JP2012246958A - Torsional vibration damping device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a torsional vibration damping device that prevents an elastic member from being inclined when a torsion angle between a first rotary member and a second rotary member is increased, thereby achieving desired stiffness of the elastic member.SOLUTION: In the torsional vibration damping device 1, a spring sheet 16 is rotatably mounted on the other end of an arm member 18 via a pin 20, and spaces are formed both between a projection 16B of the spring sheet 16 and an inner periphery of a coil spring 4 and between an outer peripheral supporting piece and an outer periphery of the coil spring 4.

Description

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

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

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

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

  The hub has a cylindrical boss that is spline-engaged with the input shaft and a disk-shaped flange that extends radially outward from the boss. The elastic member is composed of a single coil spring. The coil spring is housed in a window hole formed in the flange and supported at both ends in the circumferential direction, and formed on a pair of disk plates. Both ends in the circumferential direction are supported by the made window holes.

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

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

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

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

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

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

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

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

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

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

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

  Further, in a region where the torsion angle between the driving side rotating member and the driven side rotating member is large, the torsion angle of the driving side rotating member and the driven side rotating member is increased to provide a high rigidity torsion characteristic that increases the torque increase rate. Trying to get.

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

JP 2003-194095 A JP 2001-74102 A

  In such a conventional torsional vibration damping device, when the driving side rotating member and the driven side rotating member rotate relative to each other, one end of the displacement member swings around the swing shaft, and the displacement member Since the elastic member is elastically deformed following the swing of the displacement member, the displacement member is greatly inclined when the torsion angle between the drive side rotation member and the driven side rotation member is increased, and as the displacement member is inclined, The elastic member is inclined.

  Here, it is considered that one end of the elastic member is fixed to a holding member such as a spring seat fixed to the displacement member, but when the holding member and the displacement member are integrated, the displacement member is The holding member tilts as it tilts greatly.

  For this reason, when the holding member is inclined, the elastic member is inclined and is not normally compressed in the central axis direction, and the spring rigidity of the elastic member may not be set to the set spring rigidity. As a result, the vibration damping performance may be deteriorated as compared with the case where the elastic member does not tilt, and there is room for improvement.

  The present invention has been made to solve the above-described conventional problems, and prevents the elastic member from being inclined when the twist angle of the first rotating member and the second rotating member becomes large. Another object of the present invention is to provide a torsional vibration damping device that can make the rigidity of an elastic member desired.

  In order to achieve the above object, the torsional vibration damping device according to the present invention is (1) provided on the same axis as the first rotating member and the first rotating member, with respect to the first rotating member. A second rotating member that is relatively rotatable, and provided between the first rotating member and the second rotating member, and the first rotating member and the second rotating member are relatively rotated. And an elastic member that is elastically deformed, and is provided in the first rotating member so as to rotate integrally with the first rotating member, and according to a change in a twist angle of the first rotating member and the second rotating member. A cam member having a cam surface with a variable curvature, and one end of the cam member is in contact with the cam surface of the cam member and the other end is in contact with one end in the extending direction of the elastic member via a holding member, When the first rotating member and the second rotating member are relatively rotated, Rotation torque between the first rotation member and the second rotation member by rotating about the rotation fulcrum provided on the second rotation member and elastically deforming the elastic member And a holding member is rotatably attached to the other end portion of the torque transmitting member.

  In this torsional vibration damping device, the first rotating member includes a cam member having a cam surface whose curvature changes with changes in the torsion angles of the first rotating member and the second rotating member, and is elastic to the cam member. Since the torque transmission member is interposed between the elastic member and the member, the cam member presses the elastic member via the torque transmission member as the cam member rotates to change the reaction force from the elastic member to the torque transmission member. Thereby, the range of the torsion angle between the first rotating member and the second rotating member can be widened, and the rotational torque can be transmitted between the first rotating member and the second rotating member.

  For this reason, the torsional rigidity of the first rotating member and the second rotating member can be lowered as a whole.

  Further, since the holding member is rotatably attached to the other end portion of the torque transmission member, the torsion angle between the first rotation member and the second rotation member is increased, and the torque transmission member is centered on the rotation fulcrum portion. By rotating the holding member relative to the other end of the torque transmission member when the torque transmitting member is rotated, the holding member can be prevented from being inclined with respect to the elastic member.

  For this reason, the elastic member can be prevented from being inclined between the other end of the torque transmitting member and the second rotating member, and the elastic member can be normally elastically deformed in the central axis direction. Can be set to a desired rigidity.

  In addition, since the elastic member can be prevented from being inclined, the elastic member can be prevented from being deformed abnormally, and the elastic member can be protected.

  In the torsional vibration damping device according to the above (1), (2) the elastic member is constituted by a coil spring, and the holding member has a main body having an abutting surface with which one end portion in the extending direction of the coil spring abuts, A first protrusion projecting from the contact surface toward the other end of the coil spring in the extending direction and inserted through the inner peripheral portion of the coil spring; and the second rotation from the radially outer end of the main body A second projecting portion projecting in a circumferential direction of the member and opposed to an outer peripheral portion of the coil spring; and between the first projecting portion and an inner peripheral portion of the coil spring and the second projecting portion. And a gap formed between the outer periphery of the coil spring.

  In this torsional vibration damping device, a gap is formed between the first protrusion of the holding member and the inner periphery of the coil spring and between the second protrusion and the outer periphery of the coil spring. When the torsional angle between the rotating member and the second rotating member becomes large and the torque transmitting member rotates about the rotation fulcrum, the first and second protruding portions and the coil spring The holding member can be moved in the radial direction of the second rotating member by the gap between them.

  For this reason, it is possible to further prevent the holding member from being inclined with respect to the elastic member, to further prevent the elastic member from being inclined, and to elastically deform the elastic member in the central axis direction.

  (1) In the torsional vibration damping device according to (1) or (2), (3) the second rotating member is inclined with respect to a radial direction of the second rotating member and extends over a predetermined length. The first guide groove, and a second guide groove positioned inward in the radial direction with respect to the first guide groove and extending in parallel with the first guide groove, and the holding The main body of the member is constituted by a member having a protrusion inserted into the guide groove.

  In the torsional vibration damping device, the first guide groove and the second guide groove in which the second rotating member is inclined with respect to the radial direction of the second rotating member and extends in parallel over a predetermined length. And the protrusion provided on the holding member is inserted into the first guide groove and the second guide groove, so that the torque transmission member rotates around the rotation fulcrum as the cam member rotates. Sometimes, the projection is moved between one end surface in the extending direction and the other end surface in the extending direction of the first guide groove and the second guide groove, so that the holding member is movably supported by the second rotating member. However, the second rotating member can be moved in the radial direction.

  At this time, the holding member can be prevented from tilting with respect to the elastic member by rotating the holding member with respect to the torque transmission member, and the elastic member can be elastically deformed in the central axis direction.

  (3) In the torsional vibration damping device according to (3), (4) when the torsion angle between the first rotating member and the second rotating member is the minimum, the protrusions are the first guide groove and the first rotating member. It is comprised from what contact | abuts the extending direction one end surface of 2 guide grooves.

  In this torsional vibration damping device, when the torsion angle between the first rotating member and the second rotating member is minimum, the holding member is aligned in the extending direction of the first guide groove and the second guide groove. Since it abuts against the end face, when the torque transmission member rotates to one side around the rotation fulcrum due to the centrifugal force during rotation of the torsional vibration damping device, the holding member is moved to the first guide groove and the second It can be made to be one end surface of the extending direction of the guide groove.

  For this reason, the torque transmission member is restricted from rotating more than necessary to one side around the rotation fulcrum, so that one end of the torque transmission member contacts the cam surface of the cam member with a large contact pressure. Can be prevented.

  Therefore, the first rotating member can be smoothly rotated relative to the second rotating member in a region where the twist angle between the first rotating member and the second rotating member is small, and the minute vibration is surely attenuated. can do.

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

  This torsional vibration damping device changes the curvature of the cam surface of the cam member with which the torque transmitting member contacts according to the change in the torsion angle between the first rotating member and the second rotating member, thereby making the first rotation. The torsional rigidity can be lowered by widening the range of the torsion angle between the member and the second rotating member.

  Further, since the torsional rigidity between the first rotating member and the second rotating member can be increased as the torsion angle between the first rotating member and the second rotating member is increased, large torque fluctuations are caused by the elastic member. Rotational torque can be smoothly transmitted between the first rotating member and the second rotating member while being attenuated by.

  (1) In the torsional vibration damping device according to (1) to (5), (6) the first rotating member has the cam member on the outer peripheral portion, and the boss to which the input shaft of the transmission is connected to the inner peripheral portion. A pair of discs, wherein the second rotating member is disposed on both sides in the axial direction of the cam member and rotatably supports the torque transmitting member via a rotating shaft constituting the rotating fulcrum portion A plate, and a support portion that is provided on the disk plate and supports the other end in the extending direction of the elastic member, and is configured to transmit the rotational torque of the internal combustion engine to the pair of disk plates. .

  In this torsional vibration damping device, one end of the elastic member in the extending direction is in contact with the other end of the torque transmitting member via the holding member, and the other end of the torque transmitting member is in contact with the cam surface of the cam member. The range of the torsion angle between the first rotating member and the second rotating member can be widened to reduce the rigidity of the elastic member.

  For this reason, in a region where the twist angle between the first rotating member and the second rotating member is small, such as when the shift position is changed to neutral and the internal combustion engine is in an idle state, the rigidity is low. The generation of rattling noise can be suppressed by attenuating minute vibrations by the elastic member.

  Further, in a region where the torsion angle between the first rotating member and the second rotating member is large, the torsion angle of the first rotating member and the second rotating member is increased to increase the rate of increase in torque. Twist characteristics can be obtained.

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

  In the torsional vibration damping device according to (6) above, (7) the pair of disk plates includes a window portion through which the elastic member is inserted.

  In this torsional vibration damping device, since the pair of disk plates has a window part through which the elastic member is inserted, when the diameter of the elastic member is large, the elastic member is inserted between the disk parts by inserting the elastic member between the disk plates. It is not necessary to accommodate the entire elastic member. For this reason, the space | interval of a disk plate can be shortened, the axial direction length of a torsional vibration damping device can be shortened, and a torsional vibration damping device can be reduced in size.

  According to the present invention, when the twist angle of the first rotating member and the second rotating member becomes large, the elastic member can be prevented from being tilted, and the rigidity of the elastic member can be set to a desired rigidity. It is possible to provide a torsional vibration damping device capable of

It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is a perspective view of a torsional vibration damping device. BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is a perspective view of the torsional vibration damping device in the state which removed one of the disk plates. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is a front view of the torsional vibration damping device. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is 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 a front view of a spring seat. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is a side view of a spring seat. 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 positional relationship of a spring seat and a coil spring. It is a figure which shows 1st 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 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is BB direction arrow sectional drawing of FIG. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is the other front view of a disk plate. 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 when the torsion angle of a disk plate and a boss | hub is +45 degrees. 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 when the torsion angle of a disk plate and a boss | hub is +90 degrees. 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 when the torsion angle of a disk plate and a boss | hub is -45 degrees. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is a torsional characteristic figure which shows the relationship between the twist angle of a torsional vibration damping device, and a torque. 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 relationship between the rotation speed of an internal combustion engine, and rotational angular velocity fluctuation | variation. It is a figure which shows 2nd Embodiment of the torsional vibration damping device which concerns on this invention, and is a perspective view of a torsional vibration damping device. It is a figure which shows 2nd Embodiment of the torsional vibration damping device which concerns on this invention, and is a perspective view of the torsional vibration damping device of the state which removed one of the disk plates. It is a figure which shows 2nd Embodiment of the torsional vibration damping device which concerns on this invention, and is a front view of the torsional vibration damping device. It is a figure which shows 2nd Embodiment of the torsional vibration damping device which concerns on this invention, and is CC sectional view taken on the line of FIG. It is a figure which shows 2nd Embodiment of the torsional vibration damping device which concerns on this invention, and is the other front view of a disk plate. It is a figure which shows 2nd Embodiment of the torsional vibration damping device which concerns on this invention, and is a figure which shows the positional relationship of a spring seat and a coil spring.

Hereinafter, embodiments of a torsional vibration damping device according to the present invention will be described with reference to the drawings.
(First embodiment)
FIGS. 1-15 is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention.
First, the configuration will be described.

  1 to 4, the torsional vibration damping device 1 includes a first rotating member 2 and a second rotating member 3 provided on the same axis as the first rotating member 2.

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

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

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

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

  The second rotating member 3 includes a pair of disk plates 7 and 8 and a clutch disk 10. The disc plates 7 and 8 are arranged on both sides of the cam member 6 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.

  A protrusion 14 a is formed on the pedestal 14 so as to be inserted into the inner peripheral portion of the other end portion in the extending direction of the coil spring 4, and the other end portion in the extending direction of the coil spring 4 is attached. A spring seat 16 as a holding member is attached to one end portion of the coil spring 4 in the extending direction.

  As shown in FIGS. 5 and 6, the spring seat 16 includes a main body 16 </ b> A having a contact surface 16 a that contacts one end of the coil spring 4 in the extending direction, and the extending direction of the coil spring 4 from the contact surface 16 a. Projecting toward the end, projecting in the circumferential direction from the radially outer end of the main body 16A, and a projection 16B as a first projecting portion that is inserted into the inner peripheral portion of the coil spring 4, and on the outer peripheral portion of the coil spring 4 It has the outer peripheral side support piece 16C as a 2nd protrusion part which opposes.

  Further, as shown in FIG. 7, a gap S <b> 1 is formed between the outer peripheral portion of the protrusion 16 </ b> B and the inner peripheral portion of the coil spring 4, and the inner peripheral surface of the outer peripheral support piece 16 </ b> C and the outer periphery of the coil spring 4. A gap S2 is formed between the two portions. That is, one end portion of the coil spring 4 in the extending direction is movable in the radial direction of the disk plates 7 and 8 with respect to the spring seat 16.

  Further, an arm member 18 as a torque transmission member is provided between the coil spring 4 and the cam member 6, and this arm member 18 is located between the disk plates 7 and 8 and is attached to the rotating shaft 9. It is supported rotatably.

  A float body 15 made of a resin material or the like is housed in the inner peripheral portion of the coil spring 4, and the float body 15 is configured to be shorter than the axial length of the coil spring 4.

  The float body 15 prevents the coil spring 4 from being deformed abnormally by having both ends abut against the protrusion 16B of the spring seat 16 and the protrusion 14a of the base 14 when the coil spring 4 is compressed. The coil spring 4 is protected.

  As shown in FIGS. 8 and 9, a needle bearing 19 is interposed between the rotating shaft 9 and the arm member 18. The needle bearing 19 includes an outer race 19a attached to the arm member 18, and a needle needle 19b interposed between the outer race 19a and the rotating shaft 9. The outer race 19a is a needle needle. It is freely rotatable with respect to the rotation shaft 9 via 19b. For this reason, the arm member 18 is rotatably attached to the rotation shaft 9 via the needle bearing 19.

  At the other end of the arm member 18, bifurcated projecting pieces 18 </ b> A and 18 </ b> B are formed, and the projecting pieces 18 </ b> A and 18 </ b> B are connected by a pin 20.

As shown in FIGS. 6, 7, and 9, a mounting portion 16D is provided on the surface of the spring seat 16 opposite to the contact surface 16a of the main body 16A, and a pin 20 is inserted into the mounting portion 16D. An insertion hole 16d is formed.
For this reason, the spring seat 16 is attached to the other end portion of the arm member 18 so as to be rotatable in the radial direction of the disk plates 7 and 8 around the pin 20.

  As shown in FIGS. 1, 3, 4, and 10, the disc plates 7 and 8 include a guide groove 31 and a first guide groove 31 as first guide grooves over a predetermined length of the disc plates 7 and 8. A guide groove 32 as a second guide groove is formed.

  The guide grooves 31 and 32 are inclined with respect to the radial direction of the disk plates 7 and 8. FIG. 10 shows an axis L in the radial direction of the disk plates 7 and 8. The guide grooves 31 and 32 are spaced apart in the circumferential direction of the disc plates 7 and 8, and the guide groove 32 is provided radially inward with respect to the guide groove 31 and parallel to the guide groove 31. Yes.

  Further, the main body 16A of the spring seat 16 is provided with a plurality of protrusions 16b and 16c protruding from the main body 16A in the axial direction of the input shaft 26. The protrusions 16b and 16c are inserted into the guide grooves 31 and 32, respectively. Yes.

  The protrusions 16b and 16c are adapted to move along the guide grooves 31 and 32 between the extending direction one end faces 31a and 32a and the extending direction other end faces 31b and 32b of the guide grooves 31 and 32, The spring seat 16 is movable along the guide grooves 31 and 32 between the radially inner side and the radially outer side of the disk plates 7 and 8.

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

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

  Therefore, the cam member 6 according to the present embodiment has the cam member 6 so that one end portion of the arm member 18 comes into contact with the cam surface 6a having a small curvature when the twist angle between the disk plates 7 and 8 and the boss 5 is minimum. The initial position of is set.

  Then, the cam member 6 rotates and the position of the cam surface 6a with which one end of the arm member 18 abuts is varied, whereby the spring seat 16 is urged by the arm member 18 and the amount of compression of the coil spring 4 is varied. Is done.

  At this time, the spring seat 16 moves between the radially inner side and the radially outer side of the disk plates 7 and 8 so as to approach and separate from the base 14.

  Further, the protrusions 16b and 16c come into contact with the end surfaces 31a and 32a in the extending direction of the guide grooves 31 and 32 when the twist angle between the disk plates 7 and 8 and the boss 5 is at the minimum neutral position. ing.

  In the present embodiment, the arm member 18 is prevented from moving in the clockwise direction in a state in which the guide grooves 31 and 32 are in contact with the extending direction end faces 31a and 32a. 4 is in contact with the cam surface 6a of the cam member 6 with a small contact pressure.

  The arm member 18 is arranged point-symmetrically with respect to the central axis of the disk plates 7 and 8, and the arm member 18 has a cam surface 6 a having the same curvature across the central axis of the disk plates 7 and 8. One end portion can be brought into contact with the.

  On the other hand, as shown in FIG. 4, a hysteresis mechanism 21 is interposed between the disk plates 7 and 8 and the cam member 6, and the hysteresis mechanism 21 includes annular friction members 22 and 23 and a disc spring 24. It is composed of

  The friction material 22 is formed of an annular member having a predetermined friction coefficient on the surface, and is attached to the disk plate 7 so as to be interposed between the disk plate 7 and the cam member 6.

  The friction material 23 is formed of an annular member having a predetermined friction coefficient on the surface, and is attached to the disk plate 8 so as to be interposed between the disk plate 8 and the cam member 6.

  The disc spring 24 is formed in a conical shape, and is interposed between the friction material 23 and the disc plate 8. The disc spring 24 generates an urging force in the axial direction of the cam member 6, thereby bringing the disc plates 7, 8 and the cam member 6 into frictional contact with each other via the friction members 22, 23. Hysteresis torque is generated between the disk plates 7 and 8.

Next, the operation will be described.
FIGS. 11 to 13 show a state in which the disk plates 7 and 8 are rotating in the clockwise direction (R1 direction) from the state of FIG. 3 in response to the rotational torque of the internal combustion engine. The description will be made assuming that the disc plates 7 and 8 are twisted in the clockwise direction (R2 direction) on the positive side and the clockwise direction (R1 direction) on the negative side.

  11 to 13 show a state in which the disk plate 8 is removed. The cam member 6 is twisted to the positive side with respect to the disk plates 7 and 8 when the vehicle is accelerating, and the cam member 6 is twisted to the negative side when the vehicle is decelerating.

  The friction materials 12 a and 12 b are pressed against the pressure plate and frictionally engaged with the flywheel and the pressure plate, whereby the 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 6 is small, that is, the torsion angle between the disk plates 7 and 8 and the cam member 6 is small near 0 °. In the state, as shown in FIG. 3, the cam member 6 is positioned at the initial position and rotates integrally with the disk plates 7 and 8.

  At this time, one end portion of the arm member 18 is in contact with the cam surface 6 a having a small curvature of the cam member 6, and the cam member 6 presses the spring seat 16 against the coil spring 4 via the arm member 18. 4 is biased by the arm member 18.

  Here, when the torsional vibration damping device 1 is rotating at a high speed, the arm member 18 is rotated clockwise around the rotation shaft 9 by centrifugal force, and one end of the arm member 18 is a cam member. There is a risk of contact with the cam surface 6 with a strong contact pressure.

  For this reason, there is a possibility that the cam member 6 cannot be smoothly rotated relative to the disk plates 7 and 8 in a region where the twist angle between the disk plates 7 and 8 and the cam member 6 is small.

  In the present embodiment, in a state where the spring seat 16 is in contact with the end surfaces 31 a and 32 a in the extending direction of the guide grooves 31 and 32, the arm member 18 is rotated in the clockwise direction that is one side around the rotation shaft 9. Since the rotation more than necessary is restricted, one end of the arm member 18 does not contact the cam surface 6a of the cam member 6 with a large contact pressure.

  Further, when the cam member 6 presses the spring seat 16 against the coil spring 4 via the arm member 18, and the coil spring 4 is urged by the cam member 6, the arm member 18 is rotated by the reaction force of the coil spring 4. Using the moving shaft 9 as a fulcrum, the cam member 6 is pressed by the lever principle.

  Therefore, the rotational torque of the disk plates 7 and 8 is transmitted to the cam member 6 via the coil spring 4 and the arm member 18. For this reason, the rotational torque of the internal combustion engine is transmitted to the input shaft 26 of the transmission, and at this time, the amount of compression of the coil spring 4 is small.

  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 transmitted from the disk plates 7 and 8 to the cam member 6 is small. To rotate in the counterclockwise direction (R2 direction).

  Then, as shown in the state shown in FIG. 11 from the state shown in FIG. 3, the cam member 6 is twisted in the R2 direction with respect to the disk plates 7 and 8 as the twist angle between the disk plates 7 and 8 and the cam member 6 increases. It is. At this time, one end of the arm member 18 slides on the cam surface 6a.

  Since the curvature of the cam surface 6a increases as the torsion angle between the disk plates 7 and 8 and the cam member 6 increases from the initial position of the cam member 6, the curvature of one end of the arm member 18 gradually increases. When the cam surface 6 a of the cam member 6 becomes large, the other end of the arm member 18 moves inward in the radial direction of the disk plates 7 and 8.

At this time, the spring seat 16 has a clearance S1 between the outer peripheral portion of the protrusion 16B and the inner peripheral portion of the coil spring 4 and a clearance S2 between the inner peripheral surface of the outer peripheral support piece 16C and the outer peripheral portion of the coil spring 4. Move inward in the radial direction.
At this time, the spring seat 16 moves radially inward as the protrusions 16b, 16c move radially inward along the guide grooves 31, 32.

  As the spring seat 16 moves inward in the radial direction, the other end of the arm member 18 presses the coil spring 4 through the spring seat 16, thereby moving the spring seat 16 toward the base 14. The coil spring 4 is compressed and deformed.

  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 6 is large, and the cam member 6 rotates counterclockwise with respect to the disk plates 7 and 8. Further relative rotation in the (R2 direction).

  When the torsional angle between the disk plates 7 and 8 and the cam member 6 reaches, for example, the maximum + 90 ° as in the state illustrated in FIG. 12 from the state illustrated in FIG. 11, the curvature of the cam surface 6 a increases to the top 6 b. One end of the arm member 18 is positioned, and the cam member 6 biases the coil spring 4 with a larger biasing force via the arm member 18.

  In this state, the curvature of the cam surface 6a becomes larger as the torsional angle between the disk plates 7 and 8 and the cam member 6 increases from when the cam member 6 is in the initial position. When the portion is pressed against the cam surface 6a of the cam member 6 whose curvature gradually increases, the other end of the arm member 18 further moves inward in the radial direction of the disk plates 7 and 8.

At this time, the spring seat 16 has a clearance S1 between the outer peripheral portion of the protrusion 16B and the inner peripheral portion of the coil spring 4 and a clearance S2 between the inner peripheral surface of the outer peripheral side support piece 16C and the outer peripheral portion of the coil spring 4. Only move further radially inward.
At this time, the spring seat 16 further moves radially inward as the protrusions 16b, 16c move radially inward along the guide grooves 31, 32.

  In the present embodiment, the twist angle between the disk plates 7 and 8 and the cam member 6 is +90 by appropriately setting the shape of the arm member 18, the shape of the cam member 6, the shape of the guide grooves 31 and 32, and the like. When the angle is at 0 °, the protrusion 16B of the spring seat 16 abuts on the radially inner periphery of the coil spring 4, and the inner periphery of the outer support piece 16C is on the radially outer periphery of the coil spring 4. It is comprised so that it may contact | abut.

  Further, when the arm member 18 moves inward in the radial direction, the spring seat 16 rotates with respect to the other end portion of the arm member 18 via the pin 20 so that the coil spring 4 does not tilt, and the current state Will be maintained.

  Further, when excessive torque is input to the disk plates 7 and 8 from the internal combustion engine, the other end portion of the arm member 18 gets over the top portion 6b having the largest curvature of the cam surface 6a and the disk plates 7 and 8 are moved to the cam member. 6, the cam member 6 can function as a torque limiter when the vehicle is accelerated.

  As a result, it is possible to prevent an excessive torque from being transmitted from the disk plates 7 and 8 to the cam member 6 and to protect the transmission gear set of the transmission.

  Further, since the hysteresis mechanism 21 is interposed between the disk plates 7 and 8 and the cam member 6, a certain hysteresis torque is generated when the disk plates 7 and 8 and the cam member 6 rotate relative to each other. be able 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 from the input shaft 26 of the transmission to the cam member 6. When the rotational fluctuation due to the torque fluctuation of the internal combustion engine is small at the time of deceleration, the fluctuation torque between the cam member 6 and the disk plates 7 and 8 is small, so that the cam member 6 is relative to the disk plates 7 and 8. It will be twisted to the negative side (R1 direction).

  When the disk plates 7 and 8 and the cam member 6 are rotated relative to each other as shown in FIG. 12 from the state shown in FIG. As the cam member 6 rotates with respect to the plates 7 and 8, one end portion of the arm member 18 slides on the cam surface 6a.

  Then, as the cam member 6 rotates in the R1 direction, the other end portion of the arm member 18 presses the spring seat 16, and the spring seat 16 moves toward the pedestal 14, thereby causing the coil spring 4 to move. Is compressed and deformed.

  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 6 is large, and the cam member 6 rotates counterclockwise with respect to the disk plates 7 and 8. Further relative rotation in the (R1 direction).

  When the torsional angle between the disk plates 7 and 8 and the cam member 6 reaches, for example, the maximum + 90 °, one end of the arm member 18 is positioned at the top 6b where the curvature of the cam surface 6a is maximum, and the cam member 6 urges the coil spring 4 with a larger urging force via the arm member 18.

  When the cam member 6 is twisted to the negative side with respect to the disk plates 7 and 8, the cam surface 6a of the cam member 6 is gradually increased in curvature at one end of the arm member 18 in the same manner as when the cam member 6 is twisted to the positive side. Therefore, the other end of the arm member 18 moves inward in the radial direction of the disk plates 7 and 8.

  At this time, similarly to when the spring sheet 16 is twisted to the positive side, the clearance S1 between the outer peripheral portion of the protrusion 16B and the inner peripheral portion of the coil spring 4 and the inner peripheral surface of the outer peripheral support piece 16C and the coil spring 4 It moves inward in the radial direction by the gap S2 between the outer peripheral portion and the outer peripheral portion.

  At this time, the spring seat 16 further moves radially inward as the protrusions 16b, 16c move radially inward along the guide grooves 31, 32. When the arm member 18 moves inward in the radial direction, the spring seat 16 rotates with respect to the other end of the arm member 18 via the pin 20 so that the coil spring 4 does not tilt, and the current posture is maintained. Will be maintained.

  As the arm member 18 biases the coil spring 4 in this way, the arm member 18 strongly presses the cam member 6 based on the lever principle by the reaction force of the coil spring 4 to be compressed and the pivot shaft 9 as a fulcrum. Since pressure is applied by pressure, the power of the drive transmission system is transmitted from the cam member 6 to the disk plates 7 and 8 and the torsional vibration between the disk plates 7 and 8 and the cam member 6 is absorbed and attenuated.

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

  As described above, in the present embodiment, the torsional vibration damping device 1 includes the cam member 6 and the cam member 6 that is provided on the outer peripheral portion of the cam member 6 and has an elliptical cam surface 6 a that rotates integrally with the cam member 6. Provided between the cam member 6 and the coil spring 4, one end of which is in contact with the cam surface 6 a and the other end is in contact with the spring seat 16 of the coil spring 4 and is bridged by the disk plates 7 and 8. And an arm member 18 that rotates about the moving shaft 9.

  For this reason, the torsional rigidity of the torsional vibration damping device 1 can be reduced as a whole by widening the range of the torsional angle between the disk plates 7 and 8 and the cam member 6, and the torsional characteristics can be made non-linear. Rotational torque can be smoothly transmitted from the disk plates 7 and 8 to the cam member 6.

FIG. 14 is a diagram showing the torsional characteristics of the disc plates 7 and 8 and the cam member 6. The torsion angle between the disc plates 7 and 8 and the cam member 6 and the output output from the cam member 6 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 6 with respect to the disk plates 7 and 8, and the vertical axis represents the output torque output from the cam member 6.

  As shown in FIG. 14, in the present embodiment, the coil spring 4 contracts as the torsion angle of the cam member 6 with respect to the disk plates 7 and 8 increases, so that the pressing force on the cam member 6 by the arm member 18 increases. Become.

  And the output torque becomes large because the pressing force to the cam member 6 by the arm member 18 becomes large. The change in the output torque at this time becomes a curved torsional characteristic that continuously changes without having a step portion.

  In the present embodiment, since one end of the arm member 18 is in contact with the elliptical cam surface 6a, the twist angle between the disk plates 7 and 8 and the cam member 6 is set to the positive side and the cam member 6 as the cam member 6 rotates. The total angle on the negative side can be widened to 180 °.

  The torsional characteristics and the torsional angle when the disk plates 7 and 8 and the cam member 6 rotate relative to each other are the shape of the cam surface 6a of the cam member 6, the spring constant of the coil spring 4, and the shape of the arm member 18. By adjusting the above, it is possible to set an arbitrary twist characteristic and twist angle.

  Further, as shown in FIG. 14, the torsional vibration damping device 1 of the present embodiment has a torsional rigidity between the disc plates 7 and 8 and the cam member 6 when the torsion angle between the disc plates 7 and 8 and the cam member 6 is small. Low flat torsional characteristics can be achieved.

  Therefore, a region where the rotational torque (output torque of the cam member 6) transmitted from the disk plates 7 and 8 to the cam member 6 is small, such as when the shift position is changed to neutral and the internal combustion engine is in an idle state. Then, it is possible to attenuate the torsional vibration caused by the rotation fluctuation caused by the torque fluctuation of the internal combustion engine, and to suppress the rattling noise from the gear pair of the transmission in the no-load state.

  On the other hand, as shown in FIG. 15, the torsional resonance point of the drive transmission system provided with the transmission exists so as to occur in the steady rotation (for example, around 2000 rpm) of the internal combustion engine. Sometimes, torsional resonance of the drive transmission system occurs when passing through 2000 rpm.

  In the present embodiment, the torsional rigidity of the disc plates 7 and 8 and the cam member 6 can be widened to reduce the overall torsional rigidity. In an operating state with a large rotational torque, the torsional vibration caused by the rotational fluctuation caused by the torque fluctuation of the drive source is attenuated to suppress the jagged noise generated by the collision of the idle gear pair of the transmission gear set. it can.

  In addition, when the torsion angle between the disk plates 7 and 8 and the cam member 6 is large, the coil spring 4 can be greatly compressed to increase the rigidity of the coil spring 4, so that the torsional vibration due to the torsional resonance of the drive transmission system. It is possible to suppress the generation of a booming sound in the vehicle interior by attenuating the noise.

  In FIG. 15, the torsional vibration near the resonance point is found when the torsional characteristic (indicated by a broken line) that cannot be widened is compared with the torsional characteristic (indicated by the solid line) of the torsional vibration damping apparatus 1 of the present embodiment. Shows a significant drop.

  In addition, in the present embodiment, since the hysteresis mechanism 21 is interposed between the disk plates 7 and 8 and the cam member 6, when the disk plates 7 and 8 and the cam member 6 rotate relative to each other, a constant value is obtained. Hysteresis torque can be generated.

  For this reason, during acceleration / deceleration with a large rotational torque transmitted from the disk plates 7 and 8 to the cam member 6, a hysteresis torque is generated against a large torsional vibration caused by a rotational fluctuation caused by a torque fluctuation of the drive source. Can be made.

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

  Further, in the present embodiment, the spring seat 16 is rotatably attached to the other end portion of the arm member 18 via the pin 20, and between the protrusion 16 </ b> B of the spring seat 16 and the inner peripheral portion of the coil spring 4 and the outer periphery. The gaps S <b> 1 and S <b> 2 are formed between the side support piece 16 </ b> C and the outer periphery of the coil spring 4.

  Therefore, when the torsion angle between the disk plates 7 and 8 and the cam member 6 increases and the arm member 18 rotates about the rotation shaft 9, the protrusion 16B, the outer peripheral support piece 16C, the coil spring 4, The spring seat 16 can be moved in the radial direction of the disk plates 7 and 8 by the gaps S1 and S2.

  In the present embodiment, the arm member 18 can be rotated with respect to the other end portion of the arm member 18 via the pin 20, so that the spring seat 16 can be further prevented from being inclined with respect to the coil spring 4. The posture of the spring seat 16 can be maintained more reliably.

  For this reason, the coil spring 4 can be prevented from being inclined between the spring seat 16 and the pedestal 14, and the coil spring 4 can be normally elastically deformed in the central axis direction. For example, the rigidity can be obtained to obtain the torsional characteristics shown in FIG.

  In addition, since the coil spring 4 can be prevented from tilting, the coil spring 4 can be prevented from being deformed abnormally, and the coil spring 4 can be protected.

  In the present embodiment, the disc plates 7 and 8 are inclined with respect to the radial direction of the disc plates 7 and 8 and extend over a predetermined length. The main body 16 </ b> A of the spring seat 16 has protrusions 16 b and 16 c inserted into the guide grooves 31 and 32. The guide groove 32 is located inward in the radial direction and extends in parallel with the guide groove 31.

  For this reason, when the arm member 18 rotates about the rotation shaft 9 as the cam member 6 rotates, the protrusions 16b and 16c extend from the end surfaces 31a and 32a in the extending direction of the guide grooves 31 and 32. It is possible to move the spring seat 16 in the radial direction of the disc plates 7 and 8 while moving the spring seat 16 relative to the disc plates 7 and 8 by moving between the other end surfaces 31b and 32b in the direction. it can.

  At this time, the spring seat 16 can be prevented from tilting with respect to the coil spring 4 by rotating the spring seat 16 with respect to the arm member 18, and the posture of the spring seat 16 can be maintained.

  Further, when the torsion angle between the disk plates 7 and 8 and the cam member 6 is minimum, the protrusions 16b and 16c are in contact with the end surfaces 31a and 32a in the extending direction of the guide grooves 31 and 32. By restricting the member 18 from rotating more than necessary in the clockwise direction around the rotation shaft 9, one end of the arm member 18 is prevented from contacting the cam surface 6 a of the cam member 6 with a strong contact pressure. can do.

  Therefore, the cam member 6 can be smoothly rotated relative to the disc plates 7 and 8 in a region where the twist angle between the disc plates 7 and 8 and the cam member 6 is small, and the shift position is changed to neutral, so that the internal combustion engine is changed. When the motor is in an idle state or the like, minute vibrations can be reliably attenuated and a rattling sound can be reliably suppressed.

  In the present embodiment, the curvature of the cam surface 6a of the cam member 6 is increased as the torsion angle increases from the initial position of the cam member 6 when the torsion angle between the disk plates 7 and 8 and the cam member 6 is minimum. Consists of things.

  For this reason, the curvature of the cam surface 6a of the cam member 6 with which the arm member 18 contacts can be varied in accordance with the change in the twist angle between the disk plates 7 and 8 and the cam member 6. The torsional rigidity can be reduced by widening the range of the torsion angle with the member 6.

  Further, since the torsional rigidity between the disc plates 7 and 8 and the cam member 6 can be increased as the torsion angle between the disc plates 7 and 8 and the cam member 6 increases, a large torque fluctuation is attenuated by the coil spring 4. However, the rotational torque can be smoothly transmitted between the disk plates 7 and 8 and the cam member 6.

(Second Embodiment)
FIGS. 16-21 is a figure which shows 2nd Embodiment of the torsional vibration damping device based on this invention, attaches | subjects the same number to the same structure as 1st Embodiment, and abbreviate | omits description .

  The torsional vibration 30 of the present embodiment is different from the first embodiment in that the window holes 41 and 42 are formed in the disk plates 7 and 8 and the shapes of the spring seat 43 and the coil spring 44 are different.

  16 to 20, the disc plates 7 and 8 are formed with window holes 41 and 42 as window portions, respectively. The window holes 41, 42 are circumferentially arranged at outer peripheral edges 41 a, 42 a (see FIG. 19), inner peripheral edges 41 b, 42 b located on the inner peripheral side with respect to the outer peripheral edges 41 a, 42 a, and one end of the coil spring 44. One end surfaces 41c and 42c facing each other in the direction, and the other end surfaces 41d and 42d facing the other end of the coil spring 44 in the circumferential direction are provided. The other end surfaces 41d and 42d are composed of opposing surfaces of the column 14 that oppose the one end surfaces 41c and 42c.

  The outer peripheral edges 41a and 42a are curved along the circumferential direction of the disk plates 7 and 8, and the inner peripheral edges 41b and 42b extend substantially linearly.

  Further, outer peripheral side support pieces 41e and 42e are formed on the outer peripheral edges 41a and 42a so as to protrude from the outer peripheral edges 41a and 42a outward in the axial direction of the disk plates 7 and 8, and the inner peripheral edges 41b and 42b have outer peripheral edges. Inner peripheral side support pieces 41f and 42f are formed so as to protrude outward in the axial direction of the disk plates 7 and 8 from 41a and 42a.

  In the present embodiment, the spring seat 43 is located between the disk plates 7 and 8, and the outer diameter of the coil spring 44 is larger than the separation distance of the disk plates 7 and 8.

  For this reason, a part of the coil spring 44 is inserted into the window holes 41 and 42 and protrudes outward of the disk plates 7 and 8 through the window holes 41 and 42.

  The outer peripheral support pieces 41e and 42e and the inner peripheral support pieces 41f and 42f are opposed to the coil spring 44, and the coil spring 44 is provided with the outer peripheral support pieces 41e and 42e and the inner peripheral support pieces 41f and 42f. It is designed to be elastically deformed along.

  As shown in FIG. 21, the spring seat 43 includes a main body 43 </ b> A having a contact surface 43 a with which one end of the coil spring 44 extends and a second end of the coil spring 44 extending from the contact surface 43 a. A protrusion 43B as a first protrusion that protrudes toward the inner periphery of the coil spring 44, and a second protrusion that protrudes in the circumferential direction from the radially outer end of the main body 43A and faces the coil spring 44. 43C of outer peripheral side support pieces as a part.

  A mounting portion 43D is provided on the surface of the spring seat 43 opposite to the contact surface 43a of the main body 43A, and an insertion hole 43d through which the pin 20 is inserted is formed in the mounting portion 43D.

  Further, the main body 43A of the spring seat 43 is provided with a plurality of protrusions 43b and 43c protruding from the main body 43A in the axial direction of the input shaft 26. The protrusions 43b and 43c are inserted into the guide grooves 31 and 32, respectively. Yes.

  In the present embodiment, the length of the main body 43A is formed longer than the length of the main body 16A of the spring seat 16 of the first embodiment, and the window holes 41 and 42 and the guide grooves 31 and 32 are circumferentially arranged. The protrusions 43b and 43c can be reliably inserted into the guide grooves 31 and 32 in a state separated in the direction.

  Further, as shown in FIG. 21, a gap S <b> 1 is formed between the outer peripheral portion of the protrusion 43 </ b> B and the inner peripheral portion of the coil spring 44, and the inner peripheral surface of the outer peripheral support piece 43 </ b> C and the outer periphery of the coil spring 44. A gap S2 is formed between the two portions. That is, one end portion of the coil spring 44 in the extending direction is movable in the radial direction of the disk plates 7 and 8 with respect to the spring seat 43.

  In the present embodiment, when the cam member 6 is twisted to the positive side and the negative side with respect to the disk plates 7, 8, the spring seat 43 is located between the outer peripheral portion of the projection 43 B and the inner peripheral portion of the coil spring 44. The gap S1 and the gap S2 between the inner peripheral surface of the outer peripheral side support piece 43C and the outer peripheral portion of the coil spring 44 move inward in the radial direction.

  At this time, the spring seat 43 further moves radially inward as the protrusions 43b, 43c move radially inward along the guide grooves 31, 32. When the arm member 18 moves inward in the radial direction, the spring seat 43 rotates with respect to the other end portion of the arm member 18 via the pin 20 so that the coil spring 44 does not tilt, and the current posture is maintained. Will be maintained.

  As a result, the coil spring 44 can be prevented from inclining between the spring seat 43 and the pedestal 14, and the coil spring 44 can be normally elastically deformed in the central axis direction. For example, the rigidity can be obtained).

  In addition, since the coil spring 44 can be prevented from tilting, the coil spring 44 can be prevented from being deformed abnormally, and the coil spring 44 can be protected.

In this embodiment, the disk plates 7 and 8 have window holes 41 and 42 through which the coil springs 44 are inserted. Therefore, when the diameter of the coil springs 44 is large, the coil springs 44 are connected to the window holes 41 and 42. Therefore, it is unnecessary to accommodate the entire coil spring 44 between the disk plates 7 and 8.
For this reason, the space | interval of the axial direction of the torsional vibration damping device 40 can be shortened by shortening the space | interval of the disk plates 7 and 8, and the torsional vibration damping device 40 can be reduced in size.

  In the present embodiment, when the disk plates 7 and 8 and the cam member 6 are in the neutral position, both end portions of the coil spring 44 and one end surfaces 41c and 42c and the other end surfaces 41d and 42d of the window holes 41 and 42 are provided. The both ends of the coil spring 44 may be in contact with the one end surfaces 41c, 42c and the other end surfaces 41d, 42d of the window holes 41, 42.

  In each of the above embodiments, 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 provided in the system may be used.

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

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

In each of the above embodiments, the cam surface 6a of the cam member 6 has an elliptical shape. However, the cam surface has a curvature that changes with the change in the twist angle between the disk plates 7 and 8 and the boss 5. If it exists, it is not limited to an elliptical shape.
In the above embodiments, two guide grooves 31 and 32 are provided in parallel to the radial direction. However, there may be three or more guide grooves.

  As described above, the torsional vibration damping device according to the present invention can prevent the elastic member from tilting when the torsion angle of the first rotating member and the second rotating member is increased, and the elastic member The rigidity of the first rotating member and the second rotating member is interposed between the internal combustion engine of the vehicle and the drive transmission system. This is useful as a torsional vibration damping device or the like in which the first rotating member and the second rotating member are connected to each other through an elastic member so as to be relatively rotatable.

DESCRIPTION OF SYMBOLS 1, 40 Torsional vibration damping device 2 1st rotation member 3 2nd rotation member 4, 44 Coil spring (elastic member)
5 Boss (first rotating member)
6 Cam member (first rotating member)
6a Cam surface 7, 8 Disc plate (second rotating member)
9 Rotating shaft (Rotating fulcrum)
14 pedestal (support)
16 Spring seat (holding member)
16A, 43A Main body 16a, 43a Abutting surface 16b, 16c, 43b, 43c Protrusion 16B, 43B Protrusion (first protrusion)
16C, 43C Outer peripheral side support piece (second protrusion)
18 Arm member (torque transmission member)
21 Hysteresis mechanism 26 Input shaft 31 Guide groove (first guide groove)
31a, 32a One end surface in the extending direction 32 Guide groove (second guide groove)
41, 42 Window hole (window)
S1, S2 gap

Claims (7)

A first rotating member;
A second rotating member provided on the same axis as the first rotating member and rotatable relative to the first rotating member;
An elastic member provided between the first rotating member and the second rotating member, and elastically deformed when the first rotating member and the second rotating member rotate relative to each other;
A cam surface is provided on the first rotating member so as to rotate integrally with the first rotating member, and the curvature of the cam surface changes with a change in torsion angle of the first rotating member and the second rotating member. A cam member having
One end portion contacts the cam surface of the cam member, and the other end portion contacts one end portion in the extending direction of the elastic member via the holding member, and the first rotating member, the second rotating member, And the second rotation member by elastically deforming the elastic member by rotating about a rotation fulcrum provided on the second rotation member when the first rotation member and the second rotation member rotate relative to each other. A torque transmission member that transmits rotational torque to and from the member;
The torsional vibration damping device, wherein the holding member is rotatably attached to the other end of the torque transmission member. The elastic member is constituted by a coil spring, and the holding member has a main body having a contact surface with which one end portion in the extending direction of the coil spring contacts, and the other end portion in the extending direction of the coil spring from the contact surface. Projecting toward the inner periphery of the coil spring, and projecting from the radially outer end of the main body in the circumferential direction of the second rotating member, the outer periphery of the coil spring A second projecting portion opposite to
The clearance gap is formed between the said 1st protrusion part and the inner peripheral part of the said coil spring, and between the said 2nd protrusion part and the outer peripheral part of the said coil spring. Torsional vibration damping device. The second rotating member is inclined with respect to the radial direction of the second rotating member and extends over a predetermined length, and the first guiding groove A second guide groove located radially inward and extending in parallel with the first guide groove;
The torsional vibration damping device according to claim 1, wherein the main body of the holding member has a protrusion inserted into the guide groove.   When the torsion angle between the first rotating member and the second rotating member is minimum, the protrusion comes into contact with one end surface in the extending direction of the first guide groove and the second guide groove. The torsional vibration damping device according to claim 3.   The curvature of the cam surface of the cam member increases as the torsion angle increases from the initial position of the cam member when the torsion angle between the first rotation member and the second rotation member is minimum. The torsional vibration damping device according to any one of claims 1 to 4, wherein the torsional vibration damping device is characterized. The first rotating member includes a boss having the cam member on an outer peripheral portion and an input shaft of a transmission connected to an inner peripheral portion;
A pair of disk plates, wherein the second rotating member is disposed on both sides in the axial direction of the cam member, and rotatably supports the torque transmitting member via a rotating shaft constituting the rotating fulcrum portion; A support portion provided on the disk plate and supporting the other end of the elastic member in the extending direction;
6. The torsional vibration damping device according to claim 1, wherein a rotational torque of the internal combustion engine is transmitted to the pair of disk plates.   The torsional vibration damping device according to claim 6, wherein the pair of disk plates have a window portion through which the elastic member is inserted.

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