JP2013174294A - Torsional vibration damping device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a torsional vibration damping device that can increase torsional rigidity without radially increasing the size of an elastic member.SOLUTION: A torsional vibration damping device 1 includes a cam member 2; a cam member 2 provided on an outer periphery of the cam member 2 and having an elliptically-shaped cam surface 2a rotating integrally with the cam member 2; and an arm member 16 that is provided between the cam member 2 and a torsion spring 4, of which one end 16a comes into contact with the cam surface 2a and the other end 16b of the arm member 16 abuts against the other end 4c of the torsion spring 4, and that turns around a rotary shaft 9 bridged between disk plates 7 and 8. One end 4b of the torsion spring 4 is attached to the disk plate 7 in a slidable manner, and the other end 4c of the torsion spring 4 is attached to the one end 16a of the arm member 16.

Description

  The present invention relates to a torsional vibration damping device, and more particularly to a rotating member interposed between an internal combustion engine of a vehicle and a transmission of a drive transmission system so that torque is transmitted between the rotating member and the cam member. The present invention relates to a torsional vibration damping device in which a cam member and a cam member are connected so as to be rotatable relative to each other.

  Conventionally, a drive source such as an internal combustion engine or an electric motor is connected to a wheel or the like via a drive transmission system having a transmission or the like, and power is transmitted from the drive source to the wheel via the drive transmission system. However, in the drive transmission system connected to the drive source, for example, a jarr sound or a humming noise is generated by torsional vibration using a rotational fluctuation due to a torque fluctuation of the internal combustion engine as a vibration source.

A jagged noise is a jagged sound that is generated when a pair of idling gears of a transmission gear set that constitutes a transmission provided in a drive transmission system collides with a torsional vibration caused by a fluctuation in rotation caused by a torque fluctuation of an internal combustion engine. It is a sound.
Further, the muffled noise is 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 internal combustion engine as an excitation force. The torsional resonance of the drive transmission system is, for example, in a steady region. Exists.

  Conventionally, a drive source such as an internal combustion engine or an electric motor is connected to wheels and the like to transmit torque from the drive source and torsion that absorbs torsional vibration between the drive source and a drive transmission system having a transmission gear set. A vibration damping device is known (see, for example, Patent Document 1).

  This torsional vibration damping device has a cam surface on the outer peripheral portion, and is provided on the same axis as the cam member, and a cam member configured such that the curvature of the cam surface changes along the circumferential direction. A pair of disk plates that are rotatable relative to each other, and a coil spring that is provided between the cam member and the pair of disk plates and elastically deforms when the cam member and the pair of disk plates rotate relative to each other. Yes.

  The torsional vibration damping device also has a pair of discs when one end contacts the cam surface of the cam member and the other end is biased by a coil spring, and the cam member and the pair of disc plates rotate relative to each other. An arm member that transmits torque between the cam member and the pair of disk plates is provided by rotating about a rotation fulcrum provided on the plate and elastically deforming the coil spring.

In the torsional vibration damping device having such a configuration, the cam member and the pair of discs are formed by elastically deforming the coil spring by rotating the arm member around the rotation axis as the cam member rotates. The range of the twist angle with the plate can be widened.
For this reason, the torsional rigidity between the cam member and the pair of disk plates can be lowered as a whole, and the dampening noise and the booming noise can be sufficiently attenuated to improve the vibration damping performance.

International Publication No. 2011-067815

  However, in the conventional torsional vibration damping device, the arm member is configured to rotate about the rotation shaft provided on the disk plate to elastically deform the coil spring, so that it is paired with the cam member. When the disk plate rotates relatively, the other end of the arm member receives a reaction force in the circumferential direction from the coil spring while being displaced in the radial direction of the disk plate.

  For this reason, the arm member cannot greatly deform the coil spring in the circumferential direction by the amount that the other end of the arm member is displaced in the radial direction. For this reason, the arm member cannot receive a large reaction force in the circumferential direction from the coil spring, and it is difficult for the torsional vibration damping device to generate a large torsional rigidity, and there is still room for improvement.

  In order to increase the rigidity of the coil spring and increase the torsional rigidity of the torsional vibration damping device, it is conceivable to increase the coil spring in the radial direction. However, when the coil spring is enlarged in the radial direction, the disk plate is enlarged in the radial direction because the coil spring that is large in the radial direction is attached to the pair of disk plates. Therefore, there arises a problem that the torsional vibration damping device is increased in size.

  The present invention has been made to solve the above-described conventional problems, and an object thereof is to provide a torsional vibration damping device capable of increasing torsional rigidity without increasing the elastic member in the radial direction. And

  In order to achieve the above object, a torsional vibration damping device according to the present invention includes (1) a cam member having a cam surface on an outer peripheral portion, and the curvature of the cam surface varies along a circumferential direction, and the cam member And a rotating member that is rotatable relative to the cam member, and is provided between the cam member and the rotating member, and the cam member and the rotating member are rotated relative to each other. The elastic member that is elastically deformed, the one end portion of which is in contact with the cam surface of the cam member, and the other end portion is urged by the elastic member, and the rotation when the cam member and the rotating member rotate relative to each other. Torsional vibration damping provided with an arm member that transmits torque between the cam member and the rotating member by elastically deforming the elastic member by rotating around a rotation fulcrum provided on the member An apparatus comprising the elastic member One end of slidably mounted to said rotary member, and a what the other end is composed of a torsion spring mounted slidably to the other end of the arm member.

In this torsional vibration damping device, an arm member is rotatably provided at a rotation fulcrum portion of a rotating member, one end portion of the arm member contacts the cam surface of the cam member, and the other end portion is urged by an elastic member. Since the elastic member is elastically deformed when the rotation member and the cam member rotate relative to each other, the cam member presses the elastic member via the arm member as the cam member rotates, so that the elastic member is transferred from the elastic member to the arm member. By changing the reaction force, it is possible to widen the range of the torsion angle between the rotating member and the cam member, and to transmit the torque between the rotating member and the cam member.
For this reason, the torsional rigidity between the rotating member and the cam member can be reduced as a whole, and the torsional vibration can be attenuated.

  The elastic member is composed of a torsion spring having one end slidably attached to the rotating member and the other end slidably attached to the other end of the arm member. The other end of the torsion spring is elastically deformed in the radial direction of the rotating member following the displacement of the portion in the radial direction of the rotating member. At this time, when the torsion spring is twisted around the central axis of the torsion spring, the reaction force applied from the torsion spring to the other end of the arm member can be increased.

  Further, since the torsion spring has a configuration in which a linear body is wound, the torsion spring is not enlarged in the radial direction of the rotating member, and the torsional vibration damping device can be prevented from being enlarged. .

  In the torsional vibration damping device according to (1), (2) the other end portion of the arm member is formed with a holding portion that slidably holds the other end portion of the torsion spring.

  In this torsional vibration damping device, since the holding portion that slidably holds the other end of the torsion spring is formed at the other end of the arm member, the other end of the arm member is displaced in the radial direction of the rotating member. Sometimes, the other end portion of the torsion spring slides with respect to the other end portion of the arm member, thereby preventing the torsion spring from being deformed abnormally. For this reason, a reaction force corresponding to the elastic deformation of the torsion spring can be applied to the other end of the arm member. As a result, the torsional characteristics desired by the torsional vibration damping device can be obtained.

  In the torsional vibration damping device according to (1) and (2) above, (3) one end portion of the torsion spring is attached to the other end portion of the torsion spring inward in the radial direction of the rotating member. Has been.

  In this torsional vibration damping device, one end of the torsion spring is attached radially inward of the rotating member to the other end of the torsion spring, so that the other end of the arm member is radially inward of the rotating member. When displaced, the other end of the torsion spring is displaced inward in the radial direction of the rotating member, and the one end and the other end of the torsion spring are close to each other in the radial direction of the rotating member.

  For this reason, when the torsion spring is twisted around the central axis of the torsion spring, a reaction force can be reliably applied from the torsion spring to the other end of the arm member.

  In the torsional vibration damping device according to any one of (1) to (3), (4) the torsion spring extends from one of the winding portion around which the linear body is wound, and the rotating member. The one end portion slidably attached to the other end of the arm member and the other end portion slidably attached to the other end of the arm member. The portion is configured to be supported on the outer peripheral portion of a support shaft provided on the rotating member.

  In this torsional vibration damping device, the winding portion of the torsion spring is supported on the outer peripheral portion of the support shaft provided on the rotating member, and one end portion of the torsion spring is slidably attached to the rotating member. It can be positioned on the member and stably held on the rotating member.

  (1) In the torsional vibration damping device according to (1) to (4), (5) a boss to which an input shaft of a transmission of a drive transmission system is connected is provided on an inner peripheral portion of the cam member, and the rotating member is The cam members are arranged on both sides in the axial direction and are fixed to each other at a predetermined interval in the axial direction, and the arm member is rotatably supported via the rotation fulcrum, so that power is transmitted from the internal combustion engine. A pair of disc plates, and one end of the torsion spring is slidably attached to one of the pair of disc plates.

  In this torsional vibration damping device, one end of the arm member is in contact with the cam surface of the cam member, and the other end of the torsion spring is slidably attached to the other end of the arm member. By relatively rotating the two, the range of the torsion angle between the pair of disk plates and the cam member can be widened, and the rigidity of the torsion spring can be reduced.

  For this reason, in a region where the twist angle between the pair of disk plates and the cam member is small, such as when the shift position is changed to neutral and the internal combustion engine is in an idle state, the low-rigid elastic member makes the minute It is possible to suppress the generation of a rattling sound from the transmission gear set constituting the transmission by attenuating the vibration.

  Further, in a region where the torsion angle between the pair of disk plates and the cam member is large, it is possible to obtain a highly rigid torsion characteristic that increases the torsion angle between the pair of disk plates and the cam member and increases the torque increase rate. .

  Therefore, a large torsional vibration caused by a rotational fluctuation caused by a torque fluctuation of the internal combustion engine and a torsional resonance of the drive transmission system are attenuated, and a jagged wheel generated by a collision of the idle gear pair of the transmission gear set constituting the transmission collides. It is possible to suppress the generation of a booming noise due to sound or torsional resonance of the drive transmission system.

  According to the present invention, it is possible to provide a torsional vibration damping device capable of increasing torsional rigidity without increasing the elastic member in the radial direction.

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. 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 the torsional vibration damping device of the state which removed one of the disk plates. 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 front view of the torsional vibration damping device when the torsion angle of a disk plate and a cam member is +30 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 cam member is +60 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 cam member 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 cam member 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.

Hereinafter, embodiments of a torsional vibration damping device according to the present invention will be described with reference to the drawings.
1 to 4, the torsional vibration damping device 1 includes a cam member 2 and a rotating member 3 provided on the same axis as the cam member 2.

  Torque from an internal combustion engine (not shown), which is a driving source, is input to the rotating member 3, and the cam member 2 transmits the torque of the rotating member 3 to a transmission of a drive transmission system (not shown). It has become.

  A pair of torsion springs 4 as elastic members are provided between the cam member 2 and the rotation member 3, and the torsion springs 4 are elastically deformed when the cam member 2 and the rotation member 3 rotate relative to each other. It has become.

  A boss 5 that is spline-fitted to the outer peripheral portion of the input shaft 6 (see FIG. 4) of the drive transmission transmission is attached to the inner peripheral portion of the cam member 2. It is configured to include.

  The boss 5 and the cam member 2 may be integrally formed. Further, the boss 5 and the cam member 2 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 2, and the boss 5 and the cam member 2 are spline-fitted. Also good.

  The 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 2 in the axial direction, and are connected by a rotation shaft 9 as a rotation fulcrum at a predetermined interval in the axial direction.

  The rotating 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 disc plates 7 and 8 are integrally rotated by being integrated by the rotation 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 torque of the internal combustion engine is input to the disk plates 7 and 8.

  Further, 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. 8 is not entered.

  The torsion spring 4 is slidably attached to a winding portion 4a around which the linear body is wound, and a fitting hole 7b (see FIG. 4) extending from one of the winding portions 4a. One end portion 4b and another end portion 4c extending from the other end of the winding portion 4a and slidably attached to the other end portion 16b of the arm member 16 are provided. Instead of the disk plate 7, a fitting hole may be formed in the disk plate 8, and the one end 4 a of the torsion spring 4 may be slidably attached to the fitting hole of the disk plate 8.

  The disk plates 7 and 8 are connected by a support shaft 17, and the winding portion 4 a of the torsion spring 4 is supported on the outer peripheral portion of the support shaft 17.

Further, an arm member 16 is provided between the torsion spring 4 and the cam member 2, and this arm member 16 is located between the disk plates 7 and 8 and is rotatably supported on the rotation shaft 9. Has been.
The other end portion 16b of the arm member 16 is formed with a notch 16c as a holding portion, and the other end portion 4c of the torsion spring 4 is slidably fitted into the notch 16c.

  Also, as shown in FIG. 3, one end 4b of the torsion spring 4 is attached radially inward of the disk plates 7 and 8 with respect to the other end 4c, and when the torsion spring 4 is elastically deformed, The one end 4b is displaced so as to approach and separate from the other end 4c in the radial direction of the disk plates 7 and 8.

  As shown in FIGS. 5 and 6, a needle bearing 18 is interposed between the rotating shaft 9 and the arm member 16. The needle bearing 18 includes an outer race 18 a attached to the arm member 16, and a needle needle 18 b interposed between the outer race 18 a and the rotation shaft 9.

  In the needle bearing 18, the outer race 18a is slidable with respect to the rotary shaft 9 via the needle needle 18b. Therefore, the arm member 16 slides on the rotary shaft 9 via the needle bearing 18. It is mounted movably.

  One end portion 16 a of the arm member 16 is formed with protruding pieces 16 A and 16 B as bifurcated plate-like portions, and the protruding pieces 16 A and 16 B are connected by a pin 19.

A roller member 20 as a rolling element is slidably attached to the pin 19. The roller member 20 includes an outer race 20a provided on the outer peripheral portion of the pin 19 and a needle bearing composed of a needle needle 20b interposed between the outer race 20a and the pin 19, and an outer race on the outer peripheral portion of the outer race 20a. The roller 20c is attached to the roller 20c. The roller 20c is slidable with respect to the pin 19 via a needle bearing.
The roller 20c rotates in contact with the cam surface 2a of the cam member 2, and one end 16a of the arm member 16 contacts the cam surface 2a of the cam member 2 via the roller 20c.

  Further, when the distance from the rotation center of the cam member 2 to the cam surface 2a with which the one end portion 16a of the arm member 16 contacts is an action radius r, the torsion angle between the disc plates 7 and 8 and the cam member 2 is the smallest. The curvature of the cam surface 2a is set so that the action radius r increases as the torsion angle between the disk plates 7 and 8 and the cam member 2 increases from the neutral position with respect to the action radius r at the neutral position.

  That is, the curvature of the cam member 2 is such that the torsion angle between the disc plates 7 and 8 and the cam member 2 from the neutral position where the torsion angle between the disc plates 7 and 8 and the cam member 2 is minimum (the torsion angle is approximately 0 °). It gets bigger as it gets bigger.

  For this reason, when the cam member 2 rotates and the position of the cam surface 2a where the one end 16a of the arm member 16 contacts is varied, the one end 4b and the other end 4c of the torsion spring 4 are close to each other in the radial direction. Elastically deformed so as to be separated.

  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 2a having the same curvature across the central axis of the disk plates 7 and 8. The one end 16a of the arm member 16 can be brought into contact with the arm member 16.

On the other hand, as shown in FIG. 4, a hysteresis mechanism 21 is interposed between the disk plates 7 and 8 and the cam member 2, and the hysteresis mechanism 21 is an annular friction material 22, 23, 24, 25. And a disc spring 26.
The friction members 22 and 23 are formed of an annular member having a predetermined friction coefficient on the surface, and are attached to both sides of the cam member 2 in the width direction.

  The friction members 24 and 25 are formed of annular members having surfaces having a predetermined friction coefficient, and are attached to the disk plates 7 and 8 so as to face the friction members 22 and 23 in the axial direction, respectively.

  The disc spring 26 is formed in a conical shape, and is interposed between the friction material 25 and the disk plate 8. The disc spring 26 generates an elastic force in the axial direction of the cam member 2, thereby bringing the friction material 22 and the friction material 24 into frictional contact with each other, and bringing the friction material 23 and the friction material 25 into friction contact with each other. Hysteresis torque is generated between the cam member 2 and the disk plates 7 and 8.

Next, the operation will be described.
7 to 10 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 due to the 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.

  7 to 10 show a state where the disk plate 8 is removed. The cam member 2 is twisted to the positive side with respect to the disk plates 7 and 8 when the vehicle is accelerating, and the cam member 2 is twisted to the negative side when the vehicle is decelerating.

  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 torque of the internal combustion engine is input to the disk plates 7 and 8.

  If the rotational fluctuation due to the torque fluctuation of the internal combustion engine is small at the time of acceleration of the vehicle, the fluctuation torque between the disk plates 7 and 8 and the cam member 2 is small, and the cam member 2 watches the disk plates 7 and 8 with respect to the clock. Relative rotation in the rotation direction (R1 direction).

  At this time, when the cam member 2 rotates in the R1 direction as the torsion angle between the disk plates 7 and 8 and the cam member 2 increases as in the state shown in FIG. 7 from the state shown in FIG. 20c rolls along the cam surface 2a. For this reason, the one end 16a of the arm member 16 slides on the cam surface 2a via the roller 20c. FIG. 7 shows a state where the twist angle is + 30 °.

  Since the curvature of the cam surface 2a increases as the torsional angle between the disk plates 7 and 8 and the cam member 2 increases from the neutral position of the cam member 2, one end portion 16a of the arm member 16 has a roller 20c. , The other end 16b of the arm member 16 moves inward in the radial direction of the disk plates 7 and 8 when the cam surface 2a of the cam member 2 gradually increases in curvature.

  When the twist angle between the disk plates 7 and 8 and the cam member 2 is small, the roller 20c of the arm member 16 is in contact with the cam surface 2a where the curvature of the cam member 2 is small. By pressing the end portion 16 b against the other end portion 4 c of the torsion spring 4, the torsion spring 4 is biased by the cam member 2.

  When the torsion spring 4 is biased by the cam member 2, the other end portion 16b of the arm member 16 is displaced in the radial direction, and the other end portion 4c of the torsion spring 4 follows the displacement in the radial direction of the other end portion 16b. Is elastically deformed in the radial direction, and the other end 4c of the torsion spring 4 approaches the one end 4b in the radial direction.

  For this reason, when the winding portion 4 a of the torsion spring 4 is twisted around the central axis of the torsion spring 4, a reaction force is applied from the torsion spring 4 to the other end portion 16 b of the arm member 16. As a result, the arm member 16 presses the cam member 2 based on the lever principle with the rotation shaft 9 as a fulcrum.

  Therefore, the torque of the disk plates 7 and 8 is transmitted to the cam member 2 via the torsion spring 4 and the arm member 16, and the torque of the internal combustion engine is transmitted to the input shaft 6 of the transmission. As a result, while transmitting the power of the internal combustion engine from the disk plates 7 and 8 to the cam member 2, the torsional vibration between the disk plates 7 and 8 and the cam member 2 is absorbed and attenuated.

  When the rotation 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 cam member 2 is large, and the cam member 2 rotates in the clockwise direction with respect to the disk plates 7 and 8 ( Further relative rotation in the R1 direction).

  When the twist angle between the disk plates 7 and 8 and the cam member 2 is further increased from the state shown in FIG. 7, the roller 20c of the arm member 16 rolls along the cam surface 2a as shown in FIG. One end 16a of 16 slides on the cam surface 2a via the roller 20c.

  Since the curvature of the cam surface 2a increases as the torsional angle between the disk plates 7 and 8 and the cam member 2 increases from the neutral position of the cam member 2, one end portion 16a of the arm member 16 has a roller 20c. Is pressed against the cam surface 2a of the cam member 2 whose curvature increases, the other end portion 16b of the arm member 16 moves inward in the radial direction of the disk plates 7 and 8, and the other end portion of the torsion spring 4 Further activate 4c.

  When the torsion spring 4 is further urged by the cam member 2, the other end 16b of the arm member 16 is further displaced in the radial direction, and the other end of the torsion spring 4 follows the displacement in the radial direction of the other end 16b. The portion 4c is further elastically deformed in the radial direction, and the other end portion 4c of the torsion spring 4 is further closer to the one end portion 4b in the radial direction. FIG. 8 shows a state where the twist angle is + 60 °.

  For this reason, when the winding portion 4 a of the torsion spring 4 is further twisted around the central axis of the torsion spring 4, a reaction force is applied from the torsion spring 4 to the other end portion 16 b of the arm member 16. The arm member 16 presses the cam member 2 by the lever principle with the pivot shaft 9 as a fulcrum by force.

  Therefore, the torque of the disk plates 7 and 8 is transmitted to the cam member 2 via the torsion spring 4 and the arm member 16, and the torque of the internal combustion engine is transmitted to the input shaft 6 of the transmission. As a result, while transmitting the power of the internal combustion engine from the disk plates 7 and 8 to the cam member 2, the torsional vibration between the disk plates 7 and 8 and the cam member 2 is absorbed and attenuated.

  As shown in FIG. 9, when an excessive torque is input to the disk plates 7 and 8 from the internal combustion engine, the other end portion 16b of the arm member 16 gets over the top portion 2b having the maximum curvature of the cam surface 2a. Since the disk plates 7 and 8 can be idled with respect to the cam member 2, the cam member 2 can function as a torque limiter when the vehicle is accelerated.

  In the present embodiment, as shown in FIG. 9, when one end 16a of the arm member 16 rides on the top 2b of the cam surface 2a, the twist angle between the disk plates 7 and 8 and the cam member 2 is + 90 ° which is the maximum. become.

  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 torque is input to the cam member 2 from the input shaft 6 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 disk plates 7 and 8 and the cam member 2 is small, so that the cam member 2 is relatively relative to the disk plates 7 and 8. It will be twisted to the negative side (R2 direction).

At this time, when the disk plates 7 and 8 and the cam member 2 are rotated relative to each other as shown in FIG. 10 from the state shown in FIG. 3, the torsion angle between the disk plates 7 and 8 and the cam member 2 is large. As the cam member 2 rotates, the roller 20c of the arm member 16 rolls along the cam surface 2a.
For this reason, when the one end portion 16a of the arm member 16 is pressed against the cam surface 2a of the cam member 2 whose curvature gradually increases via the roller 20c, the other end portion 16b of the arm member 16 is brought into contact with the disk plates 7 and 8. Move radially inward.

Also in this case, as in acceleration, the cam member 2 presses the other end portion 16 b of the arm member 16 against the other end portion 4 c of the torsion spring 4, whereby the torsion spring 4 is urged by the cam member 2.
When the torsion spring 4 is biased by the cam member 2, the other end portion 16b of the arm member 16 is displaced in the radial direction, and the other end portion 4c of the torsion spring 4 follows the displacement in the radial direction of the other end portion 16b. Is elastically deformed in the radial direction, and the other end 4c of the torsion spring 4 approaches the one end 4b in the radial direction.

  For this reason, when the winding portion 4 a of the torsion spring 4 is twisted around the central axis of the torsion spring 4, a reaction force is applied from the torsion spring 4 to the other end portion 16 b of the arm member 16. As a result, the arm member 16 presses the cam member 2 based on the lever principle with the rotation shaft 9 as a fulcrum.

  Therefore, while transmitting the power of the drive transmission system from the cam member 2 to the disk plates 7 and 8, the torsional vibration between the disk plates 7 and 8 and the cam member 2 is absorbed and attenuated. FIG. 10 shows a state where the twist angle is −45 °.

  In addition, in the torsional vibration damping device 1 of the present embodiment, since the hysteresis mechanism 23 is interposed between the disk plates 7 and 8 and the cam member 2, the disk plates 7 and 8 are accelerated during vehicle acceleration / deceleration. When the cam member 2 and the cam member 2 rotate relative to each other, a certain hysteresis torque can be generated.

  Thus, in the torsional vibration damping device 1 of the present embodiment, the arm member 16 is rotatably provided on the rotating shaft 9 of the disk plates 7 and 8, and the one end portion 16 a of the arm member 16 is connected to the cam surface of the cam member 2. When the other end portion 16b is twisted, it is urged by a spring 4 so that the torsion spring 4 is elastically deformed when the disk plates 7 and 8 and the cam member 2 rotate relative to each other.

  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 cam member 2, and the vibration damping performance can be improved. .

  Since the elastic member is composed of the torsion spring 4 having one end 4b slidably attached to the disk plate 7 and the other end 4c slidably attached to the other end 16b of the arm member 16, The other end 4 c of the torsion spring 4 can be elastically deformed in the radial direction of the disk plates 7, 8 following the displacement of the one end 16 a of the arm member 16 in the radial direction of the disk plates 7, 8.

The torsion spring 4 has a winding portion 4a around which the linear body is wound, and one end portion that extends from one of the winding portions 4a and is slidably attached to the fitting hole 7b of the disk plate 7. 4b and the other end part 4c extended from the other side of the winding part 4a and attached to the notch 16c of the arm member 16 so as to be slidable.
For this reason, the torsion spring 4 is not increased in size in the radial direction of the disk plates 7 and 8, and the torsional vibration damping device 1 can be prevented from increasing in size.

  Further, when the other end portion 16 b of the arm member 16 is displaced in the radial direction of the disk plates 7, 8, the other end portion 4 c of the torsion spring 4 is moved with respect to the notch 16 c formed in the other end portion 16 b of the arm member 16. Therefore, the torsion spring 4 can be prevented from being deformed abnormally.

  Therefore, the reaction force corresponding to the elastic deformation of the torsion spring 4 can be applied to the other end portion 16b of the arm member 16, and the torsional characteristics desired by the torsional vibration damping device 1 can be obtained.

  In particular, in the torsional vibration damping device 1 of the present embodiment, the one end 4b of the torsion spring 4 is attached to the other end 4c inward in the radial direction of the disk plates 7 and 8. When the portion 16b is displaced inward in the radial direction of the disk plates 7 and 8, the other end 4c of the torsion spring 4 is displaced inward in the radial direction of the disk plates 7 and 8, and the radial direction of the disk plates 7 and 8 is reached. The one end 4b and the other end 4c of the torsion spring 4 can be brought close to each other.

  For this reason, when the torsion spring 4 is twisted around the central axis of the torsion spring 4, a reaction force can be reliably applied from the torsion spring 4 to the other end portion 16b of the arm member 16.

  FIG. 11 is a diagram showing the torsional characteristics of the disc plates 7 and 8 and the cam member 2. The torsion angle between the disc plates 7 and 8 and the cam member 2 in this embodiment and the output output from the cam member 2. It is a graph explaining the relationship with a torque.

  The horizontal axis represents the relative twist angle of the cam member 2 with respect to the disk plates 7 and 8, and the vertical axis represents the output torque output from the cam member 2. The output torque on the vertical axis corresponds to the reaction force of the cam member 2 on the disk plates 7 and 8.

  As shown in FIG. 11, in the present embodiment, the disc plates 7, 8 and cam from the neutral position with respect to the operating radius r at the neutral position when the twist angle between the disc plates 7, 8 and the cam member 2 is minimum. The curvature of the cam surface 2a is set so that the operating radius r increases as the twist angle with the member 2 increases.

  For this reason, the torsion spring 4 is elastically deformed as the torsion angle of the cam member 2 with respect to the disk plates 7 and 8 increases, and the pressing force of the arm member 16 to the cam member 2 increases.

  And the output torque becomes large because the pressing force to the cam member 2 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, the one end 16a of the arm member 16 is brought into contact with the elliptical cam surface 2a via the roller member 20, so that the disk plates 7, 8 and the cam member 2 Can be widened to 180 ° in total on the positive and negative sides.

  The torsional characteristics and the torsional angle when the disk plates 7 and 8 and the cam member 2 rotate relative to each other are the shape of the cam surface 2a of the cam member 2, the spring constant of the torsion spring 4, and the shape of the arm member 16. By adjusting the above, it is possible to set an arbitrary twist characteristic and twist angle.

  In the torsional vibration damping device 1 of the present embodiment, as shown in FIG. 11, when the torsional angle between the disk plates 7 and 8 and the cam member 2 is small, the torsional rigidity between the disk plates 7 and 8 and the cam member 2 is low. Can be characteristic.

Therefore, in a region where the torque transmitted from the disk plates 7 and 8 to the cam member 2 is small, such as when the shift position is changed to neutral and the internal combustion engine is in an idle state, the rotational fluctuation due to the torque fluctuation of the internal combustion engine. It is possible to attenuate torsional vibration using the vibration source as a vibration source and suppress the generation of a rattling sound from the transmission gear set of the transmission in an unloaded state.
Note that the rattling noise is a rattling noise generated when a gear pair in an unloaded state collides with a torsional vibration caused by a rotational fluctuation caused by a torque fluctuation of the internal combustion engine during idling when the speed is changed to neutral. .

  Further, since the torsional vibration damping device 1 of the present embodiment can widen the range of the torsion angle between the disk plates 7 and 8 and the cam member 2 to reduce the overall torsional rigidity, In an operating state in which the torque transmitted from the cam member 2 to the cam member 2 is large, the transmission gear set constituting the transmission of the drive transmission system is damped by torsional vibration caused by rotational fluctuation caused by torque fluctuation of the driving source. It is possible to suppress the jagged noise generated by the collision of the idle gear pair.

  Further, since the torsional rigidity can be reduced when the torsion angle between the disk plates 7 and 8 and the cam member 2 is large, the torsional vibration due to the torsional resonance of the drive transmission system is attenuated more than before, and the vehicle It is possible to suppress the occurrence of a booming sound in the room.

  In addition, in the present embodiment, since the hysteresis mechanism 21 is interposed between the disk plates 7 and 8 and the cam member 2, when the disk plates 7 and 8 and the cam member 2 rotate relative to each other, a constant value is obtained. Hysteresis torque can be generated.

  For this reason, during acceleration / deceleration with a large torque transmitted from the disk plates 7 and 8 to the cam member 2, 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, in the present embodiment, as the torsion angle between the cam member 2 and the disk plates 7 and 8 increases, the curvature of the cam surface 2a increases and the amount of elastic deformation of the torsion spring 4 increases. For this reason, if the roller member 20 does not exist at the one end 16 a of the arm member 16, the contact pressure between the one end 16 a of the arm member 16 and the cam member 2 increases.
In the torsional vibration damping device 1 of the present embodiment, the one end portion 16a of the arm member 16 slides on the cam surface 2a of the cam member 2 via the roller 20c. It is possible to prevent the contact pressure of the arm member 16 from increasing and to prevent wear of the one end portion 16a of the arm member 16 and the cam member 2.

  Further, the torsional vibration damping device 1 of the present embodiment supports the winding portion 4a of the torsion spring 4 on the outer peripheral portion of the support shaft 17 provided on the disk plates 7 and 8, and one end portion 4b of the torsion spring 4. Is slidably attached to the fitting hole 7b of the disk plate 7, so that the torsion spring 4 can be positioned on the disk plates 7 and 8 and stably held on 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 this embodiment, the cam surface 2a of the cam member 2 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, the torsional vibration damping device according to the present invention has the effect that the torsional rigidity can be increased without increasing the elastic member in the radial direction. Useful as a torsional vibration damping device or the like that is interposed between a rotating machine and a rotating member and a cam member that are relatively rotatably connected via an elastic member so that torque is transmitted between the rotating member and the cam member. It is.

DESCRIPTION OF SYMBOLS 1 Torsional vibration damping device 2 Cam member 2a Cam surface 3 Rotating member 4 Torsion spring (elastic member)
4a Winding part 4b One end part of torsion spring 4c Other end part of torsion spring 6 Input shaft 7, 8 Disc plate (rotating member)
9 Rotating shaft (Rotating fulcrum)
16 Arm member 16a One end portion of arm member 16b Other end portion of arm member 16c Notch (holding portion)
20 Roller member (rolling element)

Claims (5)

A cam member having a cam surface on an outer peripheral portion, and a curvature of the cam surface changing along a circumferential direction;
A rotating member provided on the same axis as the cam member, and rotatable relative to the cam member;
An elastic member provided between the cam member and the rotating member and elastically deformed when the cam member and the rotating member are relatively rotated;
One end of the cam member is in contact with the cam surface and the other end is urged by the elastic member, and the cam member and the rotating member are rotated relative to each other. A torsional vibration damping device comprising an arm member that rotates about a fulcrum and elastically deforms the elastic member to transmit torque between the cam member and the rotating member,
A torsion characterized in that the elastic member comprises a torsion spring having one end slidably attached to the rotating member and the other end slidably attached to the other end of the arm member. Vibration damping device.   The torsional vibration damping device according to claim 1, wherein a holding portion that slidably holds the other end of the torsion spring is formed at the other end of the arm member.   3. The torsional vibration damping device according to claim 1, wherein one end of the torsion spring is attached radially inward of the rotating member with respect to the other end of the torsion spring. 4. The torsion spring includes a winding portion around which a linear body is wound, the one end portion extending from one of the winding portions and slidably attached to the rotating member, and the winding portion. The other end extending from the other and slidably attached to the other end of the arm member,
The torsional vibration damping device according to claim 1, wherein the winding portion is supported by an outer peripheral portion of a support shaft provided in the rotating member. A boss to which an input shaft of a drive transmission transmission is connected is provided on the inner peripheral portion of the cam member,
The rotating members are disposed on both sides of the cam member in the axial direction and are fixed to each other at a predetermined interval in the axial direction, and the arm member is rotatably supported via the rotating fulcrum, It has a pair of disc plates that transmit power from the engine,
5. The torsional vibration damping device according to claim 1, wherein one end of the torsion spring is slidably attached to one of the pair of disk plates. 6.

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