JP2012215265A - Torsional vibration damping device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a torsional vibration damping device which can prevent an excessive load from being applied to a rocking fulcrum part or a part of a torque transmission member supported by the rocking fulcrum part by preventing the inclination of the torque transmission member, and can prevent the rocking fulcrum and the torque transmission member from deteriorating in durability.SOLUTION: An overlap part 16a is provided for a projection 16A of an arm member 16 of the torsional vibration damping device 1, and the overlap part 16a and a cam member 6 are overlapped in a radial direction of a disk plate 7. Moreover, an overlap part 16c is provided for a projection 16C of the arm member 16, and the overlap part 16c and a spring seat 15 are overlapped in the radial direction of the disk plate 7.

Description

  The present invention relates to a torsional vibration damping device, and in particular, is interposed between an internal combustion engine of a vehicle and a drive transmission system so that rotational torque is transmitted between a first rotating member and a second rotating member. Furthermore, the present invention relates to a torsional vibration damping device in which a first rotating member and a second rotating member are connected to each other via an elastic member so as to be relatively rotatable.

  Conventionally, a drive source such as an internal combustion engine or an electric motor is connected to wheels and the like to transmit rotational torque from the drive source and torsional vibration between the drive source and a drive transmission system having a transmission gear set is absorbed. Torsional vibration damping devices are known.

  The torsional vibration damping device includes, for example, a first rotating member connected to an input shaft of a transmission, a second rotating member fastened and released to a flywheel on the drive source side, a first rotating member, and It is comprised from the elastic member which connects the 2nd rotation member elastically in the circumferential direction (for example, refer patent document 1).

  The first rotating member is composed of a hub that is connected to the input shaft of the transmission so as not to rotate and to be movable in the axial direction, and the second rotating member is positioned inward in the radial direction of the clutch disk. And it is comprised from a pair of disk plate which opposes the axial direction of an input shaft on both sides of a hub.

  The hub has a cylindrical boss that is spline-engaged with the input shaft and a disk-shaped flange that extends radially outward from the boss. The elastic member is composed of a single coil spring. The coil spring is accommodated in a window hole formed in the flange, and both ends in the circumferential direction are supported in the circumferential direction. It is supported in the circumferential direction by a window formed in the disk plate.

  In the torsional vibration damping device having such a configuration, when the clutch disk and the pair of disk plates and the hub rotate relative to each other, the coil spring is disposed in the circumferential direction between the clutch disk, the pair of disk plates and the hub. By being compressed, the torsional vibration input from the disk plate to the hub is absorbed and damped by the coil spring.

  By the way, as noise on the transmission side generated by torsional vibration, there are known abnormal noise during idling, abnormal noise during traveling, and booming noise. Therefore, in order to absorb the torsional vibration that causes each abnormal noise, it is necessary to appropriately set the torsional characteristics of the torsional vibration damping device.

  Here, as an abnormal noise during idling, when the shift position is changed to neutral and the internal combustion engine is in an idling state, it is caused by torsional vibration using rotational fluctuation due to torque fluctuation of the driving source as a no-load state. There is known a rattling noise, that is, a so-called rattling sound, which is generated when a pair of gears collide with each other.

  In addition, as an abnormal noise during traveling, the idle gear pair of the transmission gear set is caused by torsional vibration caused by rotational fluctuation caused by torque fluctuation of the drive source or torsional resonance of the drive transmission system during acceleration / deceleration of the vehicle. There is a known jagged noise generated by a collision, a so-called jagged sound.

  Also, as a booming noise, an abnormal noise generated in the vehicle interior due to vibration caused by torsional resonance of the drive transmission system using the torque fluctuation of the drive source as an excitation force is known, and the torsional resonance of the drive transmission system is usually Since it exists during steady running (for example, the rotational speed of the internal combustion engine is around 2000 rpm), a muffled noise is generated during steady running.

  Conventionally, as a torsional vibration damping device in which torsional characteristics are appropriately set, for example, a device described in Patent Document 2 is known.

  The torsional vibration damping device is formed on a driving side rotating member that rotates integrally with the internal combustion engine, a driven side rotating member that is coaxial with the driving side rotating member, and that is relatively rotatable, and a driving side rotating member. A rolling element that moves along the contacted surface and follows the relative rotation between the driving side rotating member and the driven side rotating member so that the rolling element moves along the contacted surface, thereby driving the driven side. A displacement member that is relatively displaced with respect to the rotating member, and an elastic member that is elastically deformed following the relative displacement of the displacement member are provided.

  The contacted surface is configured such that the curvature changes according to the relative rotation angle between the driving side rotating member and the driven side rotating member. Further, the displacement member is provided on the driving side rotation member so that one end thereof swings around the swing shaft, and a rolling element that rolls on the contacted surface is rotatably provided at the other end. ing.

  In this torsional angle attenuating device, when the internal combustion engine is driven, the driving side rotating member is rotationally driven, and the rotational driving of the driving side rotating member is transmitted to the driven side rotating member via the elastic member. When the torque of the internal combustion engine fluctuates and the driving side rotating member and the driven side rotating member rotate relative to each other, the rolling element of the displacement member moves along the contacted surface, and the driving side rotating member or the driven side rotating member Relative displacement with respect to.

  When the displacement member is relatively displaced, the elastic member is compressed, and the torque fluctuation of the internal combustion engine is absorbed and output to the driven side rotation member.

  As described above, the displacement member relatively displaces following the torsion angle, and the compression of the elastic member is defined by this relative displacement, so that the torsion characteristic can be defined by the displacement member, the contacted surface, and the elastic member.

  For this reason, the torsion angle between the driving side rotating member and the driven side rotating member can be widened using an elastic member having low rigidity, and the internal combustion engine is in an idle state when the shift position is changed to neutral. As described above, in the region where the twist angle between the driving side rotating member and the driven side rotating member is small, the vibration can be attenuated by the low rigidity elastic member to suppress the generation of the rattling sound.

  Further, in a region where the torsion angle between the driving side rotating member and the driven side rotating member is large, the torsion angle of the driving side rotating member and the driven side rotating member is increased to provide a high rigidity torsion characteristic that increases the torque increase rate. By obtaining this, it is possible to suppress the jallah sound.

  As a result, large torsional vibrations caused by rotational fluctuations due to torque fluctuations of the internal combustion engine and torsional resonance of the drive transmission system are attenuated, and the jagged noise generated by the collision of the idle gear pairs of the transmission gear set and the drive transmission It is possible to suppress the occurrence of a booming noise due to the torsional resonance of the system.

JP 2003-194095 A JP 2001-74102 A

  However, in such a conventional torsional vibration damping device, since the displacement member is attached to the drive side rotation member so as to oscillate about the oscillation axis, the displacement member is pressed against the contacted surface. When the elastic member is compressed, a sliding moment between the rolling element and the contacted surface generates a rotational moment in the axial direction of the displacing member around the swing axis.

  For this reason, the displacement member is greatly inclined in the axial direction of the swing shaft, and an excessive load is applied to the swing shaft and the portion of the displacement member supported by the swing shaft. There was a problem of getting worse.

  In order to improve the durability of the displacement member and the swing shaft, the displacement member and the swing shaft should be reinforced to increase the strength by increasing the thickness of the displacement member or increasing the diameter of the swing shaft. However, if the displacement member and the swing shaft are reinforced, the displacement member and the swing shaft become large, and as a result, the torsional vibration damping device cannot be reduced in size.

  The present invention has been made in order to solve the above-described conventional problems, and prevents the torque transmission member from being tilted so as to be provided at a swing fulcrum portion or a portion of the torque transmission member supported by the swing fulcrum portion. It is an object of the present invention to provide a torsional vibration damping device that can prevent an excessive load from being applied and can prevent the durability of a swing fulcrum portion and a torque transmission member from deteriorating.

  In order to achieve the above object, the torsional vibration damping device according to the present invention is (1) provided on the same axis as the first rotating member and the first rotating member, with respect to the first rotating member. A second rotating member that is relatively rotatable, and provided between the first rotating member and the second rotating member, and the first rotating member and the second rotating member are relatively rotated. Elastically deforming the first rotation member so as to rotate integrally with the first rotation member, and an elastic member that transmits a rotation torque between the first rotation member and the second rotation member. A cam member provided on the member and having a cam surface whose curvature changes with a change in torsion angle of the first rotating member and the second rotating member; and one end portion of the cam member contacting the cam surface of the cam member And the other end abuts against one end of the elastic member in the extending direction, When the first rotating member and the second rotating member rotate relative to each other, the elastic member is elastically deformed by swinging about a swing fulcrum provided on the second rotating member. And a torque transmission member that transmits rotational torque between the first rotation member and the second rotation member, and a cam surface of the cam member that is rotatably provided at one end of the torque transmission member. And one end of the torque transmitting member and the cam member are overlapped in the radial direction of the first rotating member and the second rotating member.

  In this torsional vibration damping device, the first rotating member has a cam member having a cam surface whose curvature changes with a change in torsion angle of the first rotating member and the second rotating member, Since the torque transmission member that contacts the cam surface of the cam member via the rolling element is interposed between the elastic member and the elastic member, the cam member presses the elastic member via the torque transmission member as the cam member rotates. Thus, by changing the reaction force from the elastic member to the torque transmitting member, the range of the torsion angle between the first rotating member and the second rotating member can be widened. The torsional rigidity of the second rotating member can be reduced as a whole.

  Further, when the torque transmission member is pressed against the cam surface of the cam member by the compression of the elastic member, a rotational moment is generated in the axial direction of the torque transmission member around the swing shaft.

  In this torsional vibration damping device, one end of the torque transmitting member and the cam member are overlapped in the radial direction of the first rotating member and the second rotating member. When a rotational moment is generated in the axial direction of the member, one end of the torque transmission member can be brought into contact with the cam member, and the torque transmission member can be prevented from tilting in the axial direction of the swing fulcrum portion. .

  For this reason, it is possible to prevent an excessive load from being applied to the swing fulcrum portion and the portion of the torque transmission member supported by the swing fulcrum portion, and the durability of the swing fulcrum portion and the torque transmission member is deteriorated. Can be prevented.

  In the torsional vibration damping device according to (1) above, (2) a support member that is provided at one end of the elastic member in the extending direction and that supports the elastic member, and is rotatably provided at the other end of the torque transmitting member. A rolling member that contacts the support member, and the other end portion of the torque transmission member and the support member are overlapped in the radial direction of the first rotating member and the second rotating member. Consists of things.

  In this torsional vibration damping device, the other end of the torque transmitting member and the support member are overlapped in the radial direction of the first rotating member and the second rotating member. When a rotational moment is generated in the axial direction of the member, the other end of the torque transmission member can be brought into contact with the holding member, and the torque transmission member can be further prevented from tilting.

  For this reason, it is possible to further prevent an excessive load from being applied to the swing fulcrum part and the portion of the torque transmission member supported by the swing fulcrum part, and the durability of the swing fulcrum part and the torque transmission member is deteriorated. This can be further prevented.

  In the torsional vibration damping device according to the above (1) or (2), (3) a pair of plate-like portions to which at least one end portion of the torque transmission member is connected via a shaft member that rotatably supports the rolling element. The pair of plate-like portions are configured to overlap the cam member so as to sandwich the cam member in the axial direction.

  In this torsional vibration damping device, the pair of plate-like portions of the torque transmitting member overlap in the radial direction of the cam member and the second rotating member so that the cam member is sandwiched in the axial direction. Thus, when a rotational moment is generated in one axial direction of the torque transmitting member, one plate-like portion of the torque transmitting member can be brought into contact with the cam member, and the torque transmitting member can be moved in the axial direction of the swing fulcrum portion. Inclination to one side can be prevented.

  Further, when a rotational moment is generated in the other axial direction of the torque transmission member around the swing fulcrum, the other plate-like portion of the torque transmission member can be brought into contact with the cam member, and the torque transmission member Can be prevented from tilting to the other of the swing fulcrum portions in the axial direction.

  In the torsional vibration damping device according to (2) above, (4) at least the other end portion of the torque transmission member is composed of a pair of plate-like portions connected via a shaft member that rotatably supports the rolling member. The pair of plate-like portions are configured to overlap the support member so as to sandwich the support member in the axial direction.

  In this torsional vibration damping device, the pair of plate-like portions of the torque transmitting member overlap in the radial direction of the supporting member and the second rotating member so as to sandwich the supporting member supporting the elastic member in the axial direction. When a rotational moment is generated in one of the axial directions of the torque transmission member with the fulcrum as the center, one plate-like portion of the torque transmission member can be brought into contact with the support member, and the torque transmission member Inclination to one side in the axial direction of the portion can be prevented.

  Further, when a rotational moment is generated in the other axial direction of the torque transmission member around the swing fulcrum, the other plate-like portion of the torque transmission member can be brought into contact with the support member, and the torque transmission member Can be prevented from tilting to the other of the swing fulcrum portions in the axial direction.

  (1) In the torsional vibration damping device according to (1) to (4), (5) the curvature of the cam surface of the cam member is the above when the torsion angle between the first rotating member and the second rotating member is minimum. The cam member is configured to increase as the twist angle increases from the initial position of the cam member.

  This torsional vibration damping device varies the curvature of the cam surface of the cam member with which the torque transmitting member comes into contact according to the change in the torsion angle of the first rotating member and the second rotating member. And the torsional rigidity can be lowered by widening the range of the torsion angle of the second rotating member.

  In addition, since the torsional rigidity between the first rotating member and the second rotating member can be increased as the torsion angle between the first rotating member and the second rotating member is increased, a large torque fluctuation is caused by the elastic member. The rotational torque can be smoothly transmitted from the first rotating member to the second rotating member while being attenuated.

  Further, even when the curvature of the cam surface of the cam member that contacts the torque transmission member increases according to the change in the twist angle of the first rotation member and the second rotation member, one end of the torque transmission member is the rolling element. Since the cam surface of the cam member is slid through the cam member, the contact pressure between the one end portion of the torque transmitting member and the cam member can be prevented from being increased, and the wear between the one end portion of the arm portion and the cam member can be prevented. Can be suppressed.

  (1) In the torsional vibration damping device according to (1) to (5), (6) the torque transmitting member is arranged point-symmetrically with respect to the central axes of the first rotating member and the second rotating member. It is composed of

  In this torsional vibration damping device, since the torque transmission member is arranged point-symmetrically with respect to the central axes of the first rotating member and the second rotating member, the central axes of the first rotating member and the second rotating member Thus, the torque transmission member sandwiches the cam member.

  For this reason, when the cam member urges the elastic member via the torque transmission member, the torque transmission member clamps the cam member with a strong pressing force across the central axis of the first rotating member by the reaction force of the elastic member. To do. For this reason, rotational torque can be more reliably transmitted between the first rotating member and the second rotating member, and the first rotating member and the second rotating member can be reliably rotated integrally. .

  (1) In the torsional vibration damping device according to (1) to (6) above, (7) the first rotating member has the cam member on the outer peripheral portion, and the boss to which the input shaft of the transmission is connected to the inner peripheral portion. The second rotating member is disposed on both sides of the cam member in the axial direction, fixed to each other at a predetermined interval in the axial direction, and via a swing shaft constituting the swing fulcrum portion A pair of disk plates that swingably support the torque transmission member is provided, and a support portion that supports the other end in the extending direction of the elastic member is provided on the pair of disk plates.

  In the torsional vibration damping device, a pair of disk plates is provided with a support portion that supports the other end portion in the extending direction of the elastic member, and one end portion in the extending direction of the elastic member is in contact with the other end portion of the torque transmitting member. Since the other end portion of the torque transmitting member contacts the cam surface of the cam member via the rolling element, the range of the torsion angle between the first rotating member and the second rotating member is widened to reduce the rigidity of the elastic member. The rotational torque can be smoothly transmitted from the first rotating member to the second rotating member.

  As a result, large torsional vibrations caused by fluctuations in rotation due to torque fluctuations of the drive source and torsional resonances of the drive transmission system are attenuated, and the jagged noise and drive transmission generated when the idle gear pair of the transmission gear set collides with each other. It is possible to suppress the occurrence of a booming noise due to the torsional resonance of the system.

Further, when excessive torque is input to the first rotating member, when the first rotating member and the second rotating member rotate relative to each other, the torque transmitting member has a peak portion with the largest curvature of the cam surface. In order to get over, the first rotating member can be idled with respect to the second rotating member, and the cam member can function as a torque limiter.
As a result, it is possible to prevent an excessive torque from being transmitted between the first rotating member and the second rotating member, and to protect the transmission gear set of the transmission.

  In the torsional vibration damping device according to the above (1) to (7), (8) the first rotating member and the second rotating member between the first rotating member and the second rotating member; It is comprised from what is equipped with the hysteresis mechanism which makes a frictional contact.

  In this torsional vibration damping device, since a hysteresis mechanism is interposed between the first rotating member and the second rotating member, the torsional angle between the first rotating member and the second rotating member is large. It is possible to increase the hysteresis torque between the first rotating member and the second rotating member, and it is possible to further suppress the occurrence of a booming noise and a jagged noise due to torsional resonance of the drive transmission system.

  According to the present invention, it is possible to prevent the torque transmission member from being inclined and to prevent an excessive load from being applied to the swing fulcrum portion and the portion of the torque transmission member supported by the swing fulcrum portion. It is possible to provide a torsional vibration damping device that can prevent the durability of the fulcrum part and the torque transmission member from deteriorating.

It is a figure which shows one Embodiment of the torsional vibration damping device which concerns on this invention, and is a perspective view of a torsional vibration damping device. 1 is a diagram showing an embodiment of a torsional vibration damping device according to the present invention, and is a perspective view of the torsional vibration damping device in a state where one of disk plates is removed. It is a figure which shows one Embodiment of the torsional vibration damping device which concerns on this invention, and is a front view of a torsional vibration damping device. It is a figure which shows one Embodiment of the torsional vibration damping apparatus which concerns on this invention, and is AA direction arrow sectional drawing of FIG. It is a figure which shows one Embodiment of the torsional vibration damping device which concerns on this invention, and is a top view of an arm member. It is a figure which shows one Embodiment of the torsional vibration damping device which concerns on this invention, and is BB direction sectional drawing of FIG. It is a figure which shows one Embodiment of the torsional vibration damping device which concerns on this invention, and is a figure which shows the positional relationship of the one end part of an arm member, and a cam member. It is a figure which shows one Embodiment of the torsional vibration damping device which concerns on this invention, and is a figure which shows the positional relationship of the other end part of an arm member, and a spring seat. It is a figure which shows one Embodiment of the torsional vibration damping device which concerns on this invention, and is a front view of a torsional vibration damping device when the torsion angle of a disk plate and a boss | hub is +45 degrees. It is a figure which shows one Embodiment of the torsional vibration damping device which concerns on this invention, and is a front view of the torsional vibration damping device when the torsion angle of a disk plate and a boss | hub is +90 degrees. It is a figure which shows one Embodiment of the torsional vibration damping device which concerns on this invention, and is a front view of the torsional vibration damping device when the torsion angle of a disk plate and a boss | hub is -45 degrees. It is a figure which shows one Embodiment of the torsional vibration damping device which concerns on this invention, and is a figure which shows the relationship between the twist angle of a torsional vibration damping device, and a torque. It is a figure which shows one Embodiment of the torsional vibration damping device which concerns on this invention, and is a figure which shows the relationship between the rotation speed of an internal combustion engine, and rotational angular velocity fluctuation | variation. FIG. 3 is a diagram showing an embodiment of the torsional vibration damping device according to the present invention, and when the arm member is tilted to one of the axis directions of the swing shaft, the overlap portion of one protruding piece contacts the cam member. It is a figure which shows the state which carried out. FIG. 5 is a diagram showing an embodiment of the torsional vibration damping device according to the present invention, and when the arm member is tilted to one side in the axial direction of the swing shaft, the overlap portion of the other protruding piece comes into contact with the spring seat. It is a figure which shows the state which carried out. FIG. 3 is a diagram showing an embodiment of the torsional vibration damping device according to the present invention, and when the arm member is inclined to the other of the swing shafts, the overlap portion of the other protruding piece comes into contact with the cam member. It is a figure which shows the state which carried out. FIG. 3 is a diagram showing an embodiment of the torsional vibration damping device according to the present invention, and when the arm member is tilted to the other of the swing shafts, the overlap portion of one protruding piece contacts the cam member. It is a figure which shows the state which carried out.

Hereinafter, embodiments of a torsional vibration damping device according to the present invention will be described with reference to the drawings.
1 to 17 are views showing an embodiment of a torsional vibration damping device according to the present invention.
First, the configuration will be described.
1 to 4, the torsional vibration damping device 1 includes a first rotating member 2 and a second rotating member 3 provided on the same axis as the first rotating member 2.

  Rotational torque from an internal combustion engine (not shown) that is a drive source is input to the second rotating member 3, and the first rotating member 2 does not show the rotational torque of the second rotating member 3. It is transmitted to the transmission of the drive transmission system.

  A pair of coil springs 4 as elastic members are provided between the first rotating member 2 and the second rotating member 3, and the coil spring 4 is composed of the first rotating member 2 and the second rotating member. When the 3 rotates relatively, it is compressed in the circumferential direction of the first rotating member 2.

  The first rotating member 2 includes a boss 5 that is spline-fitted to the outer peripheral portion of the input shaft 26 of the transmission of the drive transmission system, and a cam member 6 that is provided on the outer peripheral portion of the boss 5. .

  The boss 5 and the cam member 6 may be integrally formed. Further, the boss 5 and the cam member 6 are formed separately, spline portions are formed on the outer peripheral portion of the boss 5 and the inner peripheral portion of the cam member 6, and the boss 5 and the cam member 6 are spline-fitted. Also good.

  The second rotating member 3 includes a pair of disk plates 7 and 8 and a clutch disk 10. The disc plates 7 and 8 are disposed on both sides of the cam member 6 in the axial direction, and are connected by a swing shaft 9 as a swing fulcrum at a predetermined interval in the axial direction.

The swing shaft 9 is bridged to the disk plates 7 and 8, and both end portions in the axial direction are formed to have a large diameter, and are thereby locked to the disk plates 7 and 8. For this reason, the disk plates 7 and 8 are integrally rotated by being integrated by the swing shaft 9.
A boss 5 is accommodated in the circular center holes 7 a and 8 a of the disk plates 7 and 8, and the boss 5 is provided on the same axis as the disk plates 7 and 8.

  The clutch disk 10 is provided radially outward of the disk plate 7 and includes a cushioning plate 11 and friction materials 12a and 12b. The cushioning plate 11 is composed of a ring-shaped member that undulates in the thickness direction, and is fixed to the disc plate 7 by rivets 13a.

  The friction materials 12a and 12b are fixed to both surfaces of the cushioning plate 11 by rivets 13b. The friction materials 12a and 12b are bolted to a flywheel (not shown) fixed to the crankshaft of the internal combustion engine and to the flywheel. It is located between the pressure plate of the clutch cover.

  The friction materials 12a and 12b are pressed against the pressure plate and frictionally engaged with the flywheel and the pressure plate, whereby the rotational torque of the internal combustion engine is input to the disk plates 7 and 8.

  When a clutch pedal (not shown) is depressed, the pressure plate releases the pressing of the friction materials 12a and 12b, and the friction materials 12a and 12b are separated from the flywheel, so that the rotational torque of the internal combustion engine can be reduced. , 8 is not input.

  The disk plate 7 is provided with a pedestal 14 as a support portion. The pedestal 14 is attached to the disk plate 8 so as to protrude from the disk plate 7 in the axial direction.

  The other end portion in the extending direction of the coil spring 4 as an elastic member is attached to the pedestal 14, and a spring seat 15 as a support member is attached to one end portion in the extending direction of the coil spring 4. The other end of is a free end.

  Further, an arm member 16 as a torque transmission member is provided between the coil spring 4 and the cam member 6, and this arm member 16 is located between the disk plates 7 and 8 and is attached to the swing shaft 9. It is swingably supported.

  As shown in FIGS. 5 and 6, a needle bearing 17 is interposed between the swing shaft 9 and the arm member 16. The needle bearing 17 includes an outer race 17a attached to the arm member 16, and a needle needle 17b interposed between the outer race 17a and the swing shaft 9, and the outer race 17a is a needle needle. It is freely rotatable with respect to the swing shaft 9 via 17b. For this reason, the arm member 16 is rotatably attached to the swing shaft 9 via the needle bearing 17.

  As shown in FIGS. 5 and 6, projecting pieces 16A and 16B as bifurcated plate-like portions are formed at one end of the arm member 16, and the projecting pieces 16A and 16B are pins as shaft members. 18 are connected.

  A roller member 19 as a rolling element is rotatably attached to the pin 18. The roller member 19 includes an outer race 19a provided on the outer periphery of the pin 18, a needle bearing including a needle needle 19b interposed between the outer race 19a and the pin 18 (see FIG. 7), and the outer race 19a. The roller 19c is attached to the outer race 19a at the outer periphery, and the roller 19c is rotatable with respect to the pin 18 via a needle bearing.

  The roller 19c rotates in contact with the cam surface 6a of the cam member 6, and one end of the arm member 16 contacts the cam surface 6a of the cam member 6 through the roller 19c.

  The other end of the arm member 16 is formed with bifurcated projecting pieces 16C and 16D as plate-like parts, and the projecting pieces 16C and 16D are connected by a pin 20 as a shaft member.

  A roller member 21 as a rolling member is rotatably attached to the pin 20. The roller member 21 includes an outer race 21a provided on an outer peripheral portion of the pin 20, a needle bearing including a needle needle 21b interposed between the outer race 21a and the pin 20, and an outer race on the outer peripheral portion of the outer race 21a. The roller 21c is attached to the roller 21c. The roller 21c is rotatable with respect to the pin 20 via a needle bearing.

  The roller 21c comes into contact with the outer peripheral surface of the spring seat 15. The other end of the arm member 16 comes into contact with the outer peripheral surface of the spring seat 15 through the roller 21c.

  Further, the cam member 6 has a cam surface 6 a whose curvature changes as the twist angle between the disk plates 7 and 8 and the boss 5 changes.

  In this embodiment, the cam member 6 has an elliptical cam surface, and the curvature of the cam surface 6a is the smallest torsion angle between the disk plates 7 and 8 and the boss 5 (the torsion angle is approximately 0 °). From the initial position of the cam member 6 at this time, it increases as the torsion angle between the disk plates 7 and 8 and the boss 5 increases.

  Therefore, the cam member 6 according to the present embodiment is configured so that the roller 19c of the arm member 16 comes into contact with the cam surface 6a having a small curvature when the twist angle between the disk plates 7 and 8 and the boss 5 is minimum. The initial position of is set.

  For this reason, when the cam member 6 rotates and the position of the cam surface 6a where the roller 19c of the arm member 16 abuts is changed, the spring seat 15 is biased by the arm member 16 and the compression amount of the coil spring 4 is reduced. Variable. At this time, the spring seat 15 moves so as to approach and separate from the base 14.

  The arm member 16 is arranged point-symmetrically with respect to the central axis of the disk plates 7 and 8, and the arm member 16 is a cam surface 6a having the same curvature across the central axis of the disk plates 7 and 8. One end portion can be brought into contact with the.

  On the other hand, as shown in FIG. 4, a hysteresis mechanism 22 is interposed between the disk plates 7 and 8 and the cam member 6, and the hysteresis mechanism 22 includes annular friction members 23 and 24 and a disc spring 25. It is composed of

  The friction material 23 is formed of an annular member having a predetermined friction coefficient on the surface, and is attached to the disk plate 7 so as to be interposed between the disk plate 7 and the cam member 6.

  The friction member 24 is formed of an annular member having a predetermined friction coefficient on the surface, and is attached to the disc plate 8 so as to be interposed between the disc plate 8 and the cam member 6.

  The disc spring 25 is formed in a conical shape, and is interposed between the friction material 24 and the disk plate 8. The disc spring 25 generates elastic force in the axial direction of the cam member 6, thereby bringing the disc plates 7 and 8 and the cam member 6 into frictional contact with each other via the friction members 23 and 24. Hysteresis torque is generated between the disk plates 7 and 8.

  On the other hand, as shown in FIG. 7, the protruding portions 16A and 16B of the arm member 16 are formed with overlapping portions 16a and 16b. The overlapping portions 16a and 16b are connected to the cam member 6 from the protruding pieces 16A and 16B. The cam member 6 and the disc plates 7 and 8 and the cam member 6 are overlapped in the radial direction (see FIG. 3). That is, the protruding pieces 16 </ b> A and 16 </ b> B face each other in the axial direction of the cam member 6 so as to sandwich the cam member 6.

  Further, as shown in FIG. 8, the protruding portions 16C and 16D of the arm member 16 are formed with overlapping portions 16c and 16d, and the overlapping portions 16c and 16d are formed as protruding pieces as shown in FIG. By projecting from 16C and 16D to the cam member 6 side, the cam member 6, the disk plates 7 and 8, and the cam member 6 are overlapped in the radial direction (see FIG. 3). That is, the protruding pieces 16C and 16D are opposed to each other in the axial direction of the spring seat 15 so as to sandwich the spring seat 15.

Next, the operation will be described.
9 to 11 show a state in which the disk plates 7 and 8 are rotating in the counterclockwise rotation direction (R2 direction) from the state of FIG. 3 in response to the rotational torque of the internal combustion engine. The description will be made assuming that the disk plates 7 and 8 are twisted in the clockwise direction (R1 direction) on the positive side.

  9 to 11 show a state where the disk plate 8 is removed. The boss 5 is twisted to the positive side with respect to the disk plates 7 and 8 when the vehicle is accelerated.

  The friction materials 12 a and 12 b are pressed against the pressure plate and frictionally engaged with the flywheel and the pressure plate, whereby the rotational torque of the internal combustion engine is input to the disk plates 7 and 8.

  In the torsional vibration damping device 1 according to the present embodiment, the relative rotation between the disk plates 7 and 8 and the boss 5 is small, that is, the torsion angle between the disk plates 7 and 8 and the boss 5 is small near 0 °. As shown in FIG. 3, the cam member 6 is positioned at the initial position and rotates integrally with the boss 5.

  At this time, the roller 19c of the arm member 16 is in contact with the cam surface 6a having a small curvature of the cam member 6, and the cam member 6 presses the arm member 16 against the spring seat 15, whereby the coil spring 4 is moved by the cam member 6. Be energized.

  At this time, the arm member 16 presses the cam member 6 by the lever principle with the swing shaft 9 as a fulcrum by the reaction force of the coil spring 4. Therefore, the rotational torque of the disk plates 7 and 8 is transmitted to the cam member 6 through the coil spring 4 and the arm member 16. For this reason, the rotational torque of the internal combustion engine is transmitted to the input shaft of the transmission, and at this time, the amount of compression of the coil spring 4 is small.

  For this reason, while transmitting the power of the internal combustion engine from the disk plates 7 and 8 to the boss 5, the torsional vibration between the disk plates 7 and 8 and the boss 5 is absorbed and attenuated.

  On the other hand, when the rotational fluctuation due to the torque fluctuation of the internal combustion engine is small during acceleration of the vehicle, the fluctuation torque between the disk plates 7 and 8 and the boss 5 is small. In the clockwise direction (R1 direction).

  At this time, when the cam member 6 rotates in the R1 direction as the torsion angle between the disk plates 7 and 8 and the boss 5 increases as in the state shown in FIG. 9 from the state shown in FIG. 3, the roller 19c of the arm member 16 is rotated. Rolls along the cam surface 6a. For this reason, the one end part of the arm member 16 slides on the cam surface 6a via the roller 19c.

  Since the curvature of the cam surface 6a increases as the torsional angle between the disk plates 7 and 8 and the boss 5 increases from the initial position of the cam member 6, one end of the arm member 16 passes through the roller 19c. When the cam surface 6a of the cam member 6 having a gradually increasing curvature is pressed, the other end of the arm member 16 moves radially inward and circumferentially of the disk plates 7 and 8.

  As the cam member 6 rotates in the R1 direction, the other end portion of the arm member 16 moves inward in the radial direction of the disk plates 7 and 8, thereby bringing the spring seat 15 close to the pedestal 14.

  Further, the other end of the arm member 16 moves along the circumferential outer peripheral surface of the spring seat 15 via the roller 21c, so that the spring seat 15 can be prevented from moving in the circumferential direction. FIG. 9 shows a state in which the twist angle between the disk plates 7 and 8 and the boss 5 is + 45 °.

  As the arm member 16 biases the coil spring 4 in this way, the arm member 16 uses the swinging shaft 9 as a fulcrum by the reaction force of the coil spring 4 to be compressed, and the cam member 6 is strongly pressed by the lever principle. Press with pressure.

  Therefore, while transmitting the power of the internal combustion engine from the disk plates 7 and 8 to the boss 5, the torsional vibration between the disk plates 7 and 8 and the boss 5 is absorbed and damped.

  When the rotational fluctuation due to the torque fluctuation of the internal combustion engine further increases, the fluctuation torque transmitted from the disk plates 7 and 8 to the boss 5 is large, and the boss 5 rotates clockwise (R1 direction) with respect to the disk plates 7 and 8. ) Further relative rotation.

  When the torsional angle between the disk plates 7 and 8 and the boss 5 is, for example, the maximum + 90 ° as in the state shown in FIG. 10 from the state shown in FIG. 9, the cam surface 6a has the maximum curvature at the top 6b. The roller 19c of the member 16 is positioned, and the cam member 6 biases the coil spring 4 through the arm member 16 with a larger biasing force.

  For this reason, the reaction force of the coil spring 4 is further increased, and the power of the internal combustion engine is transmitted from the disk plates 7 and 8 to the boss 5 while absorbing the torsional vibration between the disk plates 7 and 8 and the boss 5 to be damped. To do.

  In this case, the curvature of the cam surface 6a becomes larger as the torsional angle between the disk plates 7 and 8 and the boss 5 increases from the initial position of the cam member 6, so that one end of the arm member 16 is increased. When the portion is pressed against the cam surface 6a of the cam member 6 whose curvature gradually increases via the roller 19c, the other end of the arm member 16 moves inward in the radial direction of the disk plates 7 and 8.

  Also in this case, the other end of the arm member 16 moves along the circumferential outer peripheral surface of the spring seat 15 via the roller 21c so as not to prevent the spring seat 15 from moving in the circumferential direction. Can be.

  Further, when an excessive torque is input to the disk plates 7 and 8 from the internal combustion engine, the roller 19c of the arm member 16 gets over the top 6b where the curvature of the cam surface 6a is the largest, and the disk plates 7 and 8 are moved to the cam member 6. Therefore, the cam member 6 can function as a torque limiter when the vehicle is accelerated.

  As a result, it is possible to protect the transmission gear set of the transmission by preventing an excessive torque from being transmitted from the disk plates 7 and 8 to the boss 5.

  Further, since the hysteresis mechanism 22 is interposed between the disk plates 7 and 8 and the cam member 6, a constant hysteresis torque is generated when the disk plates 7 and 8 and the cam member 6 rotate relative to each other. Can do.

  On the other hand, when the vehicle is decelerated, the driving torque of the internal combustion engine is reduced and engine braking occurs, so that rotational torque is input to the boss 5 from the input shaft 26 of the transmission. When the rotational fluctuation due to the torque fluctuation of the internal combustion engine is small during deceleration, the fluctuation torque between the boss 5 and the disk plates 7 and 8 is small, so the boss 5 is relatively negative with respect to the disk plates 7 and 8. It will be twisted (R2 direction).

  At this time, when the disk plates 7 and 8 and the boss 5 rotate relative to each other as in the state shown in FIG. 11 from the state shown in FIG. 3, the twist angle between the disk plates 7 and 8 and the boss 5 increases. As the cam member 6 rotates, the roller 19c of the arm member 16 rolls along the cam surface 6a. For this reason, the one end part of the arm member 16 slides on the cam surface 6a via the roller 19c.

  Since the curvature of the cam surface 6a increases as the torsional angle between the disk plates 7 and 8 and the boss 5 increases from the initial position of the cam member 6, one end of the arm member 16 passes through the roller 19c. When the cam surface 6a of the cam member 6 having a gradually increasing curvature is pressed, the other end of the arm member 16 moves radially inward and circumferentially of the disk plates 7 and 8.

  As the cam member 6 rotates in the counterclockwise direction (R2 direction), the other end of the arm member 16 moves inward in the radial direction of the disk plates 7 and 8, thereby causing the spring seat 15 to move. Close to the base 14.

  Further, the other end portion of the arm member 16 moves along the circumferential outer peripheral surface of the spring seat 15 via the roller 21c so as not to hinder the spring seat 15 from moving in the circumferential direction. Can do. FIG. 11 shows a state where the twist angle between the disk plates 7 and 8 and the boss 5 is + 45 °.

  As the arm member 16 biases the coil spring 4 in this way, the arm member 16 uses the swinging shaft 9 as a fulcrum by the reaction force of the coil spring 4 to be compressed, and the cam member 6 is strongly pressed by the lever principle. Press with pressure.

  Therefore, while transmitting the power of the drive transmission system from the boss 5 to the disk plates 7 and 8, the torsional vibration between the disk plates 7 and 8 and the boss 5 is absorbed and damped.

  Further, when the boss 5 is further twisted to the negative side (R2 direction) relative to the disk plates 7 and 8, and the twist angle between the disk plates 7 and 8 and the boss 5 becomes, for example, the maximum + 90 °, the cam surface Since the roller 19c of the arm member 16 is positioned on the top 6b having the maximum curvature of 6a and the cam member 6 biases the coil spring 4 with a larger biasing force via the arm member 16, the reaction force of the coil spring 4 Becomes larger and absorbs and attenuates the torsional vibration between the disk plates 7 and 8 and the boss 5 while transmitting the power of the drive transmission system from the boss to the disk plates 7 and 8.

Further, when excessive torque is input from the internal combustion engine to the boss 5 from the disk plates 7 and 8, the roller 19c of the arm member 16 gets over the top 6b where the curvature of the cam surface 6a is the largest and the cam member 6 is moved to the disk plate. 7 and 8, the cam member 6 can function as a torque limiter.
As a result, it is possible to prevent transmission of excessive torque from the disk plates 7 and 8 to the boss 5 when the vehicle is decelerated, thereby protecting the transmission gear set of the transmission.

  Even when the vehicle is decelerating, a constant hysteresis torque can be generated when the disk plates 7 and 8 and the cam member 6 rotate relative to each other.

  As described above, in this embodiment, the torsional vibration damping device 1 includes the boss 5, the cam member 6 having the elliptical cam surface 6 a that is provided on the outer peripheral portion of the boss 5 and rotates integrally with the boss 5, and the cam member. 6 and the coil spring 4, one end of which contacts the cam surface 6a and the other end contacts the spring seat 15 of the coil spring 4, and the swing shaft 9 is bridged by the disk plates 7 and 8. And a roller member 19 provided between the cam member 6 and the cam surface 6a of the cam member 6 at one end of the arm member 16.

  For this reason, the torsional rigidity of the torsional vibration damping device 1 can be reduced as a whole by widening the range of the torsional angle between the disk plates 7 and 8 and the boss 5, and the torsional characteristics can be made nonlinear. The rotational torque can be smoothly transmitted from the disk plates 7 and 8 to the boss 5.

  FIG. 12 is a diagram showing the torsional characteristics of the disc plates 7 and 8 and the boss 5. The torsion angle between the disc plates 7 and 8 and the boss 5 and the output torque output from the boss 5 in the present embodiment. It is a graph explaining a relationship.

  The horizontal axis represents the relative twist angle of the boss 5 with respect to the disk plates 7 and 8, and the vertical axis represents the output torque output from the boss 5. The output torque on the vertical axis corresponds to the reaction force of the boss 5 against the disk plates 7 and 8.

  As shown in FIG. 12, in this embodiment, the coil spring 4 contracts as the torsion angle of the boss 5 with respect to the disk plates 7 and 8 increases, so that the pressing force to the cam member 6 by the arm member 16 increases. .

  And the output torque becomes large because the pressing force to the cam member 6 by the arm member 16 becomes large. The change in the output torque at this time becomes a curved torsional characteristic that continuously changes without having a step portion.

  In the present embodiment, one end of the arm member 16 is brought into contact with the elliptical cam surface 6a via the roller member 19, so that the disc plates 7 and 8 and the boss 5 are twisted as the cam member 6 rotates. The angle can be widened to 180 ° in total on the positive side and the negative side.

  Note that the torsional characteristics and the torsional angle when the disk plates 7 and 8 and the boss 5 are rotated relative to each other are the shape of the cam surface 6a of the cam member 6, the spring constant of the coil spring 4, the shape of the arm member 16, etc. By adjusting, it is possible to set an arbitrary twist characteristic and twist angle.

  As shown in FIG. 12, the torsional vibration damping device 1 of the present embodiment is a flat torsion with low torsional rigidity between the disk plates 7 and 8 and the boss 5 when the torsion angle between the disk plates 7 and 8 and the boss 5 is small. Can be characteristic.

  Therefore, in a region where the rotational torque (output torque of the boss 5) transmitted from the disc plates 7 and 8 to the boss 5 is small, such as when the shift position is changed to neutral and the internal combustion engine is in an idle state, the internal combustion engine Torsional vibration caused by rotational fluctuation caused by engine torque fluctuation can be attenuated, and the rattling noise can be suppressed from the gear pair of the transmission in an unloaded state.

  On the other hand, as shown in FIG. 13, the torsional resonance point of the drive transmission system provided with the transmission exists so as to occur in the steady rotation (for example, around 2000 rpm) of the internal combustion engine. Sometimes, torsional resonance of the drive transmission system occurs when passing through 2000 rpm.

  In the present embodiment, the range of torsion angles between the disk plates 7 and 8 and the boss 5 can be widened to reduce the overall torsional rigidity, so that the rotation transmitted from the disk plates 7 and 8 to the boss 5 can be reduced. In an operating state with a large torque, it is possible to attenuate torsional vibrations caused by rotational fluctuations caused by torque fluctuations of the drive source, and to suppress the jagged noise generated when the idle gear pair of the transmission gear set collides.

  Further, when the torsion angle between the disk plates 7 and 8 and the boss 5 is large, the torsional rigidity is set to be lower than the conventional torsional rigidity (the torsional characteristics of the conventional torsional vibration damping device are indicated by broken lines in FIG. 13). Therefore, the torsional vibration due to the torsional resonance of the drive transmission system can be attenuated to a greater extent than before, and the generation of a muffled noise in the vehicle interior can be suppressed.

  In addition, in the present embodiment, since the hysteresis mechanism 22 is interposed between the disk plates 7 and 8 and the cam member 6, when the disk plates 7 and 8 and the cam member 6 rotate relative to each other, a constant value is obtained. Hysteresis torque can be generated.

  For this reason, during acceleration / deceleration with a large rotational torque transmitted from the disk plates 7 and 8 to the boss 5, a hysteresis torque is generated against a large torsional vibration caused by a rotational fluctuation caused by a torque fluctuation of the drive source. be able to.

  Therefore, it is possible to further attenuate the torsional vibration due to the torsional resonance of the drive transmission system and further suppress the generation of a muffled sound in the vehicle interior, and it is possible to further suppress the generation of the jagged sound.

  Further, when an excessive torque is input to the disk plates 7 and 8 from the internal combustion engine, the roller 19c of the arm member 16 gets over the top 6b where the curvature of the cam surface 6a is the largest, and the disk plates 7 and 8 are moved to the cam member 6. Therefore, the cam member 6 can function as a torque limiter.

  As a result, it is possible to protect the transmission gear set of the transmission by preventing an excessive torque from being transmitted from the disk plates 7 and 8 to the boss 5.

  In the present embodiment, the curvature of the cam surface 6a increases as the torsion angle between the boss 5 and the disk plates 7 and 8 increases, and the amount of elastic deformation of the coil spring 4 increases. For this reason, if the roller member 19 does not exist at one end of the arm member 16, the contact pressure between the one end of the arm member 16 and the cam member 6 increases, and the contact surface between the arm member 16 and the cam member 6 wears. There is a fear.

  In the present embodiment, since one end portion of the arm member 16 slides on the cam surface 6a of the cam member 6 via the roller 19c, the contact pressure between the one end portion of the arm member 16 and the cam member 6 is increased. This can prevent the wear of the one end portion of the arm member 16 and the cam member 6.

  In this embodiment, the roller 21c is rotatably provided at the other end of the arm member 16, and the other end of the arm member 16 is in contact with the spring seat 15 via the roller 21c. The coil spring 4 can be elastically deformed in the circumferential direction of the disk plates 7 and 8 while smoothly sliding the other end of 16 along the circumferential outer peripheral surface of the spring seat 15 via the roller member 21. it can.

  In the present embodiment, the twist angle of the disk plates 7 and 8 and the boss 5 is simply configured by simply providing the coil spring 4, the arm member 16 and the cam member 6 between the disk plates 7 and 8 and the boss 5. Can be widened, and the configuration of the torsional vibration damping device 1 can be simplified.

  In the present embodiment, the arm member 16 is arranged point-symmetrically with respect to the central axis of the disk plates 7 and 8, so that the arm member 16 sandwiches the central axis of the disk plates 7 and 8 and the cam member 6. Can be pinched.

  For this reason, when the cam member 6 biases the coil spring 4 via the arm member 16, the arm member 16 strengthens the cam member 6 across the central axes of the disk plates 7 and 8 by the reaction force of the coil spring 4. It can be held by pressing force. For this reason, it is possible to reliably transmit the rotational torque from the disk plates 7 and 8 to the boss 5.

  On the other hand, since the arm member 16 is provided on the disc plates 7 and 8 so as to swing around the swing shaft 9, the arm member 16 is pressed against the cam surface 6 a of the cam member 6 by the compression of the coil spring 4. When this occurs, a rotational moment is generated in the axial direction of the arm member 16 around the rocking shaft 9 due to slippage between the roller 19c and the cam surface 6a.

  In the present embodiment, overlapping portions 16a and 16b are provided on the protruding pieces 16A and 16B of the arm member 16, and the overlapping portions 16a and 16b and the cam member 6 are overlapped in the radial direction of the disk plates 7 and 8. Yes.

  Further, overlap portions 16c and 16d are provided on the projecting pieces 16C and 16D of the arm member 16, and the overlap portions 16c and 16d and the spring seat 15 are overlapped in the radial direction of the disk plates 7 and 8.

  For this reason, when a rotational moment is generated in one axial direction of the arm member 16 around the swing shaft 9, the overlap portion 16 a at one end of the arm member 16 can be brought into contact with the cam member 6. At the same time (see FIG. 14), the overlap portion 16d at the other end of the arm member 16 can be brought into contact with the spring seat 15 (see FIG. 15).

  In addition, when a rotational moment is generated in the other axial direction of the arm member 16 around the swing shaft 9, the overlap portion 16b at one end of the arm member 16 can be brought into contact with the cam member ( 16), the overlap portion 16c at the other end of the arm member 16 can be brought into contact with the spring seat 15 (see FIG. 17).

  For this reason, it is possible to prevent the arm member 16 from being tilted in one or the other direction in the axial direction of the swing shaft 9. As a result, it is possible to prevent an excessive load from being applied to the swing shaft 9 and the portion of the arm member 16 supported by the swing shaft 9, and the durability of the swing shaft 9 and the arm member 16 deteriorates. Can be prevented.

  For this reason, it is unnecessary to reinforce the swing shaft 9 and the arm member 16, and it is possible to prevent the swing shaft 9 and the arm member 16 from increasing in size. Therefore, the torsional vibration damping device 1 can be reduced in size.

  In the present embodiment, bifurcated protruding pieces 16A and 16B are formed at one end of the arm member 16, and a roller member 19 is rotatably provided between the protruding pieces 16A and 16B. A bifurcated projecting piece 16C, 16D is formed at one end of 16 and a roller member 21 is rotatably provided between the projecting pieces 16C, 16D.

  Instead, the arm member 16 is composed of a pair of plates, one end portions of the pair of plates are connected by pins 18, and the roller member 19 is rotatably provided between the one end portions of the plates via the pins 18. The other end of the pair of plates may be connected by a pin 20 and the roller member 21 may be rotatably provided between the other end of the plate via the pin 20.

  In this case, one end and the other end of the plate may be overlapped with the cam member 6 and the spring seat 15 in the radial direction of the disk plates 7 and 8.

  Further, in the present embodiment, the torsional vibration damping device 1 is interposed between the internal combustion engine of the vehicle and the drive transmission system having the transmission. Any torsional vibration damping device may be used.

  For example, in a hybrid vehicle, the present invention is applied to a torsional vibration damping device such as a hybrid damper interposed between an output shaft of an internal combustion engine and a power split mechanism that splits power into an electric motor and a wheel side output shaft. May be.

  Further, the present invention may be applied to a torsional vibration damping device such as a lockup damper interposed between a lockup clutch device of a torque converter and a transmission gear set. Further, a torsional vibration damping device may be provided between the differential case and a ring gear provided on the outer periphery of the differential case.

  In the present embodiment, the cam surface 6a of the cam member 6 has an elliptical shape. However, the cam surface may be a cam surface whose curvature changes as the twist angle between the disk plates 7 and 8 and the boss 5 changes. For example, the shape is not limited to an elliptical shape.

  As described above, in the torsional vibration damping device according to the present invention, the torque transmission member is prevented from being inclined, and an excessive load is applied to the swing fulcrum portion or the portion of the torque transmission member supported by the swing fulcrum portion. Between the internal combustion engine of the vehicle and the drive transmission system, and the durability of the swing fulcrum and the torque transmission member can be prevented from deteriorating. Torsion in which the first rotating member and the second rotating member are connected to each other via an elastic member so as to be rotatable relative to each other so that rotational torque is transmitted between the first rotating member and the second rotating member. It is useful as a vibration damping device.

DESCRIPTION OF SYMBOLS 1 Torsional vibration damping device 2 1st rotation member 3 2nd rotation member 4 Coil spring (elastic member)
5 Boss 6 Cam member 6a Cam surface 7, 8 Disc plate 9 Oscillating shaft (oscillating fulcrum)
14 pedestal (support)
15 Spring seat (support member)
16 Arm member (torque transmission member)
16A, 16B, 16C, 16D Protruding piece (plate-like part)
18, 20 pins (shaft member)
19 Roller member (rolling element)
21 Roller member (rolling member)
22 Hysteresis mechanism

Claims (8)

A first rotating member;
A second rotating member provided on the same axis as the first rotating member and rotatable relative to the first rotating member;
The first rotating member is provided between the first rotating member and the second rotating member, and elastically deforms when the first rotating member and the second rotating member rotate relative to each other, whereby the first An elastic member for transmitting rotational torque between the rotating member and the second rotating member;
A cam surface is provided on the first rotating member so as to rotate integrally with the first rotating member, and the curvature of the cam surface changes with a change in torsion angle of the first rotating member and the second rotating member. A cam member having
When one end contacts the cam surface of the cam member and the other end contacts one end in the extending direction of the elastic member, and the first rotating member and the second rotating member rotate relative to each other. Further, the elastic member is elastically deformed by oscillating around an oscillating fulcrum provided on the second rotating member, so that the elastic member is elastically deformed between the first rotating member and the second rotating member. A torque transmission member for transmitting rotational torque;
A rolling element provided rotatably at one end of the torque transmission member and in contact with the cam surface of the cam member, the one end of the torque transmission member and the cam member being connected to the first rotation member and A torsional vibration damping device, wherein the second rotating member is overlapped in the radial direction.   A support member that is provided at one end of the elastic member in the extending direction and supports the elastic member; and a rolling member that is rotatably provided at the other end of the torque transmission member and contacts the support member. The torsional vibration damping according to claim 1, wherein the other end portion of the torque transmitting member and the support member are overlapped in the radial direction of the first rotating member and the second rotating member. apparatus.   At least one end portion of the torque transmission member is composed of a pair of plate-like portions connected via a shaft member that rotatably supports the rolling element, and the pair of plate-like portions push the cam member in the axial direction. The torsional vibration damping device according to claim 1 or 2, wherein the torsional vibration damping device is overlapped with the cam member so as to sandwich the cam member.   At least the other end portion of the torque transmission member is constituted by a pair of plate-like portions connected via a shaft member that rotatably supports the rolling member, and the pair of plate-like portions serves as an axis of the support member. The torsional vibration damping device according to claim 2, wherein the torsional vibration damping device is overlapped with the support member so as to be sandwiched in a direction.   The curvature of the cam surface of the cam member increases as the torsion angle increases from the initial position of the cam member when the torsion angle of the first rotating member and the second rotating member is minimum. The torsional vibration damping device according to any one of claims 1 to 5.   The said torque transmission member is arrange | positioned point-symmetrically with respect to the central axis of a said 1st rotation member and a said 2nd rotation member, The claim of any one of Claim 1 thru | or 5 characterized by the above-mentioned. The torsional vibration damping device described in 1. The first rotating member includes a boss having the cam member on an outer peripheral portion and an input shaft of a transmission connected to an inner peripheral portion;
The second rotating members are arranged on both sides in the axial direction of the cam member, are fixed to each other at a predetermined interval in the axial direction, and transmit the torque via a swing shaft constituting the swing fulcrum portion. A pair of disc plates that support the member in a swingable manner,
The torsional vibration damping device according to any one of claims 1 to 6, wherein the pair of disk plates is provided with a support portion that supports the other end in the extending direction of the elastic member. .   The hysteresis mechanism that frictionally contacts the first rotating member and the second rotating member is interposed between the first rotating member and the second rotating member. The torsional vibration damping device according to any one of claims 1 to 7.

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