阅读说明：本技术 离合器从动盘及离合器 (Clutch driven plate and clutch ) 是由 肖荣亭 周文敏 于 2019-11-22 设计创作，主要内容包括：本发明提供了一种离合器从动盘及包括该离合器从动盘的离合器。该离合器从动盘包括两个侧板以及介于两个侧板之间的一个盘毂法兰和多个主减振弹簧。多个主减振弹簧被划分为多组,每组主减振弹簧都包括彼此串联的至少两个主减振弹簧,从而使得两个侧板相对于盘毂法兰转动的最大扭转角度等于一组主减振弹簧的总压缩角度(也就是说等于一组主减振弹簧中的串联的主减振弹簧的压缩角度之和)。这样,根据本发明的离合器从动盘的各组主减振弹簧中的主减振弹簧串联配置,因而能够实现较大的扭转角度和较小的扭转刚度,进而提高了对扭振的衰减效果,提高了减振效果。(The invention provides a clutch driven disc and a clutch comprising the same. The clutch driven disc includes two side plates and a hub flange and main damper springs between the two side plates. The plurality of main damping springs are divided into groups, each group of main damping springs comprising at least two main damping springs connected in series with each other, such that the maximum torsion angle of the two side plates rotating relative to the hub flange is equal to the total compression angle of a group of main damping springs (that is to say equal to the sum of the compression angles of the main damping springs connected in series in a group of main damping springs). In this way, the main damper springs in each set of main damper springs of the clutch driven disc according to the present invention are arranged in series, so that a large torsion angle and a small torsion rigidity can be achieved, thereby improving the damping effect on torsional vibration and improving the damping effect.)

1. A clutch driven disc having an axial direction (a), a radial direction (R) and a circumferential direction (C) and comprising:

two side plates (21, 22), the two side plates (21, 22) being spaced apart in the axial direction (A) and fixed to each other, a plurality of main damper spring mounting portions being formed between the two side plates (21, 22), and one side plate (21) of the two side plates (21, 22) being for receiving torque from outside of the clutch driven disc;

a hub flange (3), the hub flange (3) being located between the two side plates (21, 22) in the axial direction (A), the two side plates (21, 22) being capable of a predetermined range of rotation in the circumferential direction (C) relative to the hub flange (3), the hub flange (3) being for transmitting torque to the outside of the clutch driven disc; and

the main damping springs (4) are divided into multiple groups, each group of the main damping springs (4) comprises at least two main damping springs (4) which are connected in series, each group of the main damping springs (4) is respectively installed on one main damping spring installation part, and in the process that the two side plates (21 and 22) transmit torque to the disc hub flange (3) through the main damping springs (4), the maximum torsion angle of the two side plates (21 and 22) rotating relative to the disc hub flange (3) is equal to the sum of the compression angles of the main damping springs (4) in one group of the main damping springs (4).

2. A clutch driven disc according to claim 1, characterized in that it further comprises a connecting flange (51), said connecting flange (51) being provided between two adjacent main damping springs (4) in each set of main damping springs (4), which connecting flange (51) connects said two adjacent main damping springs (4) in series.

3. The clutch driven disc according to claim 2, characterized in that the connecting flange (51) includes a flange body and protrusions protruding from the flange body toward both circumferential sides, the protrusions protruding into the coils of the main damper springs (4) located on both sides of the connecting flange (51), respectively.

4. The clutch driven disk according to claim 2,

the clutch driven plate further includes a guide pin (52), the guide pin (52) being mounted to the two side plates (21, 22) in such a manner as to pass through the connection flange (51), and

the two side plates (21, 22) are formed with guide holes (21h2, 22h2) corresponding to the guide pins (52) and extending along the circumferential direction (C), and both ends of the guide pins (52) are installed in the guide holes (21h2, 22h2) to be slidable along the guide holes (21h2, 22h2) so as to define a movement locus of the connecting flange (51).

5. A clutch driven disc according to any one of claims 1 to 4, characterized in that the hub flange (3) is formed with an abutment surface (32s) for abutment with an end of the main damping spring (4) during torque transmission, the abutment surface (32s) being substantially orthogonal to the central axis of the corresponding main damping spring (4).

6. The clutch driven disc according to any one of claims 1 to 4, characterized in that the two side plates (21, 22) respectively include windows (21h1, 22h1) extending along the circumferential direction (C) and opposing each other, the windows (21h1, 22h1) of the two side plates (21, 22) form the main damper spring mounting portion so that the main damper spring (4) can be mounted between the two side plates (21, 22), and the hub flange (3) is formed with a cutout portion that avoids the main damper spring (4).

7. The clutch driven disc according to any one of claims 1 to 4, characterized in that the clutch driven disc further comprises:

a friction cushioning portion (1) that is fixed to the one side plate (21) and includes a friction plate arranged along the circumferential direction (C) to be able to receive a torque from outside through the friction plate; and

a hub core (8), the hub core (8) being mounted radially inside the two side plates (21, 22) and the hub flange (3) and being drivingly coupled with the hub flange (3) to enable torque to be transmitted externally through the hub core (8).

8. The clutch driven disc according to claim 7, characterized in that the hub flange (3) is capable of a predetermined range of rotation in the circumferential direction (C) relative to the hub core (8), and

the clutch driven disc further comprises a plurality of pre-damper springs (9), the plurality of pre-damper springs (9) being mounted between the hub core (8) and the hub flange (3) such that the pre-damper springs (9) can be compressed to achieve damping when the hub flange (3) rotates relative to the hub core (8).

9. A clutch driven disc according to any of claims 1 to 4, characterized in that it further comprises a plurality of friction discs/friction sleeves (61, 62, 63, 64) arranged between the two side plates (21, 22) and the hub flange (3) and the hub core (8).

10. A clutch comprising the clutch disk of any one of claims 1 to 9.

Technical Field

The invention relates to the field of clutches of automobiles, in particular to a clutch driven disc and a clutch comprising the same.

Background

In the prior art, friction clutches are commonly used for controlled torque transfer between a power source (e.g., an engine) and a transmission of an automobile.

As shown in fig. 1a and 1b, a clutch disc of a friction clutch, which has a disc shape as a whole, includes a friction cushioning portion 10, a retaining plate 20, a cover plate 30, a hub flange 40, a plurality of main damper springs 50, and a hub core 60.

The friction cushioning portion 10 includes a friction plate and a cushioning portion assembled together by rivets, and the cushioning portion is fixed to the retaining plate 20 by rivets. Both the retainer plate 20 and the cover plate 30 are located radially inward of the friction cushioning portion 10. The retainer plate 20 is fixed with the cover plate 30. In this way, the torque from the friction cushioning portion 10 can be transmitted to both the retainer plate 20 and the cover plate 30.

The hub flange 40 is interposed between the retainer plate 20 and the cover plate 30 in the axial direction a, and is mounted in a space surrounded by the retainer plate 20 and the cover plate 30. A plurality of main damper springs 50 are arranged evenly in the circumferential direction C on a main damper spring mounting portion formed by the retainer plate 20 and the cover plate 30. When the retainer plate 20 and the cover plate 30 are rotated by torque from the friction cushioning portion 10, the retainer plate 20 and the cover plate 30 are rotated relative to the hub flange 40 such that the plurality of main damper springs 50 are compressed, and the plurality of main damper springs 50 damp torsional vibration while performing a function of transmitting torque to the hub flange 40.

The hub core 60 is disposed in the central through hole of the hub flange 40, and the hub core 60 and the hub flange 40 are coupled via spline transmission, so that torque from the friction cushioning portion 10 can be transmitted to a transmission shaft, such as an input shaft of a transmission, via the retainer plate 20 and the cover plate 30, the main damper spring 50, the hub flange 40, and the hub core 60.

In the clutch driven disc having the structure as described above, all the main damper springs 50 are straight cylindrical coil springs and the torsion angle of the hub flange 40 relative to the retainer plate 20 and the cover plate 30 is equal to the compression angle of one of the main damper springs 50, in which case the torsion angle of relative rotation between the hub flange 40 and the retainer plate 20 and the cover plate 30 depends on the compression angle of one of the main damper springs 50. Since the length of one main damping spring 50 is limited by the operating principle of the clutch driven disc in the case that the main damping spring 50 is a cylindrical coil spring, the torsion angle is small, and thus the damping effect of the clutch driven disc is poor.

Disclosure of Invention

The present invention has been made in view of the above-mentioned drawbacks of the prior art. It is an object of the present invention to provide a novel clutch driven plate which enables an improved damping effect compared to existing clutch driven plates. It is another object of the present invention to provide a clutch including the clutch disk described above.

In order to achieve the above object, the present invention adopts the following technical solutions.

The present invention provides a clutch driven disc having an axial direction, a radial direction and a circumferential direction and comprising:

two side plates spaced apart in the axial direction and fixed to each other, a plurality of main damper spring mounting portions being formed between the two side plates, and one of the two side plates for receiving torque from an outside of the clutch driven plate;

a hub flange located between the two side plates in the axial direction, the two side plates being capable of rotating relative to the hub flange in the circumferential direction for a predetermined range, the hub flange being configured to transmit torque to an outside of the clutch driven disc; and

the main damping springs are divided into multiple groups, each group of main damping springs comprises at least two main damping springs which are connected in series, each group of main damping springs is respectively installed on one main damping spring installation part, and therefore in the process that the two side plates transmit torque to the hub flange through the main damping springs, the maximum torsion angle of the two side plates rotating relative to the hub flange is equal to the sum of the compression angles of the main damping springs in one group of main damping springs.

Preferably, the clutch driven disc further includes a connecting flange, and the connecting flange is disposed between two adjacent main damping springs in each set of the main damping springs, and the connecting flange connects the two adjacent main damping springs in series.

More preferably, the connection flange includes a flange body and protrusions protruding from the flange body toward both circumferential sides, the protrusions protruding into the coils of the main damping spring located at both sides of the connection flange, respectively.

More preferably, the clutch driven plate further includes guide pins that are mounted to the two side plates in such a manner as to pass through the connection flanges, and

the two side plates are formed with guide holes corresponding to the guide pins and extending along the circumferential direction, and both ends of the guide pins are installed in the guide holes to be slidable along the guide holes, thereby defining a movement locus of the coupling flange.

More preferably, the hub flange is formed with an abutment surface for abutting against an end portion of the main damper spring during torque transmission, the abutment surface being substantially orthogonal to a central axis of the corresponding main damper spring.

More preferably, the two side plates respectively include windows extending along the circumferential direction and facing each other, the windows of the two side plates form the main damper spring mounting portion so that the main damper spring can be mounted between the two side plates, and the hub flange is formed with a cutout portion avoiding the main damper spring.

More preferably, the clutch driven plate further includes:

a friction cushioning portion fixed to the one side plate and including a friction plate arranged along the circumferential direction to be able to receive a torque from outside through the friction plate; and

a hub core mounted radially inside the two side plates and the hub flange and drivingly coupled with the hub flange to enable torque transmission externally therethrough.

More preferably, the hub flange is rotatable relative to the hub core in the circumferential direction for a predetermined range, and

the clutch driven disc further includes a plurality of pre-damper springs mounted between the hub core and the hub flange such that the pre-damper springs can be compressed to effect damping when the hub flange rotates relative to the hub core.

More preferably, the clutch driven plate further comprises a plurality of friction discs/friction sleeves disposed between the two side plates and the hub flange and the hub core.

The invention provides a clutch comprising a clutch driven plate according to any one of the above technical aspects.

By adopting the technical scheme, the invention provides a novel clutch driven disc and a clutch comprising the same. The clutch driven disc includes two side plates and a hub flange and main damper springs between the two side plates. The plurality of main damping springs are divided into groups, each group comprising at least two main damping springs connected in series with one another, so that the maximum torsion angle of the two side plates with respect to the hub flange is equal to the total compression angle of a group of main damping springs (that is to say to the sum of the compression angles of the main damping springs connected in series in a group of main damping springs). In this way, the main damper springs of the respective sets of main damper springs of the clutch disk according to the present invention are arranged in series, so that the hub flange and the side plate of the clutch disk according to the present invention can achieve a larger relative torsion angle and a smaller torsional rigidity than the clutch disk of the related art described in the above-mentioned background art, thereby improving the damping effect against torsional vibration and improving the damping effect.

Drawings

FIG. 1a is a schematic front view showing halves of a clutch driven plate; fig. 1b is a cross-sectional schematic view including a center axis, taken in an axial direction, showing the clutch driven plate in fig. 1 a.

FIG. 2a is a front view schematically showing a clutch driven plate according to an embodiment of the present invention, of which a partial structure is omitted in order to show its internal construction; FIG. 2b is a schematic diagram showing an exploded view of the clutch driven plate of FIG. 2 a; FIG. 2c is a partial cross-sectional schematic view including a central axis taken along line L1-L1 showing the clutch driven plate in FIG. 2 a; FIG. 2d is a partial cross-sectional schematic view including a central axis taken along line L2-L2 showing the clutch driven plate in FIG. 2 a; FIG. 2e is a partial cross-sectional schematic view including a central axis taken along line L3-L3 showing the clutch driven plate in FIG. 2 a.

Description of the reference numerals

10 friction cushioning portion 20 retaining plate 30 cover plate 40 hub flange 50 main damper spring 60 hub core

1 friction buffer 11 friction plate 12 friction plate rivet 13 buffer

21 first side plate 21h1 first window 21h2 first guide hole 22 second side plate 22h1 second window 22h2 second guide hole 23 connector

3 flange of hub 31 and wing 32s of flange body 32

4 main damping spring

51 attachment flange 52 guide pin 53 spacer

61 a first friction disk 62, a first friction sleeve 63, a second friction disk 64, and a second friction sleeve

71 first diaphragm spring 72 second diaphragm spring

8 hub core

9 Pre-damping spring

R is radial A to axial C.

Detailed Description

Exemplary embodiments of the present invention are described below with reference to the accompanying drawings. It should be understood that the detailed description is intended only to teach one skilled in the art how to practice the invention, and is not intended to be exhaustive or to limit the scope of the invention.

In the present invention, axial, radial and circumferential directions refer to axial, radial and circumferential directions of the clutch driven plate, respectively, unless otherwise specified. The axial side refers to the left side in fig. 2c to 2e, for example the side on which the engine is located; the other axial side is the right side in fig. 2c to 2e, for example the side on which the transmission is located. The radially outer side refers to a side distant from the central axis in the radial direction (upper side in fig. 2c to 2 e), and the radially inner side refers to a side close to the central axis in the radial direction (lower side in fig. 2c to 2 e). Additionally, "drive coupled" means that drive force and torque can be transmitted directly or indirectly between two components/parts.

The structure of a clutch driven plate according to an embodiment of the present invention will be described below with reference to the accompanying drawings.

As shown in fig. 2a to 2e, the clutch driven plate according to an embodiment of the present invention has a disk shape as a whole and includes a friction cushioning portion 1, two side plates (a first side plate 21 and a second side plate 22), a plurality of coupling pieces 23, a hub flange 3, a plurality of (four in this embodiment) main damper springs 4, a coupling flange 51, a guide pin 52, a spacer 53, a plurality of friction disks/friction sleeves (a first friction disk 61, a first friction sleeve 62, a second friction disk 63, a second friction sleeve 64), a plurality of diaphragm springs (a first diaphragm spring 71, a second diaphragm spring 72), a hub core 8, and a plurality of (two in this embodiment) pre-damper springs 9, which are assembled with each other.

Specifically, in the present embodiment, the friction cushioning portion 1 includes a friction plate 11 and a cushioning portion 13 assembled together by friction plate rivets 12, and the cushioning portion 13 is fixed to the first side plate 21 by rivets. The buffer 13 may be, for example, a corrugated sheet. Thus, torque from a drive source such as an engine can be smoothly transmitted to the first side plate 21 via the friction cushioning portion 1.

Further, in the present embodiment, the two side plates 21, 22 include a first side plate 21 on one axial side and a second side plate 22 on the other axial side. The two side plates 21, 22 are fixedly connected coaxially to each other via the hub flange 3 by four connecting pieces 23. The torque from the friction cushioning portion 1 can drive the two side plates 21, 22 to rotate together, the two side plates 21, 22 as a whole can rotate in the circumferential direction C by a predetermined range relative to the hub flange 3, and the two side plates 21, 22 form a main damper spring mounting portion to define the position of the corresponding main damper spring 4.

The first side plate 21 includes two first windows 21h1 corresponding to the main damper springs 4 that penetrate the first side plate 21 in the axial direction a, and the second side plate 22 includes two second windows 22h1 corresponding to the main damper springs 4 that penetrate the second side plate 22 in the axial direction a. The first windows 21h1 and the second windows 22h1 are disposed opposite to each other in the axial direction a and the first windows 21h1 and the second windows 22h1 each extend a predetermined length in the circumferential direction C, and the positions of the respective main damper springs 4 can be defined by the peripheral edges of the first windows 21h1 and the peripheral edges of the second windows 22h1, thereby forming main damper spring mount portions. Thus, the position of the main damper spring 4 in the axial direction a, the radial direction R, and the circumferential direction C can be defined by this main damper spring mounting portion.

In addition, the first side plate 21 further includes two first guide holes 21h2 corresponding to the guide pins 52 that penetrate the first side plate 21 in the axial direction a, and the second side plate 22 further includes two second guide holes 22h2 corresponding to the guide pins 52 that penetrate the second side plate 22 in the axial direction a. The first guide hole 21h2 and the second guide hole 22h2 are disposed opposite to each other in the axial direction a and the first guide hole 21h2 and the second guide hole 22h2 each extend in the circumferential direction C. The circumferential length of the first guide hole 21h2 is smaller than the circumferential length of the first window 21h1, and the circumferential length of the second guide hole 22h2 is smaller than the circumferential length of the second window 22h 1. The two first guide holes 21h2 are located radially inward of the corresponding first windows 21h1 and spaced apart from the first windows 21h1, respectively, and the circumferential center lines of the two first guide holes 21h2 are aligned with the circumferential center lines of the corresponding first windows 21h1, respectively. The two second guide holes 22h2 are located radially inward of the corresponding second windows 22h1 and spaced apart from the second windows 22h1, respectively, and the circumferential center lines of the two second guide holes 22h2 are aligned with the circumferential center lines of the corresponding second windows 22h1, respectively.

Further, in the present embodiment, the hub flange 3 is located between the two side plates 21, 22 in the axial direction a, and the two side plates 21, 22 are rotatable in the circumferential direction C relative to the hub flange 3 by a predetermined range. The hub flange 3 includes a flange body 31 at the center and two wings 32 protruding from the flange body 31 toward both sides. Both circumferential side surfaces of the two wing portions 32 are formed as abutment surfaces 32s for abutting against the end portions of the main damper spring 4 during torque transmission, the abutment surfaces 32s being substantially orthogonal to the central axis of the corresponding main damper spring 4 in the form of a cylindrical coil spring. When the clutch driven disc is completely mounted, it is necessary that two wing portions 32 are alternately arranged with two sets of main damper springs 4 in the circumferential direction C, and therefore the hub flange 3 is formed with cutout portions that avoid the main damper spring mounting portions, the two cutout portions being alternately arranged with the two wing portions 32 in the circumferential direction C. In addition, the central through hole of the flange body 31 is formed with an internal spline for engagement with the external spline of the hub 8.

Further, in the present embodiment, the four main damper springs 4 are all linear cylindrical coil springs. The four main damper springs 4 are divided into two groups, each group of main damper springs 4 including two main damper springs 4 connected in series with each other via a connecting flange 51. Each set of main damping springs 4 is mounted on a main damping spring mounting portion, so that during the process of transmitting torque from the two side plates 21 and 22 to the hub flange 3 via the main damping springs 4, the maximum torsion angle of the two side plates 21 and 22 relative to the hub flange 3 is equal to the total compression angle of the set of main damping springs 4 (i.e., the sum of the compression angles of the two main damping springs 4).

Further, in the present embodiment, one connecting flange 51 is provided between adjacent two main damper springs 4 in each set of main damper springs 4. The connecting flange 51 includes a flange body and two protrusions protruding from the flange body toward both sides in the circumferential direction, the two protrusions protruding into the coils of the main damper spring 4 located on both sides of the connecting flange 51, respectively. Therefore, first, the connecting flange 51 enables the series arrangement of two adjacent main damper springs 4; secondly, the connecting flange 51 can achieve a certain radial limiting effect on the main damper springs 4 located at both sides thereof, so as to suppress possible radial play of the compressed main damper springs 4 under the action of centrifugal force in the main damper spring mounting portion formed by the first windows 21h1 and the second windows 22h1 of the two side plates 21, 22; again, the two convex portions of the connecting flange 51 are formed to have a predetermined included angle, so that the two main damper springs 4 of the set of main damper springs 4 are arranged in the main damper spring mounting portion in such a manner that their central axes form a predetermined included angle, thereby avoiding interference that may occur between the two main damper springs 4 in direct series and avoiding interference that may occur with the two side plates 21, 22 due to deformation of the main damper springs 4 during compression to the maximum extent.

Further, in the present embodiment, the guide pin 52 is attached to the two side plates 21, 22 so as to pass through the connection flange 51. The connecting flange 51 is rotatable with respect to the guide pin 52, and both ends of the guide pin 52 are fitted in the guide holes 21h2, 22h2 of the two side plates 21, 22 to be slidable along the guide holes 21h2, 22h 2. Thus, when the two main damping springs 4 connected by the connecting flange 51 are compressed, the guide pin 52 and the guide holes 21h2 and 22h2 can guide the movement of the connecting flange 51, thereby defining the movement track of the connecting flange 51 and further avoiding the main damping springs 4 from interfering with the two side plates 21 and 22 to the greatest extent during the compression process.

Further, in the present embodiment, two spacers 53 are externally fitted on the guide pin 52, the two spacers 53 being located on both sides of the connecting flange 51 between the connecting flange 51 and the two side plates 21, 22, so that the guide pin 52 is prevented from rattling in the axial direction a while defining the relative positions of the connecting flange 51 and the two side plates 21, 22 in the axial direction a.

Further, in the present embodiment, in order to provide a proper damping action while limiting the hub flange 3, the hub core 8, and the two side plates 21, 22 in the axial direction a, two friction disks 61 and 63, two friction sleeves 62 and 64, and two diaphragm springs 71 and 72 are provided.

Specifically, the first friction disk 61 extends in the radial direction R and is disposed between the first side plate 21 and the hub flange 3 in the axial direction a.

The first diaphragm spring 71 is fixed to the first side plate 21 and abuts against the first friction disk 61 from the axial side so that the first friction disk 61 abuts against the hub flange 3.

A radial portion of the first friction sleeve 62 extending in the radial direction R is provided between the first side plate 21 and the hub 8 in the axial direction a, an axial portion of the first friction sleeve 62 extending in the axial direction a is provided between the first side plate 21 and the hub 8 in the radial direction R, the first side plate 21 abuts against the axial portion from the radially outer side and the axial portion abuts against the hub 8 from the radially outer side.

The second diaphragm spring 72 is fixed to the first side plate 21 and abuts against a radial portion of the first friction sleeve 62 from the axial side so that the radial portion abuts against the hub 8.

The second friction disk 63 extends in the radial direction R and is disposed between the hub flange 3 and the second side plate 22 in the axial direction a, and the second friction disk 63 abuts against the hub flange 3 and the second side plate 22 under the spring force of the first diaphragm spring 71.

The second friction sleeve 64 includes an annular main body portion and a projecting portion projecting from the main body portion toward one side in the axial direction. The body portion is located between the hub core 8 and the second side plate 22 in the axial direction a and abuts against the hub core 8 and the second side plate 22, and the extension portion extends through the external spline of the hub core 8 and is mainly used for axially and circumferentially limiting the pre-damper spring 9.

Further, in the present embodiment, the hub core 8 is formed with internal and external splines. The hub core 8 can be splined by its external splines to the internal splines of the hub flange 3, and the hub core 8 can be splined by its internal splines to a drive shaft, such as an input shaft of a transmission. Via the hub core 8, the hub flange 3 can be drivingly coupled with a drive shaft, for example an input shaft of a transmission. In the initial state shown in fig. 2a (with both the main damper springs 4 and the pre-damper springs 9 uncompressed), the hub flange 3 is able to rotate in the circumferential direction C for a predetermined range relative to the hub 8, so that during this relative rotation the pre-damper springs 9 are compressed and perform the damping function.

Further, in the present embodiment, both the pre-damper springs 9 are linear cylindrical coil springs. Two pre-damper springs 9 are provided at 180 degrees apart in the circumferential direction C at pre-damper spring mounting portions formed between the hub core 8 and the hub flange 3, so that the pre-damper springs 9 are compressed during relative rotation of the hub flange 3 with respect to the hub core 8.

By adopting the above technical means, the torque from the friction cushioning portion 1 is transmitted in the following order: friction cushioning portion 1 → two side plates 21, 22 → main damper spring 4 → hub flange 3, and then transmitted to hub core 8 via pre-damper spring 9 or directly to hub core 8. The main damper springs 4 of each group of main damper springs 4, which are arranged in series, are compressed together during the above-described torque transmission, so that the relative rotational angle of the two side plates 21, 22 with respect to the hub flange 3 is equal to the sum of the compression angles of the main damper springs 4 in series. Thus, the vibration damping effect of the clutch driven plate can be improved.

In addition to providing the clutch driven plate having the above-described structure, the present invention also provides a clutch including the clutch driven plate.

It should be understood that the above embodiments are only exemplary and are not intended to limit the present invention. Various modifications and alterations of the above-described embodiments may be made by those skilled in the art in light of the teachings of the present invention without departing from the scope thereof. In addition, the following supplementary explanation is entered.

(i) Although it has been described in the above embodiment that the pre-damper spring 9 and the main damper spring 4 connected in series with each other are both straight cylindrical coil springs, the present invention is not limited thereto. For example, the pre-damper spring 9 and the main damper spring 4 may also be arc-shaped coil springs; it may also be a rubber spring, or a combination or combination of a coil spring and a rubber spring.

(ii) Although not described in the above embodiment, it is understood that the abutment surface 32s of the hub flange 3 may be formed as a convex portion protruding into the turn of the main damper spring 4 in order to secure the running locus of the main damper spring 4 when compressed by the hub flange 3 and further suppress the radial play of the compressed main damper spring 4 that may occur in the main damper spring mounting portion.

(iii) Although the total number of the main damper springs 4 is four in the above embodiment, the present invention is not limited thereto. The total number of main damping springs 4 may also be six, etc. The number of the group of main damper springs 4 is also not limited to two, and may be three or more, and one connecting flange 51 is provided between adjacent main damper springs 4 of the group of main damper springs 4.

Although not specifically described in the above embodiment, each main damper spring 4 in the form of a cylindrical coil spring should be housed in the main damper spring mounting portion as described above in such a manner that the longitudinal direction thereof coincides with the direction of one tangent line to the circumferential direction C of the clutch driven plate.

(iv) In addition, the main damping springs in the clutch driven disc according to the present invention employ cylindrical coil springs connected in series with each other, so that the clutch driven disc according to the present invention not only achieves substantially the same relative torsion angle as the clutch driven disc employing the long-arc-shaped coil springs, but also saves costs.