JPH0989026A - Damper disk assembly - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the shock of an impact caused by a change in a twisting characteristic between first and second stages in a damper disk assembly having two-stage characteristic. SOLUTION: In a clutch disk, a small coil spring 6 is arranged so as to be compressed when the flange 2b and the sub-plate 5 of a hub are rotated in a relative manner. A float rubber 30 is arranged inside the small coil spring 6 and its both ends are placed away from the flange 2b and the sub-plate 5. A large coil spring is arranged so as to be compressed when a plate and the sub-plate 5 are rotated in a relative manner and has rigidity higher that that of the small coil spring 6.

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 having a two-step characteristic.

[0002]

2. Description of the Related Art A clutch disc assembly used for a vehicle clutch, for example, includes a disc-shaped input side plate, an output side hub integrally provided with a flange on the outer circumference, and a relative position between the input side plate and the flange. And an elastic member arranged to limit rotation. Further, there is also provided a separated hub type clutch disc assembly in which the conventional flange is separated from the hub and the separated flange and the hub are connected by a low-rigidity elastic member.

Further, in the separated hub type clutch disc assembly, a friction generating mechanism is arranged so that hysteresis torque is generated when the input side plate and the hub rotate relative to each other. The friction generating mechanism generates low hysteresis torque in the first stage and high hysteresis torque in the second stage. In this type of damper disk assembly, the relative twist angle between the input side plate and the hub is widened, and further two-step twist characteristics of low rigidity and high rigidity are obtained. In the range where the twist angle is small, the input side plate and the intermediate disc member rotate integrally, and relative rotation occurs between them and the output side hub. At this time, the low-rigidity elastic member is compressed,
The friction generating mechanism generates low hysteresis torque. When the twisting angle becomes large, the intermediate disk member rotates integrally with the output hub, and relative rotation occurs between them and the input plate. At this time, the high-rigidity elastic member is compressed, and the friction generating mechanism generates high hysteresis torque.

[0004]

In the above-mentioned conventional damper disk assembly, when torsional vibration at idle is transmitted, periodic relative rotation occurs within the range of the first stage. If the characteristics may vary from the first stage to the second stage, the protruding portion of the hub and the protruding portion of the separation flange collide with each other to cause a jumping phenomenon. This jumping phenomenon causes rattling noise on the transmission side.

SUMMARY OF THE INVENTION It is an object of the present invention to mitigate the shock of collision in the change between the first and second torsional characteristics in a damper disk assembly having two characteristics.

[0006]

A damper disk assembly according to a first aspect of the present invention comprises a first rotating member, a second rotating member, a coil spring, an elastic body, a third rotating member and an elastic member. The second rotating member is arranged so as to be rotatable relative to the first rotating member. The coil spring is arranged so as to be compressed when the first rotating member and the second rotating member rotate relative to each other. The elastic body is arranged inside the coil spring, and both ends thereof are arranged apart from the first rotating member and the second rotating member. The third rotating member is arranged so as to be relatively rotatable with respect to the second rotating member. The elastic member is arranged so as to be compressed when the second rotating member and the third rotating member rotate relative to each other, and has higher rigidity than the coil spring.

When the third rotating member rotates, the torque is transmitted to the first rotating member via the elastic member, the second rotating member and the coil spring. When the torsional vibration is transmitted to the third rotating member, periodic relative rotation occurs between the rotating members.
In terms of twisting characteristics, in the range where the twisting angle is small,
The third rotating member and the second rotating member rotate integrally, and they and the first rotating member rotate relative to each other. At this time, the coil spring is compressed and the first stage characteristic of low rigidity is obtained. When the twisting angle increases, the second rotating member and the first rotating member rotate together, and the third rotating member and the third rotating member rotate relative to each other. At this time, the elastic member is compressed and the second stage characteristic of high rigidity is obtained. The elastic body is compressed between the second rotating member and the first rotating member between the first stage and the second stage. As a result, the shock when shifting between the first stage and the second stage is absorbed.

In the damper disk assembly according to the second aspect, the elastic body is a columnar member. In the damper disk assembly according to the third aspect, the elastic body includes the elastically deformable main body portion and the seat portions fixed to both ends of the main body portion. In the damper disk assembly according to the fourth aspect, the main body is made of rubber.

According to another aspect of the damper disk assembly of the present invention, the second rotating member is arranged on the outer periphery of the first rotating member, and the first rotating member and the second rotating member have teeth extending alternately in the radial direction. Each has a section. In the damper disk assembly according to the sixth aspect of the present invention, the first rotating member and the second rotating member are formed with notches for accommodating the coil spring and the elastic body.

In the damper disk assembly according to the present invention, sheet members are arranged at both ends of the coil spring, and both ends of the elastic body are separated from the both sheet members.

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A clutch disc assembly 1 according to an embodiment of the present invention shown in FIG. 1 has torque from an engine (not shown) arranged on the left side of FIG. 1 arranged on the right side of FIG. It is a device for transmitting to and disconnecting from a transmission (not shown). In FIG. 1, OO
Is the axis of rotation of the clutch disc assembly 1.

The clutch disk assembly 1 mainly includes:
A hub 2 as an output side member, a clutch disc 3 and a retaining plate 4 as an input side member, a sub plate 5 as an intermediate member, and a relative rotation between the sub plate 5 and the hub 2 are restricted between the sub plate 5 and the hub 2. Of the small coil spring 6 arranged as described above, the large coil spring 7 arranged between the plates 3, 4 and the sub-plate 5 so as to limit the relative rotation therebetween, and the plates 3, 4 and the hub 2. And a frictional resistance generating mechanism 8 that generates a predetermined hysteresis torque when relative rotation occurs.

The hub 2 is arranged at the center of the clutch disc assembly 1 and is connected to a transmission shaft (not shown). The hub 2 has a cylindrical boss 2 extending in the axial direction.
a and a flange 2b integrally formed on the outer periphery of the boss 2a
It is composed of A plurality of projections 2c are formed on the outer periphery of the flange 2b at equal intervals in the circumferential direction. As shown in FIG. 3, notches 2d for receiving both ends in the circumferential direction of a small coil spring 6 which will be described later are formed at two locations facing each other in the radial direction of the flange 2b. Also, boss 2
On the inner peripheral side of a, the shaft of the transmission (not shown)
Is formed with a spline hole 2e for spline engagement.

A sub plate 5 is arranged on the outer periphery of the flange 2b of the hub 2. The sub-plate 5 is a disk-shaped plate. As is apparent from FIG. 2, the sub-plate 5 has four protrusions 5a extending radially outward. Each protruding portion 5a is formed with a window hole 5b extending in the circumferential direction. Outer notches 5c are formed between the protrusions 5a. On the inner peripheral side of the sub plate 5, the hub 2
Inner protrusions 5d are formed on the corresponding portions between the protrusions 2c. A predetermined circumferential gap is provided between the protrusion 2c and the inner protrusion 5d, so that the hub 2 and the sub-plate 5 can rotate by a predetermined angle. Inner notches 5e are formed at two locations on the inner peripheral side of the subrate 5 corresponding to the notches 2d of the hub 2. A small coil spring 6 is arranged in each of the notches 2d and the inner notches 5e. Seat members 30 are arranged at both ends of the small coil spring 6, and the seat member 3
0 is in contact with the side of the cutout 2d and both ends of the inner cutout 5e in the circumferential direction.

Inside the small coil spring 6, as shown in detail in FIG. 13, a rubber float 31 is arranged. The rubber float 31 includes a rubber main body 31a,
It is a columnar member having a sheet portion 31b made of a hard material such as resin fixed to both ends of the main body portion 31a. The seat portion 31a has a larger diameter than the main body portion 31a. A predetermined distance is secured between the seat portion 31a and the seat member 6a.

In the neutral state shown in FIG. 2, the protrusion 2c
Are arranged on the R ₂ side between the inner protrusions 5d. The clutch plate 3 and the retaining plate 4 are arranged on both sides of the sub plate 5. The clutch plate 3 and the retaining plate 4 are a pair of substantially disk-shaped members, and are rotatably arranged on the outer peripheral side of the boss 2 a of the hub 2. The clutch plate 3 and the retaining plate 4 are fixed to each other by a contact pin 11 at the outer peripheral portion. The contact pin 11 is inserted through an outer cutout 5c formed in the sub plate 5. Contact pin 1
Since a predetermined gap is secured in the circumferential direction between 1 and the outer cutout 5c, the plates 3 and 4 and the sub-plate 5 can rotate relative to each other.

A friction coupling portion 10 is arranged on the outer periphery of the clutch disc 3. The friction connecting portion 10 mainly includes an annular cushioning plate 12 and a friction facing 13. The cushioning plate 12 has an annular portion 12 a fixed to the clutch plate 3 by a contact pin 11. Cushioning plate 1
2 A plurality of cushioning portions 12b are formed on the outer peripheral side. Friction facings 13 are fixed to both surfaces of the cushioning portion 12b. A flywheel (not shown) on the engine side is arranged on the left side of the friction facing 13 in FIG. 1, and when the friction facing 13 is pressed against the flywheel by a pressure plate (not shown), the clutch disc assembly 1 is attached. The engine torque is input.

Window holes 3a and 4a are formed in the clutch plate 3 and the retaining plate 4 at positions corresponding to the window holes 5b of the sub-plate 5, respectively. The second coil spring 7 is arranged in the window hole 3a and the window hole 4a. A pressing portion 3 cut and raised axially outward is provided on both sides of each window hole 3a and 4a in the radial direction.
a and a pressing portion 4b are formed.

There are four large coil springs 7 in total,
It is composed of two first spring assemblies 7a and two second spring assemblies 7b. The first spring assembly 7a includes a window hole 5 of the sub-plate 5 that faces the radial direction.
It is located in b. The first spring assembly 7a is
It is composed of a large-diameter coil spring and a small-diameter coil spring arranged inside thereof. Both ends of the first spring assembly 7a in the circumferential direction are located at both ends of the window hole 5b of the sub plate 5 in the circumferential direction, both ends of the window hole 3a of the clutch plate 3 in the circumferential direction, and the window hole 4 of the retaining plate 4.
It is in contact with both circumferential ends of a.

The second spring assembly 7b is arranged in the window hole 5b of the sub-plate 5 which faces in the radial direction.
The second spring assembly 7b is a coil spring. The circumferential ends of the coil spring of the second spring assembly 7b are in contact with the circumferential ends of the window holes 5b, 3a and the window hole 4a. The large coil spring 7 described above is restricted from moving in the axial direction by the holding portion 4b of the retaining plate 4 and the holding portion 3b of the clutch plate 3.

On the inner peripheral sides of the clutch plate 3 and the retaining plate 4, four holes 3c and 4c with which a part (described later) of the frictional resistance generating mechanism 8 engages are formed at equal intervals in the circumferential direction. There is. Next, the frictional resistance generating mechanism 8 will be described. The frictional resistance generating mechanism 8 is composed of annular members disposed on the outer peripheral side of the boss 2a between the inner peripheral portion of the clutch plate 3 and the inner peripheral portion of the retaining plate 4 in the axial direction. The members constituting the frictional resistance generating mechanism 8 are the first friction washer 14, the second friction washer 15, the first cone spring 16, the second cone spring 17, and the third friction washer 18.

The first friction washer 14 is a resin disk plate. 1st friction washer 1
As shown in FIGS. 5 to 7, the inner peripheral end of the No. 4 is close to the boss 2a, and one side surface is in contact with the flange 2b of the hub 2 and the transmission side surface of the protrusion 2c. First
The friction washer 14 has a disc portion 14a and an annular protrusion 14b that protrudes from the inner peripheral side of the disc portion 14a toward the transmission. An annular cutout groove 14c is formed on the transmission side of the annular protrusion 14b. Further, four protrusions 14d extending outward in the radial direction are formed on the outer circumference of the disc portion 14a.

A first cone spring 16 is arranged between the first friction washer 14 and the retaining plate 4 in the axial direction. An outer peripheral end of the first cone spring 16 is supported by the retaining plate 4, and an inner peripheral end of the first cone spring 16 is in contact with an annular cutout groove 14c formed in the annular protruding portion 14b of the first friction washer 14. The first cone spring 16 is arranged in a compressed state and biases the first friction washer 14 toward the flange 2b and the protrusion 2c of the hub 2. As shown in FIG. 11, the first cone spring 16 is formed with a plurality of notches 16a on the outer peripheral side. This notch 16a is
It is formed to reduce the change in the urging force of the first cone spring 16 when the posture of the first cone spring 16 changes due to the wear of the first friction washer 14.

The second friction washer 15 is shown in FIG.
As is clear from FIG. 10, it is a disk-shaped member, and
On the outer peripheral side of the friction washer 14, the friction washer 14 is arranged on the same plane as the plane on which the first friction washer 14 is arranged and concentrically. The second friction washer 15 is made of the same material as the first friction washer 14 and has the same friction coefficient. The second friction washer 15 includes a disc portion 15a and a disc portion 15a.
And an annular protrusion 15b that protrudes toward the transmission on the inner peripheral side of the. The engine-side end surface of the disk portion 15a is in contact with the inner peripheral end surface of the sub plate 5.
On the transmission-side end surface of the annular protrusion 15b, four notches 15e are formed at equal intervals in the circumferential direction. The protrusion 14d of the first friction washer 14 is engaged in the notch 15e such that it cannot rotate relative to the circumferential direction and can move in the axial direction. A predetermined gap is secured between the protrusion 14d and the recess 15e in the axial direction. Four protrusions extending toward the transmission are formed between the recesses 15e in the annular protrusion 15b. This protrusion is composed of two snap protrusions 15c and two rod-shaped protrusions 15d. Here, the protrusions of the same type are arranged so as to face each other in the radial direction. Snap projection 15
The c is divided into two by a slit extending in the axial direction and has a hook-shaped snap at the tip. The snap projection 15c is inserted into the hole 4c formed in the retaining plate 4. The second friction washer 15 is hard to come off from the retaining plate 4 in the axial direction due to the snap portion formed on the snap projection 15c. The rod-shaped projection 15d is inserted into the other hole 4c of the retaining plate 4.

The second cone spring 17 is arranged axially between the second friction washer 15 and the retaining plate 4. As shown in FIG. 12, the second cone spring 17 has a plurality of notches 17a on the inner peripheral side.
Are formed. The notch 17a is provided in the second cone spring 1 when the posture of the second cone spring 17 changes due to wear of the second friction washer 15.
7 is formed to reduce the change in biasing force. The second cone spring 17 is arranged in a compressed state, its outer peripheral edge abuts on the retaining plate 4, and its inner peripheral edge, that is, the protrusion 17b, is the second friction washer 15.
Is in contact with the side surface of the annular protrusion 15b on the transmission side. In this way, the second cone spring 17
Biases the second friction washer 15 to the side surface of the sub plate 5 on the transmission side. The biasing force of the second cone spring 17 at this time is set to be larger than the biasing force of the first cone spring 16. The notch 17a portion of the second cone spring 17 corresponds to the snap projection 15c, the rod-shaped projection 15d and the recess 15e of the second friction washer 15 so that the second cone spring 17 and these members do not interfere with each other. It has become.

A third friction washer 18 is arranged axially between the inner peripheral portion of the clutch plate 3 and the flange 2b of the hub 2 and the inner peripheral end of the sub plate 5. The third friction washer 18 is made of the same material as the first friction washer 14 and the second friction washer 15, and has the same friction coefficient. The transmission side surface of the third friction washer 18 contacts the side surface of the flange 2b and the inner peripheral end surface of the sub plate 5, and the engine side surface contacts the clutch plate 3. A snap projection 18a (see FIG. 1) extending toward the engine in the axial direction is formed on the outer peripheral portion of the third friction washer 18.
8a is engaged in a hole 3c formed in the clutch plate 3. The snap projection 18a has the same shape as the snap projection 15c of the second friction washer 15 described above. An annular protrusion 18b extending axially toward the engine is formed on the inner peripheral portion of the third friction washer 18. The inner peripheral end of the clutch plate 3 is in contact with the outer peripheral side of the annular protruding portion 18b.

Next, the operation of the clutch disc assembly 1 will be described. When the friction facing 13 is pressed against a flywheel (not shown) on the engine side, the torque of the flywheel on the engine side increases the clutch plate 3.
And input to the retaining plate 4. This torque is transmitted to the hub 2 via the large coil spring 7, the sub-plate 5, and the small coil spring 6, and is further transmitted to a transmission-side shaft (not shown).

Flywheel on the engine side (not shown)
When the torsional vibration is transmitted from the clutch disc assembly 1 to the clutch disc assembly 1, periodic relative rotation occurs between the plates 3 and 4, the sub plate 5, and the hub 2. At this time, the small coil spring 6 and the large coil spring 7 are compressed, and the friction generating mechanism 8 generates hysteresis torque. The twist characteristic will be described. In the range where the twist angle is small, the plates 3 and 4 and the sub plate 5 rotate integrally, and relative rotation occurs between them and the hub 2. At this time, the small coil spring 6 is compressed in the circumferential direction, and the first friction washer 14 and the third friction washer 1 are
8 slides on the flange 2b and the protrusion 2c of the hub 2. If the twist angle increases, the flow traverse 31
Both ends contact the sheet member 6a and are thereafter compressed. Next, the protrusion 2c and the inner protrusion 5d come into contact with each other, and the sub-plate 5 and the hub 2 rotate integrally, and relative rotation occurs between these and the plates 3 and 4. At this time, the large coil spring 7
Is compressed and the first friction washer 14 is attached to the hub 2
Sliding on the flange 2b of the hub 2, the second friction washer 15 slides on the inner peripheral side surface of the sub-plate 5, and the third friction washer 18 further moves to the flange 2b of the hub 2.
To the side surface on the flywheel side of the sub plate 5 and the side surface on the flywheel side of the inner peripheral side of the sub plate 5. Here, the second
Since the biasing force of the cone spring 17 is set to be larger than the biasing force of the first cone spring 16, high hysteresis torque is generated.

When a slight torsional vibration is input to the clutch disc assembly 1 during idling, the torsion angle changes in the first step area on both sides of the neutral position. When the twist angle enters the second step, the protrusion 2c and the inner protrusion 5d come into contact with each other. But,
At the time of this contact, the flow travers 30 are compressed to absorb the shock at the time of collision. In the torsion characteristic diagram shown in FIG. 14, the torsional rigidity smoothly changes in a parabolic shape.

[0030]

In the damper disk assembly according to the present invention, when torsional vibration is transmitted to the third rotating member, periodic relative rotation occurs between the rotating members. Regarding the twisting characteristic, in the range where the twisting angle is small, the third rotating member and the second rotating member rotate integrally, and they and the first rotating member rotate relative to each other. At this time, the coil spring is compressed and the first stage characteristic of low rigidity is obtained. When the twisting angle increases, the second rotating member and the first rotating member rotate together, and the third rotating member and the third rotating member rotate relative to each other. At this time, the elastic member is compressed and the second stage characteristic of high rigidity is obtained. The elastic body is compressed between the second rotating member and the first rotating member between the first stage and the second stage. As a result, the shock when shifting between the first stage and the second stage is absorbed.

[Brief description of drawings]

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

FIG. 2 is a partially cut-away view taken along the arrow II in FIG.

FIG. 3 is a plan view of the hub.

4 is a sectional view taken along line IV-IV in FIG.

5 is an enlarged view of circle A in FIG.

FIG. 6 is a plan view of a first friction washer.

7 is a sectional view taken along line VII-VII of FIG.

FIG. 8 is a plan view of a second friction washer.

FIG. 9 is a sectional view taken along line IX-IX of FIG. 8;

10 is a sectional view taken along line XX of FIG.

FIG. 11 is a plan view of a first cone spring.

FIG. 12 is a plan view of a second cone spring.

FIG. 13 is a partially enlarged view of FIG.

FIG. 14 is a characteristic diagram of torsional vibration that acts at the first stage.

[Explanation of symbols]

 1 Clutch Disc Assembly 2 Hub 3 Clutch Plate 4 Retaining Plate 5 Sub Plate 6 Small Coil Spring 7 Large Coil Spring 8 Frictional Resistance Generation Mechanism 31 Rubber Float

Claims (7)

[Claims] 1. A first rotating member, a second rotating member rotatably arranged on the first rotating member, and a compression member when the first rotating member and the second rotating member rotate relative to each other. A coil spring arranged, an elastic body arranged inside the coil spring, and having both ends separated from the first rotating member and the second rotating member, and arranged to be rotatable relative to the second rotating member. A damper disk assembly comprising: a third rotating member; and an elastic member that is arranged to be compressed when the second rotating member and the third rotating member rotate relative to each other and has a rigidity higher than that of the coil spring. 2. The damper disk assembly according to claim 1, wherein the elastic body is a cylindrical member. 3. The damper disk assembly according to claim 2, wherein the elastic body is composed of an elastically deformable main body portion and seat portions fixed to both ends of the main body portion. 4. The damper disk assembly according to claim 3, wherein the main body is made of rubber. 5. The second rotating member is arranged on the outer periphery of the first rotating member, and the first rotating member and the second rotating member each have tooth portions extending alternately in the radial direction. The damper disk assembly according to any one of claims 1 to 4, wherein: 6. The damper according to claim 1, wherein the first rotating member and the second rotating member are formed with notches for accommodating the coil spring and the elastic body. Disk assembly. 7. The damper disk according to claim 1, further comprising seat members arranged at both ends of the coil spring, wherein both ends of the elastic body are separated from the both seat members. Assembly.