JP2013190092A - Torsional vibration damping device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a torsional vibration damping device capable of changing torsional stiffness at a positive side and at a negative side while widening a torsion angle of a first rotating member and a second rotating member.SOLUTION: A torsional vibration damping device 20 includes a cum member 25 provided on a first rotating member 21, wherein cum surfaces 25a and 25b whose curvatures vary along with changes in a torsion angle of the cum member 25 and the boss 33, and cum surfaces 25c and 25d spaced in an axial direction of the cum member 25 and also spaced in a circumferential direction of the cum member 25 relative to the cum surfaces 25a and 25b, and whose curvatures vary along with changes in a torsion angle of the boss 33 and the cum member 25 are formed on the cum member. In addition, each of roller members 41 and 42 and roller members 43 and 44 of a torsional vibration damping mechanism 23 is slid along the cum surfaces 25a and 25b and the cum surfaces 25c and 25d to elastically deform coil springs 37 and 38 and coil springs 39 and 40.

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 transmission of a drive transmission system, and a first rotating member and a second rotating member are relatively opposed to each other via an elastic member. The present invention relates to a torsional vibration damping device that is rotatably connected.

  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).

  The torsional vibration damping device includes a pair of disk plates having cam surfaces extending in a circumferential direction on an inner periphery, a clutch hub provided on the same axis as the pair of disk plates, and a clutch A coil spring provided on the hub, and a sliding member attached to the tip of the coil spring and in sliding contact with the cam surface are provided.

  In this torsional vibration damping device, when the pair of disk plates and the clutch hub rotate relative to each other, the sliding member biased by the coil spring slides on the cam surface. At this time, the coil spring is elastically deformed to attenuate torsional vibration between the pair of disk plates and the clutch hub.

  This torsional vibration damping device widens the torsion angle between the pair of disk plates and the clutch hub by sliding the sliding member on the cam surface when the pair of disk plates and the clutch hub rotate relative to each other. Thus, the torsional rigidity between the cam member and the pair of disk plates can be lowered as a whole to sufficiently attenuate the jagged noise and the booming noise, thereby improving the vibration damping performance.

No. 2-1539

  However, in such a conventional torsional vibration damping device, the sliding member slides on the cam surface when the pair of disk plates and the clutch hub rotate relative to each other. On the inner peripheral surface of the disc plate, only one cam surface is provided in the same plane.

  Therefore, the torsional rigidity is the same when the clutch hub is twisted to the positive side with respect to the pair of disk plates from the neutral state where the torsion angle between the pair of disk plates and the clutch hub is the minimum, and when twisted to the negative side. End up.

  In general, it is desired that the torsional rigidity of the torsional vibration damping device, that is, the spring rigidity of the elastic member, be different between the positive side (acceleration side) and the negative side (deceleration side). Specifically, high rigidity is preferable on the positive side, and low rigidity is preferable on the negative side.

If the spring stiffness is changed on the positive side and the negative side in this way, fluctuations in rotation when passing through the resonance point can be suppressed when the clutch hub is twisted to the positive side with respect to the pair of disk plates. Further, when the clutch hub is twisted to the negative side with respect to the pair of disk plates, the damping performance can be improved over the entire negative twist region.
Since the conventional torsional vibration damping device has the same spring stiffness on the positive side and the negative side, the above-described effects cannot be obtained.

  The present invention has been made to solve the above-described conventional problems. The torsional rigidity is increased on the positive side and the negative side while the torsion angle between the first rotating member and the second rotating member is widened. An object of the present invention is to provide a torsional vibration damping device that can be changed.

  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, and is rotated relative to the first rotating member. A second rotating member that is freely provided, a cam member that is provided on the first rotating member, and that rotates integrally with the first rotating member, and is provided on the second rotating member. A torsional vibration damping device comprising a torsional vibration damping mechanism for attenuating torsional vibration between the first rotating member and the second rotating member when the rotating member and the second rotating member rotate relative to each other. And the cam member has a first cam surface whose curvature changes with a change in a twist angle of the first rotating member and the second rotating member, and the first cam surface. The first rotating member is spaced apart in the axial direction, and the circumferential direction of the first rotating member And a second cam surface whose curvature changes with a change in the torsion angle, and the torsional vibration damping mechanism is attached to the second rotating member, and the second rotating member A first mechanism main body that can rotate integrally, a first elastic member provided on the first mechanism main body, and a tip of the first elastic member that slides on the first cam surface. A first sliding member that moves, a second mechanism body that is attached to the second rotating member and is rotatable together with the second rotating member, and a second mechanism body is provided on the second mechanism body. And a second sliding member that is provided at the tip of the second elastic member and slides on the second cam surface.

  In this torsional vibration damping device, the cam member provided on the first rotating member has a first cam surface whose curvature changes with changes in the torsion angles of the first rotating member and the second rotating member. For example, when the second rotating member is twisted to the positive side with respect to the first rotating member, the first sliding member that slides on the first cam surface is pressed against the first cam surface. Thus, the first elastic member is elastically deformed.

  When the first elastic member is elastically deformed, the reaction force from the first elastic member acting on the first cam surface changes as the first elastic member is twisted to the positive side, and the first elastic member changes the first elasticity. Torque is transmitted to the second rotating member via the member and the first mechanism body.

  Further, the cam member provided on the first rotating member is spaced apart from the first cam surface in the axial direction of the first rotating member, and spaced apart in the circumferential direction of the first rotating member, and twisted. For example, when the second rotating member twists to the negative side with respect to the first rotating member, the second cam surface slides on the second cam surface. The second sliding member that moves is pressed against the second cam surface, and the second elastic member is elastically deformed.

  When the second elastic member is elastically deformed, the reaction force of the second elastic member acting on the second cam surface is changed as the second elastic member is twisted to the negative side, and the second mechanism body changes from the second rotating member. Torque is transmitted to the first rotating member via the second elastic member.

  As described above, when the second rotating member rotates relative to the first rotating member in the positive side or the negative side, the first sliding member and the second sliding member move to the first cam surface and the first cam surface. By sliding along the second cam surface, the first elastic member and the second elastic member are elastically deformed, so that the torsion angle range between the first rotating member and the second rotating member is widened. It can be made. For this reason, it is possible to attenuate torsional vibration while transmitting torque between the first rotating member and the second rotating member, and to improve the vibration damping performance.

  In the present invention, the cam member is thus provided with the first cam surface and the second cam surface separated in the axial direction, and, for example, the radius of curvature between the first cam surface and the second cam surface is changed. Accordingly, the first elastic member and the second elastic member have different spring stiffnesses when the second rotating member is twisted to the positive side with respect to the first rotating member and when the second rotating member is twisted to the negative side. be able to.

Therefore, the torsional rigidity of the first elastic member when the second rotating member is twisted to the positive side with respect to the first rotating member can be made high, and the second rotating member is the first rotating member. The torsional rigidity of the second elastic member when twisted to the negative side with respect to the rotating member can be made low.
That is, the torsional vibration damping device of the present invention can increase the degree of freedom in setting the positive side spring stiffness and the negative side spring stiffness.

In the torsional vibration damping device of (1), (2) the second cam surface has a larger radius of curvature than the radius of curvature of the first cam surface.
In this torsional vibration damping device, since the curvature radius of the second cam surface is larger than the curvature radius of the first cam surface, the second rotating member is on the positive side with respect to the first rotating member. The first sliding member slides on the first cam surface having a smaller radius of curvature than the second cam surface.
For this reason, the amount of elastic deformation of the first elastic member can be increased, and the spring rigidity of the first elastic member can be made high.

  Further, when the second rotating member is twisted to the negative side with respect to the first rotating member, the second sliding member slides on the second cam surface having a radius of curvature larger than that of the first cam surface. Move. For this reason, the amount of elastic deformation of the second elastic member can be made smaller than that of the first elastic member, and the spring rigidity of the second elastic member can be lowered.

  (1) In the torsional vibration damping device according to (1) and (2), (3) the first elastic member and the second elastic member are constituted by coil springs having the same spring rigidity, and the first rotation In the case where the second rotating member is twisted to the positive side and the negative side relative to the first rotating member from the neutral state where the twist angle of the member and the second rotating member is the minimum, The first elastic member is deformed so that the elastic deformation amount of the second elastic member per unit twist angle on the negative side is smaller than the elastic deformation amount of the first elastic member per unit twist angle on the positive side. The cam surface and the radius of curvature of the second cam surface are set.

The torsional vibration damping device includes a first elastic member per unit torsion angle on the positive side when the second rotating member is twisted to the positive side and to the negative side with respect to the first rotating member. The radius of curvature of the first cam surface and the second cam surface is set so that the elastic deformation amount of the second elastic member per unit twist angle on the negative side is smaller than the elastic deformation amount of When the second rotating member is twisted to the positive side with respect to the first rotating member, the spring rigidity of the first elastic member can be made high.
Further, when the second rotating member is twisted to the negative side with respect to the first rotating member, the spring rigidity of the second elastic member can be lowered.

  In the torsional vibration damping device according to (1), (4) the first elastic member and the second elastic member have different spring rigidity.

In this torsional vibration damping device, the first elastic member and the second elastic member have different spring rigidity. Therefore, when the first cam surface and the second cam surface have the same radius of curvature, the second rotation When the member is twisted to the positive side with respect to the first rotating member, the spring rigidity of the first elastic member can be made high.
Further, when the second rotating member is twisted to the negative side with respect to the first rotating member, the spring rigidity of the second elastic member can be lowered.

  In the torsional vibration damping device according to any one of (1) to (4), (5) the second rotating member has a boss to which an input shaft of a transmission of a drive transmission system is coupled, and the first rotating member In this configuration, torque is transmitted from the internal combustion engine.

  In this torsional vibration damping device, the second rotating member has a boss to which the input shaft of the transmission of the drive transmission system is connected, and torque is transmitted from the internal combustion engine to the first rotating member. The range of the torsion angle between the rotating member and the second rotating member can be widened to reduce the rigidity of the first elastic member and the second elastic member.

  For this reason, in a region where the torsion angle between the first rotating member and the second rotating member is small, such as when the shift position is changed to neutral and the internal combustion engine is in an idle state, the rigidity is low. It is possible to suppress the generation of a rattling sound from the transmission gear set constituting the transmission by attenuating minute vibrations by the first elastic member and the second elastic member.

  Further, in a region where the torsion angle between the first rotating member and the second rotating member is large, the torsion angle between the pair of disk plates and the cam member is increased to increase the torque increase rate, thereby providing a high rigidity torsion characteristic. Can be obtained.

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

  In particular, since the torsional rigidity of the first elastic member when the second rotating member is twisted to the positive side (acceleration side) with respect to the first rotating member can be made high, resonance of the drive transmission system can be achieved. The rotational fluctuation at the time of passing the point can be suppressed, and the torsional resonance of the drive transmission system can be further attenuated.

  Further, since the torsional rigidity of the second elastic member when the second rotating member is twisted to the negative side (deceleration side) with respect to the first rotating member can be made low, the torsional area on the negative side The attenuation performance can be improved over the whole.

  According to the present invention, it is possible to provide a torsional vibration damping device capable of changing the torsional rigidity between the positive side and the negative side while widening the torsion angle between the first rotating member and the second rotating member. .

It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is a front view of the torsional vibration damping device. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is a side view of a torsional vibration damping device. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is AA direction arrow sectional drawing of FIG. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is BB direction arrow sectional drawing of FIG. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is CC sectional view taken on the line of FIG. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, (a) is a front view of one arm member, (b) is a side view of one arm member. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, (a) is a front view of the other arm member, (b) is a side view of the other arm member. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is a front view of a roller member. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is DD sectional view taken on the line of FIG. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is a figure which shows the state which the boss | hub twisted to the positive side with respect to the cam member. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is a figure which shows the state which further twisted the boss | hub to the positive side with respect to the cam member. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is a figure which shows the state which the boss | hub twisted to the negative side with respect to the cam member. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is a figure which shows the state which further twisted the boss | hub to the negative side with respect to the cam member. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is a figure which shows the torsion characteristic of a torsional vibration damping device. It is a figure which shows 2nd Embodiment of the torsional vibration damping device which concerns on this invention, and is a front view of the torsional vibration damping device. It is a figure which shows 2nd Embodiment of the torsional vibration damping device which concerns on this invention, and is EE direction arrow sectional drawing of FIG. It is a figure which shows 2nd Embodiment of the torsional vibration damping device which concerns on this invention, (a) is a front view of one arm member, (b) is a side view of one arm member. It is a figure which shows 2nd Embodiment of the torsional vibration damping device which concerns on this invention, (a) is a front view of the other arm member, (b) is a side view of the other arm member. It is a figure which shows 2nd Embodiment of the torsional vibration damping device which concerns on this invention, and is a figure which shows the state which the boss | hub twisted to the positive side with respect to the cam member. It is a figure which shows 2nd Embodiment of the torsional vibration damping device which concerns on this invention, and is a figure which shows the state which the boss | hub twisted to the negative side with respect to the cam member.

Hereinafter, embodiments of a torsional vibration damping device according to the present invention will be described with reference to the drawings.
(First embodiment)
FIGS. 1-14 is a figure which shows 1st Embodiment of the torsional vibration damping device based on this invention.
First, the configuration will be described.
1 to 4, the torsional vibration damping device 20 is provided on a first rotating member 21 and the same axis as the first rotating member 21 and is rotatable relative to the first rotating member 21. The two rotating members 22 and the torsional vibration damping mechanism 23 are included.

  Torque from an internal combustion engine (not shown) that is a driving source is input to the first rotating member 21, and the second rotating member 22 transmits drive torque (not shown) of the torque of the first rotating member 21. Is transmitted to the transmission of the system.

  The first rotating member 21 includes a plate-like cam member 25 and a clutch disk 26. The clutch disk 26 is provided on the outer peripheral portion of the cam member 25, and includes a cushioning plate 27 and friction materials 28a and 28b constituting a facing member. The cushioning plate 27 is composed of a ring-shaped member that undulates in the thickness direction, and is fixed to the outer peripheral portion of the cam member 25 by a rivet (not shown).

  The friction materials 28a and 28b are fixed to both surfaces of the cushioning plate 27 by rivets 29 (see FIGS. 3 and 4). The friction materials 28a and 28b are connected to a flywheel 30 fixed to a crankshaft of the internal combustion engine. It is located between the pressure plate 31 of the clutch cover bolted to the flywheel 30 (see FIGS. 2 to 4).

  The friction members 28 a and 28 b are pressed against the pressure plate 31 and frictionally engaged with the flywheel 30 and the pressure plate 31, whereby the torque of the internal combustion engine is input to the first rotating member 21.

  When a clutch pedal (not shown) is depressed, the pressure plate 31 is released from pressing the friction materials 28a and 28b, and the friction materials 28a and 28b are separated from the flywheel 30, whereby the torque of the internal combustion engine is reduced to the first. Is not input to the rotating member 21.

Also, cam surfaces 25a and 25b as first cam surfaces and cam surfaces 25c and 25d as second cam surfaces are formed on the inner peripheral surface of the cam member 25. The cam surfaces 25a and 25b The member 25 is formed on the same circumferential surface, and the cam surfaces 25 c and 25 d are formed on the same circumferential surface of the cam member 25. Each of the cam surfaces 25a to 25d extends in a range of a certain angle (for example, 70 °) in the circumferential direction of the cam member 25.
The curvatures of the cam surfaces 25a to 25d change with changes in torsion angles of the first rotating member 21 and the second rotating member 22. That is, the curvatures of the cam surfaces 25a to 25d are formed on the inner peripheral portion of the cam member 25 so as to increase as the torsion angles of the first rotating member 21 and the second rotating member 22 increase. The cam member 25 of the present embodiment is a so-called inner cam.

  The torsion angles of the first rotating member 21 and the second rotating member 22 are the first to the first from the neutral state where the torsion angles of the first rotating member 21 and the second rotating member 22 are minimum (approximately 0 °). The rotating member 21 becomes larger when the second rotating member 22 is twisted to the positive side and the negative side opposite to the positive side.

  The cam surfaces 25 a and 25 b are provided on one side in the axial direction of the first rotating member 21, that is, in the axial direction of the input shaft 32 described later, and the cam surfaces 25 a and 25 b are the rotation centers of the cam member 25. The axis O, that is, the rotation center axis O of the first rotating member 21 is sandwiched therebetween. In the present embodiment, since the axial direction of the first rotating member 21 is the same as the axial direction of the input shaft 32, the axial direction is hereinafter assumed to be the axial direction of the input shaft 32. Do.

  The cam surfaces 25c and 25d are spaced apart from the cam surfaces 25a and 25b in the axial direction, and are spaced from the cam surfaces 25a and 25b in the circumferential direction of the cam member 25 and provided on the other side in the axial direction. Yes. The cam surfaces 25c and 25d are opposed to each other with the rotation center axis O of the cam member 25 interposed therebetween.

  Further, the curvature radii of the cam surfaces 25c and 25d are formed larger than the curvature radii of the cam surfaces 25a and 25b. Further, the curvature of the cam surfaces 25a and 25b increases as the first rotating member 21 is twisted to the positive side with respect to the second rotating member 22 from the neutral state, and the curvature of the cam surfaces 25c and 25d is From the neutral state, the first rotating member 21 becomes larger as the second rotating member 22 is twisted to the negative side.

  Further, at both ends of the cam surfaces 25a to 25d in the axial direction, edge portions 25A are formed so as to protrude inward in the radial direction from the cam surfaces 25a to 25d with a certain width. The roller members 41 to 44 of the torsional vibration damping mechanism 23 which will be described later function as an axial guide when sliding along the cam surfaces 25a to 25d. The radial direction refers to the radial direction of the cam member 25.

  On the other hand, the second rotating member 22 is provided on the outer periphery of the boss 33 and the boss 33 that is spline-fitted to the outer periphery spline 32a of the input shaft 32 (see FIGS. 2 to 4) of the transmission of the drive transmission system. And a torsional vibration damping mechanism 23.

  The boss 33 is composed of divided bosses 33A and 33B. Inner circumferential splines 33a and 33b are formed on the inner circumferential surfaces of the divided bosses 33A and 33B. The inner circumferential splines 33a and 33b are fitted to the outer circumferential splines 32a of the input shaft 32, respectively. Yes.

  The torsional vibration damping mechanism 23 includes a plate-like arm member 35 as a first mechanism body, a plate-like arm member 36 as a second mechanism body, and coil springs 37 and 38 as first elastic members. , Coil springs 39 and 40 as second elastic members, roller members 41 and 42 as first sliding members, and roller members 43 and 44 as second sliding members. .

  The arm member 35 is provided integrally with the divided boss 33A and is rotatable integrally with the divided boss 33A. As shown in FIGS. 5 and 6, the arm member 35 extends outward from the divided boss 33A, and the extending direction of the arm member 35 is on the same axis as the radial axis. The coil springs 37 and 38 are respectively inserted into square through holes 35 a formed at both ends in the extending direction of the arm member 35. A protrusion 35b is formed on the bottom surface of the through hole 35a, and the base end portions of the coil springs 37 and 38 are fitted to the protrusion.

  The arm member 36 is provided integrally with the divided boss 33B and is rotatable integrally with the divided boss 33B. As shown in FIGS. 5 and 7, the arm member 36 extends outward from the split boss 33B, and the extending direction of the arm member 36 is on the same axis as the radial axis. The coil springs 39 and 40 are respectively inserted into square through holes 36 a formed at both ends in the extending direction of the arm member 36. A protrusion 36b is formed on the bottom surface of the through hole 36a, and the base end portions of the coil springs 39 and 40 are fitted to the protrusion 36b.

  The roller members 41 to 44 are attached to the tip portions of the coil springs 37 to 40, and the roller members 41 to 44 include an inner ring 51, an outer ring 52, and a rolling element 53, as shown in FIGS. And a cage 54.

  The inner ring 51 has a cylindrical part 51a and a pressing part 51b formed to protrude from the cylindrical part 51a. The outer periphery of the cylindrical part 51a is configured by a raceway surface on which the rolling elements 53 roll smoothly. The pressing part 51b is formed integrally with the cylindrical part 51a, and as shown in FIGS. 6 and 7, the end part engages with the tip part of the coil springs 37 to 40 to press the coil springs 37 to 40. It has become.

  The inner periphery of the outer ring 52 is formed by a raceway surface on which the rolling elements 53 roll smoothly, and the outer periphery of the outer ring 52 is formed so as to protrude in a substantially arc shape. The rolling elements 53 are formed of rollers such as cylindrical rollers and needle rollers, and a plurality of rolling elements 53 are disposed between the inner ring 51 and the outer ring 52.

  The cage 54 is formed in an annular shape, and holds the rolling elements so that they are uniformly arranged between the inner ring 51 and the outer ring 52 on the circumference.

  As shown in FIGS. 5 to 7, the arm members 35, 36 above the through holes 35a, 36a are formed with locking members 35c, 36c. The locking members 35c, 36c have roller members. Each pressing part 51b of 41-44 contacts.

  Therefore, the roller members 41 to 44 can freely move in the through holes 35a and 36a within a range in which the coil springs 37 to 40 are elastically deformed until the pressing portion 51b is locked to the locking members 35c and 36c. The natural lengths of the coil springs 37 to 40 are the same, and the spring rigidity is also the same.

  Further, as shown in FIG. 1, the roller members 41 and 42 are configured such that the outer ring 52 slides on the cam surfaces 25a and 25b of the cam member 25, and the roller members 43 and 44 are configured such that the outer ring 52 cams. It slides on the cam surfaces 25c and 25d of the member 25. Further, when the outer ring 52 of the roller members 41 to 44 slides on the cam surfaces 25a to 25d of the cam member 25, the outer ring 52 of the roller members 41 to 44 is guided to the edge portion 25A.

  In the present embodiment, the curvatures of the cam surfaces 25c and 25d are formed larger than the curvature radii of the cam surfaces 25a and 25b. The curvatures of the cam surfaces 25a and 25b are the same as those of the first rotating member 21 and the second rotation member 21. As the rotating member 22 is twisted from the neutral state to the positive side, the curvatures of the cam surfaces 25c and 25d are twisted from the neutral state to the negative side. It grows according to. Since the first rotating member 21 includes the cam member 25 and the second rotating member 22 includes the boss 33, the twisting of the first rotating member 21 and the second rotating member 22 will be described. For the sake of convenience, the description will be made assuming that the boss 33 and the cam member 25 are twisted.

  In the torsional vibration damping device 20 of the present embodiment, when the arm members 35 and 36 together with the boss 33 are twisted from the neutral state to the positive side, the roller members 41 and 42 slide on the cam surfaces 25a and 25b whose curvature gradually increases. The amount of compression of the coil springs 37 and 38 is gradually increased, and the spring rigidity of the coil springs 37 and 38 is gradually increased.

  Further, when the arm members 35 and 36 together with the boss 33 are twisted from the neutral state to the negative side, the roller members 43 and 44 slide on the cam surfaces 25c and 25d where the curvature gradually increases, and the coil springs 39 and 40 are compressed. The amount gradually increases, and the spring stiffness of the coil springs 39, 40 gradually increases.

  However, since the curvature radii of the cam surfaces 25c and 25d are larger than the curvature radii of the cam surfaces 25a and 25b, when the arm members 35 and 36 together with the boss 33 are twisted from the neutral state to the negative side, the coil spring The compression amount per unit twist angle of the coil springs 39 and 40 is smaller than the compression amount (elastic deformation amount) per unit twist angle of 37 and 38.

  In other words, the torsional vibration damping device 20 of the present embodiment has a unit twist angle on the positive side when the arm members 35 and 36 together with the boss 33 are twisted from the neutral state to the positive side and to the negative side. The curvature radii of the cam surfaces 25a and 25b and the cam surfaces 25c and 25d so that the compression amount of the coil springs 39 and 40 per unit twist angle on the negative side is smaller than the compression amount of the contact coil springs 37 and 38. Is set.

  The cam surfaces 25e other than the cam surfaces 25a and 25b on the same circumferential surface as the cam surfaces 25a and 25b are the same as when the roller members 43 and 44 of the arm member 36 slide on the cam surfaces 25c and 25d. The cam surfaces 25f other than the cam surfaces 25c and 25d on the same circumferential surface as the cam surfaces 25c and 25d are configured as sliding portions, and the roller members 41 and 42 of the arm member 35 slide on the cam surfaces 25a and 25b. It constitutes the escape when moving.

Next, the operation will be described.
10 to 13 show a state in which the torsional vibration damping device 20 receives the torque of the internal combustion engine and rotates in the clockwise direction (R1 direction). For convenience of explanation, the boss 33 is relative to the cam member 25. The description will be made assuming that the twisted state is from the neutral state to the positive counterclockwise rotation direction (R2 direction) and the negative clockwise rotation direction (R1 direction). The boss 33 is twisted to the positive side with respect to the cam member 25 when the vehicle is accelerating, and the boss 33 is twisted to the negative side when the vehicle is decelerating.

  The friction members 28 a and 28 b are pressed by the pressure plate 31 and frictionally engaged with the flywheel 30 and the pressure plate 31, whereby the torque of the internal combustion engine is input to the cam member 25.

  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 cam member 25 and the boss 33 is small, and the boss 33 is counterclockwise with respect to the cam member 25 (R2 direction). ) Relative rotation.

  At this time, as shown in FIG. 10 from the state shown in FIG. 1, when the boss 33 rotates in the R2 direction with respect to the cam member 25 as the torsion angle between the cam member 25 and the boss 33 increases, the boss 33 and the arm member Since 35 and 36 rotate in the R2 direction, the outer ring 52 of the roller members 41 and 42 rolls along the cam surfaces 25a and 25b.

  Since the curvature of the cam surfaces 25a and 25b gradually increases from the neutral state as the boss 33 is twisted to the positive side with respect to the cam member 25, the coil springs 37 and 38 are compressed, and the reaction force of the coil springs 37 and 38 is increased. Acts on the cam surfaces 25a, 25b.

  When the reaction force of the coil springs 37 and 38 acts on the cam surfaces 25a and 25b, torque is transmitted from the cam member 25 to the boss 33 via the coil springs 37 and 38 and the arm member 35, and the torque of the internal combustion engine is transmitted to the input shaft. 32 is input to the drive transmission transmission. Further, when the coil springs 37 and 38 are elastically deformed, torque fluctuations of the internal combustion engine are attenuated by the coil springs 37 and 38 and are not transmitted to the transmission.

  The cam surfaces 25c and 25d are offset in the axial direction with respect to the cam surfaces 25a and 25b, and the cam surfaces 25c and 25d are opposed to the cam surfaces 25a and 25b across the rotation center axis O. It has become a relationship.

  For this reason, when the arm member 36 rotates in the R2 direction, the outer ring 52 of the roller members 43 and 44 slides on the cam surface 25f which is the escape portion, but at this time, the coil springs 39 and 40 are not compressed, The reaction force of the coil springs 39 and 40 does not act on the cam surface 25f.

  Further, as shown in FIG. 11 from the state shown in FIG. 10, when the torsion angle between the cam member 25 and the boss 33 is further increased, the boss 33 further rotates in the R2 direction with respect to the cam member 25, so , 36 rotate in the R2 direction with the boss 33, and the outer ring 52 of the roller members 41, 42 rolls along the cam surfaces 25a, 25b.

  Since the curvature of the cam surfaces 25a and 25b further increases as the boss 33 is twisted to the positive side with respect to the cam member 25 from the neutral state, the coil springs 37 and 38 are further compressed, and the reaction force of the coil springs 37 and 38 is increased. Acts on the cam surfaces 25a and 25b.

  When the reaction force of the coil springs 37 and 38 acts on the cam surfaces 25a and 25b, a larger torque is transmitted from the cam member 25 to the boss 33 via the coil springs 37 and 38 and the arm member 35, and the torque of the internal combustion engine is increased. This is input to the drive transmission transmission via the input shaft 32. Further, when the coil springs 37 and 38 are elastically deformed, torque fluctuations of the internal combustion engine are attenuated by the coil springs 37 and 38 and are not transmitted to the transmission.

  On the other hand, when the vehicle is decelerated, the driving torque of the internal combustion engine is reduced and engine braking is generated, so that torque is input from the input shaft 32 of the transmission to the boss 33. When the rotational fluctuation due to the torque fluctuation of the internal combustion engine is small during deceleration, the fluctuation torque between the boss 33 and the cam member 25 is small, so the boss 33 is negative in the clockwise direction relative to the cam member 25. It will be twisted to the side (R1 direction).

  At this time, as shown in FIG. 12 from the state shown in FIG. 1, when the boss 33 rotates in the R <b> 1 direction with respect to the cam member 25 as the torsion angle between the cam member 25 and the boss 33 increases, Since 35 and 36 rotate in the R1 direction, the outer ring 52 of the roller members 43 and 44 rolls along the cam surfaces 25c and 25d.

  Since the curvature of the cam surfaces 25c and 25d gradually increases from the neutral state as the boss 33 is twisted to the negative side with respect to the cam member 25, the coil springs 39 and 40 are compressed, and the reaction force of the coil springs 39 and 40 is increased. Acts on the cam surfaces 25c, 25d.

  When the reaction force of the coil springs 39 and 40 acts on the cam surfaces 25c and 25d, torque is transmitted from the boss 33 to the cam member 25 via the arm member 36 and the coil springs 39 and 40, and the transmission of the drive transmission system Torque is transmitted from the input shaft 32 to the internal combustion engine. Further, when the coil springs 39 and 40 are elastically deformed, torque fluctuations of the internal combustion engine are attenuated by the coil springs 39 and 40 and are not transmitted to the transmission.

  The cam surfaces 25c and 25d are offset in the axial direction with respect to the cam surfaces 25a and 25b, and the cam surfaces 25c and 25d are opposed to the cam surfaces 25a and 25b across the rotation center axis O. It has become a relationship.

  For this reason, when the arm member 35 rotates in the R1 direction, the outer ring 52 of the roller members 41 and 42 slides on the cam surface 25e which is the escape portion, but at this time, the coil springs 37 and 38 are not compressed, The reaction force of the coil springs 37 and 38 does not act on the cam surface 25e.

  In addition, as shown in FIG. 13 from the state shown in FIG. 12, when the torsion angle between the cam member 25 and the boss 33 is further increased, the boss 33 further rotates in the R1 direction with respect to the cam member 25. The arm members 35 and 36 rotate in the R1 direction, and the outer ring 52 of the roller members 43 and 44 rolls along the cam surfaces 25c and 25d.

  The curvatures of the cam surfaces 25c and 25d are further increased from the neutral state as the boss 33 is twisted to the negative side with respect to the cam member 25. Therefore, the coil springs 39 and 40 are further compressed, and the reaction force of the coil springs 39 and 40 is increased. Acts on the cam surfaces 25c and 25d.

  When the reaction force of the coil springs 39 and 40 acts on the cam surfaces 25c and 25d, torque is transmitted from the boss 33 to the cam member 25 via the arm member 36 and the coil springs 39 and 40, and the transmission of the drive transmission system Torque is transmitted from the input shaft 32 to the internal combustion engine.

  Further, when the coil springs 39 and 40 are elastically deformed, torque fluctuations of the internal combustion engine are attenuated by the coil springs 39 and 40 and are not transmitted to the transmission.

  Further, since the curvature radii of the cam surfaces 25c and 25d are larger than the curvature radii of the cam surfaces 25a and 25b, the boss 33 and the arm members 35 and 36 are twisted to the negative side with respect to the cam member 25. The spring stiffness of the coil springs 39 and 40 per unit torsion angle is smaller than the spring stiffness of the coil springs 37 and 38 per unit torsion angle when twisted to the positive side. That is, the coil springs 39 and 40 that function on the negative side are softer than the coil springs 37 and 38 that function on the positive side.

  As described above, the torsional vibration damping device 20 according to the present embodiment has a cam surface whose curvature changes with changes in the torsion angles of the cam member 25 and the boss 33 on the cam member 25 provided on the first rotating member 21. 25a, 25b and cam surfaces 25a, 25b are spaced apart in the axial direction and spaced apart in the circumferential direction of the cam member 25, and the curvature changes as the twist angle between the boss 33 and the cam member 25 changes. Cam surfaces 25c and 25d were formed.

  The roller members 41 and 42 and the roller members 43 and 44 of the torsional vibration damping mechanism 23 are slid along the cam surfaces 25a and 25b and the cam surfaces 25c and 25d, so that the coil springs 37 and 38 and the coil springs are slid. By elastically deforming the members 39 and 40, the torsional vibration can be attenuated while transmitting the torque between the cam member 25 and the boss 33 by widening the range of the torsion angle between the cam member 25 and the boss 33. , Vibration damping performance can be improved.

  FIG. 14 is a diagram showing the torsional characteristics of the cam member 25 and the boss 33, and explains the relationship between the torsional angle between the cam member 25 and the boss 33 and the torsional torque in the torsional vibration damping device 20 of the present embodiment. It is a graph to do.

  In the present embodiment, as the boss 33 rotates, the torsion angle between the cam member 25 and the boss 33 can be widened to about 140 ° in total on the positive side and the negative side.

  Note that the torsional torque and the torsional angle when the cam member 25 and the boss 33 rotate relative to each other are the radius of curvature of the cam surfaces 25a to 25d of the cam member 25, the spring rigidity of the coil springs 37 to 40, and the arm member 35. , 36 can be adjusted to an arbitrary torsion torque and angle. For this reason, a twist angle of 140 ° or more can also be realized.

  Further, as shown in FIG. 14, the torsional vibration damping device 20 of the present embodiment has a flat torsional characteristic in which the torsional rigidity of the coil springs 37 to 40 is low when the torsion angle between the cam member 25 and the boss 33 is small. can do.

  Therefore, in a region where the torque transmitted from the cam member 25 to the boss 33 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 is generated. The torsional vibration as a source can be attenuated to suppress a rattling noise, that is, a so-called rattling noise, which is generated when a transmission gear set of a transmission in an unloaded state collides.

  In addition, the torsional vibration damping device 20 of the present embodiment can widen the range of the torsion angle between the cam member 25 and the boss 33 and reduce the torsional rigidity of the coil springs 37 to 40 as a whole. In an operating state in which the torque transmitted from the member 25 to the boss 33 is large, the torsional vibration caused by the rotational fluctuation due to the torque fluctuation of the driving source is attenuated, and the idle gear pair of the transmission gear set collides. Jara noise can be suppressed.

  Further, when the torsion angle between the cam member 25 and the boss 33 is large, the torsional rigidity of the torsional vibration damping device 20 can be made lower than the conventional torsional rigidity, so that the torsional vibration due to the torsional resonance of the drive transmission system is conventionally caused. It is possible to suppress the occurrence of a muffled sound in the vehicle interior by being greatly attenuated.

  In the present embodiment, since the cam surfaces 25a and 25b and the cam surfaces 25c and 25d are formed apart from each other in the axial direction, the radius of curvature between the cam surfaces 25a and 25b and the cam surfaces 25c and 25d can be changed. It becomes possible.

  In the present embodiment, by increasing the curvature radius of the cam surfaces 25c and 25d with respect to the curvature radius of the cam surfaces 25a and 25b, the boss 33 is twisted to the positive side with respect to the cam member 25 and negatively. The spring stiffness of the coil springs 37, 38 and the coil springs 39, 40 can be made different depending on the twisted state.

For this reason, as shown in FIG. 14, the torsional rigidity of the coil springs 37 and 38 when the boss 33 is twisted to the positive side with respect to the cam member 25 can be made high, and the boss 33 is connected to the cam member 25. On the other hand, the torsional rigidity of the coil springs 39 and 40 when twisted to the negative side can be made lower than that of the positive side.
That is, the torsional vibration damping device 20 according to the present embodiment can increase the degree of freedom in setting the positive side spring stiffness and the negative side spring stiffness.

  As a result, the rotational fluctuation at the time of passing through the resonance point of the drive transmission system is achieved by increasing the torsional rigidity of the coil springs 37 and 38 when the boss 33 is twisted to the positive side (acceleration side) with respect to the cam member 25. Can be further suppressed, and the torsional resonance of the drive transmission system can be further attenuated to further suppress the generation of a booming noise.

  Further, by reducing the torsional rigidity of the coil springs 39 and 40 when the boss 33 is twisted to the negative side (deceleration side) with respect to the cam member 25, as shown in FIG. The attenuation performance can be improved over the whole.

  In the present embodiment, the coil springs 37 and 38 and the coil springs are configured such that the curvature radii of the cam surfaces 25a and 25b of the cam member 25 and the curvature radii of the cam surfaces 25c and 25d are different between the positive side and the negative side. Although the torsional rigidity of the positive side and the negative side of 39 and 40 is made different, the configuration for making the torsional rigidity different between the positive side and the negative side is not limited to this.

  For example, the cam surfaces 25a to 25d may have the same radius of curvature, and the spring stiffness of the coil springs 37 and 38 may be larger than the spring stiffness of the coil springs 39 and 40. In this way, the torsional rigidity on the positive side can be increased, and the torsional rigidity on the negative side can be reduced compared to the positive side.

  Thus, in the present embodiment, the cam surfaces 25a and 25b and the cam surfaces 25c and 25d are separated (offset) in the axial direction, so that the degree of freedom in setting the positive side spring stiffness and the negative side spring stiffness is set. Can be increased.

(Second Embodiment)
15 to 20 are diagrams showing a second embodiment of the torsional vibration damping device according to the present invention. In the present embodiment, the configuration of the cam member and the torsional vibration damping mechanism is the first embodiment. And different. Accordingly, the same components as those in the first embodiment are denoted by the same reference numerals and description thereof is omitted.

  15 and 16, the first rotating member 21 includes a clutch disk 26 and a cam member 61, and a cam surface 61 a as a first cam surface and a second cam surface are provided on the inner peripheral surface of the cam member 61. A cam surface 61b is formed as a cam surface. The cam surfaces 61 a and 61 b extend within a certain angular range (for example, 70 °) in the circumferential direction of the cam member 61, and the torsion angles of the first rotating member 21 and the second rotating member 22. The curvature changes with the change of.

  That is, the curvatures of the cam surfaces 61a and 61b are formed on the inner peripheral portion of the cam member 61 so as to increase as the torsion angles of the first rotating member 21 and the second rotating member 22 increase from the neutral state. . The cam member 61 of the present embodiment is a so-called inner cam.

  The cam surface 61a is provided on one side in the axial direction, and the cam surface 61b is provided on the other side in the axial direction so as to be separated from the cam surface 61a in the axial direction. The cam surface 61b is provided to be spaced apart from the cam surface 61a in the circumferential direction of the cam member 61. The cam surfaces 61a and 61b are opposed to each other with the rotation center axis O of the cam member 61 interposed therebetween. Yes.

  Further, the curvature radius of the cam surface 61b is formed larger than the curvature radius of the cam surface 61a. Further, the curvature of the cam surface 61a increases as the first rotating member 21 and the second rotating member 22 are twisted from the neutral state to the positive side, and the curvature of the cam surface 61b is the first rotating member 21. The second rotating member 22 becomes larger as it is twisted from the neutral state to the negative side.

  Further, at both ends in the axial direction of the cam surfaces 61a and 61b, there are formed edge portions 61A formed to protrude inward in the radial direction from the cam surfaces 61a and 61b with a certain width. The roller members 41 and 43 of the torsional vibration damping mechanism 62, which will be described later, function as an axial guide when sliding along the cam surfaces 61a and 61b.

  The second rotating member 22 includes a boss 33 and a torsional vibration damping mechanism 62 provided on the outer periphery of the boss 33.

  The torsional vibration damping mechanism 62 includes a plate-like arm member 63 as a first mechanism body, a plate-like arm member 64 as a second mechanism body, a coil spring 65 as a first elastic member, The coil spring 66 as the second elastic member, the roller member 41 as the first sliding member, and the roller member 43 as the second sliding member.

  The arm member 63 is provided integrally with the divided boss 33A and is rotatable integrally with the divided boss 33A. The arm member 63 extends radially outward from the divided boss 33A, and as shown in FIG. 17, the coil spring 65 has a rectangular through hole 63a formed at the distal end in the extending direction of the arm member 63. Is inserted. A protrusion 63b is formed on the bottom surface of the through hole 63a, and the base end portion of the coil spring 65 is fitted to the protrusion 63b.

  The arm member 64 is provided integrally with the divided boss 33B, and is rotatable integrally with the divided boss 33B. The arm member 64 extends radially outward from the divided boss 33B. As shown in FIG. 18, the coil spring 66 has a rectangular through hole 64a formed at the distal end portion in the extending direction of the arm member 64. Is inserted. A protrusion 64b is formed on the bottom surface of the through hole 64a, and the base end portion of the coil spring 66 is fitted to the protrusion 64b.

In addition, the arm member 64 and the arm member 65 are inclined by a predetermined angle with respect to the rotation center axis O and extend outward in the radial direction from the boss 33.
A semicircular opening 61e for accommodating the arm member 63 is formed on the inner peripheral surface of the cam member 61, and the arm member 63 moves within the opening 61e.

A semicircular opening 61f for accommodating the arm member 64 is formed on the inner peripheral surface of the cam member 61. The opening 61f is spaced apart from the opening 61e in the axial direction. . The arm member 63 moves in the opening 61e.
The roller members 41 and 43 are attached to the tip portions of the coil springs 65 and 66, and the roller members 41 and 43 have the same configuration as that shown in FIGS.

  As shown in FIGS. 17 and 18, locking members 63c and 64c are formed on the arm members 63 and 64 above the through holes 63a and 64a. The locking members 63c and 64c include the roller member 41, Each pressing part 51b of 43 contacts.

  Therefore, the roller members 41 and 43 can freely move in the through holes 63a and 64a within a range in which the coil springs 65 and 66 are elastically deformed until the pressing portion 51b is locked to the locking members 63c and 64c. In addition, the natural length and spring rigidity of the coil springs 65 and 66 are the same.

  In the present embodiment, the radius of curvature of the cam surface 61b is formed larger than the radius of curvature of the cam surface 61a, and the curvature of the cam surface 61a is neutral between the first rotating member 21 and the second rotating member 22. The curvature of the cam surface 61b increases as the first rotating member 21 and the second rotating member 22 are twisted from the neutral state to the negative side, as the twist is increased from the state to the positive side.

  In addition, since the 1st rotation member 21 contains the cam member 61 and the 2nd rotation member 22 contains the boss | hub 33, description about the twist of the 1st rotation member 21 and the 2nd rotation member 22 is demonstrated. For convenience of explanation, the boss 33 and the cam member 61 will be described as being twisted.

  In the torsional vibration damping device 20 of the present embodiment, when the arm members 63 and 64 together with the boss 33 are twisted from the neutral state to the positive side, the roller member 41 slides on the cam surface 61a where the curvature gradually increases, and the coil The compression amount of the spring 65 is gradually increased, and the spring rigidity of the coil spring 65 is gradually increased.

  When the arm members 63 and 64 together with the boss 33 are twisted from the neutral state to the negative side, the roller member 43 slides on the cam surface 61b where the curvature gradually increases, and the compression amount of the coil spring 66 gradually increases. The spring stiffness of the coil spring 66 gradually increases.

In other words, the torsional vibration damping device 20 of the present embodiment has a unit twist angle on the positive side when the arm members 63 and 64 together with the boss 33 are twisted from the neutral state to the positive side and to the negative side. The curvature radii of the cam surface 61a and the cam surface 61b are set so that the compression amount of the coil spring 66 per unit twist angle on the negative side becomes smaller than the compression amount (elastic deformation amount) of the contact coil spring 65. ing.
Further, the cam surface 61c other than the cam surface 61a on the same circumferential surface as the cam surface 61a constitutes an escape portion when the roller member 43 of the arm member 64 slides on the cam surface 61b. The cam surface 61d other than the cam surface 61b on the same circumferential surface as the cam surface 61b constitutes an escape portion when the roller member 41 of the arm member 63 slides on the cam surface 61a.

Next, the operation will be described.
A case where the torsional vibration damping device 20 is rotating in the clockwise direction (R1 direction) will be described.

  As shown in FIG. 19, when the boss 33 rotates relative to the cam member 61 in the counterclockwise direction (R2 direction) during acceleration of the vehicle, the boss 33 increases as the torsion angle between the cam member 61 and the boss 33 increases. Rotates relative to the cam member 61 in the R2 direction. At this time, since the boss 33 and the arm members 63 and 64 rotate in the R2 direction, the outer ring 52 of the roller member 41 rolls along the cam surface 61a.

  Since the curvature of the cam surface 61a gradually increases from the neutral state as the boss 33 is twisted to the positive side with respect to the cam member 61, the coil spring 65 is compressed, and the reaction force of the coil spring 65 acts on the cam surface 61a. To do.

  When the reaction force of the coil spring 65 acts on the cam surface 61a, torque is transmitted from the cam member 61 to the boss 33 via the coil spring 65 and the arm member 63, and the torque of the internal combustion engine is transmitted to the drive via the input shaft 32. It is input to the transmission of the system. Further, since the coil spring 65 is elastically deformed, the torque fluctuation of the internal combustion engine is attenuated by the coil spring 65 and is not transmitted to the transmission.

  Further, the cam surface 61b is offset in the axial direction with respect to the cam surface 61a, and the cam surface 61b is in a positional relationship facing the cam surface 61a across the rotation center axis O.

  For this reason, when the arm member 64 rotates in the R2 direction, the outer ring 52 of the roller member 43 slides on the cam surface 61d which is the escape portion. At this time, the coil spring 66 is not compressed, and the coil spring 66 The reaction force does not act on the cam surface 61d.

  On the other hand, when the vehicle decelerates, as shown in FIG. 20, when the boss 33 rotates in the clockwise direction (R1 direction) with respect to the cam member 61 as the torsion angle between the cam member 61 and the boss 33 increases, the boss 33 Since the arm member 64 rotates in the R1 direction, the outer ring 52 of the roller member 43 rolls along the cam surface 61b.

  Since the curvature of the cam surface 61b gradually increases from the neutral state as the boss 33 is twisted to the negative side with respect to the cam member 61, the coil spring 66 is compressed, and the reaction force of the coil spring 66 acts on the cam surface 61b. To do.

  When the reaction force of the coil spring 66 acts on the cam surface 61b, torque is transmitted from the boss 33 to the cam member 61 via the arm member 64 and the coil spring 66, and the internal combustion engine is transmitted from the input shaft 32 of the transmission of the drive transmission system. Torque is transmitted to. Further, since the coil spring 66 is elastically deformed, the torque fluctuation of the internal combustion engine is attenuated by the coil spring 66 and is not transmitted to the transmission.

  Further, the cam surface 61b is offset in the axial direction with respect to the cam surface 61a, and the cam surface 61b is in a positional relationship facing the cam surface 61a across the rotation center axis O.

  For this reason, when the arm member 63 rotates in the R1 direction, the outer ring 52 of the roller member 41 slides on the cam surface 61c that is the escape portion. At this time, the coil spring 65 is not compressed, and the coil spring 65 The reaction force does not act on the cam surface 61c.

  As described above, in the present embodiment, by increasing the curvature radius of the cam surface 61b with respect to the curvature radius of the cam surface 61a, the boss 33 is twisted to the positive side and to the negative side with respect to the cam member 61. The spring stiffness of the coil spring 65 and that of the coil spring 66 can be made different from each other.

For this reason, when the boss 33 is twisted to the positive side with respect to the cam member 61, the torsional rigidity of the coil spring 65 can be increased, and when the boss 33 is twisted to the negative side with respect to the cam member 61. The torsional rigidity of the coil spring 66 can be lowered.
That is, the torsional vibration damping device 20 according to the present embodiment can increase the degree of freedom in setting the positive side spring stiffness and the negative side spring stiffness.

  As a result, by increasing the torsional rigidity of the coil spring 65 when the boss 33 is twisted to the positive side (acceleration side) with respect to the cam member 61, the rotational fluctuation when passing through the resonance point of the drive transmission system is suppressed. Therefore, the torsional resonance of the drive transmission system can be further attenuated, and generation of a muffled sound can be further suppressed.

  Further, by reducing the torsional rigidity of the coil spring 66 when the boss 33 is twisted to the negative side (deceleration side) with respect to the cam member 61, the damping performance is improved over the entire negative twisted region. Can be made.

  Further, in the first embodiment, the coil springs 37 to 40 are provided at both ends in the extending direction of the arm members 35 and 36, whereas in the present embodiment, the arm members 63 and 64 are extended. Coil springs 65 and 66 are provided only in one direction, and the arm members 63 and 64 are about half the size of the arm members 35 and 36 of the first embodiment.

  Therefore, the arm members 63 and 64 can be accommodated in the openings 61e and 61f formed in the inner peripheral portion of the cam member 61, and the axial lengths of the cam member 61 and the arm members 63 and 64 are shortened. Thus, the installation space in the axial direction of the torsional vibration damping device 20 can be reduced.

  In each of the embodiments described above, the torsional vibration damping device 20 is interposed between the internal combustion engine of the vehicle and the drive transmission system having the transmission. Any torsional vibration damping device provided in the system 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 each of the above embodiments, the first rotating member includes the cam member 25 and the clutch disk 26, or the cam member 61 and the clutch disk 26, and the second rotating member includes the boss 33 and the torsional vibration damping. The mechanism 23 or the boss 33 and the torsional vibration damping mechanism 62 are configured, but the reverse is also possible.

  Specifically, the second rotating member is composed of the cam member 25 and the clutch disk 26, or the cam member 61 and the clutch disk 26, and the first rotating member is the boss 33 and the torsional vibration damping mechanism 23, or The boss 33 and the torsional vibration damping mechanism 62 may be used.

  As described above, the torsional vibration damping device according to the present invention can change the torsional rigidity between the positive side and the negative side while widening the torsion angle between the first rotating member and the second rotating member. Torsional vibration having an effect and interposed between an internal combustion engine of a vehicle and a transmission of a drive transmission system, wherein the first rotating member and the second rotating member are connected to each other via an elastic member so as to be relatively rotatable. It is useful as an attenuation device.

20 Torsional vibration damping device 21 First rotating member 22 Second rotating member 23, 62 Torsional vibration damping mechanism 25, 61 Cam members 25a, 25b, 61a Cam surface (first cam surface)
25c, 25d, 61b Cam surface (second cam surface)
32 Input shaft 33 Boss 35, 63 Arm member (first mechanism body)
36, 64 arm member (second mechanism main body)
37, 38, 65 Coil spring (first elastic member)
39, 40, 66 Coil spring (second elastic member)
41, 42 Roller member (first sliding member)
43, 44 Roller member (second sliding member)

Claims (5)

A first rotating member, a second rotating member provided on the same axis as the first rotating member, and provided so as to be relatively rotatable with respect to the first rotating member, and provided on the first rotating member A cam member that rotates integrally with the first rotating member, and the second rotating member, and the first rotating member and the second rotating member rotate relative to each other when the first rotating member and the second rotating member rotate relative to each other. A torsional vibration damping device comprising a torsional vibration damping mechanism for damping torsional vibration between a rotating member and the second rotating member,
The cam member has a first cam surface whose curvature changes with a change in torsion angle of the first rotating member and the second rotating member, and the first cam surface with respect to the first cam surface. A second cam surface spaced apart in the axial direction of the rotating member, spaced apart in the circumferential direction of the first rotating member, and having a curvature that changes with a change in the twist angle;
The torsional vibration damping mechanism is attached to the second rotating member, and a first mechanism body that is rotatable integrally with the second rotating member; and a first elastic member provided in the first mechanism body A first sliding member that is provided at a tip of the first elastic member and slides on the first cam surface; and the second rotating member that is attached to the second rotating member. A second mechanism main body that can rotate integrally with the second mechanism main body, a second elastic member provided on the second mechanism main body, and a tip of the second elastic member, on the second cam surface. A torsional vibration damping device comprising a second sliding member that slides.   The torsional vibration damping device according to claim 1, wherein a radius of curvature of the second cam surface is larger than a radius of curvature of the first cam surface. The first elastic member and the second elastic member are composed of coil springs having the same spring rigidity,
When the second rotating member is twisted to the positive side and the negative side with respect to the first rotating member from the neutral state where the twist angle of the first rotating member and the second rotating member is minimum In some cases, the elastic deformation amount of the second elastic member per unit negative twist angle is smaller than the elastic deformation amount of the first elastic member per positive unit twist angle. The torsional vibration damping device according to claim 1, wherein radii of curvature of the first cam surface and the second cam surface are set.   The torsional vibration damping device according to claim 1, wherein the first elastic member and the second elastic member have different spring rigidity.   The first rotating member has a boss to which an input shaft of a transmission of a drive transmission system is connected, and torque is transmitted from the internal combustion engine to the first rotating member. The torsional vibration damping device according to claim 4.

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