JPH11173380A - Damper disc assembly - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress the jumping phenomenon between a first step and a second step of twisting characteristic. SOLUTION: A clutch disc assembly 1 is provided with an output rotary body 4, an intermediate member 3, a first spring 7, a damper 8, plates 12, 13, and a third spring 5. The intermediate member 3 is arranged on an outer peripheral side of the output rotary body 4. The first spring 7 is arranged between the output rotary body 4 and the intermediate member 3 and is compressed in the circumferential direction when a hub and the intermediate member 3 rotate relatively. The damper 8 is arranged between the output rotary body 4 and the intermediate member 3 and has a second spring 10 which is not compressed in a zone where a twisting angle is small in operation twisting angle of the first spring 7 but is elastically compressed in the circumferential direction in a zone where a twisting angle is large. The plates 12, 13 are arranged on an axial direction side of the intermediate member 3. The third spring 5 connects the intermediate member 3 with the plates 12, 13 elastically in the circumferential direction.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a damper disk assembly, and more particularly to a damper disk assembly for transmitting torque and absorbing and attenuating torsional vibration.

[0002]

2. Description of the Related Art A clutch disk assembly used for a vehicle clutch has a clutch function for connecting and disconnecting to and from a flywheel, and a damper function for attenuating torsional vibration. The clutch disk assembly
A clutch connecting portion, an input side plate fixed to the clutch connecting portion, a hub disposed on the inner peripheral side of the input side plate, and an elasticity for elastically connecting the flange of the hub and the input side plate in a circumferential direction. And a member. When the clutch connecting portion is biased by the flywheel, torque is input from the flywheel. The torque is transmitted to the hub via the elastic member, and is output to a shaft extending from the transmission. When torque fluctuations from the engine are input to the clutch disk assembly, relative rotation occurs between the input side plate and the hub, and the elastic member is compressed in the circumferential direction. The clutch disk assembly further includes a friction mechanism for generating frictional resistance between the input side plate and the hub when the two members rotate relative to each other. The friction mechanism includes a plurality of washers, urging members, and the like.

The separated hub type clutch disk assembly is one in which a flange is separated from a hub to be an intermediate member, and the hub and the intermediate member are circumferentially connected by a low-rigidity elastic member. In this clutch disk assembly, the torsion angle between the input side plate and the hub increases, and
Step characteristics (low rigidity / high rigidity) can be obtained.

[0004]

In a torsional vibration system composed of a clutch disk assembly and a transmission, a gear pair of the transmission continuously collides due to steady rotation fluctuations of the engine and generates rattling noise. . In order to reduce the torsional vibration that causes the rattling noise in the clutch disk assembly, it is necessary to reduce the spring constant of the first-stage low-rigidity elastic member. On the other hand, in order to attenuate torsional vibration having a large displacement angle such as low frequency vibration, the spring constant of the elastic member functioning in the second stage must be increased. In a conventional device having such characteristics, for example, when a torque variation is input during idling, a jumping phenomenon occurs in which the operating angle extends from the first stage region to the second stage region. The jumping phenomenon is a phenomenon in which the transmission inertia is caught and ball between the second-stage elastic member having the torsion characteristic of the clutch disk assembly. Much larger than that.

It is an object of the present invention to provide the first and second torsion characteristics.
The object is to suppress a jumping phenomenon between the steps.

[0006]

According to a first aspect of the present invention, there is provided a damper disk assembly comprising a hub, a first disk-shaped member, a first elastic member, a damper, a second disk-shaped member, and a third elastic member. Have. The first disc-shaped member is arranged on the outer peripheral side of the hub. The first elastic member is disposed between the hub and the first disk-shaped member, and is compressed in a circumferential direction when the hub and the first disk-shaped member rotate relative to each other. The damper is disposed between the hub and the first disk-shaped member, and is not compressed in a small torsion angle region within a working torsion angle of the first elastic member and is circular in a large torsion angle region. A second elastic member elastically compressed in a circumferential direction; The third elastic member elastically connects the first disk-shaped member and the second disk-shaped member in a circumferential direction. The second disk-shaped member is arranged on the axial direction side of the first disk-shaped member.

In this damper disk assembly, when the hub and the second disk-shaped member rotate relative to each other, the first elastic member moves between the hub and the first disk-shaped member in a region where the torsion angle is small. It is compressed in the circumferential direction. When the torsion angle increases, the second elastic member is compressed in the circumferential direction between the hub and the first disk-shaped member, and high rigidity characteristics can be obtained. When the torsion angle is further increased, the third elastic member is eventually compressed in the circumferential direction between the first and second disk-shaped members, and higher rigidity is obtained. In this damper disk assembly, the second elastic member is provided between the first elastic member and the third elastic member.
Since an intermediate rigidity in which the elastic member acts is obtained, a jumping phenomenon due to vibration during idling is less likely to occur.

According to a second aspect of the present invention, in the damper disk assembly according to the first aspect, the damper is engaged with the second elastic member and has a first torsional angular clearance in a circumferential direction between the damper disk and the hub. Further comprising an intermediate member. In this damper disk assembly, when the first elastic member is compressed by the first torsion angle, the second elastic member comes into contact with the intermediate member, and thereafter, the second elastic member is compressed in the circumferential direction. .

According to a third aspect of the present invention, in the damper disk assembly according to the second aspect, the second disk-shaped member supports both ends of the second elastic member in the circumferential direction, and the intermediate member has a circumference of the second elastic member. It supports both ends in the direction. The intermediate member has a first torsion angle gap in the circumferential direction between the intermediate member and the hub. Claim 4
In the damper disk assembly according to the third aspect, a second torsional angle gap larger than the first torsional angle gap is formed between the hub and the first disk-shaped member in the circumferential direction. ing.

In this damper disk assembly, when the torsion angle between the hub and the second disk-shaped member exceeds the second torsion angle, the compression of the second elastic member is stopped, and thereafter the third elastic member is stopped. The member is compressed between the intermediate member and the second disk-shaped member. In this damper disk assembly, the compression of the second elastic member is stopped at the third stage, so that the second elastic member is unlikely to be damaged.

According to a fifth aspect of the present invention, in the second aspect, the hub has a plurality of first teeth extending outward. The intermediate member includes a plurality of second members arranged at a first torsion angle gap circumferentially with respect to the first teeth.
It has teeth on its inner periphery. The first disk-shaped member has a plurality of third teeth arranged on the inner peripheral edge of the first teeth with a second torsion angle gap in the circumferential direction. The second torsion angle gap is larger than the first torsion angle gap.

In this damper disk assembly, the stopper between the hub and the intermediate member is formed by the first and second stoppers.
The teeth and the second teeth, and the stopper between the hub and the first disk-shaped member includes first and third teeth, respectively. Here, the structure is simple because the stopper portion is composed of a plurality of teeth that abut in the circumferential direction. In the damper disk assembly according to the sixth aspect, in the fifth aspect, the intermediate member has a plate shape and extends radially outward from the annular portion and engages with both circumferential ends of the second elastic member. Joint part,
A plurality of second teeth extending radially inward from the annular portion.

In this damper disk assembly, the intermediate member has a plate shape and each part is bent, so that the shape is simple. In the damper disk assembly according to claim 7, in any one of claims 1 to 6, the second elastic members are arranged in the axial direction so as to act in parallel between the intermediate member and the first disk-shaped member. Consists of a pair of springs arranged at.

In this damper disk assembly, since the second elastic member is formed of a pair of springs arranged in the axial direction, a relatively large rigidity can be obtained in the second stage.

[0015]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS First Embodiment FIGS. 1 and 2 show a clutch disk assembly 1 as one embodiment of the present invention. The clutch disk assembly 1 is used for a vehicle clutch. A flywheel (not shown) is arranged on the left side of the clutch disc assembly 1 in FIG. 1, and a transmission (not shown) is arranged on the right side in FIG. Hereinafter, the left side of FIG. 1 is referred to as a first axial direction side, and the right side of FIG. 1 is referred to as a second axial direction side. OO in FIG. 1 is a rotation axis of the clutch disk assembly 1. The rotation direction R1 shown in FIG. 2 is the rotation direction of the flywheel and clutch disc assembly 1, and the rotation direction R2 is the opposite direction.

The clutch disc assembly 1 mainly includes an input rotating body 2, an intermediate body 3, an output rotating body 4, and a third spring 5
, A fourth spring 6, a second spring 10, and a damper 8. The input rotating body 2 is a member to which torque is input from a flywheel (not shown). The output rotator 4 is a hub in this embodiment, and is engaged with a shaft (not shown) extending from a transmission (not shown) so as to be relatively non-rotatable and axially movable.
The intermediate body 3 is a member disposed between the input rotator 2 and the output rotator 4. The third spring 5 and the fourth spring 6 are members for elastically connecting the input rotary body 2 and the intermediate rotary body in the circumferential direction. The first spring 7 is a member for elastically connecting the intermediate body 3 and the output rotating body 4 in the circumferential direction. The damper 8 is a mechanism arranged between the output rotating body 4 and the intermediate body 3 in parallel with the first spring 7.

Next, each structure of the clutch disk assembly 1 will be described in detail. The input rotator 2 includes a friction portion 11
(Clutch disc), the first plate 12 and the second plate 13. The friction part 11 is an annular member arranged near the friction surface of the flywheel.
The friction portion 11 mainly includes a pair of facings and a cushioning plate.

The first plate 12 and the second plate 13 are disk-shaped or ring-shaped plate members, and are separated from each other by a predetermined axial distance. The outer peripheral portions of the first plate 12 and the second plate 13 are fixed to each other by a plurality of pins 15 arranged in a circumferential direction. Thereby, the first
The axial distance between the plate 12 and the second plate 13 is determined, and the plates 12 and 13 rotate integrally. A cushioning plate is fixed to the outer peripheral portion of the first plate 12 with a plurality of rivets 14.

The first plate 12 has a plurality of first storage portions 19 formed at regular intervals in the circumferential direction. The first housing portion 19 is a portion slightly swelled in the axial direction, and has first contact portions 20 on both sides in the circumferential direction. The first contact portions 20 are circumferentially opposed to each other. Also, the first plate 1
2, a plurality of second storage portions 21 arranged in the circumferential direction are formed. The second accommodating portion 21 has a shape slightly bulging toward the first axial direction, and has second contact portions 22 on both sides in the circumferential direction. The second contact portions 22 face each other in the circumferential direction.

The second plate 13 has a plurality of first storage portions 23 formed at equal intervals in the circumferential direction. The first accommodating portion 23 is formed corresponding to the first accommodating portion 19, and has first contact portions 24 on both circumferential sides. The second plate 13 is further formed with a plurality of second housing portions 25 arranged in the circumferential direction. The second accommodating portion 25 corresponds to the second accommodating portion 21 and has second abutting portions 26 on both circumferential sides. The first storage sections 19 and 23 are
The length in the circumferential direction and in the radial direction is longer than that of No. 25.

An annular bush 16 is disposed on the inner peripheral edge of the first plate 12. The bush 16 is rotatably supported on the outer peripheral surface of the hub 56 of the output rotating body 4. Thus, the input rotator 2 and the output rotator 4 are positioned in the radial direction. The bush 16 has a flange 57 described later.
And the outer peripheral teeth 58 are in contact with the first axial side surface. The intermediate body 3 is a disc-shaped or annular member disposed between the first plate 12 and the second plate 13 in the axial direction. Intermediate 3
Is thicker in the axial direction than the first and second plates 12 and 13. As shown in FIG. 2, a first window hole 29 extending in the circumferential direction is formed in the intermediate body 3. First
The window hole 29 is provided in the first accommodating portion 19,2 of the plate 12,13.
3 is supported. Further, the intermediate body 3 has a plurality of second window holes 30 arranged in the circumferential direction. The second window hole 30 corresponds to the second housing portions 21 and 25.

The third spring 5 is housed in the first window hole 29. As is clear from FIG. 2, the third spring 5 is a coil spring formed by combining large and small coil springs 5a and 5b. Both ends in the circumferential direction of the third spring 5 are in contact with both ends in the circumferential direction of the first window hole 29 and the first contact portions 20 and 24 of the plates 12 and 13. The third spring 5 is restricted from moving outward in the radial direction and outward in the axial direction by the housing portions 19 and 23.

The fourth spring 6 is arranged in the second window hole 30. The fourth spring 6 is a coil spring as is clear from FIG. Both ends of the fourth spring 6 in the circumferential direction are the second ends.
It is in contact with both circumferential ends of the window hole 30. Between the circumferential ends of the fourth spring 6 and the contact portions 22 and 26, a gap having a twist angle θ ₃ −θ ₂ is secured. A plurality of notches 69 are formed on the outer peripheral edge of the intermediate body 3 in the circumferential direction. The notch 69 extends long in the circumferential direction, and the pin 15 extends between the notches 69. A fourth torsion angle θ ₄ − is provided between the pin 15 and both circumferential ends of the notch 69.
clearance only theta ₂ is secured respectively in the circumferential direction on both sides.

A third window hole 31 is formed in the intermediate body 3 between the adjacent first window holes 29 on the inner peripheral side of the second window hole 30. The third window hole 31 has a substantially rectangular shape that extends long in the circumferential direction. A cylindrical portion 17 extending in the first axial direction is formed on the inner peripheral portion of the intermediate body 3. A plurality of second inner peripheral teeth 70 extending inward in the radial direction are formed in the cylindrical portion 17. An R1 side surface 7 is provided on the rotation direction R1 side of the second inner peripheral tooth 70.
1, and an R2 side surface 72 is formed on the R2 side.

The output rotator 4 is mainly composed of a cylindrical boss 56 extending in the axial direction. Boss 56 is plate 1
2, 13 extend into the central hole. A plurality of spline grooves 64 are formed in the inner peripheral hole of the boss 56. Boss 56
Is formed with a flange 57 extending outward in the radial direction. The flange 57 corresponds to the cylindrical portion 17 of the intermediate body 3. The flange 57 is formed with a plurality of outer teeth 58 extending radially outward. Outer teeth 58 are second inner teeth 70
, And has a gap at a predetermined angle on both sides in the circumferential direction. An R1 side surface 59 is formed on the rotation direction R1 side of the outer peripheral tooth 58, and an R2 side surface 60 is formed on the R2 side. Notches 62 are formed on the outer peripheral edge of the outer peripheral teeth 58 at two positions corresponding to the radial direction. Contact portions 63 are formed on both sides of the notch 62.

Next, the damper 8 will be described in detail. The damper 8 mainly includes a plate 9 and a second spring 10. The plate 9 is an annular member as shown in FIG. 3, and is disposed between the first plate 12 and the intermediate body 3. The plate 9 mainly includes the annular portion 34 and the engagement portion 3.
And 5. A plurality of first inner peripheral teeth 39 extending radially inward are formed on the inner peripheral edge of the annular portion 34. The first inner peripheral teeth 39 correspond to the plurality of second inner peripheral teeth 70 and overlap in the axial direction. The first inner peripheral teeth 39 are wider in the circumferential direction than the second inner peripheral teeth 70, and extend on both circumferential sides from the second inner peripheral teeth 70. Also, the first inner peripheral teeth 39
Are inserted between the outer teeth 58 so as to be able to abut against the outer teeth 58 in the circumferential direction. An R1 side surface 40 is formed on the rotation direction R1 side of the first inner peripheral tooth 39, and an R1 side surface is formed on the R2 side.
Two side surfaces 41 are formed.

The outer teeth 58 and the first inner teeth 3 on both sides in the circumferential direction.
9, a gap having a first torsion angle θ ₁ is secured. Specifically, between the R1 side surface 59 of the outer peripheral tooth 58 and the R2 side surface 41 of the first inner peripheral tooth 39, and between the R2 side surface 60 of the outer peripheral tooth 58 and the R1 side surface 40 of the first inner peripheral tooth 39, between the first torsion angle theta ₁ only gap is ensured.

The outer teeth 58 and the second inner teeth 7 on both sides in the circumferential direction.
0 second torsion angle theta ₂ of the gap is formed between the. In other words, the second between the R1 side surface 59 of the outer peripheral tooth 58 and the R2 side surface 72 of the second inner peripheral tooth 70 and the R2 side surface 60 of the outer peripheral tooth 58 and the R1 side surface 71 of the second inner peripheral tooth 70, respectively. A gap having a torsion angle θ ₂ is formed. Outer teeth 5
8, the second torsion angle θ
₂ is larger than the first torsion angle θ ₁ . 1st torsion angle θ
_The R2 side is larger than the R1 side when viewed from _one outer peripheral tooth 58. Second
Torsion angle theta ₂ is greater than R2 side is R1 side when viewed from the outer teeth 58.

Further, the fourth torsion angle theta ₄ described above greater than the third torsion angle theta _3, third torsion angle theta ₃ and 4
Each of the torsion angles θ ₄ is greater than the second torsion angle θ ₂ . The inner peripheral portion of the plate 9 is sandwiched between the bush 16 and the cylindrical portion 17 in the axial direction. A friction washer 92 is disposed between the annular portion 34 of the plate 9 and the engine-side end surface of the tubular portion 17. This is a member for generating frictional resistance between the plate 9 and the intermediate rotating body 3 when they rotate relative to each other. The friction washer 92 has a high friction coefficient similarly to the second friction member 76 described later, and is sandwiched between the plate 9 and the cylindrical portion 17 by a biasing member 77 described later.

The engaging portion 35 is a portion for supporting the second spring 10, and is mainly composed of a projecting portion 36, a contact portion 37 and a pressing portion 38. A plurality of projecting portions 36 are formed, and project radially outward from the annular portion 34. The contact portions 37 extend in the axial direction from both circumferential ends of the projecting portion 36. The pressing portion 38 extends in the axial direction from a radially outer edge of the projecting portion 36. The contact portion 37 and the pressing portion 38 are bent from the projecting portion 36 and extend to the vicinity of the intermediate body 3. Thus, in the engaging portion 35, a predetermined space is formed by the projecting portion 36, the contact portion 37, and the pressing portion 38. This space is the third of intermediate 3
It corresponds to the window hole 31.

A pair of seats 46 and a pair of second springs 10 are disposed in the third window hole 31 and the engagement portion 35, respectively. The second spring 10 is a coil spring as is apparent from FIG. 4, and is arranged side by side in the axial direction. One of the second springs 10 is housed in the engagement portion 35, and the other of the second spring 10 is arranged in the third window 31.

The seat 46 is a member for supporting both ends in the circumferential direction of the pair of second springs 10 and for positioning the pair of second springs 10 in the axial direction. The seat 46 has a rectangular main body 48 extending in the axial direction. Body 48
Are in contact with both circumferential ends of each second spring 10. Further, the outer periphery of the main body 48 of each sheet 46 in the circumferential direction is supported by the engaging portion 35 and the third window hole 31. Sheet 46
The insertion portion 4 extending from the main body 48 into each second spring 10 is provided.
9 are formed. The insertion portion 49 allows the second spring 10
Is inseparable from the seat 46 and is positioned in the axial direction. Therefore, the pair of second springs 10 does not easily interfere with each other in the axial direction.

The cap 51 is a member that engages with the intermediate body 3 and supports the pair of second springs 10 and the pair of seats 46 in the second axial direction. The cap 51 is a member made of a plate as is apparent from the drawing. Cap 5
1 is a second pair of the second springs 10 and the pair of seats 46.
A pressing portion 52 that supports the axial direction side, a first axial direction side extending from the pressing portion 52, and both sides in the circumferential direction of the third window hole 31, that is, the circumferential ends of the third window hole 31 and the circle of the sheet 46. An engaging portion 53 extends between the outer circumferential surface and the engaging portion 53, and a locking portion 54 that extends from the engaging portion 53 to both sides in the circumferential direction and contacts the first axial side surface of the intermediate body 3. The cap 51 cannot be removed from the intermediate body 3 in the first axial direction by the locking portion 54. As a result, the cap 51 is
2, the movement of the pair of second springs 10 and the pair of seats 46 in the second axial direction is restricted.

The first friction member 74 is provided on the second side of the flange 57.
An annular member that abuts on the axial side surface. The first friction member 74 is fixed to the flange 5 by a first urging member 75 disposed between the first friction member 74 and the inner peripheral portion of the second plate 13.
It is urged to the 7 side. The second friction member 76 is used for the intermediate 3
Is an annular member that contacts the inner peripheral portion of the second axial side surface.
The second friction member 76 is urged toward the intermediate body 3 by a second urging member 77 disposed between the second friction member 76 and the inner peripheral portion of the second plate 13. The second friction member 76
It has a locking arm 78 that engages with the second plate 13 so that it cannot rotate relatively. Further, the first friction member 74 and the second friction member 76 are engaged with each other so as to be relatively non-rotatable in the circumferential direction and movably in the axial direction. That is, the first friction member 74 and the second friction member 76
It rotates integrally with 2 and 13. The frictional resistance generated between the first frictional member 74 and the flange 57 is set to be smaller than the frictional resistance generated between the second frictional member 76 and the intermediate body 3.

When the springs are arranged in order from the one with the smallest spring constant to the one with the largest spring constant, the order of the first spring 7, the second spring 10, the third spring 5, and the fourth spring 6 is as follows. Damper 8 is an intermediate 3
And the output rotary member 4 can be mounted from the first axial direction side. That is, the cap 51, the pair of sheets 46 and the pair of second springs 10 are previously mounted on the plate 9, and in this state, the cap 51 and other parts are placed in the third window hole 31 of the intermediate body 3. insert.

FIG. 6 is a mechanical circuit diagram of the damper mechanism of the clutch disk assembly 1. This figure shows the relationship of each member in the torsional operation of the damper in one direction. As is apparent from the figure, even if the damper 8 is not mounted in the clutch disk assembly 1, the clutch disk assembly 1 is established and performs at least the same operation as the conventional one. That is, the clutch disc assembly 1
Can be manufactured with or without the damper 8 according to the required characteristics.

The torque transmitting operation of the clutch disk assembly 1 will be described. When the friction portion 11 of the input rotator 2 is pressed against a flywheel (not shown), torque is input to the clutch disc assembly 1. The torque is transmitted from the first and second plates 12 and 13 in the order of the third spring 5, the intermediate rotating body 3, the pair of second springs 10, and the output rotating body 4. The output rotator 4 outputs torque to a shaft (not shown) extending from a transmission (not shown).

When torque fluctuations from the engine are input to the clutch disk assembly 1, torsional vibration, that is, relative rotation occurs between the input rotary body 2 and the output rotary body 4, and the third rotation occurs.
The spring 5, the fourth spring 6, the second spring 10, and the first spring 7 are compressed. Next, the torsional operation of the clutch disk assembly 1 will be described with reference to the torsional characteristic diagram of FIG.
Here, a description will be given as an operation in which the input rotator 2 is fixed to another device, and the output rotator 4 is twisted in the rotation direction R2 side. Until the first torsion angle θ ₁ until the outer teeth 58 and the first inner teeth 39 come into contact with each other, the first spring 7 is mainly compressed in the circumferential direction, and low rigidity characteristics are obtained. Here, a small frictional resistance is generated between the first friction member 74 and the flange 57 of the output rotator 4. Subsequently, when the first torsion angle θ ₁ is reached, the outer teeth 58 and the first inner teeth 3
The first spring 7 and a pair of second springs 10 are compressed in parallel between the output rotary body 4 and the intermediate body 3 during the torsion angle θ ₁ to θ _2. You. Here, since the pair of second springs 10 arranged in the axial direction are compressed, relatively high rigidity can be obtained. Further, between the torsion angles θ ₁ and θ ₂ , the friction washer 92 slides between the plate 9 and the intermediate body 3 to generate a large frictional resistance. Thus, regions of medium stiffness and high hysteresis torque can be obtained between or intermediate the area of the twist angle theta ₁ to theta _2. When the second torsion angle θ ₂ is reached, the outer peripheral teeth 58
And the second inner peripheral teeth 70 contact each other, and thereafter the compression of the first and second springs 7 and 10 is stopped. That is, the relative rotation between the output rotator 4 and the intermediate member 3 stops, and thereafter, the relative rotation between them and the input rotator 2 advances. Therefore, the third spring 5
Is compressed, and a slip occurs between the intermediate body 3 and the second friction member 76. As a result, characteristics of high rigidity and large hysteresis torque can be obtained from the torsion angle θ _{2 to} θ ₃ . When the compression of the fourth spring 6 starts at the third torsion angle θ ₃ , higher rigidity is obtained thereafter. When the pin 15 comes into contact with the notch 69 at the fourth torsion angle θ ₄ , the relative rotation between the output rotator 4 and the input rotator 2 stops.

In the torsional characteristics described above, the first
To realizes the characteristics of low rigidity and small hysteresis torque to the first-stage characteristic up torsion angle theta _1, rattle during idling it is less likely to occur. Further, since a characteristic of intermediate rigidity (θ _{1 to} θ ₂ ) is provided between low rigidity and high rigidity, a jumping phenomenon does not easily occur. In particular, in this region, a large friction, that is, a high hysteresis torque is generated by the friction washer 92, so that it is more effective to prevent a jumping reduction.

In this embodiment, the characteristic of medium rigidity is realized by a simple damper 8 composed of a plate 9, a pair of second springs 10, and a pair of seats 46. The locking portion 54
As shown in FIG. 4, it is engaged in a recess 3a formed in the intermediate body 3. However, as shown in FIG. 5, the locking portion 54 may be brought into contact with the first axial side end surface of the intermediate body 3 without providing the concave portion. Second Embodiment The clutch disk assembly 1 shown in FIGS. 8 to 11 has substantially the same shape as that of the above-described embodiment except for the damper 8, so that only the damper 8 will be described here.

The plate 9 has an annular portion 84 and a plurality of engaging portions 85, as in the above embodiment. Also,
An annular reinforcing plate 90 is fixed to the inner peripheral portion of the plate 9 by rivets 91. The reinforcing plate 90 is fixed on the second axial direction side and abuts on the cylindrical portion 17 of the intermediate body 3 and the first axial side surface of the flange 57. The reinforcing plate 90 has teeth similar to the teeth of the plate 9, and can be brought into contact with the outer peripheral teeth on the hub side together with the plate 9. Due to the increase in the contact area between the teeth, wear and breakage are less likely to occur. Particularly, the strength of the plate 9 is improved by the reinforcing plate 90.

In the engaging portion 85, a protruding portion 86 extending radially outward from the annular portion 84 is formed. Contact portions 87 extend in the axial direction from both sides in the circumferential direction of the projecting portion 86. The contact portions 87 extend inside the third and third window holes 31 of the intermediate body 3 and further extend from the axial end to the inside in the circumferential direction. The axial pressing portions 89 are fixed to each other by welding. A pair of second elastic members and 1
The configuration of the pair of sheets 46 is similar to that of the above-described embodiment.

In this embodiment, instead of the cap of the above embodiment, the axial pressing portion 89 of the plate 9 regulates the movement of the pair of second springs 10 and the pair of seats 46 in the second axial direction. ing. The contact portion 87 is a member that is shorter in the radial direction than the pair of sheets 46, and the third and third window holes 31 are in contact with both sides in the radial direction at the axial center of the pair of sheets 46. .

The first inner peripheral teeth and the relationship between the first inner peripheral teeth and the other members in the annular portion 84 are the same as in the above-described embodiment, and therefore will not be described here. In this embodiment, the same excellent effects as those of the above embodiment can be obtained. The present invention is not limited to the clutch disk assembly, but can be applied to other power transmission devices.

[0045]

In the damper disk assembly according to the present invention, an intermediate rigidity in which the second elastic member acts between the first elastic member and the third elastic member is obtained, so that a jumping phenomenon due to vibration during idling. Is unlikely to occur. In the damper disk assembly according to the present invention, the intermediate member constituting the damper has a plate shape, and each portion is formed by bending, so that the shape is simple.

[Brief description of the drawings]

FIG. 1 is a schematic longitudinal sectional view of a clutch disk assembly as one embodiment of the present invention.

FIG. 2 is a plan view of the clutch disk assembly with the plate removed.

FIG. 3 is a partial plan view of the plate 9;

FIG. 4 is a sectional view of a second spring.

FIG. 5 is a modified example of FIG.

FIG. 6 is a mechanical circuit diagram of a clutch disk assembly.

FIG. 7 is a torsional characteristic diagram of a clutch disk assembly.

FIG. 8 is a schematic longitudinal sectional view of a clutch disk assembly according to a second embodiment.

FIG. 9 is a plan view of the clutch disk assembly with the plate removed.

FIG. 10 is a partial plan view of a damper.

FIG. 11 is a view corresponding to FIG. 4;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Clutch disk assembly 2 Input rotating body 3 Intermediate body 4 Output rotating body 5 Third spring 6 Fourth spring 7 First spring 8 Damper 9 Intermediate member 10 Second spring 11 Friction part

Claims (7)

[Claims] 1. A hub (4), a first disk-shaped member (3) arranged on the outer peripheral side of the hub (4), the hub (4) and the first disk-shaped member (3) A first elastic member (7) that is arranged between the hub (4) and the circumferential direction when the hub (4) and the first disk-shaped member (3) rotate relative to each other; A region which is arranged between the first disk-shaped member (3) and the region where the torsion angle is small in the region where the torsion angle is small within the operation torsion angle of the first elastic member (7). A damper (8) having a second elastic member (10) that is elastically compressed in the circumferential direction with a second disc member (3) disposed on the axial side of the first disc-shaped member (3);
Disc-shaped members (12, 13), the first disc-shaped member (3), and the second disc-shaped member (1
2, 13) are elastically connected in the circumferential direction, and the third elastic member (5) has a higher spring constant than the first elastic member (7) and a higher spring constant than the second elastic member (10). When,
A damper disk assembly (1) comprising: 2. The damper (8) engages with the second elastic member (10) and has a first torsion angle (θ ₁ ) gap in the circumferential direction with the hub (4). Intermediate member (9)
The damper disk assembly according to claim 1, further comprising: 3. The first disk-shaped member (3) supports both ends in the circumferential direction of the second elastic member (10), and the intermediate member (9) is a circle of the second elastic member (10). 3. The support of both ends in the circumferential direction, wherein the intermediate member (9) has the first torsion angle (θ ₁ ) gap in the circumferential direction with the hub (4). 4. Damper disk assembly. 4. A second torsion angle between the hub (4) and the first disc-shaped member (3), which is larger in the circumferential direction than the first torsion angle (θ ₁ ) gap. (theta ₂₎ a gap is formed, the damper disk assembly according to claim 3. 5. The hub (4) has a plurality of first hubs extending outward.
The intermediate member (9) is circumferentially connected to the first tooth (58).
The first torsion angle (θ₁) Duplex placed with a gap
A number of second teeth (39) on the inner periphery, said first circle
The plate-like member (3) is circumferentially connected to the first tooth (58) by a second
Torsion angle (θ _Two) A plurality of thirds arranged with a gap
Teeth (70) on the inner periphery, said second torsion angle
(Θ_Two) The gap is the first torsion angle (θ₁) Greater than the gap
3. The damper disk assembly according to claim 2, wherein: 6. The intermediate member (9) is plate-shaped, and has an annular portion and an engaging portion extending radially outward from the annular portion and engaging with both circumferential ends of the second elastic member (10). The damper disk assembly according to claim 5, comprising: (35) and the plurality of second teeth (39) extending radially inward from the annular portion. 7. The second elastic member (10) is arranged in the axial direction so as to act in parallel between the intermediate member (9) and the first disk-shaped member (3). The damper disk assembly according to any one of claims 1 to 6, comprising a pair of springs.