JP2001248689A - Torque fluctuation absorbing damper - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve safety by preventing the dislodgment of a pulley 6 resulting from breakage of coupling rubber 7 and the like. SOLUTION: A torque fluctuation absorbing damper comprises a hub 1 attached to a shaft end, the pulley 6 and an annular mass 2 disposed on the periphery of the hub 1, the coupling rubber 7 elastically connecting the hub 1 side and the pulley 6 side, and damper rubber 4 elastically connecting the hub 1 side and the annular mass 2 side. The annular mass 2 has on the periphery a protrusive edge 24, which interferes with an outer sleeve 71 fitted in the pulley 6 and thus functions as a movement limiting means for limiting the axial dislodging movement of the pulley 6.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a torque fluctuation absorbing damper that absorbs fluctuations in a transmission torque from a drive shaft of an engine or the like to another rotating device.

[0002]

2. Description of the Related Art A part of driving force from an automobile engine is supplied from a pulley provided at a tip of a crankshaft to an auxiliary device such as an alternator or a water pump through an endless belt. Is rotated with the torque fluctuation due to each stroke of
The pulley is provided with a torque fluctuation absorbing damper for absorbing torque fluctuation and smoothing transmission torque.

Conventionally, this type of torque fluctuation absorbing damper has been
For example, as shown in FIG. 6, a hub 101 attached to the shaft end of a crankshaft and a pulley 103 are elastically connected to the outer periphery of the hub 101 via a coupling rubber 102. Annular mass 105 via a damper rubber 104 provided side by side
Are elastically connected, and the pulley 103 is
5 has a structure supported by a bearing 106 so as to be relatively displaceable in a circumferential direction via a bearing 106. That is, the torque fluctuation absorbing damper converts the input torque fluctuation between the hub 101 and the pulley 103 to the coupling rubber 10.
The dynamic vibration absorbing portion, which is absorbed by the torsional shear deformation action of No. 2 and is composed of the damper rubber 104 and the annular mass 105,
In a predetermined frequency range where the torsional amplitude of the crankshaft is large, resonance occurs at a phase angle different from the torsional vibration of the crankshaft, thereby exhibiting a vibration damping function of reducing the torsional vibration.

[0004]

However, according to the torque fluctuation absorbing damper having the conventional structure, if the coupling rubber 102 is damaged by repeated input of excessive torque or the like, the pulley 103 is disengaged from the annular mass 105. It may be detached, causing damage to peripheral devices or impairing safety.

[0005] The present invention has been made in view of the above problems, and its main technical problem is to prevent the pulley from falling off due to breakage of coupling rubber or the like,
The purpose is to improve safety.

[0006]

As means for effectively solving the above-mentioned technical problems, a torque fluctuation absorbing damper according to the present invention is provided with a hub attached to a shaft end and an outer peripheral side of the hub. A coupling rubber for elastically connecting the hub side and the pulley side, a damper rubber for elastically connecting the hub side and the annular mass side, and the pulley for the hub or the annular mass. And movement restricting means for restricting the axial separation operation. That is, according to this configuration, even if the coupling rubber is broken, the pulley is prevented from moving in the axial direction with respect to the hub or the annular mass by the movement restricting means.

[0007]

FIG. 1 is a sectional view showing a first embodiment of a torque fluctuation absorbing damper according to the present invention, cut along a plane passing through an axis O thereof. In the following description, “front side” refers to the left side in the figure, and “back side” refers to the right side in the figure where the engine exists.

In this embodiment, reference numeral 1 denotes a hub attached to a shaft end of a crankshaft (not shown) of an automobile engine. The hub 1 includes a boss portion 11 which is a mounting portion to the crankshaft, a radial portion 12 extending from one end to the outer peripheral side, and a cylindrical outer peripheral cylinder extending further from the outer periphery to the opposite side to the boss portion 11. And 13.

An annular mass 2 is concentrically arranged on the outer peripheral side of the outer cylindrical portion 13 of the hub 1, and an inner sleeve 3 is press-fitted on the inner peripheral surface of the annular mass 2. A damper rubber 4 made of a rubber-like elastic material is vulcanized and bonded between the peripheral surfaces facing the outer cylindrical portion 13. The inner sleeve 3 has a mass mounting portion 31 located between the damper rubber 4 and the annular mass 2 and an extension portion 32 to which the coupling rubber 7 is vulcanized and bonded.
Annular mass 2, inner sleeve 3, and damper rubber 4
Constitutes a dynamic vibration absorber, and its natural frequency in the torsional direction is tuned to a predetermined frequency range in which the torsional angle of the crankshaft is maximized.

[0010] The annular mass 2 has an inner peripheral cylindrical portion 21 into which a mass mounting portion 31 of the inner sleeve 3 is press-fitted on the inner peripheral surface,
A radial portion 22 extending outward from the radial portion 22, a pulley support portion 23 formed on the outer periphery thereof,
3. A flange 2 that protrudes in a flange shape from the rear end to the outer periphery of 3
4. A pulley 6 is arranged on the outer peripheral side of the pulley support 23 via a bearing 5 so as to be relatively displaceable in a circumferential direction.

The bearing 5 supports the pulley 6 concentrically with respect to the hub 1 so as to be capable of torsional displacement so that the pulley 6 is not eccentric due to the tension of the V-belt. It is made of a synthetic resin material having a coefficient. The bearing 5 is formed by bending a radial bearing portion 51 slidably and closely in contact with the outer peripheral surface of the pulley support portion 23 of the annular mass 2 from the rear end thereof toward the outer peripheral side. It has a substantially L-shaped cross-section having a thrust bearing portion 52 slidably and closely attached to the side surface of the protruding edge 24.

The pulley 6 has a pulley body 61 having a poly-V groove 61a formed on an outer peripheral surface thereof, and an inner portion extending along the front surface of the radial portion 22 of the annular mass 2 from the front end to the inner periphery. The pulley body 61 has an extension flange 63 extending cylindrically from the outer periphery of the rear end of the pulley body 61, and the inner peripheral surface of the pulley body 61 is the outer peripheral surface of the radial bearing portion 51 of the bearing 5. The rear end surface of the pulley body 61 is slidably and closely contacted with the side surface of the thrust bearing 52 of the bearing 5.

A plurality of engaging pins 25 projecting toward the front side are provided at a predetermined phase interval on the radial portion 22 of the annular mass 2. On the other hand, in the inward flange 62 of the pulley 6, a plurality of long holes 62a extending in an arc shape centered on the axis O are formed at a phase interval corresponding to the engagement pin 25. The engagement pin 25 and the engagement pin 25 are loosely fitted to each other with an appropriate gap in the circumferential direction, thereby limiting the relative amount of torsional displacement between the annular mass 2 and the pulley 6.

The extension 63 of the pulley 6 is located on the outer peripheral side of the extension 32 of the inner sleeve 3, and the outer sleeve 71 is press-fitted on the inner peripheral surface of the extension 63 of the pulley 6. . And the outer sleeve 71
And the extension 32 of the inner sleeve 3,
The coupling rubber 7 is integrally vulcanized and bonded. That is, the pulley 6 includes an outer sleeve 71, a coupling rubber 7, an inner sleeve 3, and a damper rubber 4.
Is connected to the hub 1 in a circumferential relative displacement.

The outer peripheral surface of the protruding edge 24 formed on the annular mass 2 is close to the inner peripheral surface of the extension 63 of the pulley 6 with a slight gap therebetween. The outer sleeve 71 is formed to have a larger diameter than the inner diameter of the outer sleeve 71. That is, the protruding edge 24 prevents the axial movement of the pulley 6 to the rear side through the thrust bearing portion 52 of the bearing 5, and has a larger diameter than the outer sleeve 71, so that the projection edge 24 moves to the front side of the pulley 6. This constitutes a movement restricting means for restricting the movement in the axial direction.

In this torque fluctuation absorbing damper, a hub 1, an inner sleeve 3 and an outer sleeve 71 are concentrically arranged in a mold, and a space between the outer cylindrical portion 13 of the hub 1 and the inner sleeve 3, and Between the extension 32 of the inner sleeve 3 and the outer sleeve 71,
After the damper rubber 4 and the coupling rubber 7 are integrally molded by vulcanization molding and vulcanization bonding, the mass mounting portion 31 of the inner sleeve 3 is connected to the inner peripheral cylindrical portion 2 of the annular mass 2.
1 and press-fitted, and the outer sleeve 71 is assembled by press-fitting the extension 63 of the pulley 6 disposed on the outer periphery of the annular mass 2 via the bearing 5.

Reference numeral 8 denotes a disk-shaped sensor plate having a circumferentially toothed shape and fitted to the hub 1 for detecting misfire or the like.

The torque fluctuation absorbing damper having the above-described structure is rotated together with the crankshaft by mounting the hub 1 on the shaft end of the crankshaft of the engine. The torque of the crankshaft is transmitted from the hub 1 to the pulley 6 via the damper rubber 4, the inner sleeve 3, the coupling rubber 7, and the outer sleeve 71. A V-belt (not shown) for transmitting rotational torque to the rotation shaft of the auxiliary device is wound around the outer periphery of the pulley body 61 of the pulley 6.

The engine is driven while repeating the steps of intake, compression, explosion (expansion), and exhaust, and converts the reciprocating motion of the piston into the rotational motion of the crankshaft. Periodic torque fluctuations occur with rotation, but the torque fluctuations are effectively absorbed by the torsional shear deformation of the coupling rubber 7 having a low spring constant, and the transmission torque is smoothed. On the other hand, the annular mass 2 and the inner sleeve 3 and the damper rubber 4
Is resonated in the torsional direction in a predetermined frequency range in which the torsional angle due to the torsional vibration of the crankshaft is maximized, and the direction of the torque due to the resonance is opposite to the direction of the torque of the input vibration. Therefore, the peak of the twist angle of the crankshaft can be effectively reduced.

The annular mass 2 and the pulley 6 are relatively displaced in the circumferential direction while sliding with the bearing 5 by the torque fluctuation absorbing operation due to the shear deformation of the coupling rubber 7 in the torsional direction as described above. The vibration system composed of the coupling rubber 7 and the pulley 6 resonates at a relatively low speed rotation because the natural frequency in the torsional direction is low, but the relative displacement of the annular mass 2 and the pulley 6 in the torsional direction increases due to this. Is
The coupling rubber 7 is limited by the interference between the engaging pin 25 protruding from the annular mass 2 and the end of the elongated hole 62 a formed in the inward flange 62 of the pulley 6, so that the coupling rubber 7 causes excessive shear deformation. I will not receive it.

The axial movement of the pulley 6 toward the rear side is restricted by the protruding edge 24 of the annular mass 2 via the thrust bearing portion 52, and the axial movement of the pulley 6 toward the front side is controlled by the outer sleeve 71 or the coupling. It is regulated by interference between the outer peripheral portion of the rubber 7 and the protruding edge 24. Therefore, even if the coupling rubber 7 is broken due to fatigue or the like, the pulley 6 does not fall off the outer periphery of the annular mass 2.

Next, FIG. 2 is a sectional view showing a second embodiment of the torque fluctuation absorbing damper according to the present invention by cutting along a plane passing through an axis O thereof. In this embodiment, the hub 1 has a boss 11 attached to a crankshaft.
And a radial portion 12 extending from one end to the outer peripheral side, and a cylindrical outer cylindrical portion 13 extending further from the outer periphery to the opposite side to the boss portion 11.

An annular mass 2 is arranged concentrically on the outer peripheral side of the outer peripheral cylindrical portion 13 of the hub 1, and a space between the annular mass 2 and the outer peripheral cylindrical portion 13 facing each other is made of a rubber-like elastic material. The damper rubber 4 is press-fitted. The annular mass 2 and the damper rubber 4 constitute a dynamic vibration absorber, and the natural frequency in the torsional direction is tuned to a predetermined frequency range in which the torsional angle of the crankshaft is maximized.

The annular mass 2 has a shape composed of a second pulley 26 having a poly-V groove 26a formed on the outer peripheral surface, and a cylindrical pulley support 27 extending from the inner periphery to the rear side. A pulley 6 is arranged on the outer peripheral side of the pulley support 27 via a bearing 5 so as to be relatively displaceable in a circumferential direction.

The bearing 5 is made of a synthetic resin material having a low friction coefficient such as PTFE, for example.
And a radial bearing portion 51 slidably in contact with the outer peripheral surface of the pulley support portion 27, and a bent portion formed from the front end to the outer peripheral side, and slidable on the rear surface of the second pulley 26 in the annular mass 2. And a thrust bearing portion 52 closely contacted with the second member, and has a substantially L-shaped cross section.

The pulley 6 has a pulley body 61 having a poly-V groove 61a formed on the outer peripheral surface thereof, and an extension 63 extending cylindrically from the outer periphery of the rear end thereof. The inner peripheral surface is slidably in contact with the outer peripheral surface of the radial bearing portion 51 of the bearing 5, and the front end surface of the pulley main body 61 is slidably in contact with the thrust bearing portion 52 of the bearing 5.

An outer sleeve 71 is press-fitted on the inner peripheral surface of the extension 63 of the pulley 6, and an inner sleeve 72 is press-fitted on the outer peripheral surface of the boss 11 of the hub 1. The coupling rubber 7 is integrally vulcanized and bonded between the outer sleeve 71 and the inner sleeve 72 which face each other in the radial direction. That is, the pulley 6 is connected to the hub 1 via the outer sleeve 71, the coupling rubber 7, and the inner sleeve 72 at a relative displacement in the circumferential direction.

The outer sleeve 71 has a radial portion 71a extending from the rear end to the inner peripheral side. The inner peripheral end of the radial portion 71a has an engaging claw 7 protruding rearward.
1b are formed at predetermined intervals in the circumferential direction. On the other hand, the inner sleeve 72 extends from the rear end to the outer peripheral side, and a radial portion 71a of the outer sleeve 71 is provided.
Has an engaging projection 72a reaching the rear side of the boss. In the engagement protrusion 72a of the inner sleeve 72, an elongated hole 72b extending in an arc shape centered on the axis O is formed at a phase interval corresponding to the engagement claw 71b, and is engaged with the elongated hole 72b. The claws 71b are loosely fitted to each other with an appropriate gap in the circumferential direction.

That is, the engagement claws 71b of the outer sleeve 71 and the engagement projections 72a of the inner sleeve 72 limit the axial movement of the pulley 6 to the rear side due to mutual interference and function as movement limiting means. In addition, it functions as a means for restricting relative displacement in the torsional direction between the hub 1 and the pulley 6 by the engagement between the elongated hole 72b and the engagement claw 71b.

In the manufacture of the torque fluctuation absorbing damper, the damper rubber 4 is formed into an annular (cylindrical) shape, while the outer sleeve 71 and the inner sleeve 72 are concentric with each other, and the engagement claws of the outer sleeve 71 are engaged. 7
1b and the long hole 72b in the engagement protrusion 72a of the inner sleeve 72 are arranged in the mold in a state where they are loosely fitted to each other,
A bush-shaped molded product in which the coupling rubber 7 is vulcanized and vulcanized and bonded between the opposing peripheral surfaces of the sleeves 71 and 72.
Then, the damper rubber 4 is press-fitted from one side in the axial direction between the outer peripheral surface of the outer cylindrical portion 13 of the hub 1 and the peripheral surface of the annular mass 2, and the outer sleeve 7 of the bush-shaped molded product is formed.
1 is press-fitted onto the inner peripheral surface of the extension 63 of the pulley 6, and the pulley body 61 of the pulley 6 is
And the inner sleeve 72 is press-fitted onto the outer peripheral surface of the boss portion 11 of the hub 1.

The torque fluctuation absorbing damper having the above-described structure is also rotated with the crankshaft by mounting the hub 1 on the shaft end of the crankshaft of the engine, similarly to the damper shown in FIG. The torque of the crankshaft is transmitted from the hub 1 to the pulley 6 via the inner sleeve 72, the coupling rubber 7, and the outer sleeve 71, and is applied to auxiliary machines and the like via a V-belt (not shown). In addition to the pulley 6, the annular mass 2 is also used as a pulley, that is, a V belt is wound around the outer periphery of the second pulley 26.

The torque fluctuation caused by the rotation of the crankshaft is effectively absorbed by the torsional shear deformation of the coupling rubber 7 having a low spring constant, and the transmission torque is smoothed. On the other hand, the dynamic vibration absorber constituted by the annular mass 2 and the damper rubber 4 resonates in the torsional direction at a phase angle different from the input vibration in a predetermined frequency range where the torsional angle due to the torsional vibration of the crankshaft is maximum. , Effectively reducing the peak of the twist angle of the crankshaft.

The annular mass 2 and the pulley 6 are relatively displaced in the circumferential direction while sliding with the bearing 5 by the torque fluctuation absorbing operation due to the shear deformation of the coupling rubber 7 in the torsional direction as described above. The increase in the relative displacement of the annular mass 2 and the pulley 6 in the torsional direction due to the resonance of the vibration system constituted by the coupling rubber 7 and the pulley 6 is caused by the engagement claws 71 b of the outer sleeve 71 and the inner sleeve 72. The coupling rubber 7 is limited by interference with the end of the elongated hole 72b formed in the engagement projection 72a.
Does not suffer from excessive shear deformation.

The axial movement of the pulley 6 toward the front side is restricted by the second pulley 26 of the annular mass 2 via the thrust bearing 52 at the end face of the pulley body 61 of the pulley 6, and the pulley toward the rear side. 6 is restricted by the radial portion 71a of the outer sleeve 71 and the engagement protrusion 72a of the inner sleeve 72 extending to the rear side thereof. Therefore, even if the coupling rubber 7 is broken due to fatigue or the like, the pulley 6 does not fall off the outer periphery of the annular mass 2.

Next, FIG. 3 is a sectional view showing a third embodiment of the torque fluctuation absorbing damper according to the present invention by cutting along a plane passing through the axis O thereof. This embodiment is different from the second embodiment shown in FIG. 2 in that a means for limiting the relative displacement of the hub 1 and the pulley 6 in the torsional direction and a movement limiting means for preventing the pulley 6 from separating in the axial direction. However, the point is that a metal ring 9 described below is provided between the annular mass 2 and the pulley 6.

That is, the annular mass 2 is concentrically arranged on the outer peripheral side of the outer peripheral cylindrical portion 13 of the hub 1 similarly to the embodiment of FIG. A damper rubber 4 made of a rubber-like elastic material is press-fitted between the peripheral surfaces facing the first and second rubber members 13. The annular mass 2 includes a second pulley 26 having a poly-V groove 26a formed on an outer peripheral surface thereof;
It comprises a cylindrical pulley support 27 extending from its inner circumference to the back side.
A pulley 6 is arranged via a synthetic resin bearing 5 so as to be relatively displaceable in the circumferential direction.

The pulley 6 has a pulley body 61 having a poly-V groove 61a formed on the outer peripheral surface thereof, and an extension 63 extending cylindrically from the outer periphery of the rear end thereof. The inner peripheral surface is slidably in contact with the outer peripheral surface of the radial bearing portion 51 of the bearing 5, and the front end surface of the pulley main body 61 is slidably in contact with the thrust bearing portion 52 of the bearing 5. Extension 63 on pulley 6
The outer sleeve 71 press-fitted on the inner peripheral surface of the hub and the inner sleeve 72 press-fitted on the outer peripheral surface of the boss portion 11 of the hub 1 have a simple cylindrical shape. These outer sleeves 7 facing each other
Coupling rubber 7 is integrally vulcanized and bonded between 1 and inner sleeve 72.

A metal ring 9 is fitted on an outer peripheral surface of an end of the annular mass 2 on the back side of the second pulley 26.
At the rear end of the metal ring 9, engaging claws 91 are formed at predetermined intervals in the circumferential direction so as to bend in a hook shape toward the inner peripheral side and extend. On the other hand, on the outer peripheral surface of the front end of the pulley body 61 of the pulley 6, end engaging recesses 64 that are elongated in the circumferential direction are formed at phase intervals corresponding to the engaging claws 91. The engaging recess 64 and the engaging claw 91
As shown in the perspective view of the main part of FIG. 4, they are loosely fitted to each other with an appropriate gap in the circumferential direction.

The method of manufacturing the torque fluctuation absorbing damper is as follows.
Although it is the same as that of the embodiment of FIG. 2 described above, the metal ring 9 is fitted in advance on the outer peripheral surface of the annular mass 2 on the rear side of the second pulley 26 before the pulley 6 is assembled. You. Then, the pulley support 2 in the annular mass 2
In the process of extrapolating the pulley body 61 of the pulley 6 to the outer periphery of the pulley 6 via the bearing 5, as shown in FIG. 5, each engaging claw 91 of the metal ring 9 has a shape inclined to the front side. The end portion bent inward interferes with the end portion of the pulley main body portion 61, so that the end portion of the pulley main body portion 61 is elastically deformed and rides up. It fits into the recess 64. The engaging claw 91 once fitted into the engaging recess 64 does not come off from the engaging recess 64 even if the pulley 6 is moved in the detaching direction toward the rear side.

The function of the torque fluctuation absorbing damper having the above configuration is the same as that shown in FIG.

The relative displacement of the annular mass 2 and the pulley 6 in the torsional direction due to the resonance of the vibration system composed of the coupling rubber 7 and the pulley 6 is increased by the metal ring 9 fitted to the annular mass 2. The coupling rubber 7 is not subjected to excessive shearing deformation because it is limited by the interference between the engaging claw 91 and the circumferential end of the engaging recess 64 formed in the pulley 6.

The axial movement of the pulley 6 toward the front side is restricted by the second pulley 26 of the annular mass 2 via the thrust bearing portion 52 of the bearing 5 at the front end surface of the pulley body 61 of the pulley 6. The axial movement of the pulley 6 toward the rear side is performed by engaging the engaging claw 91 of the metal ring 9 fitted on the annular mass 2 with the engaging recess 6 formed on the pulley 6.
4 is limited by interference with the inner surface. Therefore, even if the coupling rubber 7 is broken due to fatigue or the like, the pulley 6 does not fall off the outer periphery of the annular mass 2.

The present invention is not limited to the configuration of each of the above-described embodiments. For example, the shape of each part such as the hub 1, the annular mass 2, the pulley 6, etc. may be variously changed according to the use conditions and the like. Is possible.

[0044]

As described above, according to the torque fluctuation absorbing damper according to the present invention, even if the coupling rubber is broken due to fatigue or the like, the pulley falls off the outer periphery of the hub or the annular mass. Because there is no such thing
Safety is improved.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a first embodiment of a torque fluctuation absorbing damper according to the present invention by cutting along a plane passing through an axis O. FIG.

FIG. 2 is a cross-sectional view showing a second preferred embodiment of the torque fluctuation absorbing damper according to the present invention by cutting along a plane passing through an axis O;

FIG. 3 is a cross-sectional view showing a third preferred embodiment of a torque fluctuation absorbing damper according to the present invention by cutting along a plane passing through an axis O;

FIG. 4 is a perspective view of a main part of the third embodiment.

FIG. 5 is an explanatory diagram showing a process of extrapolating a pulley to the outer periphery of a pulley supporting portion of an annular mass in the third embodiment.

FIG. 6 is a cross-sectional view showing an example of a torque fluctuation absorbing damper according to a conventional technique, cut along a plane passing through an axis O.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Hub 11 Boss part 12,22 Radial part 13 Outer peripheral cylinder part 2 Annular mass 21 Inner peripheral cylinder part 23,27 Pulley support part 24 Protrusion (movement restricting means) 25 Engagement pin 26 Second pulley 3,72 Inner sleeve 31 Mass mounting part 32, 63 Extension part 4 Damper rubber 5 Bearing 51 Radial bearing part 52 Thrust bearing part 6 Pulley 61 Pulley body part 62 Inward flange 62a, 72b Long hole 64 Engaging concave part (movement restricting means) 7 Coupling rubber 71 Outer sleeve 71a Radial portion 71b, 91 Engagement claw 72a Engagement protrusion (movement restricting means) 8 Sensor plate 9 Metal ring (movement restricting means)

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Yasushi Fukui 4-3-1 Tsujido Shinmachi, Fujisawa-shi, Kanagawa N.K.Megrastic In-house (72) Inventor Masami Hasegawa Tsujido, Fujisawa-shi, Kanagawa 4-3-1 Shinmachi N.K.Megrastic Stock Company In-house (72) Inventor Tsutomu Kano 4-3-1 Shinmachi Shinjuku, Fujisawa-shi, Kanagawa N.K.Megrastic Stock Company In-house F term (reference) 3J031 AA03 AC10 CA03

Claims (1)

[Claims] 1. A hub (1) attached to a shaft end, a pulley (6) and an annular mass (2) arranged on the outer peripheral side of the hub (1), a hub (1) side and a pulley (6). ) Side, a damper rubber (4) for elastically connecting the hub (1) side and the annular mass (2) side, and the hub (1) or the annular shape. A movement restricting means (2) for restricting the pulling-off movement of the pulley (6) with respect to the mass (2);
4, 71b, 72a, 9, 64).