JP5880405B2 - Torsional vibration damping device - Google Patents

Description

  The present invention is mounted on a vehicle or the like, and connects the first rotating member and the second rotating member via an elastic member so that rotational torque is transmitted between the first rotating member and the second rotating member. The present invention relates to a torsional vibration damping device connected in a freely rotatable manner.

  Conventionally, a drive transmission system having a transmission or the like connected to a drive source may deteriorate drivability due to torsional vibration caused by, for example, rotational fluctuation due to torque fluctuation of the internal combustion engine. A torsional vibration damping device is provided between the drive transmission system and the rotational fluctuation of the internal combustion engine is absorbed by the torsional vibration damping device so as to attenuate the torsional vibration of the drive transmission system.

  The torsional vibration damping device includes a pair of disk plates as a first rotating member that is fastened and released to a flywheel to which the power of the internal combustion engine is transmitted, and a second that is connected to an input shaft extending from the transmission. There is known one provided with a hub plate as a rotating member and a coil spring that rotatably connects the disk plate and the hub plate (for example, see Patent Document 1).

  The coil spring of the torsional vibration damping device extends in the direction orthogonal to the rotational axis direction of the disk plate and in the same direction as the torque transmission direction that is the rotational direction of the disk plate and the hub plate.

JP 2012-67877 A

  However, in such a conventional torsional vibration damping device, it is desired to reduce torque fluctuation in a high torque range where the torsion angle between the disk plate and the hub plate is large. Therefore, the rigidity of the coil spring increases as the torsion angle between the disk plate and the hub plate increases.

  For this reason, the spring rigidity of the elastic member cannot be reduced in the high torque range of the torsional characteristics of the torsional vibration damping device, and it has been difficult to improve the torsional vibration damping performance. In particular, it is desired to reduce the spring rigidity of the coil spring in a high torque range as the internal combustion engine is reduced in size. However, it is difficult to satisfy the requirement in the conventional torsional vibration damping device.

  The present invention has been made to solve the above-described conventional problems, and can reduce the spring rigidity of an elastic member in a high torque region having a large torsion angle, thereby improving the damping performance of torsional vibration. An object of the present invention is to provide a torsional vibration damping device capable of performing

  In order to achieve the above object, the torsional vibration damping device according to the present invention includes: (1) a part of the plurality of elastic members has one end in the extending direction of the elastic member and the other end in the extending direction; The rotating member and the second rotating member are disposed on the first rotating member and the second rotating member so as to be displaced in the direction of the rotation axis of the second rotating member. The second rotating member moves in the direction of the rotation axis as the second rotating member relatively rotates to the positive side or the negative side with respect to one rotating member.

  In this torsional vibration damping device, a part of the plurality of elastic members is arranged such that one end portion in the extending direction of the elastic member and the other end portion in the extending direction are displaced in the rotation axis direction of the first rotating member and the second rotating member. Since the first rotating member and the second rotating member are installed on the first rotating member and the second rotating member, the elastic member becomes the first rotating member as the torsion angle (relative rotation amount) increases. It elastically deforms in the direction of rotation between the rotating member and the second rotating member, that is, the direction inclined with respect to the torque transmission direction.

  In addition to this, as the second rotating member rotates relative to the first rotating member relative to the positive side or the negative side, one end in the extending direction of the elastic member is moved in the rotating shaft direction. Therefore, as the torsion angle between the first rotating member and the second rotating member increases, the component force of the elastic member in the torque transmission direction can be increased.

  As a result, the spring stiffness of the elastic member in the torque transmission direction of the torsional vibration damping device can be made smaller than the spring stiffness of the conventional elastic member that is not inclined, and the torsional vibration damping performance can be improved. For this reason, when the torsional vibration damping device is applied to an internal combustion engine configured with a small cylinder, the spring rigidity of the elastic member can be reduced in a high torque range of the internal combustion engine.

  In the torsional vibration damping device according to the above (1), (2) the first rotating member receives power from a driving source and has a window portion, and a pair of disk plates connected to each other. The second rotating member is formed of a hub plate provided between the disk plates and having a notch formed at a position corresponding to the window, and one end of the elastic member in the extending direction. Is supported on one end in the circumferential direction of the window portion and the notch portion via the first support member, and the other end portion in the extending direction of the elastic member is supported on the second support member via the second support member. Supported by the other circumferential end of the window and the notch, and between the first support member and one end of the pair of disk plates in the extending direction of the first. The support member is movable in the direction of the rotation axis. There is constructed from those formed.

  In this torsional vibration damping device, a gap is formed between the first support member and one end portion in the extending direction of the window portion of one disk plate so that the first support member can move in the rotation axis direction. As the second rotating member rotates relative to the first rotating member relative to the positive side or the negative side, one end portion in the extending direction of the elastic member can be moved in the rotating shaft direction. For this reason, the component force with respect to the torque transmission direction of an elastic member can be enlarged, so that the twist angle of a 1st rotation member and a 2nd rotation member becomes large.

  In the torsional vibration damping device described in (2) above, (3) the first support member is attached in the direction of the rotation axis between the first support member and one end in the extending direction of the window portion. It is comprised from what interposed the energizing member energized.

  In this torsional vibration damping device, the biasing member that biases the first support member in the direction of the rotation axis is interposed between the first support member and one end portion in the extending direction of the window portion. As the second rotating member rotates relative to the rotating member toward the positive side or the negative side, one end portion in the extending direction of the elastic member moves in the direction of the rotating shaft against the urging force of the urging member. be able to.

  For this reason, the elastic member is prevented from suddenly elastically deforming as the torsion angle between the first rotating member and the second rotating member increases, and the rigidity of the elastic member is prevented from rapidly increasing. Can be greatly elastically deformed. Therefore, the spring rigidity of the elastic member can be gradually increased, and a stable torsion characteristic can be obtained.

  In the torsional vibration damping device according to the above (2) or (3), (4) a support surface of the first support member that supports one end portion in the extending direction of the elastic member, an extending direction of the elastic member, and the like. A holding portion is formed on the support surface of the second support member that supports the end portion, and holds the elastic member so that one end in the extending direction and the other end in the extending direction are displaced in the direction of the rotation axis. It is composed of

  This torsional vibration damping device is held on the respective support surfaces of the first support member and the second support member so that one end of the elastic member in the extending direction and the other end in the extending direction are displaced in the rotational axis direction. Since the holding part to be formed is formed, the elastic member can be easily installed in a direction inclined with respect to the torque transmission direction.

  In the torsional vibration damping device according to the above (2) to (4), (5) between one of the pair of disk plates and the hub plate, between the one disk plate and the hub plate. And a hysteresis mechanism for generating a frictional force in the rotation axis direction.

  In this torsional vibration damping device, a hysteresis mechanism for generating a frictional force in the rotational axis direction is interposed between one disk plate and the hub plate, and between the one disk plate and the hub plate. A hysteresis torque can be generated between the hub plate and the hub plate. For this reason, for example, when the driving force is transmitted from the internal combustion engine to the disk plate and the input shaft of the drive transmission system such as a transmission is connected to the hub plate, the torsional resonance of the drive transmission system can be suppressed.

  Also, since the elastic member is installed such that one end portion in the extending direction and the other end portion in the extending direction are displaced in the rotating shaft direction of the first rotating member and the second rotating member, the elastic member is elastically deformed. In addition, the spring stiffness of the elastic member can be applied in the direction of the rotation axis.

  Since the spring stiffness is variable according to the torsion angle between the disc plate and the hub plate, the frictional force between the disc plate and the hub plate can be varied by the spring stiffness. The hysteresis torque can be varied according to the torsion angle.

  ADVANTAGE OF THE INVENTION According to this invention, the spring rigidity of the elastic member of a high torque area with a large torsion angle can be reduced, and the torsional vibration damping device which can improve the damping performance of a torsional vibration can be provided.

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 principal part front view of a torsional vibration damping device. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is CC direction arrow line view of FIG. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is a DD direction arrow line view of FIG. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is BB direction arrow sectional drawing of FIG. It is a figure which shows 1st Embodiment of the torsional vibration damping device which concerns on this invention, and is a figure which shows the whole operation | movement of the torsional vibration damping device 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 partial operation | movement of the torsional vibration damping device at the time of acceleration. 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) is a figure which shows the behavior of a coil spring when the torsion angle of a clutch disc and a hub plate is small at the time of acceleration, (B) is a figure which shows the magnitude | size of the component force of the coil spring of the figure (a). 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) is a figure which shows the behavior of a coil spring when the torsion angle of a clutch disc and a hub plate is large at the time of acceleration, (B) is a figure which shows the magnitude | size of the component force of the coil spring of the figure (a). 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 partial operation | movement of the torsional vibration damping device at the time of deceleration. 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) is a figure which shows the behavior of a coil spring when the torsion angle of a clutch disc and a hub plate is small at the time of deceleration, (B) is a figure which shows the behavior of a coil spring when the torsion angle of a clutch disk and a hub plate is large 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 relationship between the rotation speed of an internal combustion engine, and a torque fluctuation. 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 spring rigidity and hysteresis torque of a coil spring according to a twist angle. It is a figure which shows 2nd Embodiment of the torsional vibration damping device which concerns on this invention, and is a front view of the torsional vibration damping device. It is a figure which shows 2nd Embodiment of the torsional vibration damping device which concerns on this invention, and is EE direction arrow sectional drawing of FIG. It is a figure which shows 2nd Embodiment of the torsional vibration damping device which concerns on this invention, and is FF direction arrow directional cross-sectional view of FIG. It is a figure which shows 2nd Embodiment of the torsional vibration damping device which concerns on this invention, (a) is a figure which shows the behavior of a coil spring when the torsion angle of a clutch disc and a hub plate is small at the time of acceleration, (B) is a figure which shows the behavior of a coil spring when the torsion angle of a clutch disc and a hub plate is large at the time of acceleration. It is a figure which shows 2nd Embodiment of the torsional vibration damping device which concerns on this invention, (a) is a figure which shows the behavior of a coil spring when the torsion angle of a clutch disc and a hub plate is small at the time of deceleration, (B) is a figure which shows the magnitude | size of the component force of the coil spring of the figure (a). It is a figure which shows 2nd Embodiment of the torsional vibration damping device which concerns on this invention, (a) is a figure which shows the behavior of a coil spring when the torsion angle of a clutch disc and a hub plate is large at the time of deceleration, (B) is a figure which shows the magnitude | size of the component force of the coil spring of the figure (a). 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 spring rigidity and hysteresis torque of a coil spring according to a twist angle.

Hereinafter, embodiments of a torsional vibration damping device according to the present invention will be described with reference to the drawings.
(First embodiment)
FIGS. 1-14 is a figure which shows 1st Embodiment of the torsional vibration damping device based on this invention.
First, the configuration will be described.
1 and 2, the torsional vibration damping device 10 is provided on the same axis as the hub plate 11 as the second rotating member and the hub plate 11 so as to be rotatable relative to the hub plate 11. Disc plates 12 and 13 as first rotating members are provided.

  The torsional vibration damping device 10 includes four coil springs 14 as springs that elastically connect the hub plate 11 and the disk plates 12 and 13 in the circumferential direction, and the coil springs 14 are connected to the hub plate 11. Supporting spring seats 15 and 16 are provided.

The hub plate 11 includes a boss 17 and a flange 18 projecting radially outward from the boss 17, and an input shaft 19 of a transmission included in a drive transmission system (not shown) is provided on the inner peripheral portion of the boss 17. Are splined.
Here, the drive transmission system includes a drive line from the torsional vibration damping device 10 such as a transmission, a differential device, and a drive shaft to the drive wheels.

  The disc plates 12 and 13 are disposed on both sides of the hub plate 11 in the rotational axis direction, and the disc plates 12 and 13 are connected by rivets 27 at a plurality of locations on the outer peripheral side in the radial direction. That is, the hub plate 11 is provided between the disk plates 12 and 13.

Four spring accommodating holes 21 are formed in the hub plate 11, and four window portions 22, 23 are formed in the disk plates 12, 13 so as to face the spring accommodating holes 21 (window portions 23). The coil spring 14 is accommodated inside the spring accommodating hole 21 and the window portions 22 and 23.
The spring accommodating hole 21 is constituted by a notch formed by notching the flange 18 radially outward, and constitutes a notch of the present invention.

  In addition, the spring seat 15 and the spring seat 16 each have a circumferential end surface of the coil spring 14 at one end in the circumferential direction (hereinafter simply referred to as one end portion 21a) and the other end in the circumferential direction (hereinafter referred to as the following). The other end portion 21b) is supported. In the torsional vibration damping device 10 of the present embodiment, the spring seat 15 constitutes a first support member, and the spring seat 16 constitutes a second support member.

  Here, the circumferential direction is the same direction as the rotation direction of the disk plates 12, 13 and the hub plate 11, and the radial direction is the same direction as the radial direction of the disk plates 12, 13 and the hub plate 11. The rotation axis direction is the rotation axis direction of the disk plates 12 and 13 and is the same direction as the rotation axis of the input shaft 19.

  As shown in FIGS. 1 and 4 to 6, the spring seats 15, 16 are circumferentially arranged from the seat seating surfaces 15 a, 16 a and the seat seating surfaces 15 a, 16 a as support surfaces in which end windings are formed on the inner periphery. Protruding portions 15b and 16b protruding in the direction are provided.

  An end turn is formed on the inner periphery of the seat seating surfaces 15a, 16a, and this end turn corresponds to one turn or two turns at both ends of the coil spring 14 in the circumferential direction. The end of the coil spring 14 in the circumferential direction is seated.

  One end of the coil spring 14 in the extending direction (hereinafter simply referred to as one end 14a) is engaged with the end turn of the spring seat 15, and the direction of extension of the coil spring 14 is engaged with the end turn of the spring seat 16. The other end (hereinafter simply referred to as the other end 14b) is engaged.

  That is, one end portion 14a and the other end portion 14b of the coil spring 14 are engaged with the respective end turns of the spring seats 15 and 16, so that the rotation of the coil spring 14 is prevented and the coil spring 14 is moved to the spring seat 15, 16 is attached.

  As shown in FIGS. 1 and 6, the one end 21 a and the other end 21 b of the spring accommodating hole 21 are engaged with the back surfaces 15 c and 16 c of the seat seating surfaces 15 a and 16 a of the spring seats 15 and 16. Yes.

  Specifically, the shape of the one end portion 21a and the other end portion 21b of the spring accommodating hole 21 is a shape along the back surfaces 15c and 16c of the spring seats 15 and 16, and the one end portion 21a of the spring accommodating hole 21 and The other end 21b is in close contact with and engaged with the back surfaces 15c and 16c of the spring seats 15 and 16.

  For this reason, the spring seats 15 and 16 are biased by the one end 21 a and the other end 21 b of the spring accommodating hole 21 in response to the biasing force of the coil spring 14, so that the spring seats 15 and 16 are flanged to the hub plate 11. 18 is attached.

  As shown in FIGS. 4 to 6, the window portions 22 and 23 have window frames 22 </ b> A and 23 </ b> A that protrude outward from the disk plates 12 and 13 in the rotation axis direction, and the window frames 22 </ b> A and 23 </ b> A. The window holes 22B and 23B are formed in. The widths of the window holes 22B and 23B in the radial direction are formed to be smaller than the radial lengths of the spring seats 15 and 16.

  The both surfaces of the spring seats 15 and 16 in the rotation axis direction are supported by the window frames 22A and 23A. The rear surfaces of the spring seats 15 and 16 are provided at one end in the circumferential direction of the windows 22 and 23 (hereinafter simply referred to as one end 22C and 23C) and the other end in the circumferential direction (hereinafter simply referred to as the other end 22D and 23D). Contact portions 22E, 23E, 22F, and 23F with which 15c and 16c contact are provided.

  Accordingly, the spring seats 15 and 16 are supported by the one end 21 a and the other end 21 b of the spring accommodating hole 21 and the window frames 22 A and 23 A of the window portions 22 and 23.

  On the other hand, as shown in FIGS. 4 and 6, a gap 24 is formed between one end 23a of the window frame 23A and the side surface of the spring seat 15, and the spring seat 15 is connected to the one end 22a of the window frame 22A. A gap 24 is formed between the first position that contacts and separates from the one end portion 23a of the window frame 23A and the second position that is separated from the one end portion 22a of the window frame 22A and close to the one end portion 23a of the window frame 23A. It is free to move within the range. That is, the spring seat 15 is movable in the direction of the rotation axis of the disk plates 12 and 13.

  Further, both side surfaces of the spring seat 16 are in contact with the other end portion 22b of the window frame 22A and the other end portion 23b of the window frame 23A, and the spring seat 16 does not move in the rotation axis direction of the disk plates 12 and 13. It is like that.

  Further, a leaf spring 25 as an urging member is interposed in the gap 24 between the one end portion 23a of the window frame 23A and the side surface of the spring seat 15, and the leaf spring 25 attaches the spring seat 15 to the disc plate 12. It is energizing towards.

  The leaf spring 25 is formed in a V shape, one member 25a is fixed to one end 23a of the window frame 23A, the other member 25b abuts against the side surface of the spring seat 15, and the one member 25a A connecting portion 25 c with the other member 25 b faces the spring seat 16.

For this reason, the front-end | tip of one member 25a and the other member 25b on the opposite side to the connection part 25c is facing the contact part 23E.
Here, in the torsional vibration damping device 10 of the present embodiment, the one end portion 23a and the contact portion 23E of the window frame 23A constitute one end portion of the window portion 23 in the extending direction.

  As shown in FIG. 6, the protrusion 16b provided on the seat seating surface 16a of the spring seat 16 is provided on the spring seat 16 so that the central axis O1 of the protrusion 16b coincides with the central axis O of the spring seats 15 and 16. It has been.

  Further, the protruding portion 15b provided on the seat seating surface 15a of the spring seat 15 is arranged so that the central axis O2 of the protruding portion 15b is displaced toward the disc plate 13 with respect to the central axis O of the spring seats 15 and 16. 15 is provided.

  For this reason, the one end part 14a and the other end part 14b of the coil spring 14 are attached to the disk plates 12 and 13 so as to be displaced in the rotation axis direction. Here, the projecting portions 15b and 16b constitute a holding portion that holds the one end portion 14a and the other end portion 14b of the coil spring 14 so as to be displaced in the rotation axis direction.

  As shown in FIGS. 1 and 2, the outer peripheral portion of the disc plate 12 is connected to the inner peripheral portion of an annular cushioning plate 26, and the disc plate 12 and the cushioning plate 26 connect the disc plates 12 and 13. They are connected by rivets 27.

  On the both sides in the rotational axis direction of the cushioning plate 26, annular friction materials 29a and 29b are fixed by rivets 28. The friction materials 29a and 29b are fixed to a crankshaft of an internal combustion engine (not shown) as a drive source. It is located between a flywheel (not shown) and a pressure plate of a clutch cover bolted to the flywheel.

  The friction materials 29 a and 29 b are pressed against the pressure plate and brought into frictional contact with the flywheel and the pressure plate, whereby the rotational torque of the internal combustion engine is input to the disk plates 12 and 13.

  Further, when a clutch pedal (not shown) is depressed, the pressure plate releases the pressing of the friction materials 29a and 29b, and the friction materials 29a and 29b are separated from the flywheel, whereby the rotational torque of the internal combustion engine is reduced. , 13 is not input.

When the hub plate 11 rotates relative to the disk plates 12 and 13 in the positive side (R2 direction in FIG. 1) and the negative side opposite to the positive side (R1 direction in FIG. 1), the coil spring 14 is elastic. The spring seat 15 or the spring seat 16 is deformed, that is, compressed, and moves along the window portions 22 and 23.
In the following description, the relative rotation of the disk plates 12 and 13 and the hub plate 11 is expressed as the twist of the disk plates 12 and 13 and the hub plate 11.

  The coil spring 14 is compressed when the hub plate 11 is twisted to the positive side with respect to the disk plates 12 and 13 and when the hub plate 11 is twisted to the negative side with respect to the disk plates 12 and 13. A rotational torque is transmitted between the plate 11 and the disk plates 12 and 13 while absorbing vibration.

  The hub plate 11 is twisted to the positive side with respect to the disk plates 12 and 13 when the vehicle is accelerating. The hub plate 11 is twisted to the negative side with respect to the disk plates 12 and 13 in the engine. It is during deceleration when braking occurs.

  As shown in FIG. 2, an annular guide member 30 is provided between the disc plates 12 and 13 and the boss 17, and the guide member 30 has a rotation center axis of the disc plates 12 and 13 of the hub plate 11. The disk plates 12 and 13 are positioned on the hub plate 11 so as to coincide with the rotation center axis.

  Further, an annular guide member 33 is provided on the outer peripheral portion of the boss 17 and between the flange 18 and the disk plate 13. The guide member 33 is, for example, an elastic material that can be elastically deformed in the direction of the rotation axis. It consists of members.

In the guide member 33, both surfaces of the guide member 33 in the rotation axis direction are in contact with the flange 18 and the disk plate 13, and both surfaces of the guide member 33 in the rotation axis direction are rotated relative to each other by the flange 18 and the disk plate 13. A coating process for suppressing wear of the guide member 33 is performed.
An annular friction material 31 and an annular disc spring 32 are provided between the flange 18 and the disk plate 12.

  The friction material 31 is in frictional contact with the flange 18 with a predetermined frictional force, and the disc spring 32 biases the friction material 31 toward the flange 18. The friction material 31 and the disc spring 32 generate a hysteresis torque between the hub plate 11 and the disk plates 12 and 13 when the hub plate 11 and the disk plates 12 and 13 are twisted. In the torsional vibration damping device 10 of the present embodiment, the friction material 31 and the disc spring 32 constitute a hysteresis mechanism.

  Here, a friction material that contacts the friction material 31 is provided on the facing surface of the flange 18 that faces the friction material 31. Further, instead of the friction material contacting the friction material 31, a coating process having a high frictional force may be applied to the facing surface of the flange 18.

Next, the operation will be described.
When the rotational torque sufficient to contract the coil spring 14 is not applied to the torsional vibration damping device 10, the torsion angle between the hub plate 11 and the disk plates 12 and 13 is substantially zero.

  When the friction materials 29a and 29b are pressed against the pressure plate and frictionally contact the flywheel and the pressure plate, the rotational torque of the internal combustion engine is input to the disk plates 12 and 13 and rotated to the disk plates 12 and 13 via the cushioning plate 26. Torque is transmitted.

  At this time, rotational fluctuation due to torque fluctuation of the internal combustion engine applied to the torsional vibration damping device 10 is transmitted to the input shaft 19 of the transmission while being buffered between the disk plates 12 and 13 and the hub plate 11 by contraction of the coil spring 14. Is done.

  Next, an operation when the hub plate 11 is twisted to the positive side with respect to the disk plates 12 and 13 and an operation when the hub plate 11 is twisted to the negative side will be described. However, the rotational direction of the disk plates 12 and 13 when the rotational torque from the internal combustion engine is transmitted is the R1 direction.

  If the rotational fluctuation of the internal combustion engine increases during acceleration of the vehicle, the torsion angle between the disk plates 12 and 13 and the hub plate 11 increases, and the hub plate 11 is twisted to the positive side with respect to the disk plates 12 and 13. The coil spring 14 is compressed to transmit rotational torque from the disk plates 12 and 13 to the hub plate 11.

  When the torsion angle between the disk plates 12 and 13 and the hub plate 11 increases, the hub plate 11 moves in the R2 direction (positive side) with respect to the disk plates 12 and 13 as the disk plates 12 and 13 rotate in the R1 direction. Will be twisted.

  The operation of the disk plates 12 and 13 and the hub plate 11 at this time will be described with reference to FIGS. Although the disk plate 12 is not shown in FIGS. 8 and 11, the disk plate 12 moves in parallel with the disk plate 13, and thus performs the same operation as the disk plate 13.

  7 to 9, when the twist angle between the disc plates 12 and 13 and the hub plate 11 is small, the contact portions 22E and 23E of the window portions 22 and 23 of the disc plates 12 and 13 spring the spring seat 15. Press toward the sheet 16. At this time, the spring seat 16 is separated from the one end 21 a of the spring accommodation hole 21 of the hub plate 11.

  Further, as the hub plate 11 is twisted in the R2 direction (positive side) with respect to the disk plates 12 and 13, the other end portion 21b of the spring accommodation hole 21 of the hub plate 11 faces the spring seat 16 toward the spring seat 15. Press. At this time, the spring seat 15 is separated from the contact portions 22F and 23F of the window portions 22 and 23.

  Further, as shown in FIG. 9A, the spring seat 15 moves from the first position toward the disc plate 13 against the urging force of the leaf spring 25. Since the torsional vibration damping device 10 is attached to the disk plates 12 and 13 such that one end portion 14a and the other end portion 14b of the coil spring 14 are displaced in the rotation axis direction, the coil spring 14 is in the torque transmission direction. A component force F1 is generated in the twisting direction of the disk plates 12 and 13 and the hub plate 11 (see FIG. 9B).

  When the torsion angle between the disk plates 12 and 13 and the hub plate 11 is further increased, the spring seat 15 further moves toward the disk plate 13 against the urging force of the leaf spring 25 as shown in FIG. Move to the second position.

  At this time, the coil spring 14 generates a larger component force F1 with respect to the torsional direction of the disk plates 12 and 13 and the hub plate 11 in the torque transmission direction (see FIG. 10B). As a result, the spring rigidity of the coil spring 14 in the torque transmission direction can be reduced as the twist angle between the disk plate 12 and the hub plate 11 increases.

  On the other hand, since the friction material 31 and the disc spring 32 are interposed between the disc plate 12 and the hub plate 11, the disc spring 32 is elastic when the hub plate 11 is twisted in the R2 direction with respect to the disc plate 12. A hysteresis torque is generated between the disk plate 12 and the hub plate 11 by the force.

  In the torsional vibration damping device 10 of the present embodiment, the coil spring 14 is compressed because the one end portion 14a and the other end portion 14b of the coil spring 14 are attached to the disk plates 12 and 13 so as to be displaced in the rotation axis direction. When this occurs, the spring stiffness of the coil spring 14 indicated by F2 acts in the direction of the rotation axis, and this spring stiffness increases as the torsion angle between the disk plate 12 and the hub plate 11 increases.

  That is, as the torsion angle between the disk plate 12 and the hub plate 11 increases, the disk plate 13 is attached to the outer side in the rotation axis direction (right side in FIGS. 2, 9, and 10) by the spring rigidity F2 of the coil spring 14. The urging force to be increased is increased.

  Since the disc plates 12 and 13 are integrally provided, when the disc plates 12 and 13 are urged to the right by the coil spring 14, the disc plates 12 and 13 are shown in FIG. 9 and FIG. 10, it moves to the right.

  Since the friction material 31 and the disc spring 32 are interposed between the disc plate 12 and the flange 18, when the disc plates 12, 13 move to the right with respect to the hub plate 11, the disc plate 12 and the flange 18. And the amount of compression of the disc spring 32 increases. For this reason, the hysteresis torque generated between the disk plate 12 and the hub plate 11 increases.

  On the other hand, when the vehicle is decelerated, the rotational torque of the internal combustion engine is reduced and engine braking occurs, so that the rotational torque is input to the hub plate 11 from the input shaft 19 of the transmission.

  When the rotational fluctuation of the internal combustion engine increases during deceleration, the torsion angle between the disk plates 12 and 13 and the hub plate 11 increases, and the hub plate 11 twists to the negative side (R1 side) with respect to the disk plates 12 and 13. As a result, the coil spring 14 is compressed and rotational torque is transmitted from the hub plate 11 to the disk plates 12 and 13.

  As the torsion angle between the disk plates 12 and 13 and the hub plate 11 increases, the hub plate 11 rotates from the neutral position to the R1 direction (negative side) with respect to the disk plates 12 and 13 as the hub plate 11 rotates in the R1 direction. ).

  The operation of the disk plates 12 and 13 and the hub plate 11 at this time will be described with reference to FIGS. In FIG. 11, the disk plate 12 is not illustrated, but the disk plate 12 moves in parallel with the disk plate 13, and thus operates in the same manner as the disk plate 13.

  In FIG. 11, when the hub plate 11 is twisted in the R1 direction (negative side) with respect to the disk plates 12 and 13, the contact portions 22F and 23F of the window portions 22 and 23 of the disk plates 12 and 13 cause the spring seat 16 to move. Press toward the spring seat 15. At this time, the other end 21 b of the spring accommodating hole 21 of the hub plate 11 is separated from the spring seat 16.

  Further, as the hub plate 11 is twisted in the R1 direction (negative side) with respect to the disk plates 12 and 13, the one end 21a of the spring accommodation hole 21 of the hub plate 11 moves the spring seat 15 toward the spring seat 16. Press. At this time, the spring seat 16 is separated from the contact portions 22E and 23E of the window portions 22 and 23.

  As shown in FIG. 12A, since the spring seat 16 does not move in the rotation axis direction, the component force F1 of the coil spring 14 with respect to the torsional direction of the disk plates 12 and 13 and the hub plate 11 which is the torque transmission direction is It is smaller than the same twist angle on the acceleration side.

  When the twist angle between the disc plates 12 and 13 and the hub plate 11 is further increased, the spring seat 16 is further separated from the contact portions 22E and 23E of the window portions 22 and 23. Also at this time, as shown in FIG. 12B, the spring seat 16 does not move in the direction of the rotation axis, so that the coil spring 14 is divided with respect to the torsional direction of the disk plates 12 and 13 and the hub plate 11 in the torque transmission direction. The force is the same as when the negative twist angle is small and does not change. Therefore, the spring rigidity of the coil spring 14 in the torque transmission direction is larger than that on the positive side.

  On the other hand, since the friction material 31 and the disc spring 32 are interposed between the disc plate 12 and the hub plate 11, the disc spring 32 is elastic when the hub plate 11 is twisted in the R2 direction with respect to the disc plate 12. A hysteresis torque is generated between the disk plate 12 and the hub plate 11 by the force.

  In the torsional vibration damping device 10 of the present embodiment, on the negative side of the torsional characteristic, when the coil spring 14 is compressed, the spring stiffness of the coil spring 14 acts in the direction of the rotation axis. It is smaller than that, and does not change even if the torsion angle between the disk plates 12 and 13 and the hub plate 11 increases.

  For this reason, even when the disk plate 12 is urged in the direction of the rotation axis by the coil spring 14, the change in the compression amount of the disc spring 32 is small compared to the acceleration side, and hysteresis is generated between the disk plate 12 and the hub plate 11. The torque becomes constant according to changes in the twist angle between the disk plates 12 and 13 and the hub plate 11.

  Here, in the leaf spring 25 of the present embodiment, the connecting portion 25c between one member 25a and the other member 25b faces the spring seat 16. For this reason, when the disk plates 12 and 13 and the hub plate 11 return to the neutral position (the twist angle is substantially 0), the spring seat 15 can be brought into contact with the one member 25b.

  Therefore, it is possible to prevent the spring seat 15 from being blocked by the leaf spring 25 to a position where it comes into contact with the contact portions 22E and 23E, and the spring seat 15 can be smoothly moved to the contact portions 22E and 23E.

  As described above, the torsional vibration damping device 10 according to the present embodiment is configured so that the one end portion 14a and the other end portion 14b of the coil spring 14 are displaced in the rotational axis direction of the disk plates 12 and 13 and the disk plates 12 and 13 and the hub. Installed on plate 11.

  Therefore, as the torsional angle between the disk plates 12 and 13 and the hub plate 11 increases, the coil spring 14 is compressed in a direction inclined with respect to the torque transmission direction that is the rotational direction of the disk plates 12 and 13 and the hub plate 11. Can be made.

  In addition, as the hub plate 11 is twisted to the positive side (acceleration side) with respect to the disk plates 12 and 13, the one end portion 14a of the coil spring 14 is moved in the direction of the rotation axis. As the torsion angle between 12, 13 and the hub plate 11 increases, the component force F2 of the coil spring 14 in the torque transmission direction can be increased.

As a result, in the high torque range, the spring stiffness of the coil spring 14 in the torque transmission direction of the torsional vibration damping device 10 can be made smaller than the spring stiffness of the conventional coil spring that is not inclined, and the torsional vibration on the acceleration side The damping performance can be improved.
For this reason, it is possible to generate a jagged noise generated by torsional vibration using a rotational fluctuation due to a torque fluctuation of the internal combustion engine as a vibration source.

  Here, the jagged noise is an unusual noise called a jagged noise generated by collision of a pair of idle gears of a transmission gear set due to torsional vibration using a fluctuation of rotation caused by torque fluctuation of an internal combustion engine as a vibration source.

  In particular, the torsional vibration damping device 10 of the present embodiment can reduce the spring rigidity of the coil spring 14 in the high torque range of the internal combustion engine, and thus the small cylinder whose drivability tends to deteriorate in the high torque range of the internal combustion engine. This is preferable when applied to the internal combustion engine.

  On the other hand, the torsional vibration damping device 10 of the present embodiment can increase the hysteresis torque as the torsional angle between the disk plates 12 and 13 and the hub plate 11 increases on the acceleration side. Generation | occurrence | production can be suppressed.

  Specifically, when the rotational speed of the internal combustion engine increases, the rotational speed of the internal combustion engine passes through a rotational speed corresponding to a torsional resonance point (for example, an arbitrary steady rotational speed). Conventionally, when the rotational speed of the internal combustion engine passes through the torsional resonance point, the torsional vibration increases due to the torsional resonance of the drive transmission system in the vicinity of the resonance point, as indicated by a broken line in FIG. An abnormal noise occurs in the passenger compartment.

  In contrast, the torsional vibration damping device 10 of the present embodiment can increase the hysteresis torque as the torsional angle between the disk plates 12 and 13 and the hub plate 11 increases on the acceleration side. For this reason, the broken line in FIG. 13 can be reduced to the position indicated by the solid line, and the torsional resonance of the drive transmission system can be suppressed, and the generation of a booming noise can be suppressed.

  As shown in FIG. 14, the torsional vibration damping device 10 of the present embodiment has a coil spring 14 in a high torque region where the torsional angle between the disk plates 12 and 13 and the hub plate 11 increases on the positive side of the torsional characteristics. The spring stiffness is smaller than that in the case of using a conventional coil spring (indicated by a one-dot chain line), and the hysteresis torque can be increased. As a result, it is possible to improve the vibration damping performance and to suppress the generation of the jagged noise and the booming noise.

  Further, in the low torque region and the medium torque region where the twist angle between the disk plates 12 and 13 and the hub plate 11 is small, the drivability may be deteriorated if the spring stiffness of the coil spring 14 is low.

  In the torsional vibration damping device 10 according to the present embodiment, when the torsion angle between the disk plates 12 and 13 and the hub plate 11 is small, the torsion angle between the disk plates 12 and 13 and the hub plate 11 is large. The inclination of the coil spring 14 in the rotation axis direction can be reduced.

  For this reason, in the low torque region and the intermediate torque region, the spring rigidity of the coil spring 14 can be maintained at a high spring rigidity equivalent to that of the conventional coil spring, so that drivability can be improved.

  Further, in the torsional vibration damping device 10 of the present embodiment, a gap 24 is formed between the spring seat 15 and the one end portion 23a of the window frame 23A of the disk plate 13 so that the spring seat 15 can move in the direction of the rotation axis. . Therefore, the one end portion 14a of the coil spring 14 can be moved in the direction of the rotation axis as the torsion angle between the disk plates 12 and 13 and the hub plate 11 increases on the acceleration side. For this reason, the component force F1 with respect to the torque transmission direction of the coil spring 14 can be increased as the torsion angle between the disc plates 12 and 13 and the hub plate 11 increases.

  Further, the torsional torsional vibration damping device 10 of the present embodiment includes a leaf spring 25 that urges the spring sheet 15 in the rotational axis direction between the spring sheet 15 and the one end portion 23a of the window frame 23A of the disk plate 13. Intervened.

  Therefore, as the hub plate 11 is twisted to the positive side with respect to the disk plates 12 and 13, the one end portion 14 a of the coil spring 14 can be moved in the direction of the rotation axis against the urging force of the plate spring 25. it can.

  Therefore, the coil spring 14 is prevented from abruptly compressing as the torsion angle between the disk plates 12 and 13 and the hub plate 11 increases, and the rigidity of the coil spring 14 is prevented from increasing suddenly. It can be compressed greatly. As a result, the spring rigidity of the coil spring 14 can be gradually increased, and a stable torsion characteristic can be obtained.

  In addition, the torsional torsional vibration damping device 10 of the present embodiment includes a central axis O2 of the protrusion 15b provided on the seat seating surface 15a of the spring seat 15 and a protrusion provided on the seat seating surface 16a of the spring seat 16. The one end 14a and the other end 14b of the coil spring 14 are shifted in the rotation axis direction by shifting the center axis O1 of 16b in the rotation axis direction with respect to the center axis O.

  For this reason, the coil spring 14 can be easily installed in a direction inclined with respect to the torque transmission direction.

  Further, in the torsional vibration damping device 10 of the present embodiment, when the coil spring 14 is compressed, the friction material 31 and the dish between the disk plate 13 and the flange 18 on which the spring stiffness of the coil spring 14 indicated by F2 acts. A spring 32 was interposed.

  Therefore, the hysteresis torque can be increased as the torsion angle between the disk plates 12 and 13 and the hub plate 11 increases on the acceleration side, and the torsional resonance of the drive transmission system can be suppressed.

  Further, in the torsional vibration damping device 10 of the present embodiment, the urging member is constituted by the leaf spring 25, but is not limited to the leaf spring 25.

(Second Embodiment)
FIGS. 15-21 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 .

  15 to 17, the disk plates 12 and 13 are formed with four window portions 41 and 42, respectively, facing the spring accommodating hole 21, and inside the spring accommodating hole 21 and the window portions 41 and 42, respectively. A coil spring 14 is accommodated. One end portion 14a of the coil spring 14 is supported by a spring seat 43 as a first support member, and the other end portion 14b of the coil spring 14 is supported by a spring seat 44 as a second support member. Yes.

  As shown in FIG. 17, the spring seat 43 and the spring seat 44 are configured to support the circumferential end surfaces of the coil spring 14 on one end 21 c and the other end 21 d of the spring accommodation hole 21, respectively.

Further, the seating surfaces 43a and 44a of the spring seats 43 and 44 are provided with projecting portions 43b and 44b that protrude in the circumferential direction from the seating seating surfaces 43a and 44a.
The window portions 41 and 42 have window frames 41A and 42A that protrude outward from the disk plates 12 and 13 in the rotation axis direction, and window holes 41B and 42B are formed in the window frames 41A and 42A. . The radial width of the window holes 41B and 42B is formed smaller than the radial length of the spring seats 43 and 44.

Both surfaces of the spring seats 43 and 44 in the rotation axis direction are supported by the window frames 41A and 42A. The circumferential ends of the windows 41 and 42 (hereinafter simply referred to as one end portions 41C and 42C) and the other circumferential ends (hereinafter simply referred to as other end portions 41D and 42D) are the back surfaces of the spring seats 43 and 44. Contact portions 41E, 42E, 41F, and 42F with which 43c and 44c abut are provided.
Therefore, the spring seats 43 and 44 are supported by the one end portion 21 c and the other end portion 21 d of the spring accommodation hole 21 and the window frames 41 A and 42 A of the window portions 41 and 42.

  On the other hand, a gap 45 is formed between the one end portion 42a of the window frame 42A and the side surface of the spring seat 43, and the spring seat 43 abuts on the one end portion 41a of the window frame 41A, and one end portion of the window frame 42A. It is movable within the range of the gap 45 between a first position that is separated from 42a and a second position that is separated from one end 41a of the window frame 41A and close to one end 42a of the window frame 42A. . That is, the spring seat 43 is movable in the direction of the rotation axis of the disk plates 12 and 13.

  Further, both side surfaces of the spring seat 44 are in contact with the other end portion 41b of the window frame 41A and the other end portion 42b of the window frame 42A, and the spring seat 44 does not move in the rotation axis direction of the disk plates 12 and 13. It is like that.

  Further, a leaf spring 46 as an urging member is interposed in the gap 45 between the one end portion 42a of the window frame 42A and the side surface of the spring seat 43, and the leaf spring 46 attaches the spring seat 43 to the disc plate 12. It is energizing towards.

  The leaf spring 46 is formed in a V-shape, one member 46a is fixed to one end 42a of the window frame 42A, the other member 46b abuts against the side surface of the spring seat 43, and the one member 46a A connecting portion 46 c with the other member 46 b faces the spring seat 44.

For this reason, the tips of one member 46a and the other member 46b opposite to the connecting portion 46c are opposed to the contact portion 42E.
Here, in the torsional vibration damping device 10 of the present embodiment, the one end portion 42a and the contact portion 42E of the window frame 42A constitute one end portion of the window portion 42 in the extending direction.

  Further, the protruding portion 44 b provided on the seat seating surface 44 a of the spring seat 44 is provided on the spring seat 44 so that the central axis O 1 of the protruding portion 44 b coincides with the central axis O of the spring seats 43 and 44.

  Further, the protruding portion 44b provided on the seat seating surface 43a of the spring seat 43 is arranged so that the central axis O2 of the protruding portion 43b is displaced toward the disc plate 13 with respect to the central axis O of the spring seats 43 and 44. 43.

  For this reason, the one end part 14a and the other end part 14b of the coil spring 14 are attached to the disk plates 12 and 13 so as to be displaced in the rotation axis direction. Here, the projecting portions 43b and 44b constitute a holding portion that holds the one end portion 14a and the other end portion 14b of the coil spring 14 so as to be displaced in the rotation axis direction.

  As shown in FIG. 16, an annular guide member 47 is provided on the outer periphery of the boss 17 and between the flange 18 and the disk plate 12, and this guide member 47 is, for example, in the direction of the rotation axis. It is comprised from the elastic member which can be elastically deformed.

  In the guide member 47, both surfaces of the guide member 47 in the rotation axis direction are in contact with the flange 18 and the disk plate 12, and both surfaces of the guide member 47 in the rotation axis direction are caused by relative rotation between the flange 18 and the disk plate 12. A coating process for suppressing wear of the guide member 47 is performed.

  An annular friction material 48 and an annular disc spring 49 are provided between the flange 18 and the disk plate 13.

  The friction material 48 is in frictional contact with the flange 18 with a predetermined friction force, and the disc spring 49 urges the friction material 48 toward the flange 18. The friction material 48 and the disc spring 49 generate a hysteresis torque between the hub plate 11 and the disk plates 12 and 13 when the hub plate 11 and the disk plates 12 and 13 are twisted. In the torsional vibration damping device 10 of the present embodiment, the friction material 48 and the disc spring 49 constitute a hysteresis mechanism.

Next, the operation will be described.
An operation when the hub plate 11 is twisted to the positive side with respect to the disk plates 12 and 13 and an operation when the hub plate 11 is twisted to the negative side will be described. However, the rotational direction of the disk plates 12 and 13 when the rotational torque from the internal combustion engine is transmitted is the R1 direction.

  If the rotational fluctuation of the internal combustion engine increases during acceleration of the vehicle, the torsion angle between the disk plates 12 and 13 and the hub plate 11 increases, and the hub plate 11 is twisted to the positive side with respect to the disk plates 12 and 13. The coil spring 14 is compressed to transmit rotational torque from the disk plates 12 and 13 to the hub plate 11.

  When the torsion angle between the disk plates 12 and 13 and the hub plate 11 increases, the hub plate 11 moves in the R2 direction (positive side) with respect to the disk plates 12 and 13 as the disk plates 12 and 13 rotate in the R1 direction. Will be twisted.

  When the disc plates 12 and 13 rotate in the R1 direction, the contact portions 41F and 42F of the window portions 41 and 42 of the disc plates 12 and 13 press the spring seat 44 toward the spring seat 43. At this time, the other end portion 21 d of the spring accommodation hole 21 of the hub plate 11 is separated from the spring seat 44.

  Further, as the hub plate 11 is twisted in the R2 direction (positive side) with respect to the disc plates 12 and 13, the one end 21c of the spring accommodation hole 21 of the hub plate 11 moves the spring seat 43 toward the spring seat 44. Press. At this time, the spring seat 43 is separated from the contact portions 41E and 42E of the window portions 41 and 42.

  At this time, as shown in FIG. 18A, the spring seat 44 does not move in the direction of the rotation axis, so the component force of the coil spring 14 with respect to the torsional direction of the disk plates 12 and 13 and the hub plate 11 that is the torque transmission direction. Is smaller than the negative side.

  When the twist angle between the disk plates 12 and 13 and the hub plate 11 is further increased, the spring seat 44 is further separated from the contact portions 41E and 42E of the window portions 41 and 42. At this time, as shown in FIG. 18B, since the spring seat 44 does not move in the direction of the rotation axis, the component force of the coil spring 14 with respect to the torsional direction of the disk plates 12 and 13 and the hub plate 11 which is the torque transmission direction is ,It does not change.

  Further, since the friction material 48 and the disc spring 49 are interposed between the disc plate 13 and the hub plate 11, when the hub plate 11 is twisted in the R <b> 2 direction with respect to the disc plate 13, the elasticity of the disc spring 49. A hysteresis torque is generated between the disk plate 13 and the hub plate 11 by the force.

On the other hand, when the vehicle is decelerated, the rotational torque of the internal combustion engine is reduced and engine braking occurs, so that the rotational torque is input to the hub plate 11 from the input shaft 19 of the transmission.
If the rotational fluctuation of the internal combustion engine increases during deceleration, the torsion angle between the disk plates 12 and 13 and the hub plate 11 increases, and the hub plate 11 is twisted to the negative side with respect to the disk plates 12 and 13, thereby causing a coil spring. 14 compresses and transmits rotational torque from the hub plate 11 to the disk plates 12 and 13.

  When the hub plate 11 is twisted in the R1 direction (negative side) with respect to the disc plates 12 and 13, the contact portions 41E and 42E of the window portions 41 and 42 of the disc plates 12 and 13 become the spring seat 43 to the spring seat 44. Press towards. At this time, the one end 21c of the spring accommodation hole 21 of the hub plate 11 is separated from the spring seat 43.

Further, as the hub plate 11 is twisted in the R1 direction (negative side) with respect to the disk plates 12 and 13, the other end 21d of the spring accommodation hole 21 of the hub plate 11 faces the spring seat 44 toward the spring seat 43. And press.
At this time, the spring seat 44 is separated from the contact portions 41F and 42F of the window portions 41 and 42.

  Further, as shown in FIG. 19A, the spring seat 43 moves from the first position toward the disk plate 13 against the urging force of the leaf spring 46. Since the torsional vibration damping device 10 is attached to the disk plates 12 and 13 such that one end portion 14a and the other end portion 14b of the coil spring 14 are displaced in the rotation axis direction, the coil spring 14 is in the torque transmission direction. A component force F1 is generated in the twisting direction of the disk plates 12 and 13 and the hub plate 11 (see FIG. 19B).

  When the torsion angle between the disk plates 12 and 13 and the hub plate 11 is further increased, the spring seat 15 further moves toward the disk plate 13 against the urging force of the leaf spring 25 as shown in FIG. Move to the second position.

  At this time, the coil spring 14 generates a larger component force F1 with respect to the torsional direction of the disk plates 12 and 13 and the hub plate 11 in the torque transmission direction (see FIG. 20B). As a result, the spring rigidity of the coil spring 14 in the torque transmission direction can be reduced as the twist angle between the disk plate 12 and the hub plate 11 increases.

  On the other hand, since the friction material 48 and the disc spring 49 are interposed between the disc plate 13 and the hub plate 11, when the hub plate 11 is twisted in the R <b> 2 direction with respect to the disc plate 12, the elasticity of the disc spring 49. A hysteresis torque is generated between the disk plate 12 and the hub plate 11 by the force.

  In the torsional vibration damping device 10 of the present embodiment, the coil spring 14 is compressed because the one end portion 14a and the other end portion 14b of the coil spring 14 are attached to the disk plates 12 and 13 so as to be displaced in the rotation axis direction. When this occurs, the spring stiffness of the coil spring 14 indicated by F2 also acts in the direction of the rotational axis, and this spring stiffness increases as the torsion angle between the disc plate 12 and the hub plate 11 increases.

  That is, as the torsional angle between the disk plate 12 and the hub plate 11 increases, the disk plate 13 is attached to the outer side in the rotational axis direction (to the left in FIGS. 16, 19, and 20) by the spring rigidity F2 of the coil spring 14. The urging force to be increased is increased.

  Since the guide member 47 interposed between the disk plate 12 and the flange 18 is made of an elastic member, the guide member 47 rotates when the disk plates 12 and 13 move to the left with respect to the hub plate 11. Compress in the axial direction. At this time, the distance between the flange 18 and the disk plate 13 increases, and the compression amount of the disc spring 49 decreases. For this reason, the hysteresis torque generated between the disk plate 13 and the hub plate 11 is reduced.

  As described above, the torsional vibration damping device 10 of the present embodiment is configured so that the one end portion 14a and the other end portion 14b of the coil spring 14 are displaced in the rotational axis direction of the disc plates 12, 13, and the disc plates 12, 13, and It was installed on the hub plate 11.

  For this reason, as the torsional angle between the disk plates 12 and 13 and the hub plate 11 increases on the deceleration side, the coil spring is inclined in a direction inclined with respect to the torque transmission direction which is the rotational direction of the disk plates 12 and 13 and the hub plate 11. 14 can be compressed.

  In addition, as the hub plate 11 is twisted to the negative side with respect to the disk plates 12 and 13, the one end portion 14a of the coil spring 14 is moved in the direction of the rotation axis. As the torsion angle of the hub plate 11 increases, the component force F2 of the coil spring 14 in the torque transmission direction can be increased.

As a result, the spring stiffness of the coil spring 14 in the torque transmission direction of the torsional vibration damping device 10 can be made smaller than that of a conventional coil spring that is not inclined, and the damping performance of the torsional vibration on the deceleration side is improved. Can be made.
For this reason, it is possible to generate a jagged noise generated by torsional vibration using a rotational fluctuation due to a torque fluctuation of the internal combustion engine as a vibration source.

  Specifically, the rotational fluctuation of the internal combustion engine during acceleration is large in the low speed rotation region of the internal combustion engine, and the rotational fluctuation of the internal combustion engine during deceleration is large in the high speed rotation region of the internal combustion engine.

  Therefore, by increasing the hysteresis torque of the torsional vibration damping device 10 in the vicinity of the torsional resonance point during acceleration, the torsional resonance of the drive transmission system in the low rotation region is suppressed, and in the high rotation region where the rotational fluctuation of the internal combustion engine is large during deceleration. Thus, it is necessary to suppress the torsional vibration by increasing the damping force by reducing the hysteresis torque of the torsional vibration damping device 10.

  As shown in FIG. 21, the torsional vibration damping device 10 of the present embodiment has a coil spring 14 in a high torque region where the torsion angle between the disk plates 12 and 13 and the hub plate 11 is large on the positive side of the torsional characteristics. The spring stiffness is smaller than when a conventional coil spring (indicated by a one-dot chain line) is used, and the hysteresis torque can be reduced. For this reason, the torsional vibration can be suppressed by increasing the damping force of the drive transmission system during deceleration.

  That is, in the torsional vibration damping device 10 of the present embodiment, when the coil spring 14 is compressed, the disk plate 13 on the side opposite to the disk plate 12 on which the spring rigidity of the coil spring 14 indicated by F2 acts and the flange 18 are applied. A friction material 48 and a disc spring 49 are interposed therebetween.

  Therefore, the hysteresis torque can be reduced as the torsional angle between the disk plates 12 and 13 and the hub plate 11 increases on the deceleration side, and the torsional vibration can be attenuated.

  Further, the spring stiffness and hysteresis torque of the coil spring 14 can be increased during acceleration than during deceleration. For this reason, at the time of acceleration, the hysteresis torque of the torsional vibration damping device 10 can be increased near the torsional resonance point, and the torsional resonance of the drive transmission system in the low rotation region can be suppressed.

  In the torsional vibration damping device 10 of the present embodiment, all the coil springs 14 are inclined with respect to the torque transmission direction, but the present invention is not limited to this. For example, the coil springs 14 positioned above and below in FIG. 15 may be tilted in the same manner as the coil spring 14 of the present embodiment, and the coil springs 14 positioned on the left and right may not be tilted. That is, a part of the coil spring 14 may be inclined.

Even if comprised in this way, the spring rigidity of the coil spring 14 at the time of deceleration can be made smaller than before, and the hysteresis torque can be made smaller than before.
Further, in the torsional vibration damping device 10 of the present embodiment, the rotational direction of the disk plates 12 and 13 when the rotational torque from the internal combustion engine is transmitted is the R1 direction, but the rotational direction is limited to this. It is not a thing.

  Here, in the torsional vibration damping device 10 of each of the above embodiments, the outer peripheral portion of the boss 17 and the inner peripheral portion of the flange 18 are spline-fitted, and a part of the spline of the boss 17 and a part of the spline of the flange 18 are fitted. A small spring may be interposed between the two.

  In this way, minute torsional vibration generated between the boss 17 and the flange 18 can be absorbed by the small spring. For this reason, when the variable torque of the internal combustion engine is small, that is, when the torsion angle between the hub plate 11 and the disk plates 12 and 13 is small, such as when shifting to neutral in the idle state, the shift in the no-load state is performed. Generation of rattling noise, so-called rattling noise, from the gear pair of the machine can be suppressed.

  Further, the torsional vibration damping device 10 of the present embodiment is interposed between the internal combustion engine of the vehicle and the drive transmission system having the transmission, but is not limited thereto, and is provided in the drive transmission system of the vehicle or the like. Any torsional vibration damping device can be used.

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

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

  As described above, the torsional vibration damping device according to the present invention has the effect that the spring rigidity of the elastic member in the high torque region having a large torsion angle can be reduced, and the torsional vibration damping performance can be improved. The first rotating member and the second rotating member are mounted on a vehicle or the like via the elastic member so that the rotating torque is transmitted between the first rotating member and the second rotating member. It is useful as a torsional vibration damping device that is rotatably connected.

  DESCRIPTION OF SYMBOLS 10 ... Torsional vibration damping device, 11 ... Hub plate (2nd rotation member), 12, 13 ... Disk plate (1st rotation member), 14 ... Coil spring (elastic member), 14a ... One end part (elastic member) One end part in the extending direction), 14b ... the other end part (the other end part in the extending direction of the elastic member), 15, 43 ... the spring seat (first support member), 15a, 16a, 43a, 44a ... the seat seating surface ( Support surface), 15b, 16b, 43b, 44b ... Projection (holding part), 16, 44 ... Spring seat (second support member), 21 ... Spring accommodating hole (notch), 21a, 21c ... One end (One end in the circumferential direction of the notch), 21b, 21d ... the other end (the other end in the circumferential direction of the notch), 22, 23, 41, 42 ... window, 23E, 42E ... abutment (One end in the extending direction of the window), 23a, 42 ... one end (one end in the extending direction of the window), 24, 45 ... clearance, 25, 46 ... leaf spring (biasing member), 31, 48 ... friction material (hysteresis mechanism), 32, 49 ... disc spring ( Hysteresis mechanism)

Claims (5)

A first rotating member; a second rotating member provided coaxially with the first rotating member so as to be relatively rotatable with respect to the first rotating member; and the first rotating member; The first rotating member is provided between the first rotating member and the first rotating member when the second rotating member rotates relative to the positive side and the negative side opposite to the positive side with respect to the first rotating member. And a plurality of elastic members elastically deformed between the rotating member and the second rotating member,
A part of the plurality of elastic members is configured such that one end portion in the extending direction and the other end portion in the extending direction of the elastic member are displaced in the rotation axis direction of the first rotating member and the second rotating member, Installed on the first rotating member and the second rotating member;
One end of the elastic member in the extending direction moves in the direction of the rotation axis as the second rotating member rotates relative to the positive side or the negative side with respect to the first rotating member. Torsional vibration damping device characterized by The first rotating member is composed of a pair of disk plates that transmit power from a driving source and that each have a window portion and are connected to each other.
The second rotating member is provided between the disk plates, and includes a hub plate in which a notch is formed at a position corresponding to the window,
One end portion in the extending direction of the elastic member is supported by one end portion in the circumferential direction of the window portion and the notch portion via the first support member, and the other end portion in the extending direction of the elastic member is Supported by the other end in the circumferential direction of the window and the notch through a second support member;
A gap is formed between the first support member and one end portion in the extending direction of one of the pair of disk plates so that the first support member is movable in the rotation axis direction. The torsional vibration damping device according to claim 1.   An urging member for urging the first support member in the direction of the rotation axis is interposed between the first support member and one end portion in the extending direction of the window portion. 2. The torsional vibration damping device according to 2.   On the support surface of the first support member that supports one end portion in the extending direction of the elastic member and on the support surface of the second support member that supports the other end portion in the extending direction of the elastic member, 4. The torsional vibration damping device according to claim 2, wherein a holding portion is formed to hold one end portion in the extending direction and the other end portion in the extending direction so as to be displaced in the rotation axis direction.   A hysteresis mechanism for generating a frictional force in the rotational axis direction is interposed between the one disk plate and the hub plate between one of the pair of disk plates and the hub plate. The torsional vibration damping device according to any one of claims 2 to 4.

Images