JP2000002264A - Damper mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce abnormal sound vibration at idling by combining a friction generat ing means with a friction connecting part in the torsional characteristic of damper mechanism and stopping the slip of hysteresis torque generating part. SOLUTION: A clutch disc assembly has a hub 3, an input rotating body 2, a first spring 7, a second spring 8, a second friction mechanism 13 and a third friction mechanism 14. The first spring 7 elastically connecting the hub 3 to the input rotating body 2 in the rotational direction and is compressed in a first step range where the torsional angle of both the members 3, 2 is up to a first torsional angle. The second spring 8 elastically connecting the body 2 to the hub 3 in the rotational direction and is compressed in a second stage region, to thereby providing a higher rigidity than a rigidity in the first stage region. The second friction mechanism 13 is able to generate a first hysteresis torque in the first stage and second stage regions. The third friction mechanism 14 is able to generate a second hysteresis torque while parallely acts with the second friction mechanism 13 in only the second stage region. Gaps θAC1, θAC2 serving as hysteresis torque restraining mechanisms do not make the second and third mechanisms 13, 14 act on torsional vibration of not more than a specified torque.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a damper mechanism, and more particularly to a damper mechanism for attenuating torsional vibration in a power transmission system.

[0002]

2. Description of the Related Art A clutch disk assembly used in a vehicle has a clutch function for connecting and disconnecting to and from a flywheel, and a damper function for absorbing and attenuating vibration from the flywheel. Generally, vehicle vibration
There are abnormal sounds during idle (rattle noise), abnormal sounds during running (acceleration / deceleration rattle, muffled sound) and tip-in / tip-out (low-frequency vibration). The function as a damper of the clutch disk assembly is to remove such abnormal noise and vibration.

[0003] The abnormal noise at idling is a noise that is heard from the transmission when the shift is set to a neutral position at the time of waiting for a signal and the clutch pedal is released. The cause of this noise is that the engine torque is low near the engine idling rotation and the torque fluctuation at the time of engine explosion is large. Tip-in / tip-out (low-frequency vibration) is a large swing before and after the vehicle body that occurs when the accelerator pedal is suddenly depressed or suddenly released. Specifically, a transient vibration is generated by inputting the torque in a stepwise manner to the drive transmission system. As a result, the torque transmitted to the tire is conversely transmitted from the tire side to the drive side, and excessive torque is generated in the tire as a swing back. As a result, the vehicle body is transiently shaken back and forth greatly.

With respect to abnormal noise during idling, there is a problem in the vicinity of 0 torque in the torsional characteristics of the clutch disk assembly, and the lower the torsional rigidity, the better. Therefore, a clutch disk assembly has been provided which realizes a non-linear torsional characteristic (a two-stage characteristic including a first stage with a low rigidity and a second stage with a high rigidity) by using a low-rigidity spring. In this clutch disk assembly, the first-stage torsional rigidity and the hysteresis torque are suppressed to a low level, so that there is an effect of preventing abnormal noise during idling.

[0005]

In the damper mechanism of the conventional clutch disk assembly, when low-frequency vibration is input, the torsional characteristic causes a transition between the second stage on the positive side and the second stage on the negative side. Repeat torsional motion in high angle range. At this time, the low-frequency vibration may not be sufficiently attenuated due to the non-linearity and low rigidity of the first stage.

SUMMARY OF THE INVENTION An object of the present invention is to provide a damper mechanism having two-stage torsional characteristics, which effectively attenuates torsional vibration twisting between the second stage on both the positive and negative sides.

[0007]

According to a first aspect of the present invention, there is provided a damper mechanism comprising a first rotating member, a second rotating member, a first elastic member, a second elastic member, a friction generating means, and a friction suppressing means. I have. The second rotating member is arranged to be relatively rotatable with the first rotating member. The first elastic member includes a first rotating member and a second rotating member.
The rotating member is elastically connected in the rotating direction, and the first rotating member and the second rotating member are compressed in a first-stage range up to the first torsional angle. The second elastic member elastically connects the first rotating member and the second rotating member in the rotation direction, and in a second-stage range where the torsional angle of the first rotating member and the second rotating member exceeds the first torsional angle. It is a member that is compressed and provides higher rigidity in the second stage than in the first stage. The friction generating means frictionally engages the first rotating member and the second rotating member in a rotational direction,
It is a mechanism that can slide in the first-stage range and the second-stage range, and can generate greater friction in the second-stage range than in the first-stage range.
The friction suppressing means does not cause the friction generating means to slip against torsional vibration of a predetermined torque or less in the first stage range and the second stage range.

The torsional characteristic of the damper mechanism according to the first aspect will be described. Here, the range from 0 ° to the first torsion angle is the first range of the torsional characteristic, and the range from the first torsion angle exceeds the first torsion angle is the second range. In the first range, the first elastic member is compressed, and a relatively low torsional rigidity is obtained. In the second stage range, the second elastic member is compressed, and as a result, higher rigidity is obtained than in the first stage range. A relatively large friction (high hysteresis torque) is generated in the first stage range and the second stage range because the friction generating means slides. As a result, characteristics of low rigidity and high hysteresis torque are obtained in the first stage range, and characteristics of high rigidity and high hysteresis torque are obtained in the second stage range.

As described above, since the high hysteresis torque is generated by operating the friction generating means in the first range, vibration having a large torsion angle, such as longitudinal vibration of the vehicle body, can be effectively attenuated. Further, when torsional vibration of a predetermined torque or less is input in the first stage range and the second stage range, the friction suppressing unit does not cause the friction generating unit to slip. That is, large friction is not generated by the friction generating means, and a characteristic of low hysteresis torque is obtained. As a result, the small torsional vibration is effectively absorbed.

Furthermore, in this damper mechanism, since the friction generating means generates a smaller friction in the first range than in the second range, it is effective against abnormal noise during idling. A damper mechanism according to a second aspect includes a first rotating member, a second rotating member, a first elastic member, a second elastic member, and a friction generating mechanism. The second rotating member is arranged to be relatively rotatable with the first rotating member. The first elastic member elastically connects the first rotating member and the second rotating member in the rotation direction, and compresses the first rotating member and the second rotating member in a first-stage range up to the first torsional angle. Is done. The second elastic member elastically connects the first rotating member and the second rotating member in the rotation direction,
This is a member that is compressed in a second stage range in which the torsion angle between the rotating member and the second rotating member exceeds the first torsion angle, and provides higher rigidity in the second stage range than in the first stage range. The friction generating mechanism frictionally engages the first rotating member and the second rotating member in the rotational direction, does not slip against torsional vibrations having a predetermined torque or less in the first stage range and the second stage range, and has a predetermined torque or more. By sliding against torsional vibration, the first friction is generated in the first range, and the second friction is larger than the first friction in the second range.

In the damper mechanism according to the second aspect, since the friction generating mechanism slides in the first stage range and the second stage range, relatively large friction is generated. As a result, characteristics of low rigidity and high hysteresis torque are obtained in the first stage range, and characteristics of high rigidity and high hysteresis torque are obtained in the second stage range. Further, when torsional vibration of a predetermined torque or less is input in the first-stage range and the second-stage range, the friction generating mechanism does not slip, that is, large friction does not occur.

Further, in this damper mechanism, the friction generating mechanism generates a smaller amount of friction in the first range than in the second range, so that it is effective against, for example, abnormal noise during idling. The damper mechanism according to claim 3, wherein the first rotating member, the second rotating member, the first elastic member, the second elastic member, the first friction generating mechanism, the second friction generating mechanism, the first friction suppressing mechanism, and the second
A friction suppressing mechanism. The second rotating member is arranged to be relatively rotatable with the first rotating member. The first elastic member elastically connects the first rotating member and the second rotating member in the rotation direction, and compresses the first rotating member and the second rotating member in a first-stage range up to the first torsional angle. Is done. The second elastic member elastically connects the first rotating member and the second rotating member in the rotation direction, and in a second-stage range where the torsional angle of the first rotating member and the second rotating member exceeds the first torsional angle. It is a member that is compressed and provides higher rigidity in the second stage than in the first stage. The first friction generating mechanism is capable of frictionally engaging the first rotating member and the second rotating member in the rotational direction, and generating the first friction in the first stage range. The second friction generating mechanism is capable of frictionally engaging the first rotating member and the second rotating member in the rotational direction, and generating a second friction larger than the first friction in the second stage range. The first friction suppressing mechanism does not cause the first friction generating mechanism to slip when torsional vibration of a predetermined torque or less is input in the first stage range.
The second friction suppressing mechanism does not cause the second friction generating mechanism to slip when a torsional vibration of a predetermined torque or less is input in the second stage range.

[0013] In the damper mechanism according to the third aspect, the first friction generating mechanism generates the first friction in the first stage range, and the second friction generating mechanism generates the second friction in the second stage range. As a result, characteristics of low rigidity and high hysteresis torque are obtained in the first stage range, and characteristics of high rigidity and high hysteresis torque are obtained in the second stage range. As described above, high hysteresis torque is generated by the first friction generating mechanism in the first-stage range, so that vibration having a large torsion angle such as longitudinal vibration of the vehicle body can be effectively attenuated. Further, when the torsional vibration of a predetermined torque or less is input in the first stage range, the first friction suppressing mechanism does not cause the first friction generating mechanism to slip, and the torsional vibration of the predetermined torque or less is input in the second stage range. In this case, the second friction suppressing mechanism does not cause the second friction generating mechanism to slip. That is, in any case, a large friction does not occur, and characteristics of low hysteresis torque can be obtained.

Further, in this damper mechanism, since the first friction generating mechanism generates smaller friction than the second friction generating mechanism which functions in the second stage range, it is effective against abnormal noise during idling, for example. The damper mechanism according to claim 4, wherein the first rotating member, the second rotating member, the first elastic member, the second elastic member, the first hysteresis torque generating mechanism, and the second rotating member.
A hysteresis torque generating mechanism and a hysteresis torque suppressing mechanism are provided. The first hysteresis torque generating mechanism can generate a hysteresis torque in the first-stage range and the second-stage range. The second hysteresis torque generating mechanism is capable of generating the second hysteresis torque by acting in parallel with the first hysteresis torque generating mechanism only in the second stage range. The hysteresis torque suppressing mechanism does not cause the first and second hysteresis torque generating mechanisms to act on torsional vibrations equal to or less than a predetermined torque.

In the damper mechanism according to the fourth aspect, in the first stage range, only the first hysteresis torque generating mechanism slides to generate the first hysteresis torque. In the second stage range, the second hysteresis torque generating mechanism acts in parallel with the first hysteresis torque generating mechanism, so that a higher hysteresis torque than in the first stage range can be obtained. As a result, characteristics of low rigidity and high hysteresis torque are obtained in the first stage range, and characteristics of high rigidity and high hysteresis torque are obtained in the second stage range.

As described above, since the first hysteresis torque generating mechanism that functions in the first-stage range is provided, vibration having a large torsion angle such as longitudinal vibration of the vehicle body can be effectively attenuated. Further, when torsional vibration of a predetermined torque or less is input in the first stage range and the second stage range, the hysteresis torque suppressing mechanism does not operate the first and second hysteresis torque generating mechanisms. That is, large friction does not occur, and a characteristic of low hysteresis torque is obtained.

Further, in this damper mechanism, the hysteresis torque in the first-stage range is smaller than the hysteresis torque in the second-stage range, which is effective, for example, for abnormal noise during idling.

[0018]

FIG. 1 is a plan view of a clutch disk assembly 1 according to an embodiment of the present invention, and FIG. 2 is a sectional view thereof. The clutch disk assembly 1 is a power transmission device used for a vehicle clutch device, and has a clutch function and a damper function. The clutch function is a function of transmitting and disconnecting torque by connecting and disconnecting a flywheel (not shown).
The damper function is a function of absorbing and attenuating torque fluctuation input from the flywheel using a spring or the like.

In FIG. 1, the arrow R1 indicates the rotational direction (positive side) of the clutch disc assembly 1, and the R2 side indicates the opposite direction (negative side). In FIG. 2, OO is the rotation axis of the clutch disc assembly 1, that is, the rotation center line.
An engine and a flywheel (not shown) are arranged on the left side of FIG. 2, and a transmission (not shown) is arranged on the right side of FIG.

The clutch disk assembly 1 mainly includes an input rotary body 2, a hub 3 as an output rotary body, and a damper mechanism disposed between the input rotary body 2 and the hub 3. . The damper mechanism includes a first spring 7 and a second spring 8
And a plurality of friction generating mechanisms. Input rotator 2
Is a member to which torque from a flywheel (not shown) is input. The input rotator 2 mainly includes a clutch plate 21, a retaining plate 22, and a clutch disk 23. Clutch plate 2
1 and the retaining plate 22 are both disk-shaped or annular members made of sheet metal, and are arranged at predetermined intervals in the axial direction. The clutch plate 21 is arranged on the engine side, and the retaining plate 22 is arranged on the transmission side. The clutch plate 21 and the retaining plate 22 are fixed to each other by a plate-like connecting portion 31 to be described later, so that an axial interval is determined and the clutch plate 21 and the retaining plate 22 rotate integrally.

The clutch disk 23 is a portion that is pressed against a flywheel (not shown) and frictionally engages. The clutch disc 23 includes a cushioning plate 24
And the first and second friction facings 25. The cushioning plate 24 includes the annular portion 2.
4a, a plurality of cushioning portions 24b provided on the outer peripheral side of the annular portion 24a and arranged in the rotational direction, and a plurality of connecting portions 24c extending radially inward from the annular portion 24a. The connecting portions 24c are formed at four locations at equal intervals in the circumferential direction, and each is fixed to the outer peripheral portion of the clutch plate 21 by rivets 27 (described later). First and second friction facings 25 are fixed to both surfaces of each cushioning portion 24b of the cushioning plate 24 by a plurality of rivets 26.

The clutch plate 21 and the retaining plate 22 are formed with four window holes 35 at regular intervals in the rotation direction. Cut-and-raised portions 35a and 35b are formed in each window hole 35 on the inner peripheral side and the outer peripheral side, respectively. The cut-and-raised portions 35a and 35b correspond to a second
This is for restricting the movement of the spring 8 in the axial and radial directions. In the window hole 35, abutting portions 36 that abut or approach the circumferential end of the second spring 8 are formed at both circumferential ends. The contact portion 36 is a portion that transmits torque to the second spring 8.

Each of the clutch plate 21 and the retaining plate 22 has a center hole 37 (inner peripheral edge). The hub 3 as an output rotating body is arranged in the center hole 37. The hub 3 includes a cylindrical boss 52 extending in the axial direction, and a flange 54 extending radially outward from the boss 52. A spline hole 53 that engages with a shaft extending from a transmission (not shown) is formed in the inner peripheral portion of the boss 52. The flange 54 extends radially outward from an axially intermediate position of the boss 52. A plurality of outer peripheral teeth 55 are formed on a radially outer portion of the flange 54. The outer peripheral teeth 55 have such a shape that the width in the rotational direction decreases from the inner side to the outer side in the radial direction, and extends in the axial direction as much as the flange. Further, notches 56 are formed at two locations in the radial direction of the flange 54 and the outer peripheral teeth 55 that face each other. Notch 5
6 has contact portions 57 at both ends in the circumferential direction.

The separation flange 6 is provided on the outer peripheral side of the hub 3 and the clutch plate 21 and the retaining plate 22.
This is a disk-shaped member arranged between the members in the axial direction. The separation flange 6 is elastically connected to the hub 3 in the rotation direction via a first spring 7 (first elastic member).
It is elastically connected to the input rotating body 2 in the rotation direction via a (second elastic member). That is, the separation flange 6 functions as an intermediate member that connects the first spring 7 and the second spring 8 arranged in series. As shown in detail in FIG.
A plurality of inner peripheral teeth 66 are formed on the inner peripheral edge of the separation flange 6. The inner peripheral teeth 66 are arranged so as to be alternately arranged in the rotation direction with respect to the outer peripheral teeth 55. The length of the inner peripheral teeth 66 in the axial direction is shorter than the length of the outer peripheral teeth 55 in the axial direction. The inner peripheral teeth 66 have such a shape that the length in the rotational direction becomes shorter as going from the outer side to the inner side in the radial direction. A gap having a twist angle θ1 is secured between the outer peripheral teeth 55 and the inner peripheral teeth 66 in the circumferential direction. The first stopper 9 is formed by the outer teeth 55 and the inner teeth 66. The first stopper 9 has a twist angle θ on both the positive and negative sides between the hub 3 and the separation flange 6.
This is a mechanism for allowing relative rotation by one, and defines a first-stage range on both the positive and negative sides. The magnitude of the torsion angle θ1 is different between the positive side and the negative side. In this embodiment, for example, the torsion angle θ1 between the negative side (R2 side) and the inner peripheral teeth 66 when viewed from the outer peripheral teeth 55 is, for example, 5 °, and the torsional angle θ1 between the outer peripheral teeth 55 and the inner peripheral teeth 66 on the positive side (R1 side).
Is, for example, 2 °.

Further, a notch 67 corresponding to the notch 56 is formed on the inner peripheral edge of the separation flange 6. The notch 67 extends relatively long in the circumferential direction, and has contact portions 68 at both ends in the circumferential direction. The first spring 7 is arranged in a space formed by the notches 56 and 67. The first spring 7 is a small coil spring, and both ends in the circumferential direction are in contact with the contact portions 57 and 68 via spring seats. Thus, the first spring 7 elastically connects the hub 3 and the separation flange 6 in the rotational direction. In other words, when the hub 3 and the separation flange 6 rotate relatively, the two first springs 7 arranged in parallel are compressed between the two members. More specifically, when the two members rotate relative to each other, the first spring 7 includes the contact portion 57 and the contact portion 6 on the opposite side in the circumferential direction.
8 and compressed in the rotational direction.

Further, a plurality of notches 69 are formed in the inner peripheral edge of the separation flange 6 in the circumferential direction. Notch 6
Reference numeral 9 denotes a substantially square shape, which is formed at equal intervals in the circumferential direction. Four window holes 41 are formed in the separation flange 6 at equal intervals in the rotation direction. The window hole 41 has a shape that extends long in the rotation direction. The inner peripheral edge of the window hole 41 includes a contact portion 44 on both sides in the circumferential direction, an outer peripheral portion 45 on the outer peripheral side, and an inner peripheral portion 46 on the inner peripheral side. The outer peripheral portion 45 is formed continuously and closes the outer peripheral side of the window hole 41. In addition,
The outer peripheral side of the window hole 41 may be partially open radially outward. A notch 42 is formed in the separation flange 6 between the window holes 41 in the circumferential direction. Notch 42
Is a fan shape whose circumferential length increases from the inside to the outside in the radial direction, and edge surfaces 43 are formed on both sides in the circumferential direction.

A projection 49 is formed radially outside the portion where each window hole 41 is formed. The projection 49 extends further radially outward from the outer peripheral edge 48 of the separation flange 6. The protrusion 49 extends long in the rotation direction, and has stopper surfaces 50 at both ends in the circumferential direction. Protrusion 49
Has a width in the circumferential direction shorter than that of the window hole 41 and is formed substantially at an intermediate position in the circumferential direction. In other words, the stopper surface 50 of the projection 49 is
1, and is located further inward in the circumferential direction than the contact portion of the window hole 41.
The protrusion 49 may be formed as long as the stopper surfaces 50 are formed at both ends in the circumferential direction, and therefore need not necessarily have an intermediate portion. That is, the projections may be provided at two locations in the circumferential direction to form stopper surfaces on both sides.

The structure of the separation flange 6 described above will be described again using other expressions. The separation flange 6 has an annular portion 70 on the inner peripheral side, and further has a plurality of projecting portions 47 projecting radially outward from the annular portion 70. In this embodiment, four protrusions 47 are formed at equal intervals in the rotation direction. Each projection 47 is formed to be long in the rotation direction, and the above-described window hole 41 is formed therein. The window hole 41 is formed over the entirety of the projecting portion 47.

When the projecting portion 47 is expressed in another expression, the projecting portion 47 is formed by connecting two circumferential side window frames 91 extending in the radial direction and the radially outer ends of the circumferential side window frames 91 to each other. And an outer peripheral side window frame portion 92 to be connected. The inner side in the circumferential direction of the window frame portion 91 at both ends in the circumferential direction is the contact portion 44, and the outer side in the circumferential direction is the edge surface 43. The radially inner side of the outer peripheral side window frame portion 92 is the outer peripheral portion 45, and the radially outer side is the outer peripheral edge 48. The aforementioned protrusion 49 is formed on the outer peripheral edge 48. The outer side in the radial direction of the projection 49 is an outer side surface 51. The notch 42 described above is used.
Is a space between the window frame portions 91 at both ends in the circumferential direction of the protruding portion 47 adjacent in the rotation direction.

The second spring 8 is an elastic member or spring used for the damper mechanism of the clutch disc assembly 1. Each second spring 8 is constituted by a pair of coil springs arranged concentrically. Each second spring 8 is larger than each first spring 7 and has a larger spring constant. Second spring 8
Are accommodated in the window holes 41 and 35, respectively. Second spring 8
Extends long in the rotation or tangential direction of the clutch disk assembly 1 and is disposed over the entire window hole 41. That is, the circumferential angle of the second spring 8 is substantially equal to the circumferential angle of the window hole 41. Both circumferential ends of the second spring 8 are in contact with or close to the contact portions 44 and 36 of the window hole 41. The torque of the plates 21, 22 can be transmitted to the separating flange 6 via four second springs 8 arranged in parallel.
That is, the second spring 8 elastically connects the plates 21 and 22 and the separation flange 6 in the rotational direction. In other words, when relative rotation occurs between the plates 21 and 22 and the separation flange 6, the second spring 8 is compressed between the two members in the rotation direction. More specifically, the second spring 8 is compressed between the one contact portion 44 and the circumferentially opposite contact portion 36.

On the outer peripheral edge of the retaining plate 22,
Plate-like connecting portions 31 are formed at four locations at equal intervals in the rotation direction. The plate-shaped connecting portion 31 connects the clutch plate 21 and the retaining plate 22 to each other, and further forms a part of a second stopper 10 described later. The plate-like connecting portion 31 is provided on the retaining plate 22.
This is a plate-shaped member integrally formed from the above, and has a predetermined width in the rotation direction. The plate-shaped connecting portions 31 are arranged between the window holes 41 in the circumferential direction, that is, corresponding to the notches 42. The plate-like connecting portion 31 includes a stopper portion 32 extending in the axial direction from the outer peripheral edge of the retaining plate 22 and a fixing portion 33 extending radially inward from an end of the stopper portion 32. The stopper portion 32 is bent from the outer peripheral edge of the retaining plate 22 and extends to the clutch plate 21 side. The fixing portion 33 is bent radially inward from the end of the stopper portion 32. The plate-like connecting portion 31 described above is used for the retaining plate 22.
And the thickness is almost the same as that of the retaining plate 22. Therefore, the stopper portion 32 has only a width corresponding to the thickness of the retaining plate 22 in the radial direction. The stopper portion 32 has stopper surfaces 39 on both sides in the circumferential direction. Fixed part 33
Corresponds to the outer peripheral side portion of the window hole 41, and the circumferential position is between the window holes 41 adjacent in the rotation direction. As a result, the fixing portion 33 is arranged corresponding to the notch 42 of the separation flange 6. Notch 42 is fixed part 3
3, the fixing portion 33 can move through the notch 42 when the retaining plate 22 is axially approached to the clutch plate 21 during assembly. The fixing portion 33 is in contact with the connecting portion 24c of the cushioning plate 24 in parallel and from the transmission side. A hole 33a is formed in the fixing portion 33, and the aforementioned rivet 27 is inserted into the hole 33a. The rivet 27 integrally connects the fixed portion 33, the clutch plate 21, and the cushioning plate 24. Further, caulking holes 34 are formed in the retaining plate 22 at positions corresponding to the fixing portions 33 in the axial direction.

Next, the stopper portion 32 of the plate-like connecting portion 31
The second stopper 10 including the protrusions 49 and the protrusions 49 will be described. The second stopper 10 allows relative rotation by a torsion angle θ2 between the separation flange 6 and the input rotary body 2 and restricts the relative rotation of both members when the torsion angle becomes θ2. The second spring 8 is compressed between the separation flange 6 and the input rotating body 2 in the region of the torsion angle θ2.

In the plan view, the plate-like connecting portions 31 are located at circumferential positions between the window holes 41 in the circumferential direction, inside the cutouts 42, and between the protrusions 49 in the circumferential direction. Further, the radial position of the stopper surface 50 of the plate-shaped connecting portion 31 is further radially outward than the outer peripheral edge 48 of the separation flange 6. That is, the radial position of the stopper 32 and the protrusion 49 is substantially the same. For this reason, the stopper portion 32 and the projection 49 can abut each other when the torsion angle between the separation flange 6 and the plates 21 and 22 increases. When the stopper surface 39 of the stopper portion 32 and the stopper surface 50 of the projection 49 are in contact with each other, the stopper portion 32 is located outside the projecting portion 47 of the separation flange 6, that is, the window hole 41 in the radial direction. That is, it is possible for the stopper portion 32 to enter further in the circumferential direction than the projecting portion 47 and the window hole 41.

The advantages of the second stopper 10 described above will be described. Since the stopper portion 32 has a plate shape,
The angle in the circumferential direction can be shortened as compared with the conventional stop pin. Further, the length of the stopper portion 32 in the radial direction is significantly shorter than that of a conventional stop pin. That is, the radial length of the stopper portion 32 is only the same as the thickness of the plates 21 and 22. This means that the substantial radial length of the second stopper 10 is limited to a short portion corresponding to the thickness of the plates 21 and 22.

The stopper portion 32 is disposed at the outer peripheral edge portion of the plates 21 and 22, that is, at the outermost peripheral position. The radial position of the stopper portion 32 is the protrusion portion 47, particularly the window hole 41.
Is further radially outward than the radial position of the outer peripheral edge 48. Since the stopper portion 32 is located at a different position in the radial direction from the window hole 41, the stopper portion 32 and the window hole 41 do not interfere with each other in the rotation direction. As a result, the second
Maximum torsion angle of damper mechanism by spring 8 and second spring 8
Can be increased together. When the stopper portion is located at the same radial position as the window hole, the torsion angle of the damper mechanism by the second spring and the circumferential angle of the window hole interfere with each other, so that the damper mechanism has a wide angle and the spring has low rigidity. Cannot be realized.

In particular, since the length of the second stopper 10 in the radial direction is much shorter than that of the conventional stop pin, even if the second stopper 10 is provided radially outside of the window hole 41, the outer diameter of the plates 21 and 22 can be reduced. The diameter does not become extremely large. Further, the length of the window hole 41 in the radial direction does not become extremely short.
The intermediate plate 11 is a pair of plate members arranged on the outer peripheral side of the hub 3 between the clutch plate 21 and the separation flange 6 and between the separation flange 6 and the retaining plate 22. The intermediate plate 11 is an annular plate member, and more precisely has a substantially square shape. Note that the inner peripheral edge of the intermediate plate 11 is circular. The intermediate plate 11 is an intermediate member that functions between the separation flange 6 and the input rotator 2. Intermediate plate 11
The function of (1) is to generate large friction when the separation flange 6 and the input rotary body 2 rotate relative to each other. The pair of intermediate plates 11 cannot be rotated relative to each other by a plurality of pins 62. The pin 62 includes a body portion and small-diameter projections extending from the body portion to both sides in the axial direction. The pair of intermediate plates 11 is restricted from approaching each other in the axial direction by abutting the axial end surfaces of the body of the pin 62 in the axial direction. The protrusion of the pin 62 is inserted into a hole formed in the intermediate plate 11. Each intermediate plate 11 and the annular portion 7 of the separation flange 6
Spacers 63 are arranged between the two. The spacers 63 are annular plate members disposed between the intermediate plates 11 and the annular portion 70 of the separation flange 6, respectively. The inner diameter of the spacer 63 is substantially the same as the inner diameter of the intermediate plate 11. A hole into which the body of the pin 62 is inserted is formed in the spacer 63.
The spacer 63 rotates integrally with the intermediate plate 11 by the engagement with the intermediate plate 11. The surface of the spacer 63 on the side facing and in contact with the annular portion 70 of the separation flange 6 is coated with a coating for reducing the coefficient of friction. The annular portion 70 of the separation flange 6 is formed with a hole 71 through which the body of the pin 62 passes in the axial direction. A gap having a twist angle θ4 is secured between the pin 62 and the end of the hole 71 on both sides in the circumferential direction. The magnitude of θ4 is, for example, 0.5 degrees. An angle θAC2 obtained by combining the two torsional angles θ4 is a gap for preventing a large friction from being generated against torsional vibration of a predetermined torque or less in the second range of the torsional angle.

Next, each member constituting each friction generating mechanism will be described. The second friction washer 72 is arranged between the transmission side of the intermediate plate 11 and the inner periphery of the retaining plate 22. The second friction washer 72 mainly includes a resin-made annular main body 74 and an annular friction plate 75 molded on the main body 74. The friction plate 75 is in contact with the transmission-side surface of the transmission-side intermediate plate 11. An engaging portion 76 extends from the inner peripheral portion of the main body 74 toward the transmission. The engaging portion 76 is engaged with the retaining plate 22 so as to be relatively non-rotatable, and is locked so as not to be detachable in the axial direction. A plurality of recesses 74a are formed on the inner peripheral transmission side of the main body 74.

A second cone spring 73 is disposed between the main body 74 and the retaining plate 22. The second cone spring 73 is disposed in a state where it is compressed in the axial direction between the two members. Thereby, the friction plate 75 of the second friction washer 72 is strongly pressed against the first intermediate plate 11. In the second cone spring 73, a plurality of protrusions formed on the inner peripheral side are engaged with the engaging portion 76 so as not to rotate relatively.

The third friction washer 89 is disposed between the engine-side intermediate plate 11 and the inner peripheral portion of the clutch plate 21. The third friction washer 89 includes a main body 90 made of an annular resin, and an annular friction plate 97 molded on the main body 90. The friction plate 97 is the main body 9
0, and is in contact with the engine side of the intermediate plate 11 on the engine side. The third friction washer 89 has a plurality of engagement portions 98 extending from the main body 90 toward the engine in the axial direction. The engaging portion 98 is engaged with a hole formed in the clutch plate 21 so as to be relatively non-rotatable, and is further locked in such a manner that it cannot be detached in the axial direction.

The second and third friction washers 72 and 89 described above are members that rotate integrally with the plates 22 and 21, respectively, and are pressed against the intermediate plate 11 in the axial direction.
The third friction mechanism 14 (second hysteresis torque generation mechanism, second hysteresis torque generation unit) that generates friction when the intermediate plate 11 and the input rotary body 2 rotate relative to each other is configured. The third friction mechanism 14 generates the largest friction (high hysteresis torque) in the damper mechanism of the clutch disk assembly 1.

Next, the first and second bushes 81 and 82 will be described. The first bushes 81 and 82 are intermediate members that frictionally engage with both members between the hub 3 and the input rotating body 2. The first bush 81 is arranged on the engine side, and the second bush 82 is arranged on the transmission side.
The first bush 81 is made of resin and has an annular main body 83. An annular and flat second friction surface 83b is formed on the main body 83 on the engine side in the axial direction. Second friction surface 83b
Is in contact with the inner peripheral side surface of the clutch plate 21.
Further, the inner peripheral surface 83c of the main body 83 is in contact with the outer peripheral surface of the boss 52 so as to be relatively rotatable. That is, the first bush 81 is positioned in the radial direction with respect to the boss 52. A cylindrical portion 84 extending toward the engine in the axial direction is formed on the inner peripheral portion of the main body 83. The cylindrical portion 84 has an inner peripheral surface in contact with the outer peripheral surface of the boss 52 and an outer peripheral surface in the clutch plate 21.
Center hole 37 (inner peripheral edge). Thus, the clutch plate 21 is positioned in the radial direction so as to be rotatable relative to the cylindrical portion 84 of the first bush 81. That is, the clutch plate 21 is connected to the first bush 8.
1 and is positioned in the radial direction on the boss 52 of the hub 3 via the first. An annular and flat first friction surface 83a is formed on the inner peripheral side of the first bush 81 on the transmission side. The first friction surface 83a is in contact with the side surface of the engine of the hub 3 in the axial direction of the flange 54.

The second bush 82 is composed of an annular and resinous main body 87. An annular flat groove 8 opened inward in the radial direction is formed in the inner peripheral portion of the main body 87 in the axial direction on the engine side.
7a are formed. A wave spring 93 is disposed between the groove 87a and the flange 54 in the axial direction while being deformed in the axial direction. Wave spring 93
Is a leaf spring having an annular wavy shape. An annular flat friction surface 87 is provided on the axial transmission side of the main body 87.
b is formed. The friction plate 77
The second bush 82 is arranged on the axial transmission side. The friction plate 70 is, for example, an annular plate member made of sheet metal, and has an annular main body 77a and an annular main body 7a.
And a plurality of engagement portions 77b which are bent in the axial direction from the inner peripheral edge of 7a and extend. The main body 77a is the second
It is in contact with the friction surface 87b of the bush 82. Engaging part 7
7b is axially inserted into a notch 37a formed in the center hole 37 of the retaining plate 22. Both ends in the circumferential direction of the engaging portion 77b are in contact with both ends in the circumferential direction of the notch 37a, whereby the friction plate 77 rotates integrally with the retaining plate 22. A first cone spring 78 is arranged between the main body 77a and the inner peripheral portion of the retaining plate 22. The first cone spring 78 is arranged between the main body 77a and the inner peripheral portion of the retaining plate 22 in a state of being compressed in the axial direction. As a result, the first cone spring 78 connects the friction plate 77 to the second bush 82.
It is urging against. The first cone spring 78 has a plurality of protrusions formed on the inner peripheral side formed on the friction plate 7.
7 is engaged with the engaging portion 77b so as not to rotate relatively.

The repulsive force in the assembled state of the springs as the urging members increases in the order of the second cone spring 73, the first cone spring 78, and the wave spring 93.
In particular, the repulsive force of the wave spring 93 is extremely smaller than the first cone spring 78. Next, the engagement between the first and second bushes 81 and 82 and the engagement between the first and second bushes 81 and 82 and the hub 3 will be described. As shown in FIGS. 9 to 11, a plurality of engaging portions 95 are formed on the surfaces of the first and second bushes 81 and 82 on the side facing the flange 54. Each engagement part 95
Are arranged with a predetermined angle between them in the rotation direction with respect to the outer peripheral teeth 55 of the hub 3, and the first and second bushes 81, 8
It is a member for constituting a stopper mechanism between the hub 2 and the hub 3. The engagement portions 95 are arranged such that a set of three is opposed to each other in the radial direction. The width of the engagement portion 95 in the middle in the rotation direction of each set in the rotation direction is smaller than that of the engagement portions 95 on both sides in the circumferential direction. A gap 79 is provided between each pair of engagement portions 95 in the middle in the rotation direction and the engagement portions 95 on both sides in the circumferential direction. The gap 79 has such a shape that the width in the rotation direction becomes narrower toward the outside in the radial direction. Outer teeth 5
5 are disposed at both axial ends.

FIGS. 9 and 10 show the hub 3 and the second bush 8.
2 is shown in a plan view, and FIG. 11 is a plan view in a state where both members are combined. FIG. 11 shows a state where both members are at the neutral position. A gap having a torsion angle θ3 is secured between the outer peripheral teeth 55 and the engaging portion 95 in the circumferential direction. That is, a stopper between the hub 3 and the bushes 81 and 82 is formed by the outer peripheral teeth 55 and the engaging portions 95. The torsion angle θ3a between the outer peripheral tooth 55 and the negative (R2 side) engaging portion 95 is set.
Is larger than the torsion angle θ3b between the outer peripheral tooth 55 and the engaging portion 95 on the positive side (R1 side). As an example in this embodiment, θ3a is 3.5 °, and θ3b is 0.3 °.
5 ゜.

The engaging portions 95 on both sides of each pair of the second bush 82
Is formed with a projection 88 extending in the axial direction.
An insertion portion 99 further extending in the axial direction from 8 is formed. A projecting portion 85 extending in the axial direction is formed in the engaging portion 95 on both sides of each pair of the first bush 81, and a concave portion 86 is formed in the projecting portion 85. The protrusions 85 and 88 extend in the notch 69 of the separation flange 6, and the insertion portion 99 is
6 is inserted. With this engagement, the first bush 81 and the second bush 82 function as members that rotate together. Note that gaps larger than θ3 are secured between the protrusions 85 and 88 and the circumferential ends of the notches 69, respectively.

The first bush 81 has a first friction surface 83a in contact with the axial engine side surface of the flange 54, and a flat surface 80, which is the bottom surface of the gap 79, in contact with the axial engine side surface of the outer teeth 55. The flat surface 80 of the second bush 82 is also in contact with the axial transmission side surface of the outer peripheral tooth 55. Thus, the first friction mechanism 12 is formed between the first and second bushes 81 and 82 and the hub 3. The magnitude of the friction generated by the first friction mechanism 12 is
It is determined by the urging force of the wave spring 93 and the coefficient of friction between the first bush 81 and the flange 54.

The magnitude of the friction generated by the second friction mechanism 13 depends on the urging force of the first cone spring 78, the coefficient of friction between the clutch plate 21 and the first bush 81, and the second bush 82 and the friction plate 77. Determined by the coefficient of friction between Further, the third friction mechanism 14
Is determined by the urging force of the second cone spring 73 and the coefficient of friction between the intermediate plate 11 and the second and third friction washers 72, 89. Here, the friction of the first friction mechanism 12 is the smallest, and the friction of the second friction mechanism 13 is the second smallest. The magnitude of the friction generated by the first friction mechanism 12 is, for example, 1/10 or less of the friction of the second friction mechanism 13. The friction at the second friction mechanism 13 is half or less than the friction at the third friction mechanism 14.

Next, the structure of the damper mechanism of the clutch disk assembly 1 will be described in more detail with reference to FIG. FIG. 12 is a mechanical circuit diagram of the damper mechanism of the clutch disk assembly 1. This mechanical circuit diagram schematically illustrates a damper mechanism, and the hub 3 is connected to the input rotating body 2.
FIG. 9 is a diagram used to explain the operation and relationship of each member when twisted in one direction (for example, the R2 side) with respect to FIG. As is apparent from the drawing, a plurality of members for constituting a damper mechanism are arranged between the input rotating body 2 and the hub 3. The separation flange 6 (first intermediate member) is
And the hub 3. The separation flange 6 is elastically connected to the hub 3 via a first spring 7 in the rotational direction. Further, a first stopper 9 is formed between the separation flange 6 and the hub 3. The first spring 7 is compressible during the first torsion angle θ1 of the first stopper 9. The separation flange 6 is provided with the second
It is elastically connected in the rotation direction via a spring 8. Further, a second stopper 10 is formed between the separation flange 6 and the input rotating body 2. The second spring 8 can be compressed between the second torsion angles θ2 of the second stopper 10. The sum of θ1 and θ2 is the maximum torsional angle on either the positive or negative side of the damper mechanism. To summarize the above configuration, the first rotator 2 and the hub 3
The spring 7 and the second spring 8 elastically connect in the rotational direction. Here, the separation flange 6 functions as an intermediate member disposed between the two types of springs. The first spring 7, the second spring 8, and the separation flange form an elastic connection mechanism that elastically connects the input rotary body 2 and the hub 3 in the rotational direction.

The above-described structure has a damper composed of the first spring 7 and the first stopper 9 arranged in parallel, a second spring 8 and a second stopper 10 arranged in parallel.
Can be seen as a structure in which dampers made of are arranged in series. The rigidity of the entire first spring 7 is set to be much smaller than the rigidity of the entire second spring 8. for that reason,
In the range of the torsion angle up to the first torsion angle θ1, the second spring 8
Is hardly compressed.

In the mechanical circuit diagram, the position of the damper consisting of the first spring 7 and the first stopper 9 and the position of the damper consisting of the second spring 8 and the second stopper 10 are interchangeable. The intermediate plate 11 (third intermediate member) is arranged between the separation flange 6 and the input rotary body 2, that is, in parallel with the second spring 8. The intermediate plate 11 is engaged with the separation flange 6 so as to be relatively rotatable by a predetermined angle (θAC2). The intermediate plate 11 is in frictional engagement with the input rotary member 2, and thus forms a third friction mechanism 14 between the intermediate plate 11 and the friction washers 72, 89. The gap (θAC2) formed between the intermediate plate 11 and the separation flange 6 causes the third friction mechanism 14 to slip when a minute vibration of a predetermined torque or less is input in the second range of the torsion angle. This is a structure (a second friction suppressing mechanism, a second gap mechanism) for preventing such a situation.

The gap θAC2 and the third friction mechanism 14, which are arranged in series, constitute a first friction connecting portion for frictionally connecting the separation flange 6 and the input rotary member 2. In this mechanical circuit diagram, the gap (θAC2) and the third friction mechanism 14
The positions are interchangeable. First and second bush 8
1, 82 (second intermediate member) is arranged between the hub 3 and the input rotary body 2. First and second bushes 81, 82
Forms a first friction mechanism 12 (third hysteresis torque generating section) with the hub 3 and a second friction mechanism 13 (first friction generating mechanism, first hysteresis torque generating mechanism) with the input rotary body 2. , A first hysteresis torque generating section). That is, the first and second bushes 81, 82
Constitute two friction engagement portions that function in series between the input rotary body 2 and the hub 3. The first friction mechanism 12
The magnitude of the generated hysteresis torque is set to be small, and may be extremely small or close to zero in some cases.

The first and second bushes 81 and 82 have a gap (θAC1) between them and the hub 3. This gap (θAC1) is arranged in parallel with the first friction mechanism 12. The gap (θAC1) is arranged in series with the second friction mechanism 13, and is configured to prevent the second friction mechanism 13 from slipping when a minute vibration of a predetermined torque or less is input in the first-stage range (the first friction mechanism 13). Friction suppression mechanism, first gap mechanism).

The gap θAC1 and the second friction mechanism 13 arranged in series constitute a second friction connecting portion that frictionally connects the hub 3 and the input rotary body 2 in the rotational direction. In this mechanical circuit diagram, the gap (θAC1) and the second friction mechanism 1
The position with 3 is interchangeable. The second friction mechanism 13, the third friction mechanism 14, the gap θAC1, and the gap θA described above.
A friction generating mechanism that frictionally engages between the input rotary body 2 and the hub 3 in the rotational direction by C2 or the like and generates friction (hysteresis torque) when the two members rotate relative to each other.

Description of Operation The function of the clutch disk assembly 1 as a damper will be described. FIG. 12 shows the input rotator 2
And the hub 3 in a neutral position. FIG.
From the state described above, the input rotator 2 is fixed to another member so as not to rotate relative thereto, and the hub 3 is set to the negative side (R2 side).
Twist. At this time, the input rotating body 2 is twisted to the positive side (R1 side) with respect to the hub 3.

In the small range of the torsion angle, the first spring 7 is compressed between the hub 3 and the separation flange 6, and the first friction mechanism 12 slips. As a result, characteristics of low hysteresis torque and low rigidity are obtained. When the outer peripheral teeth 55 come into contact with the engaging portions 95, the relative rotation between the hub 3 and the bushes 81 and 82 stops as shown in FIG. If the torsion angle is further increased, the compression of the first spring 7 proceeds, and the second friction mechanism 13 slips. Therefore, high rigidity and high hysteresis torque characteristics can be obtained in the first stage. When the torsion angle becomes θ1, as shown in FIG.
Compression stops. When the torsion angle is further increased, the second spring 8 is compressed, and the second friction mechanism 13 slips. As a result, characteristics of high rigidity and high hysteresis torque can be obtained. When twisted by θ4 from the state of FIG. 14, the stop pin 62 and the hole 71 are engaged, and thereafter, the third friction mechanism 14 slips as shown in FIG. In the state shown in FIG. 16, the second spring 8 is compressed, and the second friction mechanism 13 and the third friction mechanism 14 are acting on the second spring 8 in parallel.
As a result, characteristics of high rigidity and high hysteresis torque can be obtained in the second range of the torsion angle.

Next, the damper function will be further described with reference to the torsional characteristic diagram of FIG. This torsion characteristic diagram shows the relationship between the torsion angle and the torque when the input rotary body 2 and the hub 3 are twisted between the positive and negative maximum torsion angles.
Here, FIG. 16 is described as an arrangement when the hub 3 is twisted to the negative side (R2 side) by a predetermined angle and then returned to the positive side (R1 side). The second spring 8 extends to return to the original state, and moves the separation flange 6 and the hub 3 to the R1 side. At this time, a slip occurs in the first friction mechanism 12, and a small hysteresis torque is generated. This small hysteresis section is shown in FIG.
This is the D portion of 0, which is the magnitude of θAC2. That is, when the torsional vibration acts in the torsional angle range of θAC2, no high hysteresis torque is generated. FIG.
When the separating flange 6 and the hub 3 are moved by θAC2 from above, the pin 62 and the hole 69 come into contact with each other, and thereafter, the third friction mechanism 14 slides as shown in FIG. As a result,
The first friction mechanism 12 and the third friction mechanism 14 generate a relatively high hysteresis torque. This relatively high hysteresis section is, for example, a portion E in FIG. 20, and is a range of θAC1 at the maximum after the direction is changed. When the torsional angle returning to the negative side becomes θAC1, the outer peripheral teeth 55 and the engaging portions 95 come into contact as shown in FIG. As a result, the first
The friction mechanism 12 does not slip, and the second friction mechanism 13 slips. As a result, a high hysteresis torque characteristic is obtained by the second friction mechanism 13 and the third friction mechanism 14 acting in parallel. This high hysteresis section is, for example, a portion F in FIG. 20 and can occur over the entire second stage if it exceeds θAC1 from the start of the return. FIG.
As shown in (1), when the torsion angle enters the first stage, the sliding of the third friction mechanism 14 stops, and the sliding of the second friction mechanism 13 occurs.

FIG. 21 is an enlarged view of the first range of the torsional characteristic shown in FIG. In the positive / negative first stage region, that is, in the range of −2 ° to + 5 °, θ is applied to a small torsional vibration of a predetermined torque or less.
In the range of AC1, only the first friction mechanism 12 functions, and the second friction mechanism 13 does not slip. For example, when a small torsional vibration is input in the state shown in FIGS. 12 and 13, the bushes 81 and 82 are integrally rotated with the input rotating body 2 by the second friction mechanism 13. That is, the hub 3 is connected to the input rotary body 2, the separation flange 6, and the first and second bushes 81, 8.
Rotate relative to 2.

In the torsional vibration acting beyond the range of θAC2, the second friction mechanism 13 acts at both positive and negative ends,
High hysteresis torque characteristics can be obtained. This high hysteresis torque tends to attenuate vibrations that cause abnormal noise during idling, for example. In particular, since the first-stage high hysteresis torque is lower than the second-stage high hysteresis torque, it is effective against abnormal noise during idling.
For example, if the magnitude of the first-stage high hysteresis torque is equal to the magnitude of the second-stage hysteresis torque,
The high hysteresis torque becomes a large wall for the first-stage minute vibration, and may have an adverse effect on vibration damping.

When a minute vibration is input in the second stage range, for example, as shown in FIG. 20, if it is in the range of θAC2, the intermediate plate 11 rotates integrally with the input rotating body 2 and slips between them. Does not occur. At this time, only the first friction mechanism 12 slips and generates a small hysteresis torque. When the angle of the torsional vibration exceeds θAC2 in the second stage range, the first friction mechanism 12 and the third friction mechanism 14 slide and generate a moderate hysteresis torque. Specifically, FIG.
5 or FIG. 16, when a minute vibration is input, θAC
In the range of 2, the separation flange 6 and the hub 3 rotate integrally,
At this time, no slip occurs in the third friction mechanism 14 and the second friction mechanism 13. That is, friction occurs only in the first friction mechanism 12, and a characteristic of small hysteresis torque is obtained. When the torsion angle exceeds θAC2, the intermediate plate 11 rotates integrally with the separation flange 6 as shown in FIG. 17, and the third friction mechanism 14 starts to slide. As a result, the first friction mechanism 12 and the third friction mechanism 14 operate in parallel up to the torsion angle θAC1. If the torsion angle exceeds θAC1, the bush 8
1, 82 rotate integrally with the hub 3, the first friction mechanism 12 stops sliding, and the second friction mechanism 13 starts sliding. As a result,
The second friction mechanism 13 and the fourth friction mechanism 14 act in parallel.

According to the characteristics described above, a wide torsion angle characteristic can be obtained over the entire positive and negative stages for low frequency vibration such as tip-in and tip-out. At this time, a high hysteresis torque is generated in both the first stage range and the second stage range. Therefore, low frequency vibration can be effectively attenuated. As described above, the gap (θAC2) between the separation flange 6 and the intermediate plate 11 does not allow the third friction mechanism 14 to function when a minute vibration of a predetermined torque or less is input in the second stage range. This is a structure for realizing a state of low hysteresis torque. In addition, a gap (θAC) between the hub 3 and the first and second bushes 81 and 82
1) is a structure for preventing the second friction mechanism 13 from functioning when a minute vibration of a predetermined torque or less is input in the first stage range.

In this embodiment, the second friction mechanism 13 slides over both the first stage and the second stage. That is, the second friction mechanism 13 functions in the first stage and plays the role of the first friction generating mechanism, and in the second stage functions together with the third friction mechanism 14 to constitute a part of the second friction mechanism. The second friction mechanism may be configured to slide only at the first stage, in other words, may be configured to not slide at the second stage. In that case, the second friction mechanism constitutes a first friction generation mechanism, and the third friction mechanism constitutes a second friction generation mechanism. Even in that case, it is preferable that the first-stage high hysteresis torque is smaller than the second-stage high hysteresis torque.

[0062]

According to the damper mechanism of the present invention, a high hysteresis torque can be obtained in the first-stage range by the second hysteresis torque generator functioning in the first-stage range of the torsion angle, and the damping mechanism can attenuate low-frequency vibration. High effect. Also,
When a torsional vibration of a predetermined torque or less is input in the first stage range, the first gap mechanism does not cause the first hysteresis torque generating section to slip. Further, in this damper mechanism, the first hysteresis torque generating section generates a lower hysteresis torque than the second hysteresis torque generating section, which is effective against idling noise during idling.

[Brief description of the drawings]

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

FIG. 2 is a view taken in the direction of arrows II-II in FIG.

FIG. 3 is a partially enlarged view of FIG. 1;

FIG. 4 is a view taken in the direction of arrows IV-O in FIG. 1;

FIG. 5 is a view taken in the direction of arrows VO in FIG. 1;

FIG. 6 is a view taken in the direction of arrows VI-O in FIG. 1;

FIG. 7 is an exploded sectional view of each part of the clutch disk assembly.

FIG. 8 is a plan view showing the relationship between the separation flange and the hub.

FIG. 9 is a plan view of a hub.

FIG. 10 is a plan view of a bush.

FIG. 11 is a plan view showing a relationship between a hub and a bush.

FIG. 12 is a mechanical circuit diagram of a damper mechanism of the clutch disk assembly.

FIG. 13 is a diagram for explaining the operation of the damper mechanism in the mechanical circuit diagram.

FIG. 14 is a diagram for explaining the operation of the damper mechanism in the mechanical circuit diagram.

FIG. 15 is a diagram for explaining the operation of the damper mechanism in the mechanical circuit diagram.

FIG. 16 is a diagram for explaining the operation of the damper mechanism in the mechanical circuit diagram.

FIG. 17 is a diagram for explaining the operation of the damper mechanism in the mechanical circuit diagram.

FIG. 18 is a diagram for explaining the operation of the damper mechanism in the mechanical circuit diagram.

FIG. 19 is a diagram for explaining the operation of the damper mechanism in the mechanical circuit diagram.

FIG. 20 is a torsional characteristic diagram of the clutch disk assembly of the present invention.

FIG. 21 is an enlarged view of a first range of FIG. 20;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Clutch disk assembly 2 Input rotating body 3 Hub 6 Separation flange 7 1st spring 8 2nd spring 9 1st stopper 10 2nd stopper 11 Intermediate plate 12 1st friction mechanism 13 2nd friction mechanism 14 3rd friction mechanism 81, 82 Bush

Claims (4)

[Claims] A first rotating member, a second rotating member disposed so as to be relatively rotatable with respect to the first rotating member, and a resilient connection of the first rotating member and the second rotating member in a rotating direction. A first elastic member that is compressed in a first-stage range in which a torsion angle of the first rotating member and the second rotating member is up to a first torsion angle; and the first rotating member and the second rotating member. The first rotating member and the second rotating member are compressed in a second stage range in which the torsion angle of the first rotating member and the second rotating member exceeds the first torsion angle. A second elastic member for providing a higher rigidity in the eye range than the first stage range; and a frictional engagement between the first rotating member and the second rotating member in a rotating direction. A friction can be generated in the range of the first step, and a larger friction can be generated in the range of the second step than in the first step. A damper mechanism, comprising: a raw means; and a friction suppressing means that does not cause the friction generating means to slip against torsional vibration of a predetermined torque or less in the first stage range and the second stage range. 2. A first rotating member, a second rotating member disposed so as to be relatively rotatable with respect to the first rotating member, and a resilient connection in a rotating direction between the first rotating member and the second rotating member. A first elastic member that is compressed in a first-stage range in which a torsion angle of the first rotating member and the second rotating member is up to a first torsion angle; and the first rotating member and the second rotating member. The first rotating member and the second rotating member are compressed in a second stage range in which the torsion angle of the first rotating member and the second rotating member exceeds the first torsion angle. A second elastic member for providing a higher rigidity in the eye range than the first stage range; and a frictional engagement between the first rotating member and the second rotating member in a rotating direction. In the step range, it does not slip against torsional vibration below a predetermined torque, and does not slip against torsional vibration above the predetermined torque. A friction generating mechanism that generates a first friction in the first-stage range by sliding and generates a second friction larger than the first friction in the second-stage range. 3. A first rotating member, a second rotating member disposed so as to be relatively rotatable with respect to the first rotating member, and a resilient connection of the first rotating member and the second rotating member in a rotation direction. A first elastic member that is compressed in a first-stage range in which a torsion angle of the first rotating member and the second rotating member is up to a first torsion angle; and the first rotating member and the second rotating member. The first rotating member and the second rotating member are compressed in a second stage range in which the torsion angle of the first rotating member and the second rotating member exceeds the first torsion angle. A second elastic member for providing a higher rigidity in the eye range than the first stage range; and a frictional engagement between the first rotating member and the second rotating member in a rotating direction; The first that can generate friction
A friction generating mechanism, a second friction generating mechanism capable of frictionally engaging the first rotating member and the second rotating member in a rotational direction and generating a second friction greater than the first friction in the second stage range. When a torsional vibration of a predetermined torque or less is inputted in the first stage range, the first friction generating mechanism does not cause slippage.
A friction suppressing mechanism, and a second friction generating mechanism that does not cause a slip in the second friction generating mechanism when a torsional vibration of a predetermined torque or less is input in the second stage range.
A damper mechanism including a friction suppressing mechanism. 4. A first rotating member, a second rotating member disposed so as to be rotatable relative to the first rotating member, and the first rotating member and the second rotating member are elastically connected in a rotating direction. A first elastic member that is compressed in a first-stage range in which a torsion angle of the first rotating member and the second rotating member is up to a first torsion angle; and the first rotating member and the second rotating member. The first rotating member and the second rotating member are compressed in a second stage range in which the torsion angle of the first rotating member and the second rotating member exceeds the first torsion angle. A second elastic member for providing higher rigidity in the eye range than the first stage range, a first hysteresis torque generating mechanism capable of generating a first hysteresis torque in the first stage range and the second stage range, Only in the second stage range, the second hysteresis torque generating mechanism acts in parallel with the second hysteresis torque generating mechanism. A damper mechanism comprising: a second hysteresis torque generating mechanism capable of generating a hysteresis torque; and a hysteresis torque suppressing mechanism that does not allow the first and second hysteresis torque generating mechanisms to act on torsional vibration of a predetermined torque or less. .