therefore rotates relative to the spline hub 4. That is, frictional resistance is generated between the second bush 65 and the spline hub 4, and hysteresis torque is generated therebetween.

< second-stage torsion Angle region H2 >)

When the transmission torque or the torque variation increases, the low stiffness spring 33 is compressed, and the input-side rotating member 20 further rotates with respect to the spline hub 4. Then, the teeth 21c of the hub flange 21 abut against the teeth 4c of the spline hub 4 (the gap G1 becomes "0"), and the hub flange 21 rotates integrally with the spline hub 4. In this state, the low rigidity spring 33 is not compressed more than in the previous state, and the first coil spring 221 in the high rigidity spring 22 starts to be compressed. More specifically, a projection 21e is formed in the first window hole 21a of the hub flange 21, and the first coil spring 221 is first compressed by the projection 21 e. Since the first coil spring 221 has higher rigidity than the low-rigidity spring 33, the second-stage torsional rigidity higher in rigidity than the first-stage torsional rigidity can be obtained.

In the second stage, since the first coil springs 221 are compressed, relative rotation is generated between the input-side rotating member 20 and the hub flange 21 (and the spline hub 4). On the other hand, the holding plate 25 rotates integrally with the second friction member 55, and the hub flange 21 rotates integrally with the first friction member 30.

Therefore, frictional resistance is generated between the second friction plate 59 integrally molded with the second friction member 55 and the hub flange 21. Further, frictional resistance is generated between the clutch plate 24 and the first friction plate 36 fixed to the first friction member 30. Further, as in the first stage, frictional resistance is generated between the second bush 65 and the spline hub 4. By these frictional resistances, a hysteresis torque is generated.

Here, in the second stage, the first friction member 30 rotating integrally with the hub flange 21 and the first bush 51 rotating integrally with the spline hub 4 do not rotate relative to each other, and no frictional resistance is generated between these members.

< third level torsion Angle region H3 >)

When the transmission torque or the torque variation further increases, the first coil spring 221 is compressed, and the end surface 21d of the first window hole 21a of the hub flange 21 abuts against the end surface of the second coil spring 222. That is, the gap G2 becomes "0". Therefore, the second coil spring 222 also starts to be compressed. Since the first coil spring 221 and the second coil spring 222 are arranged in parallel, when the second coil spring 222 starts to be compressed, the torsional rigidity is improved as compared with the case where only the first coil spring 221 is compressed (second stage). I.e. to the third stage of the torsional behaviour.

In this third stage, the relatively rotating components are identical to the second stage, producing the same hysteresis torque as the second stage. In the third stage, the first friction member 30 and the first bush 51 do not rotate relative to each other, and no frictional resistance is generated between these members, as in the second stage.

< fourth-stage torsion Angle region H4 >)

When the transmission torque or the torque fluctuation further increases, the first coil spring 221 and the second coil spring 222 are compressed, and the third coil spring 223 having a short free length starts to be compressed further. Since the first coil spring 221 and the second coil spring 222 are arranged in parallel with the third coil spring 223, when the third coil spring 223 starts to be compressed, the torsional rigidity is improved as compared with the case (third stage) where the first coil spring 221 and the second coil spring 222 are compressed. I.e. to the fourth stage of the torsional behaviour.

In the fourth stage, the relatively rotating components are the same as the second and third stages, and generate the same hysteresis torque. In the fourth stage, the first friction member 30 and the first bush 51 do not rotate relative to each other, and no frictional resistance is generated between these members, as in the second and third stages.

[ other embodiments ]

The present invention is not limited to the above-described embodiments, and various modifications and changes may be made without departing from the scope of the present invention.

(a) In the above-described embodiment, the present invention is applied to the clutch disc assembly having the four-stage torsion characteristic, but the number of stages of the torsion characteristic is not limited. The present invention can be applied to all power transmission devices having a damper device as well.

(b) In the foregoing embodiment, the first friction member 30 is constituted by the first body 35 and the first friction plate 36, but they may be formed integrally by one member.

(c) The number of divided pieces of the second friction plate 59 constituting the second friction member 55 is not limited to four pieces in the foregoing embodiment.

Claims (6)

1. A friction washer is characterized by comprising:

an annular holding member; and

and a plurality of friction members fixed to one side surface of the holding member in an annular arrangement.

2. The friction washer according to claim 1,

the plurality of friction members each have a first engaging portion at one end portion in the circumferential direction and a second engaging portion at the other end portion in the circumferential direction, the second engaging portion being engaged with the first engaging portion of an adjacent friction member.

3. The friction washer according to claim 2,

the first engaging portion is a projection projecting in the circumferential direction,

the second engaging portion is a recess recessed in the circumferential direction.

4. A friction washer according to any of claims 1 to 3,

the plurality of friction members are formed by punching a sheet member.

5. A friction washer according to any of claims 1 to 3,

the holding member is made of resin and is provided with a plurality of holding holes,

the plurality of friction members are integrated with the holding member by insert molding.

6. The friction washer according to claim 4,

the holding member is made of resin and is provided with a plurality of holding holes,

the plurality of friction members are integrated with the holding member by insert molding.

Images