JP2013108570A - Torsional vibration damping device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a torsional vibration damping device in which optimum hysteresis torque can be set in accordance with an angle of twist between a rotating member and a cam member.SOLUTION: Disc springs 25 and 26 of the torsional vibration damping device 1 are eccentrically installed in the radial direction of disc plates 7 and 8 with respect to the rotational center of the cam member 2 so that a distance r from a rotation axis of the cam member 2 to a contact point where the cam member 2 comes into contact with the disc springs 25 and 26 via friction plates 23 and 24 becomes longer as the angle of twist between the disc plates 7 and 8 and the cam member 2 becomes larger from a neutral position of the cam member 2, the disc plate 7, and the cam member 2.

Description

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

  Conventionally, a drive source such as an internal combustion engine or an electric motor is connected to 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 a drive transmission system connected to a drive source, for example, a humming noise or a jagged noise is generated by torsional vibration using rotational fluctuation due to torque fluctuation of the internal combustion engine as an excitation source.

  The jagged noise is an abnormal noise called a jagged noise generated when a pair of idling gears of a transmission gear set collides with a torsional vibration generated by a rotational fluctuation caused by a torque fluctuation of an internal combustion engine. 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 rotational torque from the drive source and torsional vibration between the drive source and a drive transmission system having a transmission gear set is absorbed. Torsional vibration damping devices are known.

  As this torsional vibration damping device, for example, a hub connected to an input shaft of a transmission, a disk plate having a clutch disk fastened and released to a flywheel on the drive source side, and the hub and the disk plate are elastically connected. There is one constituted by connecting and elastic members provided at equal intervals in the circumferential direction of the hub and the disk plate (see, for example, Patent Document 1).

  However, since this type of torsional damping attenuation device has a configuration in which the elastic members are provided at equal intervals in the circumferential direction of the hub and the disk plate, the torsion angle of the hub and the disk plate cannot be increased. Jara sound and humming sound cannot be attenuated sufficiently.

  As a torsion damping attenuation device capable of solving such a problem and increasing the torsion angle of rotating members that are rotatable relative to each other, a device described in Patent Document 2 is known.

  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. Are provided between the cam plate and the disc plate, and elastically deformed when the cam member and the disc plate rotate relative to each other.

  In addition, the torsional vibration damping device is provided on the disk plate when one end contacts the cam surface of the cam member and the other end is biased by the elastic member, and the cam member and the disk plate rotate relative to each other. An arm member is provided that transmits rotational torque between the cam member and the disk plate by rotating about the rotation fulcrum and elastically deforming the elastic member.

  In this torsional damping attenuation device, the range of the torsion angle between the cam member and the disk plate can be widened by swinging the arm member as the cam member rotates to elastically deform the elastic member. In a region where the torsion angle between the rotating member 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 torsional rigidity is reduced and minute torsional vibration is generated. Can be attenuated to suppress the generation of a rattling sound.

Further, in a region where the torsion angle between the rotating member and the cam member is large, the torsion angle between the rotating member and the cam member is increased to obtain a high torsional rigidity that increases the torque increase rate.
As a result, large torsional vibrations caused by rotational fluctuations due to torque fluctuations of the internal combustion engine and torsional resonance of the drive transmission system are attenuated, and the jagged noise generated by the collision of the idle gear pairs of the transmission gear set and the drive transmission It is possible to suppress the occurrence of a booming noise due to the torsional resonance of the system.

  By the way, a hysteresis torque generating mechanism is provided in the torsional vibration damping device as in the torsional rigidity. This hysteresis torque generating mechanism generates hysteresis torque by frictional force when one rotating member and the other rotating member rotate relative to each other.

  When the torsional vibration damping device of Patent Document 2 is provided with a hysteresis torque generating member, for example, a disc spring is interposed between the rotating member and the cam member, and the rotating member and the cam are utilized by using the elastic force of the disc spring. It is conceivable that a frictional force is generated between the rotating member and the disc spring when the member rotates relatively.

JP 2006-144861 A WO2011-067815

  However, when the disc spring is provided in the torsional vibration damping device shown in Patent Document 2, since the disc spring has a constant rigidity, the hysteresis torque becomes constant according to the torsion angle between the rotating member and the cam member. End up.

  That is, in a region where the torsion angle between the rotating member and the cam member is small, the torsional rigidity of the elastic member is reduced, and the hysteresis torque is reduced in accordance with the torsional rigidity of the elastic member to attenuate minute torsional vibrations. It is necessary to suppress the generation of rattling noise.

  In a region where the torsion angle between the rotating member and the cam member is large, the torsional rigidity of the elastic member is increased, and the hysteresis torque is increased in accordance with the torsional rigidity of the elastic member, thereby attenuating large torsional vibration. Therefore, it is necessary to suppress the jara sound and the muffled sound.

  However, if the hysteresis torque is constant according to the torsional angle, the region where the elastic member has a small torsional angle between the rotating member and the cam member and the torsional angle between the rotating member and the cam member having a large elastic member rigidity. The hysteresis torque cannot be optimally set in a region where the torque is large.

  In order to suppress the rattling noise, it is conceivable to reduce the rigidity of the disc spring and reduce the hysteresis torque in a region where the torsion angle between the rotating member and the cam member is small. In a region where the torsion angle between the rotating member and the cam member is large, the hysteresis torque becomes small, and there is a possibility that the jagged noise and the booming noise cannot be sufficiently suppressed.

  On the other hand, in order to suppress the noise and the booming noise, it is conceivable to increase the hysteresis torque in a region where the torsion angle between the rotating member and the cam member is large by increasing the rigidity of the disc spring. If is increased, the hysteresis torque increases in a region where the twist angle between the rotating member and the cam member is small, and there is a possibility that the rattling noise cannot be sufficiently suppressed.

  The present invention has been made to solve the above-described conventional problems, and provides a torsional vibration damping device capable of setting an optimum hysteresis torque according to the torsion angle between a rotating member and a cam member. For the purpose.

  In order to achieve the above object, the torsional vibration damping device according to the present invention is (1) an elliptical shape having a cam surface on the outer peripheral portion and configured such that the curvature of the cam surface changes along the circumferential direction. A cam member, a rotating member provided on the same axis as the cam member, and rotatable between the cam member and the rotating member. The rotating member is rotatable between the cam member and the rotating member. An elastic member that is elastically deformed when the member is rotated relative to the other member; one end of the elastic member is in contact with the cam surface of the cam member; the other end is biased by the elastic member; and the cam member and the rotating member are When relative rotation is performed, rotation torque is transmitted between the cam member and the rotation member by rotating about a rotation fulcrum provided on the rotation member and elastically deforming the elastic member. Torsional vibration with arm member An attenuator, comprising a disc spring provided between the rotating member and the cam member so as to be positioned in the axial direction of the rotating member and the cam member, wherein the disc spring includes the cam member The distance from the rotation center axis to the contact point where the cam member and the disc spring come into contact is determined by the twist angle between the cam member and the rotating member from a neutral position where the cam member and the rotating member are not relatively rotated. Is configured to be eccentric with respect to the rotation center of the cam member in the radial direction of the rotation member so as to increase.

  In this torsional vibration damping device, one end portion is in contact with the cam surface of the cam member and the other end portion is urged by the elastic member between the rotating member and the cam member, and the rotating member and the cam member rotate relative to each other. Sometimes, an arm member that transmits rotational torque between the rotating member and the cam member is interposed by rotating about the rotating fulcrum provided on the rotating member and elastically deforming the elastic member. Yes.

  Therefore, as the cam member rotates, the cam member presses the elastic member via the arm member to change the reaction force from the elastic member to the arm member, so that the range of the twist angle between the rotating member and the cam member is reached. Rotating torque can be transmitted 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 in a region where the torsional angle between the rotating member and the cam member is small, the torsional rigidity of the elastic member is reduced and minute torsional vibration is generated. Can be attenuated.
Further, in a region where the torsion angle between the rotating member and the cam member is large, the torsional rigidity of the elastic member can be increased to attenuate a large torsional vibration.

  Further, the torsional vibration damping device is provided with a disc spring between the rotating member and the cam member, and this disc spring has a distance from the rotation center axis of the cam member to a contact point where the cam member and the disc spring contact each other. Installed eccentrically in the radial direction of the rotating member with respect to the rotation center of the cam member so that the cam member increases from the neutral position where the rotating member and the cam member do not rotate relative to each other as the torsion angle with the rotating member increases. Has been.

  For this reason, in a region where the torsion angle between the rotating member and the cam member is small, the moment applied from the disc spring to the cam member by reducing the distance from the rotation center axis of the cam member to the contact point where the cam member and the disc spring come into contact with each other. Can be reduced.

  That is, if the disc spring stiffness is F (constant) and the distance from the rotation center axis of the cam member to the contact point between the cam member and the disc spring is r, the moment M applied from the disc spring to the cam member is F × r. Since the disc spring is interposed between the rotating member and the cam member, when a small moment M is applied to the cam member from the disc spring, the frictional force between the rotating member and the cam member is reduced, and the hysteresis torque is reduced. Get smaller.

  For this reason, in the region where the torsion angle between the rotating member and the cam member is small, it is possible to obtain the torsional characteristics of low rigidity and low hysteresis torque.

On the other hand, in a region where the torsion angle between the rotating member and the cam member is large, the moment M applied from the disc spring to the cam member by increasing the distance from the rotation center axis of the cam member to the contact point where the cam member and the disc spring come into contact with each other. Can be increased.
For this reason, when a large moment M is applied to the cam member from the disc spring, the frictional force between the rotating member and the cam member increases, and the hysteresis torque increases.

  Therefore, in the region where the torsion angle between the rotating member and the cam member is large, it is possible to obtain the torsional characteristics of high rigidity and high hysteresis torque.

  As a result, an optimum hysteresis torque can be set according to the twist angle between the rotating member and the cam member.

  In the torsional vibration damping device of the above (1), (2) the disc spring is formed in a circular shape.

  In this torsional vibration damping device, since the disc spring is configured in a circular shape, the cam member is decentered in the radial direction of the rotating member with respect to the rotation center of the cam member, thereby deviating from the rotation center axis of the cam member. The distance from the neutral position to the contact point where the disc spring contacts can be increased as the torsion angle between the rotating member and the cam member increases.

  Therefore, the moment applied from the disc spring to the cam member can be increased according to the torsion angle between the rotating member and the cam member, and the optimum hysteresis torque can be set according to the torsion angle between the rotating member and the cam member. Can do.

  (1) In the torsional vibration damping device according to (1) or (2) above, (3) the curvature of the cam surface of the cam member increases as the torsion angle between the rotating member and the cam member increases from the neutral position. It is composed of

In this torsional vibration damping device, since the curvature of the cam surface of the cam member increases as the torsion angle between the rotating member and the cam member increases from the neutral position, the range of the torsion angle between the rotating member and the cam member is widened. Thus, the torsional rigidity can be reduced as a whole.
Further, the torsional rigidity of the elastic member can be increased as the torsion angle between the rotating member and the cam member increases.

  In the torsional vibration damping device according to the above (1) to (3), (4) it is configured to include a rolling element that is rotatably provided at one end of the arm member and contacts the cam surface of the cam member. ing.

  In this torsional vibration damping device, a rolling element that comes into contact with the cam surface of the cam member is provided at one end of the arm member, so that the contact pressure between the one end of the arm member and the cam surface of the cam member is prevented from increasing. It is possible to suppress wear between the one end of the arm member and the cam member.

  In the torsional vibration damping device according to the above (1) to (4), (5) the rotating members are disposed on both sides in the axial direction of the cam member, and are fixed to each other at a predetermined interval in the axial direction. A pair of disk plates that rotatably support the arm member via a rotation shaft that constitutes a moving fulcrum, and a first friction plate interposed between one of the disk plates and the cam member And a second friction plate interposed between the other of the disk plates and the cam member, and the disc spring is interposed between one of the disk plates and the first friction plate. A first disc spring that contacts the cam member via the one friction plate, and the second friction plate is interposed between the other of the disk plates and the second friction plate. Through And a one and a second disc spring in contact with the cam member Te.

In this torsional vibration damping device, a disc spring is interposed between one of the disc plates and the first friction plate, and contacts the cam member via the first friction plate. Since the second disc spring is provided between the other plate and the second friction plate and contacts the cam member via the second friction plate, the first disc spring and the second disc spring are provided. The disc spring can urge the cam member so that the cam member is separated from the pair of disk plates, and the friction plate can be brought into frictional contact with the cam member.
For this reason, the friction plate and the cam member are brought into frictional contact, and a hysteresis torque corresponding to the torsion angle between the rotating member and the cam member can be generated.

  In the torsional vibration damping device of the above (1) to (5), (6) an input shaft of a transmission of a drive transmission system is connected to the cam member, and rotational torque of the internal combustion engine is transmitted to the rotating member. It is configured.

  In this torsional vibration damping device, the input shaft of the drive transmission transmission is connected to the cam member, and the rotational torque of the internal combustion engine is transmitted to the rotating member, so that the shift position is changed to neutral and the internal combustion engine is in the idle state. In the region where the torsion angle between the rotating member and the cam member is small as in the case of the above, the torsional characteristics are attenuated by the torsional characteristics of the low rigidity elastic member and the low hysteresis torque disc spring. Generation of sound can be suppressed.

  Further, in a region where the torsion angle between the rotating member and the cam member is large, the torsional characteristics of the highly rigid elastic member and the high hysteresis torque disc spring can be obtained by increasing the torsion angle between the rotating member and the cam member.

  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.

  According to the present invention, it is possible to provide a torsional vibration damping device capable of setting an optimum hysteresis torque according to the torsion angle between the rotating member and the cam member.

It is a figure which shows one Embodiment of the torsional vibration damping device which concerns on this invention, and is a perspective view of a torsional vibration damping device. 1 is a diagram showing an embodiment of a torsional vibration damping device according to the present invention, and is a perspective view of the torsional vibration damping device in a state where one of disk plates is removed. It is a figure which shows one Embodiment of the torsional vibration damping device which concerns on this invention, and is a front view of a torsional vibration damping device. It is a figure which shows one Embodiment of the torsional vibration damping apparatus which concerns on this invention, and is AA direction arrow sectional drawing of FIG. It is a figure which shows one Embodiment of the torsional vibration damping device which concerns on this invention, and is a top view of an arm member. It is a figure which shows one Embodiment of the torsional vibration damping device which concerns on this invention, and is BB direction sectional drawing of FIG. It is a figure which shows one Embodiment of the torsional vibration damping device which concerns on this invention, and is a figure which shows the positional relationship of a cam member and a disc spring. It is a figure which shows one Embodiment of the torsional vibration damping device which concerns on this invention, and is a front view of a torsional vibration damping device when the torsion angle of a disk plate and a boss | hub is +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 boss | hub 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 boss | hub is +90 degrees. It is a figure which shows one Embodiment of the torsional vibration damping device which concerns on this invention, and is a front view of the torsional vibration damping device when the torsion angle of a disk plate and a boss | hub is -45 degrees. It is a figure which shows one Embodiment of the torsional vibration damping device which concerns on this invention, and is a figure which shows the relationship between the twist angle of a torsional vibration damping device, and a torque. It is a figure which shows one Embodiment of the torsional vibration damping device which concerns on this invention, and is a figure which shows the relationship between the hysteresis torque according to the rotational position of a cam member, and r1-r4 dimension.

Hereinafter, embodiments of a torsional vibration damping device according to the present invention will be described with reference to the drawings.
1 to 13 are diagrams showing an embodiment of a torsional vibration damping device according to the present invention.

First, the configuration will be described.
1 to 4, the torsional vibration damping device 1 includes a cam member 2 and a rotating member 3 provided on the same axis as the cam member 2.

  The rotating member 3 receives a rotational torque from an internal combustion engine (not shown) that is a driving source, and the cam member 2 transmits the rotational torque of the rotating member 3 to a transmission of a drive transmission system (not shown). It is like that.

  A pair of coil springs 4 as elastic members are provided between the cam member 2 and the rotating member 3, and the coil springs 4 are compressed when the cam member 2 and the rotating 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 rotational torque of the internal combustion engine is input to the disk plates 7 and 8.

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

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

  As shown in FIG. 3, the pedestal 14 is provided with a protrusion 14a protruding from the pedestal 14, and the other end in the extending direction of the coil spring 4 is fitted to the protrusion 14a. A spring seat 15 is attached to one end of the coil spring 4 in the extending direction, and the other end of the coil spring 4 is a free end.

  Further, an arm member 16 is provided between the coil spring 4 and the cam member 2, and this arm member 16 is located between the disk plates 7 and 8 and is swingably supported on the rotating shaft 9. Has been.

  As shown in FIGS. 5 and 6, a needle bearing 17 is interposed between the rotating shaft 9 and the arm member 16. The needle bearing 17 includes an outer race 17 a attached to the arm member 16, and a needle needle 17 b interposed between the outer race 17 a and the rotation shaft 9.

  In the needle bearing 17, the outer race 17a is rotatable with respect to the rotating shaft 9 via the needle-shaped needle 17b. Therefore, the arm member 16 is rotatable on the rotating shaft 9 via the needle bearing 17. Installed on.

  One end portion of the arm member 16 is formed with projecting pieces 16A and 16B as bifurcated plate-like portions, and the projecting pieces 16A and 16B are connected by a pin 18.

A roller member 19 as a rolling element is rotatably attached to the pin 18. The roller member 19 includes an outer race 19a provided on the outer periphery of the pin 18, a needle bearing including a needle needle 19b interposed between the outer race 19a and the pin 18 (see FIG. 7), and the outer race 19a. The roller 19c is attached to the outer race 19a at the outer periphery, and the roller 19c is rotatable with respect to the pin 18 via a needle bearing.
The roller 19c rotates in contact with the cam surface 2a of the cam member 2, and one end of the arm member 16 contacts the cam surface 2a of the cam member 2 through the roller 19c.

  At the other end of the arm member 16, bifurcated projecting pieces 16 </ b> C and 16 </ b> D are formed, and the projecting pieces 16 </ b> C and 16 </ b> D are connected by a pin 20.

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

The roller 21c comes into contact with the outer peripheral surface of the spring seat 15. The other end of the arm member 16 comes into contact with the outer peripheral surface of the spring seat 15 through the roller 21c.
Further, the cam member 2 has a cam surface 2a whose curvature changes as the twist angle between the disk plates 7 and 8 and the cam member 2 changes.

  In this Embodiment, the cam member 2 has the cam surface 2a comprised so that a curvature might change along the circumferential direction. The curvature of the cam surface 2a is such that the torsion angle between the disk plates 7 and 8 and the cam member 2 is minimum (the torsion angle is approximately 0 °), that is, the neutral position where the disk plates 7 and 8 and the cam member 2 are not twisted. When the torsion angle between the disk plates 7 and 8 and the cam member 2 is increased from the initial position of the cam member 2 at the time of

  For this reason, when the cam member 2 rotates and the position of the cam surface 2a where one end of the arm member 16 abuts is changed, the spring seat 15 is biased by the arm member 16 and the compression amount of the coil spring 4 is reduced. Variable. At this time, the spring seat 15 moves so as to approach and separate from the base 14.

  The arm member 16 is arranged point-symmetrically with respect to the central axis of the disk plates 7 and 8, and the arm member 16 is a cam surface 2a having the same curvature across the central axis of the disk plates 7 and 8. One end 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 torque generating mechanism 22 is interposed between the disk plates 7 and 8 and the cam member 2, and this hysteresis torque generating mechanism 22 includes the friction plates 23 and 24 and the dish. It comprises springs 25 and 26.

  The friction plate 23 as the first friction plate is formed in a disk shape having a predetermined friction coefficient on the surface, and is interposed between the disk plate 7 and the cam member 2. The friction plate 24 as the second friction plate is formed in a disc shape having a predetermined friction coefficient on the surface, and is interposed between the disc plate 8 and the cam member 2.

  The disc spring 25 as the first disc spring is formed in a circular shape, and the disc spring 25 is compressed between the disc plate 7 and the cam member 2 in the axial direction of the disc plate 7 and the cam member 2. It is intervened.

  The disc spring 26 as the second disc spring is formed in a circular shape, and the disc spring 26 is compressed between the disc plate 8 and the cam member 2 in the axial direction of the disc plate 8 and the cam member 2. It is intervened.

  As shown in FIG. 7, the disc springs 25, 26 are distances r from the rotation center axis of the cam member 2 to the contact point where the cam member 2 and the disc springs 25, 26 contact via the friction plates 23, 24. However, the disc with respect to the center of rotation of the cam member 2 is such that the cam member 2, the disc plate 7 and the cam member 2 increase as the torsion angle between the disc plates 7, 8 and the cam member 2 increases from the neutral position. The plates 7 and 8 are installed eccentrically in the radial direction.

  The disc springs 25 and 26 increase the frictional force between the cam member 2 and the friction plates 25 and 26 by urging the cam member 2 in the direction in which the cam member 2 is separated from the disk plates 7 and 8. Thus, the frictional force between the disk plates 7 and 8 and the cam member 2 is increased. As a result, hysteresis torque can be generated between the disk plates 7 and 8 and the cam member 2.

  In FIG. 3, for convenience of explanation, illustration of the friction plates 23 and 24 and the disc spring 25 is omitted, and only the disc spring 26 is illustrated so that the positional relationship between the disc spring 26 and the cam member 2 becomes clear. . The disc spring 26 is provided at the same position as the disc spring 25 with respect to the axial direction of the cam member 2.

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

  8 to 11 show a state where the disk plate 8 is removed. Further, the cam member 2 is twisted to the positive side with respect to the disk plates 7 and 8 when the vehicle is accelerated.

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

  In the torsional vibration damping device 1 of the present embodiment, the relative rotation between the disk plates 7 and 8 and the cam member 2 is small, that is, the torsion angle between the disk plates 7 and 8 and the cam member 2 is small near 0 °. In the state, as shown in FIG. 3, the cam member 2 is positioned at the initial position and rotates integrally with the boss 5.

  At this time, the roller 19c of the arm member 16 is in contact with the cam surface 2a having a small curvature of the cam member 2, and the cam member 2 presses the arm member 16 against the spring seat 15, whereby the coil spring 4 is moved by the cam member 2. Be energized.

  At this time, the arm member 16 uses the reaction force of the coil spring 4 as a fulcrum to press the cam member 2 by the lever principle. Therefore, the rotational torque of the disk plates 7 and 8 is transmitted to the cam member 2 through the coil spring 4 and the arm member 16. For this reason, the rotational torque of the internal combustion engine is transmitted to the input shaft 21 of the transmission, and at this time, the compression amount of the coil spring 4 becomes small.

  For this reason, 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.

  On the other hand, when the rotational fluctuation due to the torque fluctuation of the internal combustion engine is small during acceleration of the vehicle, the fluctuation torque between the disk plates 7 and 8 and the cam member 2 is small. In the clockwise 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. 8 from the state shown in FIG. 19c rolls along the cam surface 2a. For this reason, the one end part of the arm member 16 slides on the cam surface 2a via the roller 19c. FIG. 8 shows a twist angle of + 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 initial position of the cam member 2, one end of the arm member 16 has a roller 19c. When the cam member 2 is pressed against the cam surface 2a of the cam member 2 that gradually increases in curvature, the other end of the arm member 16 moves inward in the radial direction and in the circumferential direction of the disk plates 7 and 8.

  As the cam member 2 rotates in the R1 direction, the other end of the arm member 16 moves inward in the radial direction of the disk plates 7 and 8, thereby bringing the spring seat 15 close to the pedestal 14.

  Further, the other end of the arm member 16 moves along the circumferential outer peripheral surface of the spring seat 15 via the roller 21c, so that the spring seat 15 can be prevented from moving in the circumferential direction.

  As the arm member 16 biases the coil spring 4 in this way, the arm member 16 strongly presses the cam member 2 based on the lever principle by the reaction force of the compressed coil spring 4 and the pivot shaft 9 as a fulcrum. Press with pressure.

  Therefore, 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 torsion angle between the disk plates 7 and 8 and the cam member 2 is further increased from the state shown in FIG. 8, the roller 19c of the arm member 16 rolls along the cam surface 2a as shown in FIG. One end of 16 slides on the cam surface 2a via the roller 19c.

  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 initial position of the cam member 2, one end of the arm member 16 has a roller 19c. Then, the other end of the arm member 16 moves in the radially inward and circumferential directions of the disk plates 7 and 8 when pressed against the cam surface 2a of the cam member 2 having a large curvature.

  As the cam member 2 rotates in the R1 direction, the other end portion of the arm member 16 further moves inward in the radial direction of the disk plates 7 and 8, thereby bringing the spring seat 15 closer to the pedestal 14. Let FIG. 9 shows a twist angle of + 60 °.

  Then, as shown in FIG. 10, when excessive torque is input to the disk plates 7 and 8 from the internal combustion engine, the cam surface 2a gets over the top 2b having the maximum curvature and the disk plates 7 and 8 are moved to the cam member 2. Therefore, the cam member 2 can function as a torque limiter during acceleration of the vehicle. In the present embodiment, when one end of the arm member 16 rides on the top 2b of the cam surface 2a, the torsion angle between the disk plates 7 and 8 and the cam member 2 becomes + 90 ° at the maximum.

  On the other hand, when the vehicle is decelerated, the driving torque of the internal combustion engine is reduced and engine braking occurs, so that rotational torque is input from the input shaft 6 of the transmission to the cam member 2. 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 rotate relative to each other as shown in FIG. 11 from the state shown in FIG. 3, the twist angle between the disk plates 7 and 8 and the cam member 2 becomes large. As the cam member 2 rotates, the roller 19c of the arm member 16 rolls along the cam surface 2a. For this reason, the one end part of the arm member 16 slides on the cam surface 2a via the roller 19c.

  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 initial position of the cam member 2, one end of the arm member 16 has a roller 19c. When the cam member 2 is pressed against the cam surface 2a of the cam member 2 that gradually increases in curvature, the other end of the arm member 16 moves inward in the radial direction and in the circumferential direction of the disk plates 7 and 8.

  Then, as the cam member 2 rotates in the counterclockwise direction (R2 direction), the other end of the arm member 16 moves inward in the radial direction of the disk plates 7 and 8, thereby causing the spring seat 15 to move. Close to the base 14.

  Further, the other end portion of the arm member 16 moves along the circumferential outer peripheral surface of the spring seat 15 via the roller 21c so as not to hinder the spring seat 15 from moving in the circumferential direction. Can do.

  As the arm member 16 biases the coil spring 4 in this way, the arm member 16 strongly presses the cam member 2 based on the lever principle by the reaction force of the compressed coil spring 4 and the pivot shaft 9 as a fulcrum. Press with pressure.

  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.

Thus, the torsional vibration damping device 1 of the present embodiment includes a cam member 2 and a cam member 2 having an elliptical cam surface 2 a that is provided on the outer peripheral portion of the cam member 2 and rotates integrally with the cam member 2. Provided between the cam member 2 and the coil spring 4, one end of which is in contact with the cam surface 2 a and the other end is in contact with the spring seat 15 of the coil spring 4, and is bridged by the disk plates 7 and 8. And an arm member 16 that swings around the moving shaft 9.
Therefore, the torsional rigidity of the torsional vibration damping device 1 can be reduced as a whole by widening the range of torsional angles between the disk plates 7 and 8 and the cam member 2.

  FIG. 12 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 and the output output from the cam member 2 in this embodiment. 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. 12, in this embodiment, the coil spring 4 contracts as the torsion angle of the cam member 2 with respect to the disk plates 7 and 8 increases, so that the pressing force on the cam member 2 by the arm member 16 increases. Become.

  And the output torque becomes large because the pressing force to the cam member 2 by the arm member 16 becomes large. As is apparent from FIG. 12, the rigidity of the coil spring 4 is low in the region where the torsion angle between the disc plates 7 and 8 and the cam member 2 is small, and the torsion angle between the disc plates 7 and 8 and the cam member 2. In a region where is large, the rigidity is high.

  The disc springs 25 and 26 of the torsional vibration damping device 1 according to the embodiment are from the rotation center axis of the cam member 2 to the contact point where the cam member 2 and the disc springs 25 and 26 contact via the friction plates 23 and 24. The distance r is increased with respect to the rotation center of the cam member 2 so that the cam member 2, the disc plate 7, and the cam member 2 become larger from the neutral position as the torsion angle between the disc plates 7, 8 and the cam member 2 increases. The disc plates 7 and 8 are installed eccentrically in the radial direction.

  As shown in FIG. 3, when the disc plates 7 and 8 and the cam member 2 are in the neutral position, the cam member 2 and the disc springs 25 and 26 from the rotation center axis of the cam member 2 The distance r1 to the contact point through which the contact is made is the smallest (see A in FIG. 13).

  Further, as shown in FIG. 8, in the region where the torsion angle between the disk plates 7 and 8 and the cam member 2 is small, the cam member 2 and the disc springs 25 and 26 from the rotation center axis of the cam member 2 are connected to the friction plate 23, The distance r2 to the contact point that contacts via 24 is larger than the distance r1 (see B in FIG. 13).

As shown in FIG. 9, in a region where the torsion angle between the disk plates 7 and 8 and the cam member 2 is larger, the cam member 2 and the disc springs 25 and 26 are connected to the friction plates 23 and 24 from the rotation center axis of the cam member 2. The distance r3 to the contact point that contacts via is larger than the distance r2 (see C in FIG. 13).
Further, as shown in FIG. 10, in a region where the torsion angle between the disk plates 7 and 8 and the cam member 2 is larger, the cam member 2 and the disc springs 25 and 26 from the rotation center axis of the cam member 2 are connected to the friction plate 23. , 24, the distance r4 to the contact point that contacts is greater than the distance r3 (see D in FIG. 13).

  Here, the rigidity of the disc springs 25 and 26 is F (constant), and the cam member 2 and the disc springs 25 and 26 contact the contact point where the cam members 2 and the disc springs 25 and 26 contact via the friction plates 23 and 24. When the distance is r, the moment M applied to the cam member 2 from the disc springs 25 and 26 is F × r.

  Since the disc springs 25 and 26 are interposed between the disc plates 7 and 8 and the cam member 2, the disc springs 25 and 26 are provided in a region where the twist angle between the disc plates 7 and 8 and the cam member 2 is large. Is applied to the friction plates 23 and 24, the frictional force between the cam member 2 and the friction plates 23 and 24 is reduced, and the hysteresis torque between the disk plates 7 and 8 and the cam member 2 is reduced.

  For this reason, in the region where the torsion angle between the disk plates 7 and 8 and the cam member 2 is small, it is possible to obtain the torsion characteristics of low rigidity and low hysteresis torque.

  On the other hand, in a region where the torsion angle between the disk plates 7 and 8 and the cam member 2 is large, the cam member 2 and the disc springs 25 and 26 come into contact with each other via the friction plates 23 and 24 from the rotation center axis of the cam member 2. By increasing the distance r to the point, the moment M applied to the cam member 2 from the disc springs 25 and 26 via the friction plates 23 and 24 can be increased.

  For this reason, when a large moment M is applied to the cam member 2 from the disc springs 25 and 26, the frictional force between the disk plates 7 and 8 and the cam member 2 increases, and the hysteresis torque increases.

Therefore, in a region where the torsion angle between the disk plates 7 and 8 and the cam member 2 is large, it is possible to obtain a torsion characteristic with high rigidity and high hysteresis torque.
As a result, an optimum hysteresis torque can be set according to the twist angle between the disk plates 7 and 8 and the cam member.

  Thus, in the present embodiment, it is possible to set an optimum hysteresis torque according to the torsion angle between the disk plates 7 and 8 and the cam member, and to reduce the torsional rigidity of the coil spring 4 as a whole. Therefore, in a region where the torsion angle between the disk plates 7 and 8 and the cam member 2 is small, minute torsional vibration is attenuated by the torsional characteristics of the low rigidity coil spring 4 and the low hysteresis torque disc springs 25 and 26. Thus, the generation of a rattling sound can be suppressed.

  Further, in a region where the torsion angle between the disc plates 7 and 8 and the cam member 2 is large, the torsion angle between the disc plates 7 and 8 and the cam member 2 is increased to provide a highly rigid coil spring 4 and a disc spring having a high hysteresis torque. The torsional characteristics of 25 and 26 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.

  Further, in the torsional vibration damping device 1 of the present embodiment, since the disc springs 25 and 26 are formed in a circular shape, the disc springs 25 and 26 are arranged on the disc plates 7 and 8 with respect to the rotation center of the cam member 2. By eccentrically in the radial direction, the distances r1 to r4 from the rotation center axis of the cam member 2 to the contact point where the cam member 2 and the disc springs 25 and 26 come into contact with each other, and the disc plates 7 and 8 and the cam from the neutral position. It can be increased as the twist angle with the member 2 increases.

  For this reason, the friction plate can increase the moment M applied to the cam member 2 via the disc springs 25 and 26 via the disc springs 25 and 26 according to the torsion angle between the disc plates 7 and 8 and the cam member 2. The optimum hysteresis torque can be set in accordance with the torsion angle between the cam member 2 and the cam member 2.

Further, in the torsional vibration damping device 1 of the present embodiment, the curvature of the cam surface 2a of the cam member 2 is increased as the torsion angle between the disk plates 7 and 8 and the cam member 2 increases from the neutral position. The torsional rigidity 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.
Further, the torsional rigidity of the coil spring 4 can be increased as the torsional angle between the disk plates 7 and 8 and the cam member 2 increases.

  Further, in the torsional vibration damping device 1 of the present embodiment, the roller member 19 that contacts the cam surface 2a of the cam member 2 is rotatably provided at one end portion of the arm member 16. The contact pressure with the cam surface 2a of the cam member 2 can be prevented from increasing, and wear between the one end portion of the arm member 16 and the cam member 2 can be suppressed.

  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.

  As described above, the torsional vibration damping device according to the present invention has an effect that an optimum hysteresis torque can be set according to the torsion angle between the rotating member and the cam member, and the internal combustion engine of the vehicle and the drive transmission Torsional vibration damping that is interposed between the rotating system and the rotating member and the cam member so that the rotating torque is transmitted between the rotating member and the cam member. It is useful as a device.

DESCRIPTION OF SYMBOLS 1 Torsional vibration damping device 2 Cam member 2a Cam surface 3 Rotating member 4 Coil spring (elastic member)
6 Input shaft 7, 8 Disc plate (rotating member)
9 Rotating shaft (Rotating fulcrum)
14 pedestal 16 arm member 19 roller member (rolling element)
23 Friction plate (first friction plate)
24 Friction plate (second friction plate)
25 Disc spring (first disc spring)
26 Disc spring (second disc spring)

Claims (6)

An elliptical cam member configured to have a cam surface on an outer peripheral portion, and the curvature of the cam surface varies 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 rotational torque between the cam member and the rotating member,
A disc spring provided between the rotating member and the cam member so as to be positioned in the axial direction of the rotating member and the cam member;
The disc spring has a distance from a rotation center axis of the cam member to a contact point where the cam member and the disc spring come into contact with each other from a neutral position where the cam member and the rotary member are not relatively rotated. The torsional vibration damping device is installed eccentrically in the radial direction of the rotating member with respect to the rotation center of the cam member so that the torsion angle between the rotating member and the rotating member increases.   The torsional vibration damping device according to claim 1, wherein the disc spring is formed in a circular shape.   The torsional vibration damping device according to claim 1 or 2, wherein a curvature of a cam surface of the cam member increases as a torsion angle between the rotating member and the cam member increases from the neutral position. .   4. The rolling device according to claim 1, further comprising a rolling element that is rotatably provided at one end of the arm member and contacts the cam surface of the cam member. 5. Torsional vibration damping device. The rotating members are arranged on both sides of the cam member in the axial direction, are fixed to each other at a predetermined interval in the axial direction, and rotate the arm member via a rotating shaft constituting the rotating fulcrum portion. A pair of disc plates supported freely, a first friction plate interposed between one of the disc plates and the cam member, and interposed between the other of the disc plates and the cam member. A second friction plate,
The disc spring is interposed between one of the disc plates and the first friction plate, the first disc spring contacting the cam member via the one friction plate, and the disc plate 2. A second disc spring interposed between the other friction plate and the second friction plate and contacting the cam member via the second friction plate. The torsional vibration damping device according to claim 4.   6. The method according to claim 1, wherein an input shaft of a drive transmission transmission is connected to the cam member, and the rotational torque of the internal combustion engine is transmitted to the rotating member. The torsional vibration damping device described.

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