JPH11280785A - Damper mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To damp torsional vibration having a wide torsional angle such as vehicle body lengthwise vibration in a damper mechanism having a two-stage characteristic. SOLUTION: A damper mechanism is equipped with: a pair of plates 21 and 22, an output rotor 3, a separation flange 6, a first and second springs 7 and 8, and an intermediate plate 11. The flange 6 is arranged between the plates 21 and 22 on the outer peripheral side of the rotor 3. The spring 7 elastically connects the rotor 3 and the flange 6 in a rotation direction. The spring 8 elastically connects the flange 6 and the plates 21 and 22 in the rotation direction, and the plate 11 is arranged between the rotor 3 and the plates 21 and 22. The plate 11 ensures the gap of a second torsional angle θ2 between the plate and a hub 3, forms a friction generation mechanism 13 between the plates 21 and 22, and partially has a third torsional angle θ3 between the plate and the spring 8 between.

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. 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. In general, vibrations of a vehicle include abnormal noises during idling (rattle noise), abnormal noises during running (acceleration / deceleration rattle, muffled noise), 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.

[0002] The idling noise is a noise that is heard from the transmission when the shift is set to neutral and the clutch pedal is released in response to a signal or the like. The cause of the abnormal 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. At this time, the input gear and the counter gear of the transmission cause a rattling phenomenon to generate abnormal noise.

[0003] Tip-in / tip-out (low-frequency vibration) refers to a large front-back vibration of the vehicle body that occurs when the accelerator pedal is suddenly depressed or suddenly released. If the rigidity of the drive transmission system is low, the torque transmitted to the tires will be transmitted from the tire side to the drive side, causing excessive torque on the tires as a backlash, and as a result, the vehicle body will transiently largely swing back and forth. Vibration back and forth.

[0004] 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 it is better that the torsional rigidity there is low. On the other hand, it is necessary for the torsional characteristics of the clutch disk assembly to be as close as possible to a solid with respect to the longitudinal vibration of the tip-in and tip-out. In order to solve the above-mentioned problem, a clutch disk assembly which realizes a two-stage characteristic by using two types of springs has been provided. In this case, the first-stage torsional rigidity and the hysteresis torque of the low torsion angle are suppressed to be low, so that there is an effect of preventing abnormal noise during idling. Further, since the second torsional rigidity and the hysteresis torque at a high torsion angle are set high, the longitudinal vibration at the time of tip-in / tip-out can be effectively attenuated.

[0005] Further, in the second stage region having a high torsion angle, for example, when minute vibrations caused by engine combustion fluctuations are input, the second stage high hysteresis torque generating mechanism is not operated, so that the minute vibrations are generated by the low hysteresis torque. There is also known a damper mechanism that effectively absorbs the pressure.

[0006]

In the damper mechanism of the conventional clutch disk assembly, when low-frequency vibration is input, the torsion characteristic causes a widening between the second stage on the positive side and the second stage on the negative side. Repeat the twisting operation in the angle range. At this time, only a low hysteresis torque is generated in the first-stage region between the positive and negative sides. Therefore, the entire vibration attenuation is small, and low-frequency vibration cannot be sufficiently attenuated. In addition, the first-positive / negative region serves as a gap in the torsional characteristics, and may deteriorate the longitudinal vibration.

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.

[0008]

According to a first aspect of the present invention, there is provided a damper mechanism including a first rotating member, a second rotating member, a first damper mechanism, and a second damper mechanism. The second rotating member is arranged to be relatively rotatable with the first rotating member. First
The damper mechanism is a mechanism for connecting the first rotating member and the second rotating member in a rotating direction to attenuate torsional vibration.
The first damper mechanism includes a first elastic member disposed between the first rotating member and the first intermediate member, the first elastic member being compressible to a first circumferential angle, and a first elastic member between the first intermediate member and the second rotating member. And a second elastic member having a larger spring constant than the first elastic member. The second damper mechanism is a mechanism that connects the first rotating member and the second rotating member in the rotation direction, is arranged in parallel with the first damper mechanism, and attenuates torsional vibration. Second
The damper mechanism includes a second intermediate member disposed between the first rotating member and the second rotating member, and a second intermediate member having a first circumferential direction angle equal to or less than a first circumferential direction angle between the first rotating member and the second intermediate member. A stopper having a gap at a circumferential angle, and a friction generating mechanism for frictionally engaging the second intermediate member and the second rotating member in a rotational direction, wherein a part of the second intermediate member is provided with a second elastic member; Has a gap at a third circumferential angle. The third circumferential angle is
It is greater than the difference between the first circumferential angle minus the second circumferential angle.

[0009] In the damper mechanism according to the first aspect,
When torque is input to the second rotating member, the torque is transmitted to the first rotating member via the first damper mechanism and the second damper mechanism arranged in parallel. The first damper mechanism functions in a small range of the torsion angle, and the second damper mechanism functions in a large range of the torsion angle. The torsional characteristics of the damper mechanism according to claim 1 will be described. here,
Description will be made based on the operation when the first rotating member is twisted in one direction with respect to the second rotating member. In the first stage up to the first circumferential angle, the first elastic member is compressed, so that relatively low rigidity characteristics can be obtained. At this time, a high hysteresis torque is generated due to slippage of the friction generating mechanism. When the torsion angle exceeds the first circumferential direction angle, the second elastic member is compressed, and a relatively high rigidity characteristic is obtained. In this case, slippage occurs in the friction generating mechanism, and high hysteresis torque characteristics can be obtained. As described above, since high hysteresis torque characteristics can be obtained in both the first stage and the second stage, it is effective for a vibration having a relatively wide torsion angle such as a vehicle longitudinal vibration.

When a small vibration having a small torque is input in the first stage range, the second intermediate member and the first rotating member move between the second intermediate member and the first rotating member.
The second intermediate member is rotatable relative to the first rotating member corresponding to the circumferential angular gap. That is, this second
No slip occurs in the friction generating mechanism within the circumferential angle range. Further, when the small torsional vibration is input in the second stage range, the third intermediate member and the second elastic member are connected between the third intermediate member and the second elastic member.
A gap having an angle equal to a value obtained by subtracting the first circumferential direction angle from the circumferential direction angle and adding the second circumferential direction angle is secured. In the second stage range, the second elastic member does not act on the second intermediate member within this gap angle range, and the second intermediate member and the second rotating member can rotate integrally. That is, no slip occurs in the friction generating mechanism at this time.

As described above, when the small torsional vibration is input in the first-stage range and the second-stage range, the friction generating mechanism does not operate, and the high hysteresis torque is not generated. As a result, the small torsional vibration can be effectively absorbed. A damper mechanism according to a second aspect includes a first rotating member, a second rotating member, a first intermediate member, a first elastic member, a second elastic member, a second intermediate member, a stopper, and a friction generating mechanism. . The second rotating member is arranged to be relatively rotatable with the first rotating member. The first intermediate member includes a first rotating member and a second rotating member.
It is arranged between the rotating member. The first elastic member is a first elastic member.
It is arranged between the rotating member and the first intermediate member and is compressible to a first circumferential angle. The second elastic member is disposed between the first intermediate member and the second rotating member, and has a larger spring constant than the first elastic member. The second intermediate member is disposed between the first rotating member and the second rotating member. The stopper has a gap between the first rotating member and the second intermediate member at a second circumferential angle that is less than or equal to the first circumferential angle. The friction generation mechanism is the second
The intermediate member and the second rotating member are frictionally engaged in the rotating direction.
A part of the second intermediate member has a gap at a third circumferential angle between the second intermediate member and the second elastic member. The third circumferential angle is the first
It is greater than the difference between the circumferential angle minus the second circumferential angle.

[0012] In the damper mechanism according to claim 2,
When torque is input to the second rotating member, the first intermediate member,
Torque is transmitted to the first rotating member via the first elastic member, the second elastic member, the second intermediate member, and the stopper. The first elastic member is compressed in a small range of the torsion angle, and the second elastic member is compressed in a large range of the torsion angle. The torsional characteristic of the damper mechanism according to claim 2 will be described. Here, the description will be made based on the operation when the first rotating member is twisted in one direction with respect to the second rotating member. In the first stage up to the first circumferential angle, the first elastic member is compressed, so that relatively low rigidity characteristics can be obtained. At this time, a high hysteresis torque is generated due to slippage of the friction generating mechanism. When the torsion angle exceeds the first circumferential angle,
The second elastic member is compressed, and a relatively rigid characteristic is obtained. In this case, slippage occurs in the friction generating mechanism, and high hysteresis torque characteristics can be obtained. As described above, since high hysteresis torque characteristics can be obtained in both the first stage and the second stage, it is effective for a vibration having a relatively wide torsion angle such as a vehicle longitudinal vibration.

When a small vibration with a small torque is input in the first stage range, the second vibration between the second intermediate member and the first rotating member is caused.
The second intermediate member is rotatable relative to the first rotating member corresponding to the circumferential angular gap. That is, this second
No slip occurs in the friction generating mechanism within the circumferential angle range. Further, when the small torsional vibration is input in the second stage range, the third intermediate member and the second elastic member are connected between the third intermediate member and the second elastic member.
A gap having an angle equal to a value obtained by subtracting the first circumferential direction angle from the circumferential direction angle and adding the second circumferential direction angle is secured. In the second stage range, the second elastic member does not act on the second intermediate member within this gap angle range, and the second intermediate member and the second rotating member can rotate integrally. That is, no slip occurs in the friction generating mechanism at this time.

As described above, when the small torsional vibration is input in the first-stage range and the second-stage range, the friction generating mechanism does not operate, and the high hysteresis torque is not generated. As a result, the small torsional vibration can be effectively absorbed. A damper mechanism according to a third aspect includes an output hub, a pair of input plates, a first intermediate member, a first elastic member, a second elastic member, and a second intermediate member. A pair of input plates are disposed for relative rotation about the output hub. The first intermediate member is disposed between the pair of input plates on the outer peripheral side of the output hub. The first elastic member elastically connects the output hub and the first intermediate member in a rotational direction. The second elastic member elastically connects the first intermediate member and the pair of input plates in the rotational direction. The second elastic member has a larger spring constant than the first elastic member. The second intermediate member is disposed between the output hub and the pair of input plates. The second intermediate member secures a gap at a second circumferential angle that is equal to or less than the first circumferential angle between the second intermediate member and the output hub, and forms a friction engagement portion between the second intermediate member and the pair of input plates. A part has a gap at a third circumferential angle with the second elastic member. The third circumferential angle is
It is greater than the difference between the first circumferential angle minus the second circumferential angle.

[0015] In the damper mechanism according to claim 3,
When the torque is input to the pair of input plates, the torque is transmitted to the output hub in the order of the second elastic member, the first intermediate member, and the first elastic member. The first elastic member is compressed in a small range of the torsion angle, and the second elastic member is compressed in a large range of the torsion angle. The torsional characteristic of the damper mechanism according to the third aspect will be described. Here, description will be made based on the operation when the hub is twisted in one direction with respect to the pair of input plates. In the first stage up to the first circumferential angle, the first
By compressing the elastic member, relatively low rigidity characteristics can be obtained. At this time, a high hysteresis torque is generated due to slippage of the friction generating mechanism. When the torsion angle exceeds the first circumferential direction angle, the second elastic member is compressed, and a relatively high rigidity characteristic is obtained. In this case, slippage occurs in the friction generating mechanism, and high hysteresis torque characteristics can be obtained. As described above, since high hysteresis torque characteristics can be obtained in both the first stage and the second stage, it is effective for a vibration having a relatively wide torsion angle such as a vehicle longitudinal vibration.

When a small vibration with a small torque is input in the first stage range, the second intermediate member can rotate relative to the hub first rotating member corresponding to the gap at the second circumferential angle. That is, no slip occurs in the friction generating mechanism within the second circumferential angle range. Further, when the small torsional vibration is input in the second range, the first circumferential angle is subtracted from the third circumferential angle between the second intermediate member and the second elastic member. A gap having an angle equal to the sum of two circumferential angles is secured. In the range of the second step, the second elastic member does not act on the second intermediate member within this gap angle range, and the second intermediate member and the pair of input plates can rotate integrally. That is, no slip occurs in the friction generating mechanism at this time.

As described above, when the small torsional vibration is input in the first-stage range and the second-stage range, the friction generating mechanism does not operate and the high hysteresis torque is not generated. As a result, the small torsional vibration can be effectively absorbed.

[0018]

FIG. 1 is a sectional view of a clutch disk assembly 1 according to an embodiment of the present invention, and FIG. 2 is a plan 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 interrupting torque by connecting and disconnecting to and from a flywheel (not shown). The damper function is a function of absorbing and attenuating a torque fluctuation or the like input from the flywheel side by a spring or the like. In FIG. 1, OO is the rotation axis of the clutch disk assembly 1, that is, the rotation center line. Further, an engine and a flywheel (not shown) are arranged on the left side of FIG. 1, and a transmission (not shown) is arranged on the right side of FIG. Further, the R1 side in FIG. 2 is the rotation direction (positive side) of the clutch disk assembly 1, and the opposite direction (negative side) from the R2 side.

The clutch disk assembly 1 mainly includes an input rotating body 2 (clutch plate 21, retaining plate 22, clutch disk 23), an output rotating body 3 (hub), an input rotating body 2 and an output rotating body. 3 and a damper mechanism arranged between them. The damper mechanism includes a first spring 7, a second spring 8, a friction generating mechanism 13, and the like.

The 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 21 and retaining plate 2
Numeral 2 is a disk-shaped or annular member made of sheet metal, and is disposed at a predetermined interval 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 pressed against a flywheel (not shown). The clutch disc 23 mainly includes a cushioning plate 24 and first and second friction facings 25.
The cushioning plate 24 includes an annular portion 24a, 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 in four places, each of which has a rivet 27.
It is fixed to the clutch plate 21 by (described later). Friction facings 25 are provided on both sides of each cushioning portion 24b of the cushioning plate 24 with rivets 2.
6 fixed.

Four window holes 35 are formed in the outer peripheral portions of the clutch plate 21 and the retaining plate 22 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 are for regulating the movement of the second spring 8 described later in the axial and radial directions. The window hole 35 has a second spring 8.
Are formed at both ends in the circumferential direction.

Each of the clutch plate 21 and the retaining plate 22 has a center hole 37 (inner peripheral edge). A spline hub as the output rotating body 3 is arranged in the center hole 37. The output rotator 3 is
It comprises a cylindrical boss 52 extending in the axial direction, and a flange 54 extending in the radial direction from the boss 52. Boss 5
A spline hole 53 that engages with a shaft extending from the transmission (not shown) is formed in the inner peripheral portion of the transmission 2. A notch 5 for accommodating a plurality of outer teeth 55 arranged in the rotation direction and a first spring 7 described later is formed in the flange 54.
6 and the like are formed. The notches 56 are formed at two locations facing each other in the radial direction.

The separation flange 6 is a disk-shaped member disposed on the outer peripheral side of the output rotating body 3 and between the clutch plate 21 and the retaining plate 22. The separation flange 6 is elastically connected to the output rotator 3 in the rotation direction via a first spring 7, and is also elastically connected to the input rotator 2 via a second spring 8. As shown in detail in FIG. 5, a plurality of inner peripheral teeth 5
9 are formed. The inner peripheral teeth 59 are the same as the aforementioned outer peripheral teeth 55.
And at a predetermined interval in the rotation direction. The outer peripheral teeth 55 and the inner peripheral teeth 59 can contact each other in the rotation direction. That is, the outer teeth 55 and the inner teeth 59
Thus, a first stopper 9 for regulating the torsion angle between the input rotating body 3 and the separation flange 6 is formed. A first torsion angle θ1 is secured between the outer teeth 55 and the inner teeth 59 on both sides in the circumferential direction. Outer teeth 55
Torsion angle θ between inner peripheral teeth 59 on the R1 side as viewed from above
1 is about 2 °, and the first torsion angle θ1 between the outer circumferential teeth 55 and the inner circumferential teeth 59 on the R2 side is about 5 °.

Further, a notch 67 is formed on the inner peripheral edge of the separation flange 6 so as to correspond to the notch 56 of the flange 54. In the notches 56, 67, two first springs 7 are arranged, one each. The first springs 7 are low-rigidity coil springs, and the two first springs 7 act in parallel. The first spring 7 is engaged with the circumferential ends 57 and 68 of the notches 56 and 67 at both ends in the circumferential direction via spring seats. With the above structure, when the output rotating body 3 and the separation flange 6 rotate relative to each other, the first spring 7 is compressed in the rotation direction within the range of the first torsion angle θ1.

The separation flange 6 is provided at regular intervals in the rotation direction.
Window holes 41 are formed. The window hole 41 has a shape that extends long in the rotation direction. The 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 have a shape in which a part is opened radially outward. A notch 42 is formed in the separation flange 6 between the window holes 41 in the circumferential direction. The notch 42 has a fan shape whose circumferential length increases from the radially inner side to the outer side, 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. That is, the protrusion 49
Is a protruding shape extending 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 a stopper surface 50 formed thereon. The protrusion 49 has a shorter circumferential width than the window hole 41 and is formed substantially at an intermediate position in the circumferential direction. That is, the stopper surface 50 of the projection 49 is disposed further inward in the circumferential direction than the edge surface 43 of the notch 42 with respect to the window hole 41, and further inward in the circumferential direction than the contact portion 44 of the window hole 41. Are located. The protrusions 49 may be formed as long as stopper surfaces are formed at both ends in the circumferential direction, and do not necessarily require an intermediate portion in the circumferential direction. That is, the projections may have a shape provided at two locations in the circumferential direction to form the 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 on the inner peripheral side, and has a plurality of projecting portions 47 projecting radially outward from the annular portion. In this embodiment, four protrusions 47 are formed at equal intervals in the rotation direction.
The protruding portion 47 is formed to be long in the rotation direction, and the above-described window hole 41 is formed therein. The window hole 41 occupies 70% or more of the area of the projection 47 and is formed over the projection 47.

The projecting portion 47 will be described in another expression. The projecting portion 47 is composed of two circumferential side window frames 91 extending in the radial direction, and two radially outer ends of the circumferential side window frames 91 connected to each other. And an outer peripheral side window frame portion 92 connecting the two. 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. Outer edge 4
The projections 49 are formed on 8. The notch 42 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, that is, a spring used for the damper mechanism of the clutch disk 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. The second spring 8 is accommodated in each of the window holes 41 and 35. Second spring 8
Is elongated in the rotation direction, 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 θB of the window hole 41 described later. Second
Both ends in the circumferential direction of the spring 8 are in contact with or close to the contact portion 44 of the window hole 41 and the contact surface 36. Plates 21, 22
Can be transmitted to the separation flange 6 via the second spring 8. When the plates 21 and 22 and the separation flange 6 rotate relative to each other, the second spring 8 is compressed between them. Specifically, the second spring 8 is compressed in the rotational direction between the contact surface 36 and the contact portion 44 on the opposite side in the circumferential direction. At this time, the four second springs 8 are acting in parallel. In a free state (a state in which no torsion occurs between the separation flange 6 and the plates 21 and 22), the radially inner portions at both ends in the circumferential direction of the second spring 8 abut or approach the abutting portion 44. However, the radially outer portions at both ends in the circumferential direction are slightly separated from the contact portion 44.

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 forms a part of a stopper of the clutch disk assembly 1 as described later. The plate-like connecting portion 31
It is a plate-shaped member integrally formed from the retaining plate 22 and has a predetermined width in the rotation direction. The plate-like connecting portion 31 is provided between the window holes 41 in the circumferential direction, that is, the notch 42.
It is arranged corresponding to. 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 extends from the outer peripheral edge of the retaining plate 22 to the clutch plate 21 side. The fixing portion 33 is bent radially inward from the end of the stopper portion 32. The plate-shaped connecting portion 31 described above is an integral part of the retaining plate 22 and has substantially the same thickness as the retaining plate 22. Therefore, the stopper 3
2 has only a width corresponding to the thickness of the retaining plate 22 in the radial direction. The stopper portion 32 has stopper surfaces 51 on both sides in the circumferential direction. The radial position of the fixing portion 33 corresponds to the outer peripheral portion of the window hole 41,
The circumferential position is between the window holes 41 adjacent in the rotation direction. As a result, the fixing portion 33 is provided with the notch 4
2 are arranged. Notch 42 is fixed part 33
The fixing portion 33 is movable through the notch 42 when the retaining plate 22 is moved in the axial direction with respect to the clutch plate 21 during assembly. The fixing portion 33 is in contact with the connection portion 24c of the cushioning plate 24 in parallel with the transmission portion. 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, a caulking hole 34 is formed in the retaining plate 22 at a position corresponding to the fixing portion 33.

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 the relative rotation of the two members in the region up to the torsion angle θ4 between the separation flange 6 and the input rotary body 2, and restricts the relative rotation of the two members when the torsion angle becomes θ4. It is. Note that this torsion angle θ4
The second spring 8 is compressed between the separation flange 6 and the input rotating body 2.

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. The radial position of the stopper surface 51 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 51 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 arranged at the outer peripheral edge portion of the plates 21 and 22, that is, at the outermost peripheral position.
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 45, 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 Twist 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 on the outside of the window hole 41 in the radial direction, the outside 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 between the clutch plate 21 and the separation flange 6 and between the separation flange 6 and the retaining plate 22 on the outer peripheral side of the output rotating body 3. Intermediate plate 1
Reference numeral 1 denotes a disk-shaped or annular plate member, which is a part of the damper mechanism between the input rotary body 2 and the output rotary body 3. A plurality of inner peripheral teeth 66 are formed on the inner peripheral edge of the intermediate plate 11. The inner peripheral teeth 66 are disposed so as to overlap the inner peripheral teeth 59 of the separation flange 6 in the axial direction. The inner peripheral teeth 66 are the outer peripheral teeth 55 of the output rotating body 3 (hub).
And a predetermined gap in the rotation direction. That is, the output rotator 3 and the intermediate plate 11 can rotate relative to each other within the range of the gap. The outer teeth 55 and the inner teeth 59 form a third stopper 12 that regulates a relative rotation angle between the output rotating body 3 and the intermediate plate 11. More specifically, as shown in FIG.
5, gaps between the inner peripheral teeth 66 on both sides in the circumferential direction are secured by the second torsion angle θ2. In this embodiment, the second torsion angles θ2 are both equal and about 2 °. The magnitude of the second torsion angle θ2 is equal to or less than the first torsion angle θ1. This comparison is made at each angle on the same side in the circumferential direction.

Each of the intermediate plates 11 has an engaging portion 61 projecting outward in the radial direction. Each engagement portion 61 is arranged between the window holes 45 of the separation flange 6. The engagement portion 61 extends to a position near the radially intermediate position of the window hole 41. The engaging portion 61 has a fan shape whose circumferential length gradually increases from the radially inner side to the outer side. Both ends in the circumferential direction of the engaging portion 61 can be engaged with the inner circumferential side portions of the second spring 8 on both sides in the circumferential direction. A gap corresponding to the third torsion angle θ3 is secured between the circumferential end surfaces 61a of the engaging portions 61 and the circumferential end portions of the second springs 8, respectively. In this embodiment, the third torsion angle θ3 between the engagement portion 61 and the second spring 8 on the R2 side is about 4 °, and the third torsion angle θ3 between the engagement portion 61 and the second spring 8 on the R1 side. θ3 is about 1 °. The third torsion angle θ3 is larger than the first torsion angle θ1 minus the second torsion angle θ2. This comparison is made at angles on the same side in the circumferential direction.

The pair of intermediate plates 11 cannot be relatively rotated by a plurality of pins 62. Pin 62
It is composed of a body and small-diameter projections extending from the body 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 against the body of the pin 62 from the axial direction. The projection is inserted into a hole formed in the plate 11. Between each intermediate plate 11 and the separation flange 6,
Spacers 63 are arranged respectively. Spacer 63
Are annular plate members respectively arranged between the inner peripheral portion of each intermediate plate 11 and the inner peripheral side annular portion of the separation flange 6. A hole into which the body of the pin 62 is inserted is formed in the spacer 63, and the spacer 63 rotates integrally with the intermediate plate 11 by engagement of the pin 62 with the hole. The surface of the spacer 63 on the side facing and contacting the separation flange 6 is coated with a coating for reducing the friction coefficient. A long hole 69 through which the pin 62 passes is formed in the separation flange 6. The long hole 69 is
Is a hole for allowing movement in the rotation direction with respect to the separation flange 6.

Next, each member constituting the friction generating mechanism will be described. The second friction washer 72 is disposed between the inner peripheral portion of the transmission-side intermediate plate 11 and the inner peripheral portion of the retaining plate 22. The second friction washer 72 mainly includes a main body 74 made of resin and a friction plate 75 molded on the main body 74. The friction plate 75 is in contact with the transmission side surface of the intermediate plate 11 on the transmission side. 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 not to rotate relatively, and is locked in the axial direction. A plurality of recesses 77 are formed on the inner peripheral transmission side of the main body 74. A second cone spring 73 is arranged between the main body 74 and the retaining plate 22. The second cone spring 73 includes a main body 74 of the second friction washer 72 and the retaining plate 2.
2 are arranged in a compressed state. As a result, the friction plate 75 of the second friction washer 72 is strongly pressed against the first intermediate plate 11. The first friction washer 79 is disposed between the flange 54 and the inner peripheral portion of the retaining plate 22. That is, the first friction washer 79 is disposed on the inner peripheral side of the second friction washer 72 and on the outer peripheral side of the boss 52. The first friction washer 79 is made of resin. The first friction washer 79 mainly includes an annular main body 81, and a plurality of protrusions 82 extend radially outward from the annular main body 81. The main body 81 is in contact with the flange 54, and the plurality of protrusions 82 are engaged with the concave portions 77 of the second friction washers 72 so as not to rotate relatively. Thus, the first friction washer 79 is connected to the retaining plate 2 via the second friction washer 72.
2 and can rotate together. A first cone spring 80 is arranged between the first friction washer 79 and the inner peripheral portion of the retaining plate 22. The first cone spring 80 is disposed between the first friction washer 79 and the inner peripheral portion of the retaining plate 22 in a state of being compressed in the axial direction. The biasing force of the first cone spring 80 is designed to be smaller than the biasing force of the second cone spring 73. Since the friction surface of the first friction washer 79 is a resin portion, the second friction washer 72
The coefficient of friction is smaller than that of. Therefore, the first
The friction (hysteresis torque) generated by the friction washer 79 is significantly smaller than the friction generated by the second friction washer 72. A third friction washer 85 is arranged between the inner peripheral portion of the clutch plate 21 and the inner peripheral portions of the flange 54 and the intermediate plate 11. Third
The friction washer 85 is an annular member made of resin. Third
The friction washer 85 mainly includes an annular main body 86. On the transmission side of the annular main body 86, a friction plate 88 is disposed on the outer peripheral side, and a friction surface 87 made of resin is formed on the inner peripheral side. The friction plate 88 is in contact with the inner peripheral portion of the intermediate plate 11 on the engine side. The friction surface 87 made of resin is in contact with the engine side surface of the flange 54. Further, an annular cylindrical portion 90 protruding toward the engine is formed on the inner peripheral portion of the third friction washer 85. The inner peripheral surface of the cylindrical portion 90 is slidably in contact with the outer peripheral surface of the boss 52. Also, from the outer peripheral side portion of the main body 86,
Engaging portions 89 projecting toward the engine are formed at a plurality of positions in the rotation direction. The engaging portion 89 is engaged in a hole formed in the clutch plate 21, whereby the third friction washer 85 is non-rotatably engaged with the clutch plate 21 and is locked in the axial direction. In the friction mechanism described above, the second friction washer 72
Friction plate 75 and the friction plate 88 of the third friction washer 85
A friction generating mechanism 13 that generates a relatively high hysteresis torque is formed between the motor and the intermediate plate 11. Further, the friction surface of the main body 81 of the first friction washer 79 and the resin friction surface 87 of the third friction washer 85 form the friction generating mechanism 15 that generates a relatively low hysteresis torque between the flange 54 and the friction surface.

Next, the angles of the respective structures of the second spring 8 and the second stopper 10 and the relationship between them will be described in detail. The “circumferential angle” described below refers to the circumferential direction (the clutch disk assembly 1) from a certain position to another position around the rotation axis O of the clutch disk assembly 1.
Rotation direction) angle. The absolute values of the angles used in the following description are those of the clutch disk assembly 1 as an example of the present invention shown in the drawings, and the present invention is not limited to those numerical values.

Each of the circumferential angles θA to θE is set forth in FIGS. FIG. 20 shows each circumferential direction θA ~.
FIG. 4 is a diagram illustrating a relationship between angles of θE. Relationship between θA and θC The circumferential angle θA of each protrusion 49 is determined by the circumferential angle θC between adjacent circumferential ends of the adjacent protrusions 49 in the rotation direction (that is, between the stopper surfaces 50 facing in the rotation direction). small. As is clear from FIG. 20, θA and θC have a relationship in which if one increases, the other decreases. Where θ
By greatly reducing A with respect to θC, θC is ensured to be larger than before. By increasing the circumferential angle θC between the projections 49 in this manner, the torsional angle θE between the separation flange 6 and the plates 21 and 22 can be increased. In the clutch disk assembly 1 shown in the drawings, which is an embodiment of the present invention, each θA is 2
1 °, and each θC is 69 °.

When θC is 40 ° or more, a sufficiently excellent effect which has not been obtained conventionally can be obtained. When θC is in the range of 50 to 80 °, a further excellent effect can be obtained. When θC is in the range of 60 to 80 °. The most excellent effect is obtained when the angle is in the range of 65 to 75 °.

If θC is equal to or less than half of θA, a sufficiently excellent effect can be obtained. More excellent effects can be obtained if θC is not more than one third of θA. The ratio to θCθA in the drawing is 1: 3.29. If the ratio is in the range of 1: 2 to 6, a sufficiently excellent effect can be obtained, and 1: 2.5 to 5.5 can be obtained.
Within this range, more excellent effects can be obtained. Relationship between θC and θD The circumferential angle θD of each plate-like connecting portion 31 (stopper portion 32) is much smaller than the aforementioned angle θC.
As is clear from FIG. 20, the value obtained by subtracting θD from θC is the maximum torsion angle θE (stopper angle of the damper mechanism) between the separation flange 6 and the plates 21 and 22. That is, in this damper mechanism, the maximum torsion angle θE is wider than before. As is clear from the figure, in order to increase θE, it is necessary to increase θC and decrease θD. In this embodiment, θD is 16 °. θD is preferably 20 ° or less, more preferably in the range of 10 to 20 °. Relationship between θA and θB The circumferential angle θA of the projection 49 is smaller than the circumferential angle θB of each window hole 41. That the ratio of θA to θB is smaller than the conventional value indicates that the ratio of θC to θB is larger than the conventional value. In other words, θC which is a premise for ensuring a wide maximum torsion angle θE for the widened window hole 41
Is sufficiently large relative to θB. The circumferential angle θA of each projection 49 may be not more than の of the circumferential angle θB of the window hole 41, more preferably not more than 、, and more preferably not more than 1/2.
It is more preferable that it is 3 or less. The ratio between θA and θB in this embodiment is 1: 2.90. Preferably, the ratio between θA and θB is in the range of 1: 2-4, and 1: 2.
More preferably, it is in the range of 5 to 4.0, and 1: 2.75.
Most preferably, it is in the range of -3.75. Note that θC is larger than θB. The relationship θE and θB between θB and θE are both larger than before, so that the maximum torsional angle of the damper mechanism increases and the torsional angle of the second spring 8 increases. The design of the second spring 8 is facilitated by increasing its size, and the second spring 8 has high performance (wide torsion angle and low rigidity).

When θB and θE are compared, θB is larger than θE, but there is only a slight difference. That is, θ
The ratio of E to θB is sufficiently large. Accordingly, when the circumferential angle of the window hole 41, that is, the second spring 8 is widened, the maximum torsion angle θE that makes full use of the wide angle is secured. The ratio of θB to θE is 1: 1.13. If the ratio is in the range of 1: 1.0 to 1.3, a sufficiently excellent effect can be obtained, and the ratio of 1: 1.1 to 1.3 can be obtained.
When it is in the range of 1.2, more excellent effects can be obtained. Radial length of window hole 41 In this damper mechanism, the radial length of window hole 41 is sufficiently larger than the radial length (outer diameter) of separation flange 6. As a result, the size of the second spring 8 housed in the window hole 41 can be increased. The radial length of the window hole 41 is 35% or more of the outer diameter of the separation flange 6. When this ratio is in the range of 35 to 55%, a sufficiently excellent effect can be obtained, and when it is in the range of 40 to 50%, a further excellent effect can be obtained.

Next, the structure of the clutch disk assembly 1 will be described in more detail with reference to FIG. FIG. 8 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 illustrates the operation and relationship of each member when the output rotator 3 is twisted in one direction (for example, the R2 side) with respect to the input rotator 2. It is a figure for explaining. As is apparent from the figure, a plurality of members for constituting a damper mechanism are arranged between the input rotary body 2 and the output rotary body 3. The separation flange 6 is arranged between the input rotary body 2 and the output rotary body 3. The separation flange 6 is connected to the output rotating body 3 by a first spring 7.
Are elastically connected to each other in the rotational direction. Further, a first stopper 9 is formed between the separation flange 6 and the output rotating body 3. The first spring 7 is compressible during the first torsion angle θ1 of the first stopper 9. The separation flange 6 is elastically connected to the input rotary body 2 via a second spring 8 in the rotation direction. Further, a second stopper 10 is formed between the separation flange 6 and the input rotating body 2. Fourth torsion angle θ at second stopper 10
4, the second spring 8 can be compressed. As described above, the input rotator 2 and the output rotator 3 are elastically connected in the rotation direction by the first spring 7 and the second spring 8 arranged in series. Here, the separation flange 6 functions as an intermediate member disposed between the two types of springs. In addition, the above-described structure is the first arrangement arranged in parallel.
It can be seen as a structure in which a damper including the spring 7 and the first stopper 9 and a damper including the second spring 8 and the second stopper 10 arranged in parallel are arranged in series. Further, the structure described above can be considered as a first damper mechanism 4 that elastically connects the input rotary body 2 and the output rotary body 3 in the rotation direction. The overall rigidity of the first spring 7 is set to be much smaller than the overall rigidity of the second spring 8. Therefore, the second spring 8 is hardly compressed in the rotation direction within the range of the torsion angle up to the first torsion angle θ1.

The intermediate plate 11 is disposed between the input rotary member 2 and the output rotary member 3. Intermediate plate 11
Is configured so that a part thereof can be engaged with the second spring 8. The intermediate plate 11 has a third stopper 1 having a gap with the output rotating body 3 by a second torsion angle θ2.
2. The third stopper 12 is a gap for allowing relative rotation between the output rotator 3 and the intermediate plate 11 when a small torsional vibration in a first-stage range described later is input. Further, the intermediate plate 11 is frictionally engaged with the input rotary body 2 via the friction generating mechanism 13 in the rotational direction. Further, in the intermediate plate 11, the engaging portion 61 is disposed at a circumferential end of the second spring 8 with a gap corresponding to the third torsion angle θ4. The intermediate plate 11 described above includes a third stopper 12 and a friction generating mechanism 13 that are arranged in series to form a second damper mechanism 5 that connects the input rotary body 2 and the output rotary body 3 in the rotation direction. Has been realized. The second damper mechanism 5 is arranged so as to act in parallel with the first damper mechanism 4.

Next, the relationship between the angles θ1 to θ4 of the damper mechanism in FIG. 8 will be described. The angle here is each angle when the input rotator 2 is viewed on the negative side from the output rotator 3 (the output rotator 3 is viewed on the positive side from the input rotator 2).
The first torsion angle θ1 is the maximum positive torsional angle of the damper mechanism in the first spring 7, and the fourth torsional angle θ4 of the second stopper 10 is the maximum positive torsional angle θE1 of the damper mechanism in the second spring 8. The sum of the first torsion angle θ1 and the fourth torsion angle θ4 is the positive maximum torsion angle of the damper mechanism as the clutch disc assembly 1 as a whole. The second torsion angle θ2 needs to be equal to or less than the first torsion angle θ1. In this embodiment, for example, the first torsion angle θ1 is 5 ° and the second torsion angle θ2 is 2 °. The difference between the first torsion angle θ1 and the second torsion angle θ2 must be smaller than the third torsion angle θ3. The difference obtained by subtracting the second torsion angle θ2 from the first torsion angle θ1 and further subtracting the difference from the third torsion angle θ3 is the difference between the first torsion angle θ1 and the third torsion angle θ3. The clearance angle A is set so as not to operate. The gap angle A is 1 ° in this embodiment, but is preferably in the range of 1 to 2 °. The sum of the second torsional angles θ2 on both the positive and negative sides is the total gap angle B for not operating the friction generating mechanism 13 when a small torsional vibration is input in the first stage of the torsional characteristics. In this embodiment, the second torsion angle θ2 is 2 ° for both positive and negative, and the total clearance angle B is 4 °. The total gap angle B is preferably larger than the gap angle A, and is desirably twice or more. Total clearance angle B
If the angle is within the range of 3 to 5 °, an excellent effect can be obtained.

As shown in FIG. 8, a friction generating mechanism 15 is provided between the input rotary member 2 and the output rotary member 3. The friction generating mechanism 15 always slides when the input rotary body 2 and the output rotary body 3 rotate relative to each other. In this embodiment, the friction generating mechanism 15 is mainly composed of the first and second friction washers 72 and 85, but may be composed of other members. In some cases, it is desirable that the hysteresis torque generated by the friction generating mechanism 15 be as low as possible.

Next, the mechanical circuit diagrams shown in FIGS.
The characteristics of the damper mechanism of the clutch disk assembly 1 will be described with reference to FIG. This torsional characteristic diagram shows the relationship between the torsion angle and the torque when the input rotary body 2 and the output rotary body 3 are twisted between the positive and negative maximum torsional angles. 8 and 15 show the input rotator 2 and the output rotator 3
Indicates a state in a stationary state, and does not appear in the torsional characteristic diagram of FIG. 9 to 14 show the operation when the output rotator 3 is twisted toward the R2 side from the input rotator 2 with respect to the input rotator 2 (ie, the input rotator 2 is shifted from the 0 deg with respect to the output rotator 3 toward the R1 side (positive). It is a figure for explaining (it twists to the side). 9 to 13 illustrate a state when the positive side area changes to the positive side, and FIG. 14 illustrates a state when the positive side area changes to the negative side. FIG.
6 to 18 show the operation when the output rotating body 3 is twisted toward the R1 side (positive side) from the input rotating body 2 with respect to the input rotating body 2 at 0 degree (that is, when the input rotating body 2 is rotated at 0 degree with respect to the output rotating body 3 as R2 from the rotating state). FIG. 4 is a diagram for explaining the side (twisted to the negative side). In addition,
FIGS. 16 and 17 illustrate a state when changing to the negative side in the negative side area, and FIG. 18 illustrates a state when changing to the positive side in the negative side area.

FIG. 9 is a diagram when the torsion characteristic is twisted from the negative side to the positive side at 0 °. At this time, the intermediate plate 11 is arranged to be shifted by 1 ° toward the output rotating body 3 (R1 side) as compared with the stationary state of FIG. For this reason, the gap between the locking portion 61 of the intermediate plate 11 and the second spring 8 has a third torsion angle θ3 + 1 ° (5 °). 1 twist angle
゜, the output rotary member 3 is displaced by 1 ° to the R2 side with respect to the input rotary member 2 from the state of FIG. 9, and the outer teeth 55 of the output rotary member 3 Tooth 6
Contact 6 Thereafter, when the torsion angle is between 1 ° and 5 °, the first spring 7 is compressed between the output rotating body 3 and the separation flange 6 as shown in FIG. As a result, low rigidity and high hysteresis torque characteristics can be obtained in the first stage range from 1 ° to 5 °.
As shown in FIG. 12, the torsion angle is the first torsion angle θ1.
When (5 °) is reached, the outer peripheral teeth 55 of the output rotating body 3 come into contact with the inner peripheral teeth 59 of the separation flange 6. As a result, in the second stage range from 5 ° to the maximum positive torsional angle θ4 (θE1), as shown in FIG. 13 (8 °), the second spring 8 moves between the separation flange 6 and the input rotary body 2. Compressed. As a result, characteristics of high rigidity and high hysteresis torque can be obtained.
In the state shown in FIG.
A gap having a gap angle B (1 °) is provided between the first spring 8 and the end of the second spring 8. The gap angle B is obtained by subtracting the second torsion angle θ2 (2 °) from the first torsion angle θ1 (5 °) at rest shown in FIG. 8 (3 °) and further adding the third torsion angle θ3 (4 °). Is equivalent to the remainder (1 ゜) subtracted from

When the torsion angle is maximized and subsequently returns to the negative side, the second spring 8 extends from the state of FIG. 13 while pressing the separation flange 6 from the compressed state, and the end of the second spring 8 is intermediate as shown in FIG. It comes into contact with the engaging portion 61 of the plate 11. Second
In the range of 1 ° until the end of the spring 8 comes into contact with the engaging portion 61, no slip occurs in the friction generating mechanism 13. Second spring 8
Pushes the intermediate plate 11 together with the separation flange 6. For this reason, the intermediate plate 11 maintains a state of being displaced toward the R1 side by 1 ° with respect to the output rotating body 3.

When the torsion angle becomes 5 °, the second spring 8 enters a free length state, and then the first spring 7 starts to extend. At this time, as shown in FIG. 14, since the intermediate plate 11 is displaced by 1 ° to the R1 side with respect to the output rotating body 3, the output rotating body 3 is moved after the extension of the first spring 7 is started. The characteristic of low rigidity and low hysteresis torque is obtained until it moves θ2 + 1 ° (3 °) with respect to the intermediate plate 11. That is, the friction generating mechanism 1 is between 5 ° and 2 °.
3 does not slip. Then, when it becomes 2 °, the output rotating body 3
Moves the intermediate plate 11 to the R1 side, thereby moving the intermediate plate 11 away from the end of the second spring 8 and causing the friction in the friction generating mechanism 13 as shown in FIG. As a result, low rigidity and high hysteresis torque characteristics are obtained in the first stage range from 2 ° to -2 °. When the torsion angle is 0 ° or less, the first spring 7 is disposed between the output rotating body 3 and the separation flange 6 as shown in FIG.
Is compressed. When the torsion angle exceeds -2 °, the second stopper 9 abuts, and the second spring 8 is compressed between the separation flange 6 and the input rotary body 2. The first stopper 9 abuts on the opposite side, and thereafter, the second spring 8 is compressed between the intermediate plate 11 and the input rotating body 2. As a result, high rigidity and high hysteresis torque characteristics can be obtained in the second stage on the negative side. When returning to the positive side after being twisted to the negative side in the second stage, the second spring 8 presses the separation flange 6 and the intermediate plate 11 as shown in FIG. At this time,
A high hysteresis torque is generated by slipping of the friction generating mechanism 13. In this return state, the intermediate plate 11 is shifted by 1 ° toward the R1 side with respect to the output rotating body 3. When the torsion angle becomes −2 °, the extension of the second spring 8 stops, and then the extension of the first spring 7 starts. Where θ
In the size of 2 + 1 ° (3 °), that is, in the range from −2 ° to 1 °, the first spring 7 pushes the output rotating body 3, but the intermediate plate 11 does not slip on the input rotating body 2 and generates a high hysteresis torque. do not do.

Next, the clutch disk assembly 1
The change in the torsional characteristics when vibration is input to the device will be described. When torsional vibration having a large amplitude such as longitudinal vibration of the vehicle occurs, the torsional angle repeatedly fluctuates between the positive and negative second stages shown by the characteristics in FIG. At this time, since the high hysteresis torque is generated in both the first stage and the second stage, the longitudinal vibration of the vehicle is rapidly attenuated.

Next, for example, during normal driving (for example, in the range of the second stage on the positive side as shown in FIG. 13), a small torsional vibration caused by the combustion vibration of the engine causes clutch disk assembly 1
Is entered. At this time, the gap between the output rotor 3 and the input rotor 2 from the state shown in FIG.
Relative rotation is possible within the range of-(θ1−θ2) = 1 ° without operating the friction generating mechanism 13. That is, as shown in FIG. 19C, the second spring 8 operates within the range of the gap angle A, but no slip occurs in the friction generating mechanism 13. As a result, it is possible to effectively absorb the slight torsional vibration that causes the rattle and muffled sound during traveling.

Next, the operation when a minute vibration such as an idle vibration is input to the clutch disk assembly 1 will be described. In this case, the positive / negative first stage range (-2 ゜ to 5 ゜,
For example, in FIGS. 9, 10, and 11, the damper mechanism operates. For example, when a minute vibration is input from the state of FIG.
The output rotator 3 rotates relative to the separation flange 6, the intermediate plate 11 and the input rotator 2. At this time, the first spring 7 operates, and no slip occurs in the friction generating mechanism 13.
At this time, the magnitude of the torsion angle of the damper mechanism is equal to or smaller than the total clearance angle B (4 °) in the third stopper 12.

By realizing low rigidity and low hysteresis torque in the first stage range, the steady tooth hitting level is improved. If the low rigidity and low hysteresis torque is advanced in the first stage range, a jumping phenomenon may occur. However, in this clutch disc assembly 1, the jumping phenomenon is provided by providing high hysteresis torque regions on both sides of the first stage range. Restrained. The jumping phenomenon referred to here is a phenomenon in which both the positive and negative sides rebound from the second-stage wall and develop into vibration over the entire first-stage region, and a phenomenon in which a sound having a higher level than a steady rattling sound is generated.

As described above, the friction generating mechanism 13
Is a mechanism capable of frictionally engaging the input rotary member 2 and the output rotary member 3 in the rotational direction, and generating a slip in the first-stage range and the second-stage range. Further, the gap of the third stopper 12 at the second torsion angle θ2 and the gap of the fourth stopper 14 at the third torsion angle θ3 are provided in the first stage range and the second stage range, respectively. 13 functions as friction suppressing means that does not cause slippage.
Further, the entire second damper mechanism 5 frictionally engages the input rotary body 2 and the output rotary body 3 in the rotational direction, and does not slip against torsional vibrations of a predetermined torque or less in the first and second ranges. It may be considered as a friction generating mechanism that generates friction by sliding against torsional vibration of a predetermined torque or more. Further, the third stopper 12 is a first friction suppressing mechanism that does not cause the friction generating mechanism 13 to slip when a torsional vibration having a predetermined torque or less is input in the first stage range, and the fourth stopper 14 is a predetermined one in the second stage range. It may be considered as a second friction suppressing mechanism that does not cause the friction generating mechanism 13 to slip when torsional vibration less than the torque is input.

As shown in this clutch disc assembly 1, by widening the range of the second-stage torsion angle by the plate-like connecting portion 31 instead of the conventional stop pin,
The resonance point at the engine speed shifts to the low speed side.
Further, the peak of the resonance point can be reduced by the high hysteresis torque. Further, by adding a structure that does not generate a high hysteresis torque against a small torsional vibration in addition to low rigidity in the range of the second torsion angle, rattle and muffled noise during traveling can be reduced.

[0059]

According to the damper mechanism of the present invention, a high hysteresis torque is generated in the first stage with respect to the vibration twisted over the first stage range and the second stage range, and when a small torsional vibration is input. Does not generate high hysteresis torque in the first and second stages.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a clutch disk assembly.

FIG. 2 is a plan view of a clutch disk assembly.

FIG. 3 is an enlarged view of FIG. 2;

FIG. 4 is an exploded sectional view of each part.

FIG. 5 is a plan view showing engagement between a hub, a separation flange, and an intermediate plate.

FIG. 6 is a plan view for explaining a relationship between torsion angles of respective parts.

FIG. 7 is a plan view for explaining the relationship between the torsional angles of each part.

FIG. 8 is a mechanical circuit diagram of a damper mechanism of the clutch disk assembly.

FIG. 9 is a mechanical circuit diagram showing an operation state of the damper mechanism.

FIG. 10 is a mechanical circuit diagram showing an operation state of a damper mechanism.

FIG. 11 is a mechanical circuit diagram showing an operation state of a damper mechanism.

FIG. 12 is a mechanical circuit diagram showing an operation state of a damper mechanism.

FIG. 13 is a mechanical circuit diagram showing an operation state of a damper mechanism.

FIG. 14 is a mechanical circuit diagram showing an operation state of a damper mechanism.

FIG. 15 is a mechanical circuit diagram showing an operation state of the damper mechanism.

FIG. 16 is a mechanical circuit diagram showing an operation state of a damper mechanism.

FIG. 17 is a mechanical circuit diagram showing an operation state of a damper mechanism.

FIG. 18 is a mechanical circuit diagram showing an operation state of the damper mechanism.

FIG. 19 is a torsional characteristic diagram of the clutch disk assembly.

FIG. 20 is a diagram for explaining the relationship between each torsion angle of the clutch disk assembly.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Clutch disk assembly 2 Input rotating body 3 Output rotating body (hub) 4 1st damper mechanism 5 2nd damper mechanism 6 Separation flange 7 1st spring 8 2nd spring 9 1st stopper 10 2nd stopper 11 Intermediate plate 12th 3 stopper 13 friction generating mechanism 14 fourth stopper

Claims (3)

[Claims] A first rotating member, a second rotating member disposed so as to be relatively rotatable with respect to the first rotating member, and the first rotating member and the second rotating member being connected in a rotating direction, torsion. A mechanism for attenuating vibration, wherein the first
A first intermediate member disposed between a rotary member and the second rotary member; and a first intermediate member disposed between the first rotary member and the first intermediate member and compressible to a first circumferential angle. A first damper mechanism having an elastic member, a second elastic member disposed between the first intermediate member and the second rotating member and having a larger spring constant than the first elastic member; A mechanism for connecting the second rotating member in the rotating direction and disposed in parallel with the first damper mechanism to attenuate torsional vibration, between the first rotating member and the second rotating member. A second intermediate member disposed, a stopper having a gap between the first rotating member and the second intermediate member having a second circumferential angle equal to or smaller than a first circumferential angle, and the second intermediate member; Friction generating mechanism for frictionally engaging a member and the second rotating member in a rotational direction And the second
A part of the intermediate member has a gap at a third circumferential angle between the second elastic member and the third elastic member, and the third circumferential angle is the first circumferential angle.
A second damper mechanism that is greater than a difference obtained by subtracting the second circumferential angle from the circumferential angle. 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 first rotating member disposed between the first rotating member and the second rotating member. An intermediate member, a first elastic member disposed between the first rotating member and the first intermediate member and compressible to a first circumferential angle, and between the first intermediate member and the second rotating member. Placed in the first
A second elastic member having a larger spring constant than an elastic member; a second intermediate member disposed between the first rotating member and the second rotating member; and a second intermediate member disposed between the first rotating member and the second intermediate member. A stopper having a gap at a second circumferential angle smaller than or equal to the first circumferential angle, and a friction generating mechanism for frictionally engaging the second intermediate member and the second rotating member in a rotating direction. A part of the second intermediate member has a gap at a third circumferential angle between the second intermediate member and the second elastic member, and the third circumferential direction angle is a second angle from the first circumferential direction angle. A damper mechanism that is larger than the difference obtained by subtracting the circumferential angle. 3. An output hub, a pair of input plates disposed so as to be relatively rotatable around the output hub, and a first input plate disposed between the pair of input plates on an outer peripheral side of the output hub. An intermediate member, a first elastic member that elastically connects the output hub and the first intermediate member in the rotational direction, and an elastic member that elastically connects the first intermediate member and the pair of input plates in the rotational direction. A second elastic member having a larger spring constant than the first elastic member, a second elastic member disposed between the output hub and the pair of input plates, and having a first circumferential angle less than or equal to the output hub. A circumferential angular gap is secured, a frictional engagement portion is formed between the pair of input plates, and a portion has a third circumferential angular gap with the second elastic member. The third circumferential angle is the angle between the first circumferential direction and the second circumferential direction. Subtracting the difference is greater than the damper mechanism comprising a second intermediate member.