JP2011241919A - Torsional vibration damping device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To restrain torsional resonance of a driving system in a low-speed rotational region during acceleration and restrain torsional vibration with increasing a damping force during deceleration by setting an optimum hysteresis torque.SOLUTION: The torsional vibration damping device 10 includes: cup members 11, 12; a coil spring 23 whose one end is coupled to the cup member 11 and whose other end is coupled to the cup member 12 and which has an elastic force in the direction of a rotational axis L and a rotational direction when the cup member 12 is distorted to the positive side and to the negative side relative to the cup member 11; and a screwing friction part 26 which is provided between the cup members 11 and 12 and relatively moves the cup members 11 and 12 under a frictional contact state in the direction of the rotational axis L by screwing the cup members 11 and 12 with each other. Friction coefficients of one slope and the other slop of a male screw 27 of the screwing friction part 26 are different from each other.

Description

  The present invention relates to a torsional vibration damping device, and more particularly to a torsional vibration of a drive system that is provided in a drive system such as a vehicle and connects a first rotating member and a second rotating member via an elastic member. The present invention relates to a torsional vibration damping device designed to dampen.

  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 system having a transmission or the like, and power is transmitted from the drive source to the wheel via the drive system. However, in a drive system connected to a drive source, for example, a humming noise or a jagged noise is generated by torsional vibration using a rotational fluctuation due to a torque fluctuation of an internal combustion engine as a vibration 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 system that uses torque fluctuation of the internal combustion engine as an excitation force, and the torsional resonance of the drive system is usually in a steady region (for example, In the case of an FF vehicle, it exists at a low vehicle speed when the rotational speed of the internal combustion engine is around 2500 rpm).

  For this reason, a torsional vibration damping device is provided between the internal combustion engine and the drive system, and rotational fluctuations of the internal combustion engine are absorbed by the torsional vibration damping device so as to absorb the torsional vibration of the drive system.

  In this conventional torsional vibration damping device, a first rotating member fastened to and released from a flywheel, a second rotating member connected to an input shaft extending from a transmission, and a first rotating member are rotated in a rotational direction. And a coil spring that is elastically connected to the coil spring (see, for example, Patent Document 1).

  The first rotating member includes a clutch disk and a pair of side plates fixed to the inner peripheral side of the clutch disk. Moreover, the 2nd rotation member is comprised from the hub, This hub is comprised from the boss | hub which carries out a spline fitting to the outer peripheral part of a shaft, and the flange extended to a radial direction outward from a boss | hub.

  The coil spring is supported by a plurality of spring housing holes formed in the flange and a spring housing portion formed in the pair of side plates so as to face the spring housing holes.

  When the pair of side plates and the hub rotate relative to each other, the coil spring is compressed between the pair of side plates and the hub in the circumferential direction of the side plate. The coil spring absorbs the torsional vibration in the circumferential direction input from the pair of side plates to the hub, and the generation of the jagged noise is suppressed.

  In addition, by providing a hysteresis mechanism composed of a thrust member between the hub and the pair of side plates, a hysteresis torque based on friction is generated between the hub and the pair of side plates, thereby torsional resonance of the drive system. This suppresses the indoor noise that becomes noticeable at low vehicle speeds.

  By the way, the characteristics of the rotational fluctuation of the internal combustion engine are that the rotational torque of the internal combustion engine is transmitted from the pair of side plates to the hub, and the hub rotates to the positive side with respect to the pair of side plates. It is known that torque is transmitted to the pair of side plates and the hub is decelerated when the hub rotates to the negative side with respect to the pair of side plates.

  FIG. 11 is a diagram showing the rotational fluctuation of the internal combustion engine during acceleration and deceleration. As shown in FIG. 11, the rotational fluctuation of the internal combustion engine during acceleration is large in the low speed rotation area of the internal combustion engine, and the rotational fluctuation of the internal combustion engine during deceleration is large in the high speed rotation area of the internal combustion engine.

  For this reason, the torsional resonance of the drive system in the low speed rotation region is suppressed by increasing the hysteresis torque of the torsional vibration damping device near the torsional resonance point during acceleration, and the torsional resonance in the high speed rotation region where the rotational fluctuation of the internal combustion engine is large during deceleration It is necessary to suppress torsional vibration by increasing the damping force by reducing the hysteresis torque of the vibration damping device.

JP 2006-144861 A

  However, in such a conventional torsional vibration damping device, since the same hysteresis torque is set during acceleration and deceleration, when the hysteresis torque is increased, it is driven in the low speed rotation region during acceleration. Although the torsional resonance of the system can be attenuated, the torsional vibration cannot be sufficiently attenuated during deceleration.

  Also, when the hysteresis torque is reduced to absorb the torsional vibration during deceleration, the torsional vibration increases due to the torsional resonance of the drive system near the resonance point during acceleration (shown by a broken line in FIG. 12). May occur.

  The present invention has been made to solve the above-described conventional problems, and provides an optimum hysteresis torque when the second rotating member is twisted to the positive side and the negative side with respect to the first rotating member. Provided is a torsional vibration damping device that can suppress the torsional resonance of the drive system in the low-speed rotation region during acceleration and can suppress the torsional vibration by increasing the damping force during deceleration. For the purpose.

  In order to achieve the above object, a torsional vibration damping device according to the present invention is provided with (1) a first rotating member that supports first power transmission means, and a first rotating member that faces the first rotating member. A second rotating member that supports two power transmission means and is relatively movable in the rotational axis direction and the rotating direction of the first rotating member, and one end portion connected to the first rotating member; An end portion is connected to the second rotating member, and the second rotating member is twisted to the positive side and to the negative side with respect to the first rotating member. An elastic member having an elastic force in the rotation direction, and provided between the first rotating member and the second rotating member, and screwed together to thereby form the first rotating member and the second rotating member. Allows relative movement in the frictional contact state in the direction of the rotation axis A hysteresis mechanism having a threaded friction part, wherein the threaded friction part is provided on a first screw part provided on the first rotating member and on the second rotating member, A second threaded portion that is screwed to the first threaded portion, and a coefficient of friction between one slope and the other slope of at least one of the first threaded portion and the second threaded portion. And the elastic member is configured such that when the second rotating member is twisted to the positive side with respect to the first rotating member, the one inclined surface of the thread of the first screw portion and the first The slope of the thread of the second threaded portion facing one slope of the thread of the threaded portion is in frictional contact, and the second rotating member is twisted to the negative side with respect to the first rotating member. In the case of the other slope of the thread of the first screw portion and the other slope of the thread of the first screw portion. And the slope of the thread of the second threaded portion which direction is composed of what is positioned in frictional contact.

  In the torsional vibration damping device, when the second rotating member is twisted to the positive side with respect to the first rotating member, for example, one slope of the thread of the first screw portion having a large friction coefficient and the first Hysteresis torque (friction resistance) can be increased by frictional contact between the slope of the second threaded portion facing the one slope of the threaded portion of the second threaded portion.

  In addition, when the second rotating member is twisted to the negative side with respect to the first rotating member, the other inclined surface of the thread of the first screw portion and the screw thread of the first screw portion having a small friction coefficient. The hysteresis torque can be reduced by the frictional contact between the slope of the second threaded portion facing the other slope.

  Since the magnitude of the hysteresis torque can be changed between the positive side and the negative side in this way, when the second rotating member is accelerated to the positive side with respect to the first rotating member, when passing through the torsional resonance point Thus, the torsional resonance of the drive system can be suppressed, and the generation of a booming noise can be suppressed.

  Further, at the time of deceleration where the second rotating member is twisted to the negative side with respect to the first rotating member, the torsional vibration of the drive system can be damped, and the jagged noise generated by collision of the idle gear pair of the transmission gear set. Can be suppressed.

  In the torsional vibration damping device described in (1) above, (2) the elastic member is configured to rotate the first rotation when the second rotating member is twisted to the positive side with respect to the first rotating member. One force is applied between the first rotating member and the second rotating member in the direction in which the member and the second rotating member are moved closer to or away from the rotation axis direction, and When the second rotating member is twisted to the negative side with respect to the first rotating member, the first rotating member and the second rotating member are moved closer to or away from the rotation axis direction. It is comprised from what is arrange | positioned so that the other force of these may be applied between a said 1st rotation member and a said 2nd rotation member.

  The elastic member of the torsional vibration damping device is configured such that, for example, when the second rotating member is twisted to the positive side with respect to the first rotating member, the first rotating member and the second rotating member are in the direction of the rotation axis. By arranging between the first rotating member and the second rotating member so that a compressive force is applied in a direction in which the first screw member and the first screw member have a large friction coefficient, The second rotating member can increase the hysteresis torque by frictionally contacting the inclined surface of the second threaded portion facing the one inclined surface of the threaded portion of the first rotating member, and the second rotating member can be the first rotating member. When the first rotating member and the second rotating member are twisted to the negative side, a tensile force is applied in a direction in which the first rotating member and the second rotating member are brought close to the rotation axis direction. By using the tension force of the elastic member Hysteresis torque by friction-contacting the other slope of the thread of the first thread with a small friction coefficient and the slope of the thread of the second thread facing the other slope of the thread of the first thread Can be reduced.

  In the torsional vibration damping device according to (1) or (2) above, (3) the elastic member is configured such that when the second rotating member is twisted to the positive side with respect to the first rotating member, When the first rotating member and the second rotating member are displaced in the first direction which is one of the directions approaching or separating from the rotation axis direction, the second rotating member is the other. Is applied between the first rotating member and the second rotating member, and the second rotating member is twisted to the negative side with respect to the first rotating member. When the first rotation member and the second rotation member are displaced in the rotation axis direction in the second direction, a force in the first direction is applied to the first rotation member and the second rotation. It is comprised from what is arrange | positioned so that it may take between between members.

  The elastic member of the torsional vibration damping device is configured so that, for example, when the second rotating member is twisted to the positive side with respect to the first rotating member, the first rotating member and the second rotating member are in the rotation axis direction. Is disposed in such a manner that a compressive force is applied between the first rotating member and the second rotating member as a force in the second direction separated in the rotation axis direction by being displaced in the first direction adjacent to the first rotating member. By using the compressive force of the elastic member, the first screw portion of the first screw portion having a large coefficient of friction and the second screw portion facing the one inclined surface of the screw thread of the first screw portion. When the second rotating member is twisted to the negative side with respect to the first rotating member, the first rotating member and the second rotating member can be increased. Is displaced in a second direction that is spaced apart in the direction of the rotation axis. By arranging the pulling force between the first rotating member and the second rotating member as the force in the first direction close to the rotation axis direction, friction is generated by using the pulling force of the elastic member. Hysteresis torque is obtained by friction-contacting the other inclined surface of the first screw portion with a small coefficient and the inclined surface of the second screw portion facing the other inclined surface of the first screw portion. Can be small.

  In the torsional vibration damping device according to the above (1) to (3), (4) the first rotating member protrudes in the direction of the rotation axis from the first disc portion and the first disc portion. And the second rotating member protrudes in the direction of the rotation axis from the second disc portion and the first cylindrical portion. And a second cylindrical portion opposed to the outer peripheral portion or the inner peripheral portion of the first cylindrical portion, and the threaded friction portion of the hysteresis mechanism is formed on the outer peripheral portion or the inner peripheral portion of the first cylindrical portion. The first screw part and the second screw part formed on the inner peripheral part or the outer peripheral part of the second cylindrical part so as to be screwed into the first screw part. ing.

  In the torsional vibration damping device, the first rotating member and the second rotating member are formed in a cup shape, the first screw portion is formed on the outer peripheral portion or the inner peripheral portion of the first cylindrical portion, and the second For example, the second rotating member is rotated to the positive side with respect to the first rotating member because the second threaded portion that is screwed into the first threaded portion is formed on the inner peripheral portion or the outer peripheral portion of the cylindrical portion. When this is done, the compressive force of the elastic member may be used to frictionally contact one slope of the thread of the first thread portion with a large coefficient of friction and one slope of the thread of the second thread portion. In addition, when the second rotating member is rotated to the negative side with respect to the first rotating member, the other screw thread of the first screw portion having a small friction coefficient is utilized by using the tensile force of the elastic member. The slope and the other slope of the thread of the second screw portion can be brought into frictional contact.

  As a result, the magnitude of the hysteresis torque can be changed between the positive side and the negative side by the torsional vibration damping device having a simple configuration, and an increase in manufacturing cost of the torsional vibration damping device can be prevented.

  In the torsional vibration damping device according to the above (1) to (4), (5) the elastic member is configured to be inclined in the rotation axis direction.

  In this torsional vibration damping device, since the elastic member is inclined in the rotation axis direction, the elastic member is used when the second rotating member is twisted to the positive side and to the negative side with respect to the first rotating member. By compressing or extending in the rotational direction, it is possible to transmit rotational torque while attenuating torsional vibration between the first rotating member and the second rotating member.

  Further, in the case where the second rotating member is twisted to the positive side with respect to the first rotating member and the case where the second rotating member is twisted to the negative side, the compression force when the elastic member is compressed in the rotation direction or the tension when the elastic member is extended. The screw thread between the first screw portion and the second screw portion of the screw-like friction portion by using the force as the compressive force and tensile force in the rotation axis direction of the first rotating member and the second rotating member. Can be switched between a friction contact surface with a large friction coefficient and a friction contact surface with a small friction coefficient, and the hysteresis torque can be made different between acceleration and deceleration.

  As a result, at least one elastic member can be used to generate an elastic force in both the rotational axis direction and the rotational direction, simplifying the configuration of the torsional vibration damping device and reducing the manufacturing cost of the torsional vibration damping device. be able to.

  (6) In the torsional vibration damping device described in (1) to (4) above, (6) one end of the elastic member is connected to the first rotating member, and the other end is the second rotating member. And extending in a direction substantially perpendicular to the direction of the rotation axis, and when the second rotating member is twisted to the positive side and to the negative side with respect to the first rotating member, A first elastic member that compresses or extends in the rotation direction, and one end portion connected to the first rotation member and the other end portion connected to the second rotation member so as to be substantially in the same direction as the rotation axis direction. A second elastic member extending in the direction of the rotation axis 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 It is comprised including.

  In this torsional vibration damping device, the elastic member has one end connected to the first rotating member and the other end connected to the second rotating member, and extends in a direction substantially perpendicular to the rotational axis direction. The second rotating member has the first elastic member that compresses or extends in the rotational direction when twisted to the positive side and when twisted to the negative side with respect to the first rotating member. When the member is twisted to the positive side or the negative side with respect to the first rotating member, the first elastic member causes the rotational torque while attenuating torsional vibration between the first rotating member and the second rotating member. Can communicate.

  Further, one end is connected to the first rotating member and the other end is connected to the second rotating member and extends in substantially the same direction as the rotation axis direction, and the second rotating member is rotated in the first direction. Since it has the 2nd elastic member which compresses or expands in the direction of a rotation axis when it twists to the positive side and the case where it twists to the negative side to the member, the 2nd rotation member is with respect to the 1st rotation member When the first elastic member and the second rotary member are twisted to the positive side or the negative side, the second elastic member is compressed or extended by moving the first rotary member and the second rotary member in the direction approaching or separating from the rotation axis direction. Can do.

  By using the compressive force or tensile force of the second elastic member, the contact positions of the first and second screw portions of the threaded friction portion and the slopes of the thread threads of the second screw portion are on the positive side and the negative side. The friction contact surface can be changed between a friction contact surface having a large friction coefficient and a friction contact surface having a small friction coefficient.

  For this reason, it is possible to increase the hysteresis torque when the second rotating member is twisted to the positive side with respect to the first rotating member, and it is possible to reduce the hysteresis torque when the second rotating member is twisted to the negative side.

  In the torsional vibration damping device according to (6) above, (7) at least one of the one end portion and the other end portion of the second elastic member is relative to the first rotating member or the second rotating member. It is comprised from what is provided slidably in a rotation direction.

  In this torsional vibration damping device, at least one of the one end and the other end of the second elastic member is provided to be slidable in the rotation direction with respect to the first rotating member and the second rotating member. When the second rotating member is twisted with respect to the first rotating member, the second elastic member slides relative to the first rotating member or the second rotating member, so that the second elastic member The member can be compressed and expanded only in the direction of the rotation axis.

  For this reason, the compressive force and the pulling force of the second elastic member can be efficiently applied in the direction in which the first rotating member and the second rotating member are close to or separated from each other in the rotation axis direction.

  As a result, it is possible to reliably increase the hysteresis torque when the second rotating member is twisted to the positive side with respect to the first rotating member, and to reliably reduce the hysteresis torque when the second rotating member is twisted to the negative side. be able to.

  According to the present invention, it is possible to set an optimum hysteresis torque when the second rotating member is twisted positive and negative with respect to the first rotating member. It is possible to provide a torsional vibration damping device that can suppress torsional resonance of the drive system and that can suppress torsional vibration by increasing the damping force during deceleration.

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 showing a 1st embodiment of a torsional vibration damping device concerning the present invention, and is a front view of a torsional vibration damping device in the state where cup member 12 was removed. 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 side surface sectional drawing of the cup member. BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, (a) shows the state which the inclined surface of the internal thread contacted the inclined surface of the external thread with a large friction coefficient, (b) These are figures which show the state in which the slope of the internal thread was friction-contacted with the slope of the external thread with a small friction coefficient. 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 of the coil spring at the time of acceleration. 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 of the coil spring at the time of deceleration. 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 and hysteresis of a torsional vibration damping device when a coil spring is twisted to the positive side and the negative side. 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 of the state which removed the cup member 12. FIG. It is a figure which shows 2nd Embodiment of the torsional vibration damping device which concerns on this invention, and is the BB direction arrow directional cross-sectional view of the state which attached the cup member 12 to the cup member 11. FIG. 1 is a diagram illustrating a first embodiment of a torsional vibration damping device according to the present invention, and is a diagram illustrating a relationship between rotational fluctuations and rotational speeds of an internal combustion engine during acceleration and deceleration. FIG. 1 is a diagram illustrating a first embodiment of a torsional vibration damping device according to the present invention, and is a diagram illustrating a relationship between a rotational fluctuation of an internal combustion engine during acceleration and the rotational speed of the internal combustion engine, and a portion indicated by a broken line is a conventional portion When the torsional vibration damping device is used, the torsional vibration is increased due to the torsional resonance of the drive system.

Hereinafter, embodiments of a torsional vibration damping device according to the present invention will be described with reference to the drawings.
(First embodiment)
1 to 8, 11, and 12 are views showing a first embodiment of a torsional vibration damping device according to the present invention.

First, the configuration will be described.
In the present embodiment, an example in which the torsional vibration damping device 10 is applied to the clutch device 1 will be described.

  1 to 3, the torsional vibration damping device 10 includes a bottomed cylindrical cup member 11 as a first rotating member and a bottomed cylindrical cup member 12 as a second rotating member, The cup member 11 and the cup member 12 are rotatable with respect to the rotation axis L.

  The cup member 11 includes a disk part 13 as a first disk part and a cylindrical part 14 as a first cylindrical part protruding in the direction of the rotation axis L from the radial outer end of the disk part 13. The cup member 12 serves as a second cylindrical part that protrudes in the direction of the rotation axis L from the radial outer end of the disk part 15 as a second disk part and faces the outer peripheral part of the cylindrical part 14. The cylindrical portion 16 is provided.

  An inner peripheral portion of an annular cushioning plate 17 is attached to the outer peripheral portion of the cup member 11, and annular friction members 18a and 18b are fixed to both sides in the axial direction of the cushioning plate 17 via rivets (not shown). ing. In addition, the cushioning plate 17 should just be attached to the outer peripheral part of the cup member 11 by welding, bolting, etc. FIG. The cushioning plate 17 and the friction materials 18a and 18b constitute power transmission means.

  The friction materials 18a and 18b are located between a flywheel (not shown) fixed to the crankshaft of the internal combustion engine and a pressure plate of a clutch cover bolted to the flywheel. The friction materials 18a and 18b are pressure plates. The rotational torque of the internal combustion engine is input to the cup member 11 by being frictionally engaged with the flywheel and the pressure plate.

  Further, when a clutch pedal (not shown) is depressed, the pressure plate releases the pressing of the friction materials 18a and 18b, and the friction materials 18a and 18b are separated from the flywheel. Is not entered.

  A boss 20 is attached to the radially inner peripheral portion of the cup member 12, and an input shaft 25 of a transmission as a second power transmission means is spline fitted to the inner peripheral portion of the boss 20. Yes.

  In addition, spring sheets 21 a and 21 b are attached to the radial outer peripheral portion of the disc portion 13 of the cup member 11, and spring sheets 22 a and 22 b are attached to the radial outer peripheral portion of the disc portion 15 of the cup member 12. One end of coil springs 23 and 24 as elastic members is attached to the spring seats 21a and 21b, and the other end of the coil springs 23 and 24 is attached to the spring seats 22a and 22b. Yes. In FIG. 2, the spring seats 22 a and 22 b attached to the cup member 12 are hatched.

  The spring seats 21 a, 21 b, 22 a, 22 b have end windings corresponding to one or two turns at both ends in the circumferential direction of the coil springs 23, 24. Both ends are seated, and one end and the other end of the coil springs 23, 24 are engaged with the end windings, thereby preventing the coil springs 23, 24 from rotating and the coil springs 23, 24 from the spring seat 21a, It can be firmly attached to 21b, 22a, 22b. The coil springs 23, 24 may be fixed to the spring seats 21a, 21b, 22a, 22b by welding or the like.

  The coil spring 23 is interposed between the cup member 11 and the cup member 12 so as to be inclined in the direction of the rotation axis L, and the coil spring 24 is inclined so as to be inclined in the direction of the rotation axis L. The coil springs 23 and 24 intersect the direction perpendicular to the rotation axis L, that is, the vertical direction in FIG. In FIG. 3, the coil spring 24 is shown in phantom so that the positional relationship between the coil spring 23 and the coil spring 24 is clear.

  The coil springs 23 and 24 extend in the rotation direction of the disc portion 13 of the cup member 11 and the disc portion 15 of the cup member 12, and elastically connect the cup members 11 and 12 in the rotation direction. ing.

  In the present embodiment, when the cup member 12 is twisted to the positive side (R2 direction in FIG. 2, that is, counterclockwise direction) with respect to the cup member 11, the coil springs 23 and 24 are compressed, so that the coil springs are compressed. Reference numerals 23 and 24 transmit rotational torque from the cup member 11 to the cup member 12 while absorbing vibration between the cup member 11 and the cup member 12.

  Further, when the cup member 12 is twisted to the negative side (R1 direction in FIG. 2, that is, the clockwise direction) with respect to the cup member 11, the coil springs 23 and 24 are extended, whereby the coil springs 23 and 24 are cupped. A rotational torque is transmitted between the member 11 and the cup member 12 while absorbing vibration.

  That is, the coil springs 23 and 24 compress when the cup member 12 is twisted to the positive side with respect to the cup member 11 and expand when the cup member 12 is twisted to the negative side. Rotational torque is transmitted while absorbing vibration.

  The cup member 12 is twisted to the positive side with respect to the cup member 11 when the vehicle is accelerated, and the cup member 12 is twisted to the negative side with respect to the cup member 11 is caused by engine braking. When the vehicle is decelerating.

  3 to 5, a threaded friction part 26 constituting a hysteresis mechanism 30 is provided between the outer peripheral part of the cylindrical part 14 and the inner peripheral part of the cylindrical part 16, and this threaded friction part. 26 is a male screw 27 as a first screw portion formed on the outer peripheral portion of the cylindrical portion 14 and a female screw as a second screw portion formed on the inner peripheral portion of the cylindrical portion 16 and screwed into the male screw 27. The cup member 11 and the cup member 12 are configured to be relatively movable in a frictional contact state in the rotation axis L direction.

  The cylindrical portion 14 may be provided so as to face the outer peripheral portion of the cylindrical portion 16. In this case, a female screw 28 is formed on the inner peripheral portion of the cylindrical portion 14, and a male screw 27 is formed on the outer peripheral portion of the cylindrical portion 16.

  As shown in FIGS. 5A and 5B, the friction coefficient of one slope 27a of the thread of the male screw 27 is larger than the friction coefficient of the other slope 27b. The friction coefficient with the inclined surface 27b is set so that the friction coefficient varies depending on the surface treatment (unevenness processing or coating of the friction material) between the one inclined surface 27a and the other inclined surface 27b or the application of the friction material. ing.

  In the present embodiment, the coil springs 23 and 24 are interposed between the cup member 11 and the cup member 12 so as to be inclined in the direction of the rotation axis L, and the coil springs 23 and 24 are inserted into the cup member 12. Is twisted to the positive side with respect to the cup member 11, the one inclined surface 27 a of the male screw 27 and the one inclined surface 28 a of the thread of the female screw 28 opposed to the inclined surface 27 a are in frictional contact, and the cup member 12. Is twisted to the negative side with respect to the cup member 11, the cup member 11 and the cup member 12 so that the other inclined surface 27b of the male screw 27 and the other inclined surface 28b of the female screw 28 opposed to the inclined surface 27b are in frictional contact. Will be placed between.

  That is, the coil springs 23 and 24 of the present embodiment are arranged in a direction that separates the cup member 11 and the cup member 12 in the direction of the rotation axis L when the cup member 12 is twisted to the positive side with respect to the cup member 11. A compressive force, which is a force, is applied between the cup member 11 and the cup member 12, and when the cup member 12 is twisted to the negative side with respect to the cup member 11, the cup member 11 and the cup member 12 are moved in the direction of the rotation axis L. It is arranged between the cup member 11 and the cup member 12 so that a pulling force which is a force in a direction to approach the cup member 11 is applied between the cup member 11 and the cup member 12.

  Further, the coil springs 23 and 24 of the present embodiment are configured such that when the cup member 12 is twisted to the positive side with respect to the cup member 11, the cup member 11 and the cup member 12 are first in the direction of the rotation axis L. Is displaced between the cup member 11 and the cup member 12, and the cup member 12 is applied to the cup member 11. When the cup member 11 and the cup member 12 are displaced in the extension direction which is the second direction with respect to the rotation axis L direction, the tensile force which is the force in the first direction is It is arranged between the cup member 11 and the cup member 12 so that (biasing force) is applied between the cup member 11 and the cup member 12.

  For this reason, at the time of acceleration of the vehicle that transmits power from the cup member 11 to the cup member 12, the cup member 11 rotates in the R1 direction and the cup member 12 is on the positive side with respect to the cup member 11 (R2 direction in FIG. 2). When the cup member 12 is twisted, the cup member 12 rotates in the R2 direction via the male screw 27 and the female screw 28, so that the cup member 11 approaches the cup member 12 in the rotation axis L direction.

  At this time, the compression of the coil springs 23 and 24 causes the cup member 11 to be urged away from the cup member 12 in the direction of the rotation axis L by the compression force of the coil springs 23 and 24. One slope 28a of the thread of the female screw 28 is in frictional contact with one slope 27a having a larger friction coefficient than the other slope 27b of the thread.

  In addition, when the vehicle that transmits power from the cup member 12 to the cup member 11 is decelerated, the cup member 11 rotates in the R2 direction so that the cup member 12 is on the negative side (R1 direction in FIG. 2). When twisted, the cup member 12 is rotated in the R1 direction via the female screw 28 and the male screw 27, so that the cup member 12 is separated from the cup member 11 in the rotation axis L direction.

  At this time, since the coil springs 23 and 24 are extended, the cup member 12 is biased so as to be close to the rotation axis L direction from the cup member 11 by the pulling force of the coil springs 23 and 24. The other inclined surface 28b of the thread of the female screw 28 is in frictional contact with the other inclined surface 27b having a smaller friction coefficient than the one inclined surface 27a of the thread.

  For this reason, during the acceleration of the vehicle, one inclined surface 28a of the thread of the female screw 28 is brought into frictional contact with one inclined surface 27a of the male screw 27 having a large friction coefficient. The threaded friction portion 26 is configured such that the other inclined surface 28 b of the female screw 28 is in frictional contact with the other inclined surface 27 b of the screw 27.

  As a result, at the time of acceleration of the vehicle in which the cup member 12 is twisted to the positive side with respect to the cup member 11, the sliding resistance (frictional force) between the cup member 11 and the cup member 12 is increased, and the cup member 12 is moved to the cup member 11. On the other hand, at the time of deceleration that is twisted to the negative side, the sliding resistance of the cup member 11 and the cup member 12 becomes small.

  Thus, in this Embodiment, the magnitude | size of the hysteresis torque (friction resistance) of the cup member 11 and the cup member 12 at the time of acceleration and deceleration can be varied.

Next, the operation will be described.
The friction members 18 a and 18 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 cup member 11. At this time, when the rotational torque for contracting the coil springs 23 and 24 is not applied to the torsional vibration damping device 10, the relative rotational angle between the cup member 11 and the cup member 12 is substantially zero.

  From this state, the driving torque (rotational torque) of the internal combustion engine is transmitted to the cushioning plate 17 of the torsional vibration damping device 10 via the friction members 18a and 18b, and the driving torque is transmitted to the cup member 11 connected to the cushioning plate 17. The At this time, when a rotational torque sufficient to contract the coil springs 23 and 24 is applied to the torsional vibration damping device 10, the cup member 12 is twisted with respect to the cup member 11.

  At this time, the rotational fluctuation due to the torque fluctuation of the internal combustion engine applied to the torsional vibration damping device 10 is transmitted to the input shaft 25 of the transmission while being buffered between the cup member 11 and the cup member 12 due to the contraction of the coil springs 23 and 24. Is done.

  Next, an operation when the cup member 12 is twisted to the positive side (R2 direction) with respect to the cup member 11 and an operation when the cup member 12 is twisted to the negative side (R1 direction) will be described. Here, the rotational direction of the cup member 11 when the rotational torque from the internal combustion engine is transmitted to the torsional vibration damping device 10 is defined as the R1 direction.

  When the rotational fluctuation of the internal combustion engine increases during acceleration of the vehicle, the relative rotation between the cup member 11 and the cup member 12 increases, that is, the torsion angle increases, and the cup member 12 twists toward the positive side with respect to the cup member 11. As a result, the coil springs 23 and 24 are compressed to transmit rotational torque from the cup member 11 to the cup member 12 via the coil springs 23 and 24.

  When the twist angle between the cup member 11 and the cup member 12 increases, the cup member 12 rotates relative to the cup member 11 in the R2 direction as the cup member 11 rotates in the R1 direction. As apparent from the above operation, the friction members 18a and 18b and the cushioning plate 17 constituting the first power transmission means transmit torque from the cup member 11 to the cup member 12 when the vehicle is accelerated.

  When the cup member 11 rotates in the R1 direction and the cup member 12 is twisted to the positive side with respect to the cup member 11 during acceleration, the cup member 12 is connected to the cup member 11 via the male screw 27 and the female screw 28. By rotating along, the cup member 11 approaches the cup member 12 in the rotation axis L direction.

  At this time, since the coil springs 23 and 24 are compressed as shown in FIG. 6, the cup member 11 is urged so as to be separated from the cup member 12 in the direction of the rotation axis L by the compression force of the coil springs 23 and 24. Therefore, as shown in FIG. 5A, one slope 28a of the thread of the female screw 28 is in frictional contact with one slope 27a having a larger friction coefficient than the other slope 27b of the thread of the male screw 27.

  For this reason, the hysteresis torque between the cup member 11 and the cup member 12 increases, and the rotational fluctuation of the internal combustion engine is buffered between the cup member 11 and the cup member 12 so that the drive torque of the internal combustion engine is reduced to the input shaft 25 of the transmission. Can be communicated to.

  On the other hand, when the vehicle is decelerated, the driving torque of the internal combustion engine is reduced and engine braking occurs, so that rotational torque is input to the cup member 12 from the input shaft 25 of the transmission.

  As the rotational fluctuation of the internal combustion engine increases during deceleration, the torsion angle between the cup member 11 and the cup member 12 increases, and the cup member 12 is twisted to the negative side with respect to the cup member 11 as shown in FIG. The coil springs 23 and 24 are extended to transmit rotational torque from the cup member 12 to the cup member 11.

  When the twist angle between the cup member 11 and the cup member 12 increases, the cup member 11 rotates relative to the cup member 12 in the R1 direction as the cup member 12 rotates in the R1 direction. As apparent from the above operation, the input shaft 25 as the second power transmission means transmits torque from the cup member 12 to the cup member 11 when the vehicle is decelerated.

  Further, when the cup member 12 rotates in the R1 direction and the cup member 12 is twisted to the negative side with respect to the cup member 11 during deceleration, the cup member 12 rotates in the R1 direction via the female screw 28 and the male screw 27. By doing so, the cup member 12 is separated from the cup member 11 in the rotation axis L direction.

  At this time, when the coil springs 23 and 24 are extended, the cup member 12 is biased from the cup member 11 in the direction of the rotation axis L by the pulling force of the coil springs 23 and 24. At this time, as the rotational torque of the cup member 12 relative to the cup member 11 increases, the cup member 12 twists in the R1 direction with respect to the cup member 11, and the twist angle between the cup member 11 and the cup member 12 increases.

  Therefore, as shown in FIG. 5B, the other inclined surface 28b of the thread of the female screw 28 is in frictional contact with the other inclined surface 27b having a smaller coefficient of friction than the one inclined surface 27a of the male screw 27. Further, as the rotational torque of the cup member 12 with respect to the cup member 11 increases, the cup member 12 twists in the R1 direction with respect to the cup member 11, and the twist angle increases.

  As a result, the hysteresis torque between the cup member 11 and the cup member 12 can be reduced, and the rotational fluctuation of the internal combustion engine can be buffered between the cup member 11 and the cup member 12.

  Here, as shown in FIG. 11, the rotational fluctuation of the internal combustion engine during acceleration of the vehicle is large in the low speed rotation region of the internal combustion engine and is smaller in the high speed rotation region than in the low speed rotation region. Further, the rotational fluctuation of the internal combustion engine during deceleration is large in the high speed rotation region of the internal combustion engine. Thus, the torque fluctuation of the internal combustion engine has different characteristics when the vehicle is accelerated and when the vehicle is decelerated.

  In the present embodiment, the torsional vibration damping device 10 is provided opposite to the cup member 11 that supports the friction members 18 a and 18 b and the cup member 11, and supports the input shaft 25. The cup member 12 is relatively movable in the rotational direction, and one end is connected to the cup member 11 via the spring seats 21a and 21b, and the other end is connected to the cup member 12 via the spring sheets 22a and 22b. Coil springs 23 and 24 having elasticity in the rotation axis L direction and the rotation direction when the cup member 12 is twisted to the positive side and the negative side with respect to the cup member 11, and the cup member 11 and Provided between the cup members 12 and screwed together, the cup member 11 and the cup member 12 are frictionally contacted in the direction of the rotation axis L Configured to include a screwed-like friction part 26 which freely relative movement in the state.

  When the coefficient of friction of the one inclined surface 27 a and the other inclined surface 27 b of the male screw 27 of the screw-like friction portion 26 is made different, and the cup member 12 is twisted to the positive side with respect to the cup member 11, the male screw 27 When the cup member 12 is twisted to the negative side with respect to the cup member 11 while the one inclined surface 27a and the one inclined surface 28a of the thread of the female screw 28 opposed to the inclined surface 27a are in frictional contact with each other, The coil springs 23 and 24 are inclined between the cup member 11 and the cup member 12 so that the other slope 27b and the other slope 28b of the female screw 28 facing the slope 27b are in frictional contact with each other. did.

  For this reason, when the cup member 12 is twisted to the positive side with respect to the cup member 11 and when it is twisted to the negative side, the coil springs 23 and 24 are compressed or extended in the rotation direction, whereby the cup member 11 and the cup member Rotational torque can be transmitted to 12 while attenuating torsional vibration.

  Further, when the cup member 12 is twisted to the positive side with respect to the cup member 11 and when the cup member 12 is twisted to the negative side, the compression force when the coil springs 23 and 24 are compressed in the rotation direction or the tensile force when the coil springs 23 are expanded. Is used as the compressive force and tensile force of the cup member 11 and the cup member 12 in the direction of the rotation axis L, and the frictional contact surfaces of the male screw 27 and the female screw 28 of the screw-like friction portion 26 have a large friction coefficient. It is possible to switch between a contact surface (one inclined surface 27a, 28a) and a small friction contact surface (the other inclined surface 27b, 28b).

  For this reason, it is possible to increase the hysteresis torque at the time of acceleration when the cup member 12 is twisted to the positive side with respect to the cup member 11, and it is possible to reduce the hysteresis torque at the time of deceleration to be twisted to the negative side.

  Therefore, as shown in FIG. 11, when the acceleration of the vehicle, the hysteresis torque of the cup member 11 and the cup member 12 increases, so that the rotational speed of the internal combustion engine reaches a torsional resonance point (for example, around 2500 rpm for an FF vehicle). When the corresponding number of revolutions is passed, torsional resonance can be suppressed and generation of a booming noise can be suppressed. That is, it is possible to suppress the booming noise indicated by the broken line in FIG. 12 and reduce the level to the level indicated by the solid line.

  In addition, the rotational fluctuation of the internal combustion engine is smaller in the high-speed rotation region of the internal combustion engine than in the low-speed rotation region, so even if the hysteresis torque increases, the torsional vibration of the drive system is attenuated without being affected by the large hysteresis torque. can do.

  Further, at the time of deceleration of the vehicle, as shown by a one-dot chain line in FIG. 8, the hysteresis torque (-B) can be made smaller than the conventional hysteresis torque (-A), so that the rotation speed of the internal combustion engine is large. In the region, the torsional vibration of the drive system can be damped by the elastic force of the coil springs 23 and 24, and the generation of the jagged noise can be suppressed.

  As described above, the torsional vibration damping device 10 of the present embodiment uses the pair of coil springs 23 and 24 to generate an elastic force in both the rotation axis L direction and the rotation direction, so that the positive side and the negative side are generated. Since the magnitude of the hysteresis torque can be changed, the configuration of the torsional vibration damping device 10 can be simplified and the manufacturing cost of the torsional vibration damping device 10 can be reduced.

  In the present embodiment, the friction coefficient of one slope 27a of the thread of the male screw 27 is larger than the friction coefficient of the other slope 27b. The friction coefficient of one slope 28a may be larger than the friction coefficient of the other slope 28b.

  That is, the friction coefficient of one slope 27a of the thread of the male screw 27 and one slope 28a of the thread of the female screw 28 is set to the same friction coefficient, and the other slope 27b of the thread of the male screw 27 and the female thread are set. You may make it make the friction coefficient of the other slope 28b of 28 threads smaller than the friction coefficient of one slope 27a, 28a.

(Second Embodiment)
FIGS. 9 and 10 are diagrams showing a second embodiment of the torsional vibration damping device according to the present invention. The same components as those in the first embodiment are denoted by the same reference numerals and description thereof is omitted. .

  In FIG. 9, spring sheets 21 a and 21 b are attached to the radially outer peripheral portion of the disc portion 13 of the cup member 11, and spring sheets 22 a and 22 b are attached to the radially outer peripheral portion of the disc portion 15 of the cup member 12. Is attached to the spring seats 21a and 21b, and the other ends of the coil springs 31 and 32 are attached to the spring seats 22a and 22b. The part is installed.

The spring seats 21 a, 21 b, 22 a, 22 b have end windings corresponding to one or two turns at both ends in the circumferential direction of the coil springs 31, 32. Both ends are seated, and one end and the other end of the coil springs 31 and 32 are engaged with the end windings to prevent the coil springs 31 and 32 from rotating, and the coil springs 31 and 32 are moved to the spring seat 21a, It can be firmly attached to 21b, 22a, 22b.
In addition, the one end part of the coil springs 33 and 34 may be attached to the spring seat provided in the disc part 13 of the cup member 11, and may be directly attached to the disc part 13 by welding etc.

  Further, as shown in FIGS. 9 and 10, one end portions of coil springs 33 and 34 as second elastic members are attached to the disc portion 13 of the cup member 11, and the disc portion of the cup member 12. 15, the other end portions of the coil springs 33 and 34 are slidably in contact with each other.

  The coil springs 33 and 34 are located between the coil springs 31 and 32, are spaced apart in the vertical direction of the disk portions 13 and 15 with the rotation axis L direction therebetween, and extend in the same direction as the rotation axis L direction. The coil springs 33 and 34 are compressed or extended in the direction of the rotation axis L when the cup member 12 is twisted to the positive side with respect to the cup member 11 and when it is twisted to the negative side.

  That is, the coil springs 33 and 34 of the present embodiment are arranged in a direction that separates the cup member 11 and the cup member 12 in the direction of the rotation axis L when the cup member 12 is twisted to the positive side with respect to the cup member 11. A compressive force, which is a force, is applied between the cup member 11 and the cup member 12, and when the cup member 12 is twisted to the negative side with respect to the cup member 11, the cup member 11 and the cup member 12 are moved in the direction of the rotation axis L. It is arranged between the cup member 11 and the cup member 12 so that a pulling force which is a force in a direction to approach the cup member 11 is applied between the cup member 11 and the cup member 12.

Further, the coil springs 33 and 34 of the present embodiment are configured such that when the cup member 12 is twisted to the positive side with respect to the cup member 11, the cup member 11 and the cup member 12 are first in the rotation axis L direction. Is displaced between the cup member 11 and the cup member 12, and the cup member 12 is applied to the cup member 11. When the cup member 11 and the cup member 12 are displaced in the extension direction which is the second direction with respect to the rotation axis L direction, the tensile force which is the force in the first direction is It is arranged between the cup member 11 and the cup member 12 so that (biasing force) is applied between the cup member 11 and the cup member 12.
Next, an operation when the cup member 12 is twisted to the positive side (R2 direction) with respect to the cup member 11 and an operation when the cup member 12 is twisted to the negative side (R1 direction) will be described.

  When the rotational fluctuation of the internal combustion engine increases during acceleration of the vehicle, the relative rotation between the cup member 11 and the cup member 12 increases, that is, the torsion angle increases, and the cup member 12 twists toward the positive side with respect to the cup member 11. It is. Therefore, when the coil springs 31 and 32 are compressed, the coil springs 31 and 32 absorb the vibration between the cup member 11 and the cup member 12, and the coil springs 31 and 32 are moved from the cup member 11 to the cup member 12. Rotational torque is transmitted through

  When the twist angle between the cup member 11 and the cup member 12 increases, the cup member 12 rotates relative to the cup member 11 in the R2 direction as the cup member 11 rotates in the R1 direction.

  Further, when the cup member 11 is rotated in the R1 direction and the cup member 12 is twisted to the positive side with respect to the cup member 11 during acceleration, the cup member 11 is rotated in the R1 direction via the male screw 27 and the female screw 28. By doing so, the cup member 11 approaches the cup member 12 in the rotation axis L direction.

  At this time, since the coil springs 33 and 34 are compressed, the cup member 11 is urged away from the cup member 12 in the direction of the rotation axis L by the compressive force of the coil springs 33 and 34. As shown in FIG. 3, one slope 28a of the thread of the female screw 28 is in frictional contact with one slope 27a having a larger coefficient of friction than the other slope 27b of the thread of the male screw 27.

  For this reason, the hysteresis torque between the cup member 11 and the cup member 12 increases, and the rotational fluctuation of the internal combustion engine is buffered between the cup member 11 and the cup member 12 so that the drive torque of the internal combustion engine is reduced to the input shaft 25 of the transmission. Can be communicated to.

  In addition, since the other end part of the coil springs 33 and 34 is slidably contacting the disc part 15 of the cup member 12, when the cup member 11 and the cup member 12 rotate relatively, the coil spring 33, 34 is not twisted in the circumferential direction.

  On the other hand, when the vehicle is decelerated, the driving torque of the internal combustion engine is reduced and engine braking occurs, so that rotational torque is input to the cup member 12 from the input shaft 25 of the transmission.

  When the rotational fluctuation of the internal combustion engine increases during deceleration, the torsion angle between the cup member 11 and the cup member 12 increases, and the cup member 12 twists to the negative side with respect to the cup member 11. For this reason, when the coil springs 31 and 32 extend, the coil springs 31 and 32 transmit rotational torque from the cup member 12 to the cup member 11 while absorbing vibration between the cup member 11 and the cup member 12.

  When the twist angle between the cup member 11 and the cup member 12 increases, the cup member 12 rotates relative to the cup member 11 in the R1 direction as the cup member 12 rotates in the R1 direction.

  Further, when the cup member 12 rotates in the R1 direction and the cup member 12 is twisted to the negative side with respect to the cup member 11 during deceleration, the cup member 12 rotates along the female screw 28 and the male screw 27. The cup member 12 is separated from the cup member 11 in the direction of the rotation axis L.

  At this time, since the coil springs 33 and 34 are extended, the cup member 12 is urged so as to be close to the rotation axis L direction from the cup member 11 by the pulling force of the coil springs 33 and 34. ), The other inclined surface 28b of the female screw 28 is in frictional contact with the other inclined surface 27b having a smaller coefficient of friction than the one inclined surface 27a of the male screw 27.

  For this reason, the hysteresis torque between the cup member 11 and the cup member 12 can be reduced, and the rotational fluctuation of the internal combustion engine can be buffered between the cup member 11 and the cup member 12.

  As described above, in the present embodiment, one end portion extends in the direction substantially orthogonal to the rotation axis L direction, and one end portion is coupled to the radial outer peripheral portion of the cup member 11, and the other end portion is the radial direction of the cup member 12. Coil members 31 and 32 that are connected to the outer periphery and compress or extend in the rotational direction depending on whether the cup member 12 is twisted to the positive side or the negative side with respect to the cup member 11 are provided. When 12 is twisted to the positive side or the negative side with respect to the cup member 11, the rotational torque can be transmitted while the torsional vibration is attenuated between the cup member 11 and the cup member 12 by the coil springs 31 and 32.

  In addition, one end is connected to the cup member 11 and the other end is connected to the cup member 12 so as to extend in substantially the same direction as the rotation axis L direction, so that the cup member 12 is on the positive side with respect to the cup member 11. Since the coil springs 33 and 34 that are compressed or extended in the direction of the rotation axis L are provided depending on whether the cup member 12 is twisted or negatively twisted, the cup member 12 is twisted positively or negatively with respect to the cup member 11. Furthermore, the coil springs 33 and 34 can be compressed or extended by moving the cup member 11 and the cup member 12 in the direction approaching or separating from the rotation axis L direction.

  By utilizing the compressive force or tensile force of the coil springs 33, 34, the contact positions of the inclined surfaces 27a, 27b of the male screw 27 and the inclined surfaces 28a, 28b of the female screw 28 of the threaded friction portion 26 are negative and positive. Can be changed on the side. For this reason, the hysteresis torque when the cup member 12 is twisted to the positive side with respect to the cup member 11 can be increased, and the hysteresis torque when the cup member 12 is twisted to the negative side can be reduced.

  As a result, as in the first embodiment, it is possible to suppress torsional resonance during the acceleration of the vehicle and suppress the generation of a booming noise, and attenuate the torsional vibration of the drive system when the vehicle is decelerated. Thus, it is possible to suppress the generation of a jagged sound.

  In the present embodiment, since the other end portions of the coil springs 33 and 34 are provided to be slidable in the rotational direction with respect to the cup member 12, when the cup member 12 is twisted with respect to the cup member 11, When the coil springs 33 and 34 slide in the rotation direction with respect to the cup member 12, the coil springs 33 and 34 can be compressed and extended only in the direction of the rotation axis L.

  For this reason, the compressive force and tensile force of the coil springs 33 and 34 can be made to act efficiently in the direction in which the cup members 11 and 12 approach or separate in the rotation axis L direction. As a result, the hysteresis torque when the cup member 12 is twisted to the positive side with respect to the cup member 11 can be reliably increased, and the hysteresis torque when the cup member 12 is twisted to the negative side can be reliably reduced.

  One end of the coil springs 33 and 34 may be provided so as to be slidable in the rotational direction with respect to the cup member 11, and both ends of the coil springs 33 and 34 are slid in the rotational direction with respect to the cup members 11 and 12. It may be provided movably.

  In each of the above embodiments, the torsional vibration damping device 10 is applied to the clutch device 1. However, the present invention is not limited to this, and any torsional vibration damping device provided in a drive system such as a vehicle 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.

  Further, in each of the above embodiments, two coil springs 23, 24, 31, 32 are provided, but the number of coil springs may be one, or three or more.

  The embodiment disclosed this time is illustrative in all respects and is not limited to this embodiment. The scope of the claims of the present invention is shown not by the above description of the embodiments but by the scope of the claims, and is intended to include all modifications within the meaning and scope equivalent to the scope of the claims. Is done.

  As described above, the torsional vibration damping device according to the present invention can set an optimum hysteresis torque when the second rotating member is twisted to the positive side and the negative side with respect to the first rotating member. Thus, the torsional resonance of the drive system in the low speed rotation region can be suppressed during acceleration, and the torsional vibration can be suppressed by increasing the damping force during deceleration. And is useful as a torsional vibration damping device or the like that attenuates torsional vibration of the drive system by connecting the first rotating member and the second rotating member via an elastic member.

10 Torsional vibration damping device 11 Cup member (first rotating member)
12 Cup member (second rotating member)
13 disc part (first disc part)
14 Cylindrical part (first cylindrical part)
15 disc part (second disc part)
16 Cylindrical part (second cylindrical part)
17 cushioning plate (first power transmission means)
18a, 18b Friction material (first power transmission means)
23, 24 Coil spring (elastic member)
25 Input shaft (second power transmission means)
26 Threaded friction part 27 Male thread (first thread part)
27a One slope 27b The other slope 28 Female thread (2nd thread part)
30 Hysteresis mechanism 31, 32 Coil spring (first elastic member)
33, 34 Coil spring (second elastic member)
L Rotating shaft

Claims (7)

A first rotating member that supports the first power transmission means; and a second rotating member that is provided opposite to the first rotating member and supports the second power transmission means; A second rotating member that is relatively movable in the rotational direction;
One end portion is connected to the first rotating member, the other end portion is connected to the second rotating member, and the second rotating member is twisted to the positive side with respect to the first rotating member. An elastic member having an elastic force in the rotation axis direction and in the rotation direction in the case and when twisted to the negative side;
The first rotating member and the second rotating member are provided between the first rotating member and the second rotating member, and are screwed together to bring the first rotating member and the second rotating member in a frictional contact state in the direction of the rotation axis. A hysteresis mechanism having a threaded friction part that allows relative movement freely,
The threaded friction portion includes a first screw portion provided in the first rotating member and a second screw portion provided in the second rotating member and screwed into the first screw portion. And the friction coefficient between one inclined surface and the other inclined surface of at least one thread of the first screw portion and the second screw portion is different,
When the second rotating member is twisted to the positive side with respect to the first rotating member, the elastic member has one inclined surface of the thread of the first screw portion and the first screw portion. When the second inclined surface of the second threaded portion facing the one inclined surface of the screw thread comes into frictional contact and the second rotating member is twisted to the negative side with respect to the first rotating member. The other inclined surface of the thread of the first screw portion and the inclined surface of the thread of the second screw portion facing the other inclined surface of the screw thread of the first screw portion are arranged in frictional contact with each other. A torsional vibration damping device.   The elastic member moves the first rotating member and the second rotating member close to each other in the rotation axis direction when the second rotating member is twisted to the positive side with respect to the first rotating member. One of the force to be moved or the direction to be separated is applied between the first rotating member and the second rotating member, and the second rotating member is on the negative side with respect to the first rotating member. When the first rotating member and the second rotating member are twisted to each other, the other force in the direction in which the first rotating member and the second rotating member are moved closer to or away from the rotation axis direction is applied to the first rotating member and the second rotating member. The torsional vibration damping device according to claim 1, wherein the torsional vibration damping device is disposed so as to be placed between the rotating members. The elastic member is configured such that when the second rotating member is twisted to the positive side with respect to the first rotating member, the first rotating member and the second rotating member are close to each other in the rotation axis direction. The displacement in the first direction, which is one of the direction to move or the direction to separate, causes the force in the second direction, which is the other, to be generated between the first rotating member and the second rotating member. As well as
When the second rotating member is twisted to the negative side with respect to the first rotating member, the first rotating member and the second rotating member are in the direction of the rotation axis and in the second direction. 3. The device according to claim 1, wherein the first rotating member and the second rotating member are arranged so that the force in the first direction is applied between the first rotating member and the second rotating member by being displaced. Torsional vibration damping device. The first rotating member includes a first disk part and a first cylindrical part protruding from the first disk part in the rotation axis direction,
The second rotating member has a second disc portion and a second disc portion protruding from the second disc portion in the direction of the rotation axis and facing the outer peripheral portion or the inner peripheral portion of the first cylindrical portion. Comprising a cylindrical portion,
The first frictional portion of the hysteresis mechanism is screwed into the first screw portion and the first screw portion formed on the outer peripheral portion or the inner peripheral portion of the first cylindrical portion. The torsional vibration damping device according to any one of claims 1 to 3, further comprising: the second screw portion formed on an inner peripheral portion or an outer peripheral portion of the two cylindrical portions. .   The torsional vibration damping device according to any one of claims 1 to 4, wherein the elastic member is inclined in the rotation axis direction. The elastic member has one end connected to the first rotating member and the other end connected to the second rotating member and extending in a direction substantially perpendicular to the rotation axis direction, A first elastic member that compresses or extends in the rotational direction when the two rotating members are twisted to the positive side and to the negative side with respect to the first rotating member;
One end portion is connected to the first rotating member and the other end portion is connected to the second rotating member and extends in substantially the same direction as the rotation axis direction, and the second rotating member is connected to the first rotating member. And a second elastic member that compresses or extends in the direction of the rotation axis when twisted to the positive side and when twisted to the negative side with respect to one rotating member. The torsional vibration damping device according to any one of claims 1 to 4.   The at least one of the one end part and the other end part of the second elastic member is provided to be slidable in the rotation direction with respect to the first rotating member or the second rotating member. 6. The torsional vibration damping device according to 6.

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