JP2015083847A - Dynamic damper device and lock-up device of torque converter - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress the generation of noise and wearing at each part when an inertia member is largely contacted in a dynamic damper device.SOLUTION: A dynamic damper device is equipped with a damper plate portion 45, an inertia ring 46, and a damper mechanism 48. The damper plate portion 45 is coupled to an intermediate member 34. The inertial ring 46 is disposed so as to relatively rotate with the damper plate portion 45 in a twist angle area in a predetermined range. The damper mechanism 48 has low stiffness twist characteristics in a low twist angle area with the damper plate 45 and the inertial ring 46, and high stiffness twist characteristics with higher stiffness than the low stiffness twist characteristics in a high twist angle area larger than the low twist angle area. The damper plate portion and the inertia ring 46 are elastically coupled in a rotating direction.

Description

  The present invention relates to a dynamic damper device, and more particularly, to a dynamic damper device that is coupled to any member constituting a power transmission path from a clutch portion of a torque converter to an output rotating member coupled to a transmission and attenuates rotational fluctuations.

  The present invention also relates to a lockup device for a torque converter having this dynamic damper device.

  In the torque converter, a lockup device is provided to reduce fuel consumption. The lockup device is disposed between the front cover and the turbine, and mechanically connects the front cover and the turbine to directly transmit torque therebetween.

  Generally, the lockup device has a piston and a damper mechanism. The piston is pressed against the front cover by the action of hydraulic pressure, and torque is transmitted from the front cover. The damper mechanism also has a plurality of torsion springs, and the plurality of torsion springs elastically connect the piston and the output-side member connected to the turbine. In such a lockup device, the torque transmitted to the piston is transmitted to the output side member via a plurality of torsion springs and further transmitted to the turbine.

  Patent Document 1 discloses a lockup device in which an inertia member is attached to a member on the output side to suppress fluctuations in the rotational speed of the engine. In the lockup device disclosed in Patent Document 1, an inertia member is attached to an output member fixed to a turbine. The output member and the inertia member are rotatable relative to each other, and a coil spring is provided between the output member and the inertia member.

  In the lockup device of Patent Document 1, since the inertia member is connected to the output member via the coil spring, the inertia member and the coil spring function as a dynamic damper, and thereby the rotational speed of the output side member (turbine). Variation is attenuated.

JP 2009-293671 A

  In the lockup device of Patent Document 1, the output member is constituted by a first output plate and a second output plate. An annular plate member constituting an inertia member is disposed between the first and second output plates, and an inertia member main body is fixed to the outer peripheral portion of the annular plate member. The first and second output plates and the annular plate member are rotatable relative to each other, and the angular range of the relative rotation is regulated by a plurality of stop pins.

  In such an apparatus of Patent Document 1, the inertia member may swing greatly with respect to the first and second output plates during sudden acceleration / deceleration. In such a case, the annular plate member constituting the inertia member Collides with the stop pin. When the plate member and the stop pin collide violently, abnormal noise is generated at the time of collision. When the collision is repeated, wear of the plate member and the stop pin increases.

  An object of the present invention is to suppress the generation of abnormal noise when the inertia member is largely touched in a dynamic damper device. Another object is to suppress wear of the inertia member and the member with which the inertia member collides.

  A dynamic damper device according to an aspect of the present invention is a device that is coupled to any member that constitutes a power transmission path from a clutch portion of a torque converter to an output rotating member that is coupled to a transmission, and attenuates rotational fluctuations. . This dynamic damper device includes a damper plate, an inertia member, and a damper mechanism. The damper plate is connected to any member of the power transmission path and rotates together with the connected member. The inertia member is disposed so as to be rotatable relative to the damper plate in a torsional angle region within a predetermined range. The damper mechanism has a low rigidity torsional characteristic in a low torsional angle region between the damper plate and the inertia member, and higher than a low torsional characteristic in a high torsional angle region larger than the low torsional angle region. It has a rigid and highly rigid torsion characteristic, and elastically connects the damper plate and the inertia member in the rotational direction.

  In this device, when the clutch portion is on (power transmission state), power from the front cover is transmitted from the clutch portion to the turbine via the output rotating member. At this time, the dynamic damper device is connected to one of the members constituting the power transmission path, and the rotational speed fluctuation can be suppressed by this dynamic damper device.

  During the operation of the dynamic damper, the damper mechanism operates due to the low-rigidity torsion characteristics in a low torsion angle region where the torsion angle of the inertia member with respect to the damper plate is small. When the torsion angle of the inertia member with respect to the damper plate is increased, the damper mechanism is acted by the high rigidity torsion characteristic.

  Here, when the torsion angle of the inertia member with respect to the damper plate is small, the damper mechanism operates with low rigidity torsional characteristics, so that the inertia member swings smoothly with a small resistance, and the rotational speed fluctuation is effectively Can be suppressed.

  On the other hand, when the deflection of the inertia member increases during sudden acceleration / deceleration, the deflection of the inertia member is stopped or suppressed by the high-rigidity torsional characteristics of the damper mechanism. Therefore, in the region where the deflection angle of the inertia member is large, the movement speed of the inertia member is suppressed, and it is possible to prevent the inertia member from colliding with a stop pin or the like for regulating the deflection. Further, even if the inertia member collides with a stop pin or the like, abnormal noise at the time of collision can be suppressed and wear can also be suppressed.

  In the dynamic damper device according to another aspect of the present invention, the damper mechanism includes a plurality of first elastic members and a plurality of second elastic members. The first elastic member elastically connects the damper plate and the inertia member in the rotation direction. The second elastic member operates behind the plurality of first elastic members when the damper plate and the inertia member rotate relative to each other, and elastically connects the damper plate and the inertia member in the rotation direction.

  In the dynamic damper device according to another aspect of the present invention, the plurality of first elastic members are large coil springs, and the plurality of second elastic members are arranged in at least one of the large coil springs, and are larger than the large coil springs. It is a small coil spring with a short length.

  In the dynamic damper device according to another aspect of the present invention, the second elastic member is disposed at a position different from the first elastic member in the circumferential direction, and has a shorter circumferential length than the second elastic member.

  In the dynamic damper device according to another aspect of the present invention, the first elastic member is a coil spring, and the second elastic member is formed of rubber.

  The dynamic damper device according to another aspect of the present invention further includes a stopper member that is provided on one of the damper plate and the inertia member and restricts relative rotation between the damper plate and the inertia member within a predetermined angle range. ing.

  In the dynamic damper device according to another aspect of the present invention, the outer peripheral surface of the stopper member is provided with a cushioning material having a rigidity lower than that of the member constituting the stopper member at a portion in contact with either the damper plate or the inertia member. Yes.

  In the dynamic damper device according to another aspect of the present invention, the inertia members are each composed of a pair of plate members disposed on both sides in the axial direction of the damper plate so as to be rotatable relative to the damper plate. The stopper member is a pin for fixing the pair of plate members so that they cannot be rotated relative to each other and cannot move in the axial direction.

  In the dynamic damper device according to another aspect of the present invention, the damper plate has a plurality of first openings extending in the circumferential direction. Each of the inertia members includes a pair of plate members that are disposed on both sides in the axial direction of the damper plate so as to be rotatable relative to the damper plate, and have a second opening extending in the circumferential direction at a position facing the first opening. The damper mechanism includes a plurality of elastic members that are accommodated in the first opening and the second opening and elastically connect the damper plate and the pair of inertia members.

  A lockup device according to the present invention is a device that is disposed between a front cover coupled to a member on an engine side and a torque converter main body, and that directly transmits torque from the front cover to a turbine of the torque converter main body. . The lockup device includes a clutch portion, an output rotation member, a plurality of lockup elastic members, and a dynamic damper device. The clutch portion transmits torque from the front cover to the output side. The output rotating member is rotatable relative to the clutch portion and is connected to the turbine. The plurality of lockup elastic members elastically connect the clutch portion and the output rotation member in the rotation direction. The dynamic damper device is connected to any one of members constituting a power transmission path from the clutch portion to the output rotation member, and is a device according to each aspect of the present invention described above.

  A dynamic damper device according to the present invention is a device that attenuates rotational fluctuations provided in a power transmission path, and includes a damper plate, an inertia member, and a damper mechanism. The damper plate is connected to any member of the power transmission path and rotates together with the connected member. The inertia member is disposed so as to be rotatable relative to the damper plate in a torsional angle region within a predetermined range. The damper mechanism has a low rigidity torsional characteristic in the low torsional angle region between the damper plate and the inertia member, and a lower rigidity torsional characteristic in a high torsional angle region larger than the low torsional angle region. It has high rigidity and high rigidity torsion characteristics, and elastically connects the damper plate and the inertia member in the rotational direction.

  According to the present invention as described above, in the dynamic damper device, it is possible to suppress the generation of abnormal noise when the inertia member swings greatly. Further, the wear of the inertia member and the member with which the inertia member collides can be suppressed.

The cross-sectional block diagram of the torque converter provided with the lockup apparatus by one Embodiment of this invention. The figure which extracts and shows the lockup apparatus of FIG. The figure which extracts and shows the intermediate member and dynamic damper apparatus of FIG. The front fragmentary view of a dynamic damper apparatus. The front fragmentary view of the inertia ring of a dynamic damper apparatus. The figure which shows the stop pin of a dynamic damper apparatus. FIG. 3 is a characteristic diagram of engine speed and rotational speed fluctuation. The figure corresponding to FIG. 4 by other embodiment of this invention. The figure which shows the stop pin by other embodiment of this invention. The figure which shows the stop pin by other embodiment on on this invention.

  FIG. 1 is a partial sectional view of a torque converter 1 having a lock-up device according to an embodiment of the present invention. An engine (not shown) is arranged on the left side of FIG. 1, and a transmission (not shown) is arranged on the right side of the figure. Note that OO shown in FIG. 1 is a rotation axis of the torque converter and the lockup device.

[Overall Configuration of Torque Converter 1]
The torque converter 1 is a device for transmitting torque from an engine-side crankshaft (not shown) to an input shaft of a transmission, and includes a front cover 2 fixed to an input-side member and three types of impellers ( A torque converter main body 6 including an impeller 3, a turbine 4, and a stator 5) and a lockup device 7 are included.

  The front cover 2 is a disk-shaped member, and an outer peripheral cylindrical portion 10 that protrudes toward the transmission is formed on the outer peripheral portion thereof. The impeller 3 includes an impeller shell 12 fixed to the outer peripheral cylindrical portion 10 of the front cover 2 by welding, a plurality of impeller blades 13 fixed to the inside thereof, and a cylindrical shape provided on the inner peripheral side of the impeller shell 12. And the impeller hub 14.

  The turbine 4 is disposed to face the impeller 3 in the fluid chamber. The turbine 4 includes a turbine shell 15, a plurality of turbine blades 16 fixed to the turbine shell 15, and a turbine hub 17 fixed to the inner peripheral side of the turbine shell 15. The turbine hub 17 has a flange 17 a extending to the outer peripheral side, and an inner peripheral portion of the turbine shell 15 is fixed to the flange 17 a by a plurality of rivets 18. An input shaft of a transmission (not shown) is splined to the inner peripheral portion of the turbine hub 17.

  The stator 5 is a mechanism for rectifying hydraulic fluid that is disposed between the impeller 3 and the inner peripheral portion of the turbine 4 and returns from the turbine 4 to the impeller 3. The stator 5 mainly includes a stator carrier 20 and a plurality of stator blades 21 provided on the outer peripheral surface thereof. The stator carrier 20 is supported by a fixed shaft (not shown) via a one-way clutch 22. Thrust bearings 24 and 25 are provided on both axial sides of the stator carrier 20.

[Lock-up device 7]
FIG. 2 shows the lock-up device 7 extracted from FIG. The lockup device 7 is disposed in a space between the front cover 2 and the turbine 4. The lock-up device 7 includes a piston 30, a drive plate 31, an outer peripheral torsion spring 32, a float member 33, an intermediate member 34, an inner peripheral torsion spring 35, a driven plate 36, and a dynamic damper device 37. ,have.

<Piston 30>
The piston 30 is formed in an annular shape and is disposed on the transmission side of the front cover 2. A cylindrical portion 30 a extending to the transmission side is formed on the inner peripheral portion of the piston 30. The cylindrical portion 30a is supported on the outer peripheral surface of the turbine hub 17 so as to be axially movable and relatively rotatable. Further, an annular friction material 38 is fixed to the surface on the front cover 2 side in the outer peripheral portion of the piston 30. When the friction material 38 is pressed against the front cover 2, torque is transmitted from the front cover 2 to the piston 30.

  A stepped portion including a small-diameter portion 17b on the engine side and a large-diameter portion 17c on the transmission side is formed on the outer peripheral surface of the turbine hub 17. The piston 30 is supported by the small diameter portion 17b, and the axial movement toward the transmission side is restricted by the side surface of the large diameter portion 17c. Further, a seal member 40 is attached to the small diameter portion 17b, and the space between the inner peripheral surface of the piston 30 and the turbine hub 17 is thereby sealed.

<Drive plate 31>
The drive plate 31 is fixed to the side surface on the transmission side on the outer peripheral side of the piston 30. Specifically, the drive plate 31 is formed in an annular shape, and the inner peripheral portion 31a is fixed to the transmission side surface of the piston 30 by a rivet (not shown). A plurality of engaging portions 31 b are formed on the outer peripheral portion of the drive plate 31. The engaging portion 31 b is bent at the outer peripheral end toward the transmission side and is engaged with both ends of the outer peripheral side torsion spring 32 in the circumferential direction.

<Outer peripheral side torsion spring 32 and float member 33>
The plurality of outer peripheral side torsion springs 32 are composed of, for example, a total of six springs in one set, and the float member 33 is provided so that the two outer peripheral side torsion springs 32 of each set act in series. Yes.

  The float member 33 is an annular member having a C-shaped cross section, and is disposed between the outer peripheral portion of the piston 30 and the outer peripheral portion of the drive plate 31 in the axial direction. The float member 33 is disposed so as to be rotatable relative to the drive plate 31, the outer peripheral portion 33 a supports the outer peripheral portion of the outer peripheral torsion spring 32, and the side portion 33 b supports the side of the outer peripheral side torsion spring 32 on the engine side. I support it.

  The tip 33c of the float member 33 on the transmission side in the axial direction is bent on the inner peripheral side and the engine side. The bent portion 33c of the tip is inserted between the pair of outer peripheral torsion springs 32. ing. That is, both end surfaces of the bent portion 33 c in the circumferential direction are in contact with the corresponding end surfaces of the outer peripheral torsion springs 32.

  The inner peripheral end 33 d of the float member 33 can abut on the piston side surface of the drive plate 31. Further, the inner peripheral end surface of the float member 33 is supported on the outer peripheral surface of a support portion 31 c formed on a part of the drive plate 31. That is, the float member 33 is restricted from moving in the axial direction by the piston 30 and the drive plate 31, and is positioned in the radial direction by the support portion 31 c of the drive plate 31.

  As described above, both ends in the circumferential direction of the set of outer peripheral side torsion springs 32 arranged so as to act in series engage with the engaging portions 31b of the drive plate 31, and the one set of outer peripheral side torsion springs 32 A bent portion 33c of the float member 33 is inserted in the intermediate portion.

<Intermediate member 34>
FIG. 3 shows the intermediate member 34 and the dynamic damper device 37 extracted from FIG. As shown in FIG. 3, the intermediate member 34 includes a first plate 41 and a second plate 42, and is rotatable relative to the drive plate 31 and the driven plate 36.

  The first and second plates 41 and 42 are annular and disk-shaped members disposed between the piston 3 and the turbine shell 15. The first plate 41 and the second plate 42 are arranged with a gap in the axial direction. The first plate 41 is disposed on the engine side, and the second plate 42 is disposed on the transmission side.

  As shown in FIG. 4, a plurality of protrusions 42 a are formed on the outer periphery of the second plate 42 at predetermined intervals in the circumferential direction. The plurality of projecting portions 42a are formed by projecting the outer peripheral portion of the second plate 42 further outward in the radial direction. The projecting portion 42a of the second plate 42 and the outer peripheral portion of the first plate 41 are connected to each other by a plurality of rivets 43 so that they cannot rotate relative to each other and cannot move in the axial direction.

  The first plate 41 and the second plate 42 are formed with windows 41b and 42b penetrating in the axial direction, respectively. The window portions 41b and 42b are formed to extend in the circumferential direction, and a cut-and-raised portion that is cut and raised in the axial direction is formed on the inner peripheral portion and the outer peripheral portion.

  As shown in FIG. 3, a plurality of locking portions 41 c extending to the outer peripheral side torsion spring 32 are formed on the outer peripheral end portion of the first plate 41. The plurality of locking portions 41c are formed by bending the tip of the first plate 41 toward the axial engine side. The plurality of locking portions 41c are arranged at predetermined intervals in the circumferential direction, and a pair of outer peripheral side torsion springs 32 that act in series are arranged between the two locking portions 41c. Yes.

  The intermediate member 34 as described above allows the outer peripheral side torsion spring 32 and the inner peripheral side torsion spring 35 to act in series.

<Inner circumference torsion spring 35>
As shown in FIGS. 3 and 4, each of the plurality of inner peripheral side torsion springs 35 is inserted into the large coil spring 35a and the small coil having the same length as the spring length of the large coil spring 35a. It consists of a combination with a coil spring 35b. Each inner peripheral side torsion spring 35 is disposed in the window portions 41 b and 42 b of both plates 41 and 42 of the intermediate member 34. Each inner torsion spring 35 is supported at both ends in the circumferential direction and both sides in the radial direction by the windows 41b and 42b. Furthermore, each inner torsion spring 35 is restricted from projecting in the axial direction by the cut-and-raised portions of the windows 41b and 42b.

<Driven plate 36>
The driven plate 36 is an annular and disk-shaped member, and an inner peripheral portion thereof is fixed to the flange 17 a of the turbine hub 17 by a rivet 18 together with the turbine shell 15. The driven plate 36 is disposed between the first plate 41 and the second plate 42 so as to be rotatable relative to the plates 41 and 42. A window hole 36 a is formed in the outer peripheral portion of the driven plate 36 corresponding to the window portions 41 b and 42 b of the first and second plates 41 and 42. The window hole 36a is a hole penetrating in the axial direction, and an inner peripheral torsion spring 35 is disposed in the window hole 36a.

  A plurality of stopper projections 36b (see FIG. 4) projecting radially outward are formed on the outer peripheral portion of the driven plate 36. The stopper projection 36b is disposed at the same position in the axial direction as the protrusion 42a of the second plate 42 and a part of the first plate 41 fixed to the protrusion 42a. The stopper protrusion 36b is disposed between the two protrusions 42a in the circumferential direction. Therefore, when the relative rotation between the first and second plates 41 and 42 and the driven plate 36 increases, the stopper projection 36b and the projection 42a come into contact with each other, and the relative rotation between the two is restricted.

<Dynamic damper device 37>
As shown in FIGS. 3 and 4, the dynamic damper device 37 includes a damper plate portion 45 that is an outer peripheral extension portion of the second plate 42 of the intermediate member 34, a pair of inertia rings 46, and a pair of lid members 47. And a damper mechanism 48 and a stop pin 49. FIG. 4 is a partial view of the dynamic damper device 34 viewed from the turbine 4 side.

  As described above, the damper plate portion 45 is a portion formed by extending the outer peripheral portion of the second plate 42 constituting the intermediate member 34 further outward in the radial direction. As shown in FIG. 4, the damper plate portion 45 is disposed between the two protruding portions 42a in the circumferential direction, and extends further outward from the protruding portions 42a. The damper plate portion 45 is formed with a spring storage portion 45a (first opening). The spring accommodating portion 45a is formed to extend in the circumferential direction and penetrates in the axial direction.

  The damper plate portion 45 has an inlay portion 45b formed by once bending the outer peripheral portion of the second plate 42 to the turbine 4 side. The inlay portion 45b is formed in a cylindrical shape.

  The pair of inertia rings 46 is formed by pressing a sheet metal member, and is disposed on both axial sides of the damper plate portion 45. The two inertia rings 46 have the same configuration. As shown in FIG. 5, the inertia ring 46 has a plurality of spring accommodating portions 46a (second openings) at predetermined intervals in the circumferential direction. The spring accommodating portion 46 a is formed at a position corresponding to the spring accommodating portion 45 a of the damper plate portion 45. The inertia ring 46 has a plurality of through holes 46b. The plurality of through holes 46 b are holes to which the stop pins 49 are attached, and are formed between the circumferential directions of the plurality of damper plate portions 45. Furthermore, a notch 46c that is recessed on the outer peripheral side is formed on the inner peripheral edge of the inertia ring 46 in order to avoid interference with the protrusions 42a of the second plate 42 during assembly.

  The pair of lid members 47 are disposed on the outer side in the axial direction of the pair of inertia rings 46. Specifically, one lid member 47 is further disposed on the front cover 2 side of the inertia ring 46 disposed on the front cover 2 side, and the other lid member 47 is further disposed on the inertia ring 46 disposed on the turbine 4 side. It is arranged on the turbine 4 side.

  As shown in FIG. 4, the lid member 47 is formed in an annular shape, the outer diameter is the same as the outer diameter of the inertia ring 46, and the inner diameter is larger than the outer diameter of the protruding portion 42 a of the second plate 42. is there. A through hole 47 b is formed in the lid member 47 at a position corresponding to the through hole 46 b of the inertia ring 46.

  As shown in FIG. 4, the damper mechanism 48 includes large and small coil springs 48a and 48b housed in a plurality of spring housing portions 45a. The large coil spring 48a has substantially the same length as the circumferential length of the spring storage portion 45a. Therefore, both end portions of the large coil spring 48 a are in contact with the end portions in the circumferential direction of the spring housing portions 45 a and 46 a of the damper plate 45 and the inertia ring 46. The small coil spring 48b is disposed on the inner peripheral portion of the large coil spring 48a, and is set shorter by the length of the large coil spring 48a. For this reason, the small coil spring 48b operates later than the operation of the large coil spring 48a.

  The stop pin 49 is attached to the inertia ring 46 and the through holes 46 b and 47 b of the lid member 47. That is, the stop pin 49 is disposed between the circumferential directions of the plurality of damper plate portions 45. As shown in FIG. 6, the stop pin 49 has a large-diameter barrel portion 49a at the center in the axial direction, and has small-diameter barrel portions 49b on both sides thereof. The large diameter body 49 a has a larger diameter than the through hole 46 b of the inertia ring 46. Further, the large-diameter trunk portion 49 a is formed to be slightly thicker than the damper plate portion 45.

  The small diameter barrel portion 49 b is inserted through the through hole 46 b of the inertia ring 46 and the through hole 47 b of the lid member 47. And the inertia ring 46 and the cover member 47 are being fixed to the axial direction both sides of the damper plate part 45 by crimping the head of the small diameter trunk | drum 49b.

  With the above-described configuration, the damper plate 45, the inertia ring 46, and the lid member 47 can be relatively rotated within a range in which the stop pin 49 can move between the adjacent damper plate portions 45. Then, when the large-diameter body portion 49a of the stop pin 49 abuts on the circumferential end surface of the damper plate portion 45, the relative rotation of both is restricted.

  Further, in a state where the inertia ring 46 and the lid member 47 are fixed by the stop pin 49, the inner peripheral surface of the inertia ring 46 abuts on the outer peripheral surface of the spigot part 45 b of the damper plate portion 45, thereby the inertia ring 46 and the lid The member 47 and the large and small coil springs 48a and 48b are positioned in the radial direction.

[Operation]
First, the operation of the torque converter body will be briefly described. In a state where the front cover 2 and the impeller 3 are rotating, hydraulic oil flows from the impeller 3 to the turbine 4, and torque is transmitted from the impeller 3 to the turbine 4 through the hydraulic oil. Torque transmitted to the turbine 4 is transmitted to an input shaft (not shown) of the transmission via the turbine hub 17.

  When the speed ratio of the torque converter 1 increases and the input shaft reaches a constant rotational speed, the hydraulic oil between the front cover 2 and the piston 30 is drained, and the hydraulic oil is supplied to the turbine 4 side of the piston 30. Then, the piston 30 is moved to the front cover 2 side. As a result, the friction member 38 fixed to the piston 30 is pressed against the front cover 2, and the lockup clutch is turned on.

  In the clutch-on state as described above, torque is transmitted through the path of the front cover 2, the piston 30, the drive plate 31, the outer peripheral torsion spring 32, the intermediate member 34, the inner peripheral torsion spring 35, and the driven plate 36. It is output to the hub 17.

  The lockup device 7 transmits torque and absorbs and attenuates torque fluctuations input from the front cover 2. Specifically, when torsional vibration occurs in the lockup device 7, the outer peripheral side torsion spring 32 and the inner peripheral side torsion spring 35 are compressed in series between the drive plate 31 and the driven plate 36. Furthermore, also in the outer peripheral side torsion spring 32, one set of outer peripheral side torsion springs 32 is compressed in series. For this reason, the twist angle can be widened.

[Operation of Dynamic Damper Device 37]
The torque transmitted to the intermediate member 34 is transmitted to the driven plate 36 via the inner peripheral side torsion spring 35 and further transmitted to the transmission side member via the turbine hub 17. At this time, since the dynamic damper device 37 is provided in the intermediate member 34, fluctuations in the rotational speed of the engine can be effectively suppressed. That is, the rotation of the damper plate portion 45 and the rotation of the inertia ring 46 and the lid member 47 cause a phase shift due to the action of the damper mechanism 48. Specifically, the inertia ring 46 and the lid member 47 fluctuate at a phase that cancels out the rotational speed fluctuation of the damper plate portion 45 at a predetermined engine speed. Due to this phase shift, the rotational speed fluctuation of the transmission can be absorbed.

  In this embodiment, the dynamic damper device 37 is fixed to the intermediate member 34, and the inner peripheral torsion spring 35 for suppressing vibration is disposed between the dynamic damper device 37 and the turbine hub 17. Due to the action of the inner peripheral side torsion spring 35, as shown in FIG. 7, it is possible to more effectively suppress the rotational speed fluctuation. In FIG. 7, the characteristic C1 shows the rotational speed fluctuation in the conventional lockup device. Characteristic C2 shows the fluctuation when the dynamic damper device is mounted on the turbine hub and there is no torsion spring on the output side of the dynamic damper device. Further, the characteristic C3 shows the fluctuation when the dynamic damper device 37 is attached to the intermediate member 34 and the inner periphery side torsion spring 35 is provided on the output side of the dynamic damper device 37 as in the present embodiment.

  As is apparent from comparison between the characteristic C2 and the characteristic C3 in FIG. 7, when the inner peripheral torsion spring 35 is provided on the output side of the dynamic damper device 37, the peak of the rotational speed fluctuation is reduced, and the engine rotation The rotational speed fluctuation can be suppressed even in the normal number range.

  Here, the damper mechanism 48 has two-stage torsional characteristics. Specifically, when relative rotation occurs between the damper plate portion 45 and the inertia ring 46 and the lid member 47, only the large coil spring 48a is first compressed, and the torsional characteristics with low rigidity (the first stage torsion) The damper mechanism 48 is operated by the twisting characteristic). In this case, the inertia ring 46 and the lid member 47 rotate relative to the damper plate portion 45 with a relatively small resistance, and the rotational speed fluctuation can be effectively suppressed.

  When a larger rotational fluctuation occurs and a larger relative rotation occurs between the damper plate portion 45 and the inertia ring 46 and the lid member 47, the small coil spring 48b is also compressed in addition to the large coil spring 48a. become. For this reason, the damper mechanism 48 operates with a torsion characteristic (stiffness characteristic of the second stage) having higher rigidity than that of the first stage.

  When such a large rotational fluctuation occurs, the damper mechanism 48 operates with the second-stage torsion characteristic through the first-stage torsion characteristic. In this case, the inertia ring 46 and the lid member 47 are less likely to rotate with respect to the damper plate portion 45 and the relative rotational speed of both is reduced compared to the case where the first stage torsion characteristic is operated. To do. For this reason, even if the circumferential end surface of the damper plate portion 45 collides with the stop pin 49, the impact is suppressed as compared with the conventional dynamic damper device having only one-stage torsional characteristics.

[Feature]
(1) When the swing of the inertia ring 46 with respect to the damper plate portion 45 becomes large during sudden acceleration / deceleration, the swing of the inertia ring 46 stops due to the second stage high rigidity torsional characteristic of the damper mechanism 48, Alternatively, the speed of swing is suppressed. Therefore, the inertia ring 46 can be prevented from colliding with the stop pin 49 in a region where the deflection angle of the inertia ring 46 is large. Further, even if the inertia ring 46 collides with the stop pin 49, abnormal noise at the time of the collision can be suppressed. Further, wear of the inertia ring 46 and the stop pin 49 is suppressed.

  (2) When the swing of the inertia ring 46 is relatively small, the damper mechanism 48 operates with the first stage low-rigidity torsional characteristics. For this reason, the inertia ring 46 operates smoothly, and a rotational speed fluctuation | variation can be suppressed effectively.

  (3) Since the pair of inertia rings 46 are arranged on both sides of the damper plate portion 45 to constitute the dynamic damper device 37, the pair of inertia rings 46 can be formed of plate members. Therefore, the manufacturing cost can be reduced as compared with the case where the inertia ring is formed of a cast product or a forged product.

  (4) Since the damper mechanism 48 is accommodated in the damper plate portion 45 and the inertia ring 46, the space occupied by the dynamic damper device in the axial direction can be made particularly compact.

  (5) Since the inertia ring 46 is divided in the axial direction, insertion of the damper plate portion 45 and assembly of the damper mechanism 48 are facilitated.

  (6) Since the dynamic damper device 37 is mounted on the intermediate member 34 and the inner peripheral side torsion spring 35 is provided on the output side of the dynamic damper device 37, fluctuations in rotational speed can be more effectively suppressed.

[Other Embodiments]
The present invention is not limited to the above-described embodiments, and various changes or modifications can be made without departing from the scope of the present invention.

  (A) In the said embodiment, although the damper mechanism was comprised with the large and small coil spring accommodated in one spring accommodating part, the structure of a damper mechanism is not limited to this.

  For example, as shown in FIG. 8, a first coil spring 51a is disposed in one spring housing portion 45a, and a second coil spring 51b having a shorter length than the first coil spring 51a is disposed in another spring housing portion 45a. May be.

  Further, instead of the small coil spring 48b shown in FIG. 4 and the second coil spring 51b shown in FIG. 8, a rubber elastic member having substantially the same length as these may be used.

  (B) In the above embodiment, the damper mechanism has a two-stage characteristic, but it may have a characteristic of three or more stages.

  (C) FIG. 9 shows another embodiment of the stop pin. In this embodiment, the configuration of the stop pin 49 itself is the same as that of the above embodiment, but a rubber collar 54, for example, is attached to the outer periphery of the large-diameter trunk portion 49a. In this case, even if the damper plate portion 45 collides with the stop pin 49, the impact is mitigated by the rubber collar 54. For this reason, wear of the damper plate portion 45 and the stop pin 49 can be suppressed, and a collision sound can be suppressed.

  (D) FIG. 10 shows still another embodiment of the stop pin. The stop pin 55 of this embodiment has a large diameter body portion 55a and a small diameter body portion 55b, as in the above embodiment. An annular groove 55c is formed in the large diameter body 55a, and an O-ring 57 is attached to the annular groove 55c.

  In this embodiment as well, even if the damper plate portion 45 collides with the stop pin 55 as in the embodiment of FIG. 9, the impact is alleviated by the O-ring 57 and wear of the damper plate portion 45 and the stop pin 55 is suppressed. In addition, the collision noise can be suppressed.

  (E) In the above embodiment, the damper plate portion 45 is formed on the outer peripheral portion of the second plate 42 of the intermediate member 34. However, the damper plate may be provided separately from the second plate.

  (F) In the above embodiment, the dynamic damper device is fixed to the intermediate member that connects the outer peripheral side torsion spring and the inner peripheral side torsion spring. However, the arrangement of the dynamic damper device is not limited to this.

  For example, the dynamic damper device may be fixed to a float member for causing two outer peripheral side torsion springs to act in series. Similarly, the dynamic damper device may be fixed to a member for causing the two inner peripheral side torsion springs to act in series. In any case, by arranging a torsion spring as a damper mechanism on the output side of the dynamic damper device, secondary resonance can be suppressed.

DESCRIPTION OF SYMBOLS 1 Torque converter 2 Front cover 4 Turbine 6 Torque converter main body 7 Lockup apparatus 30 Piston 31 Drive plate 32 Outer side torsion spring 34 Intermediate member 35 Inner side torsion spring 36 Driven plate 37 Dynamic damper device 45 Damper plate part 46 Inertia ring 47 Lid member 48 Damper mechanism 48a Large coil spring 48b Small coil spring 49, 55 Stop pin

Claims (11)

A dynamic damper device that is coupled to any of the members that constitute a power transmission path from the clutch portion of the torque converter to the output rotating member that is coupled to the transmission and attenuates rotational fluctuations,
A damper plate connected to any member of the power transmission path and rotating together with the connected member;
An inertia member arranged to be rotatable relative to the damper plate in a torsion angle region within a predetermined range;
In the low torsion angle region between the damper plate and the inertia member, it has a low rigidity torsion characteristic, and in a high torsion angle region larger than the low torsion angle region, A damper mechanism having a high rigidity and high rigidity torsion characteristic, and elastically connecting the damper plate and the inertia member in a rotation direction;
Dynamic damper device with The damper mechanism is
A plurality of first elastic members that elastically connect the damper plate and the inertia member in a rotation direction;
When the damper plate and the inertia member rotate relative to each other, a plurality of second elasticities that operate behind the plurality of first elastic members and elastically connect the damper plate and the inertia member in the rotation direction. Members,
The dynamic damper device according to claim 1, comprising: The plurality of first elastic members are large coil springs,
The plurality of second elastic members are small coil springs arranged in at least one of the large coil springs and having a shorter length than the large coil springs.
The dynamic damper device according to claim 2.   3. The dynamic damper device according to claim 2, wherein the second elastic member is arranged at a position different from the first elastic member in a circumferential direction, and has a shorter circumferential length than the second elastic member. The first elastic member is a coil spring;
The second elastic member is formed of rubber;
The dynamic damper device according to any one of claims 2 to 4.   6. The apparatus according to claim 1, further comprising a stopper member that is provided on one of the damper plate and the inertia member and restricts relative rotation between the damper plate and the inertia member within a predetermined angle range. The dynamic damper device according to claim 1.   The dynamic damper according to claim 6, wherein a cushioning material having rigidity lower than that of a member constituting the stopper member is provided on a portion of the outer peripheral surface of the stopper member that contacts either the damper plate or the inertia member. apparatus. Each of the inertia members is composed of a pair of plate members disposed on both sides in the axial direction of the damper plate so as to be rotatable relative to the damper plate,
The stopper member is a pin for fixing the pair of plate members so as not to be relatively rotatable and axially movable.
The dynamic damper device according to claim 6 or 7. The damper plate has a plurality of first openings extending in the circumferential direction,
Each of the inertia members is disposed on both sides in the axial direction of the damper plate so as to be rotatable relative to the damper plate, and has a pair of plates having a second opening extending in a circumferential direction at a position facing the first opening. Consisting of parts,
The damper mechanism includes a plurality of elastic members that are accommodated in the first opening and the second opening and elastically connect the damper plate and the pair of inertia members.
The dynamic damper device according to claim 1. A lockup device disposed between a front cover coupled to a member on an engine side and a torque converter main body, for directly transmitting torque from the front cover to a turbine of the torque converter main body,
A clutch portion for transmitting torque from the front cover to the output side;
An output rotating member that is rotatable relative to the clutch portion and coupled to the turbine;
A plurality of lock-up elastic members for elastically connecting the clutch portion and the output rotation member in the rotation direction;
The dynamic damper device according to any one of claims 1 to 9, wherein the dynamic damper device is connected to any one of members constituting a power transmission path from the clutch portion to the output rotation member.
Torque converter lockup device with A dynamic damper device that attenuates rotational fluctuations provided in a power transmission path,
A damper plate connected to any member of the power transmission path and rotating together with the connected member;
An inertia member arranged to be rotatable relative to the damper plate in a torsion angle region within a predetermined range;
In the low torsion angle region between the damper plate and the inertia member, it has a low rigidity torsion characteristic, and in a high torsion angle region larger than the low torsion angle region, A damper mechanism having a high rigidity and high rigidity torsion characteristic, and elastically connecting the damper plate and the inertia member in a rotation direction;
Dynamic damper device with

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