WO2016103890A1

WO2016103890A1 - Power transmission device and lock-up device for torque converter

Info

Publication number: WO2016103890A1
Application number: PCT/JP2015/080070
Authority: WO
Inventors: 祥行萩原
Original assignee: 株式会社エクセディ
Priority date: 2014-12-26
Filing date: 2015-10-26
Publication date: 2016-06-30
Also published as: DE112015005106T5; JP2016125511A; JP6541969B2

Abstract

The present invention more effectively suppresses rotation speed fluctuation that is transmitted by a transmission in a power transmission device for a lock-up device and the like of a torque converter. This power transmission device is provided with: a drive plate (25) into which power is input; a hub flange (30) that outputs power; an outer peripheral torsion spring (26); a float member (27); and a dynamic vibration absorber (31). The outer peripheral torsion spring (26) connects the drive plate (25) and the hub flange (30) so as to be rotatable relative to each other. The float member (27) is capable of rotation relative to the drive plate (25), the hub flange (30), and the outer peripheral torsion spring (26) and moves in a sliding manner relative to the outer peripheral torsion spring (26) during rotation. The dynamic vibration absorber (31) comprises a plurality of pendulums (50) that are connected to the float member (27) and that move relative to the float member (27) during rotation of the float member (27).

Description

Power transmission device and torque converter lockup device

The present invention relates to a power transmission device, and more particularly to a power transmission device for transmitting power from an engine to a transmission. Further, the present invention is a lock-up device, particularly, disposed between a front cover connected to a member on the engine side and a torque converter main body, for directly transmitting power from the front cover to the turbine of the torque converter main body. The present invention relates to a lockup device.

The torque converter is equipped with a lock-up device 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.

The lock-up device has a piston and a damper mechanism as disclosed in Patent Document 1, for example. The piston has a friction member, is pressed against the front cover by the action of hydraulic pressure, and torque is transmitted from the front cover. Each of the damper mechanisms includes a plurality of outer peripheral torsion springs and inner peripheral torsion springs, and intermediate members that connect the outer peripheral torsion springs and the inner peripheral torsion springs. The piston and the output side member connected to the turbine are elastically connected by a plurality of torsion springs.

Also, as shown in Patent Document 2, there is also provided a lockup device in which a dynamic vibration absorber is provided between two dampers so as to suppress the rotational speed fluctuation transmitted to the output side.

JP 2009-293671 A Special table 2011-504986 gazette

In the lockup device of Patent Document 2, a dynamic vibration absorber is disposed between two dampers. However, in the device of Patent Document 2, when rotational speed fluctuations greater than the swing angle of the dynamic vibration absorber are input, or when tuning of the dynamic vibration absorber is not appropriate, rotation speed fluctuation amplification or resonance may occur. is there.

An object of the present invention is to more effectively suppress fluctuations in rotational speed transmitted to a transmission in a power transmission device such as a lockup device of a torque converter.

(1) A power transmission device according to one aspect of the present invention is a device for transmitting power from an engine to a transmission. The power transmission device includes an input-side rotating member to which power from an engine is input, an output-side rotating member that outputs power to the transmission, a first elastic member, a float member, a rotational speed adaptive dynamic vibration absorber, It is equipped with. The first elastic member connects the input side rotating member and the output side rotating member so as to be relatively rotatable. The float member is rotatable relative to the input side rotation member, the output side rotation member, and the first elastic member, and slides relative to the first elastic member during rotation. The dynamic vibration absorber has a mass body that is connected to the float member and moves relative to the float member when the float member rotates.

In this apparatus, the power input to the input side rotating member is transmitted to the output side rotating member via the first elastic member. At this time, the rotational speed fluctuation transmitted to the transmission side by the operation of the first elastic member is suppressed. Here, when the first elastic member operates, the float member slides with the first elastic member. Accordingly, the float member is rotated around the first elastic member. With respect to the movement of the float member, the mass body of the dynamic vibration absorber acts in a direction to suppress the rotation fluctuation by centrifugal force, and the rotation speed fluctuation is further suppressed.

Here, a dynamic vibration absorber having a mass body is attached to a float member that freely rotates with respect to the first elastic member. That is, the float member is not engaged with the first elastic member. For this reason, the resonance of the damper device which has occurred in the conventional device does not occur, and the rotational speed fluctuation in the low rotational speed range can be further suppressed.

Also, since the first elastic member and the float member can be rotated relative to each other, the hysteresis torque is reduced as compared with the conventional device, and the damper function is more effectively exhibited.

(2) In the power transmission device according to another aspect of the present invention, the mass body of the dynamic vibration absorber is a plurality of pendulum members.

(3) In the power transmission device according to still another aspect of the present invention, the first elastic member is a coil spring extending in the rotation direction. The float member can come into contact with the outer peripheral portion of the coil spring and regulates the movement of the coil spring in the radial direction. Thereby, a frictional force is generated between the coil spring and the float member, and the damper device can be effectively operated.

(4) In the power transmission device according to still another aspect of the present invention, the coil spring is an arc spring that extends in an arc shape in the rotational direction in a free state. Thereby, an appropriate frictional force is generated between the coil spring and the float member, and the dynamic vibration absorber can be effectively operated.

(5) In the power transmission device according to still another aspect of the present invention, the second and / or third elastic member disposed in series with the first elastic member on at least one of the input side and the output side of the first elastic member. Is further provided. Thereby, the rotation speed range which can reduce vibration can be shifted to the low rotation side.

(6) In the power transmission device according to still another aspect of the present invention, the power transmission device is disposed between at least one of the float member and the input-side rotating member and between the float member and the output-side rotating member, and friction is generated between the two. A friction generating mechanism for generating resistance is further provided. Thereby, a dynamic vibration absorber can be made to act effectively.

(7) The power transmission device according to still another aspect of the present invention further includes a stopper mechanism for restricting the movement of the float member in the rotational direction to a predetermined range. Thereby, the imbalance of an output member can be suppressed.

(8) A torque converter lock-up device according to one aspect of the present invention is disposed between a front cover coupled to a member on an engine side and a torque converter main body, and power from the front cover is transmitted to a turbine of the torque converter main body. It is a device for transmitting directly to. The lockup device includes a clutch portion, an output flange, a plurality of elastic members, a float member, and a rotational speed adaptive dynamic vibration absorber.

The clutch part transmits power from the front cover. The output flange is connected to the turbine. The plurality of elastic members transmit power from the clutch portion to the output flange. The float member is rotatable relative to the clutch portion, the output flange, and the plurality of elastic members, slides with the plurality of elastic members at the time of rotation, and restricts radial movement of the plurality of elastic members. The dynamic vibration absorber is connected to the float member and has a mass body that moves relative to the float member when the float member rotates.

In the present invention as described above, in the power transmission device, the rotational speed fluctuation transmitted to the transmission can be more effectively suppressed by providing the float member with the rotational speed adaptive dynamic vibration absorber.

The cross-sectional block diagram of the torque converter provided with the lockup apparatus by 1st Embodiment of this invention. The figure which extracts and shows the lockup apparatus of FIG. The figure which extracts and shows a part of FIG. The enlarged partial view which shows the positioning structure of a float member. The front fragmentary figure which shows the pendulum of a dynamic vibration damper and the structure for supporting it. FIG. 3 is a characteristic diagram of engine speed and rotational speed fluctuation. The schematic diagram of 2nd Embodiment of this invention. The schematic diagram of 3rd Embodiment of this invention. The schematic diagram of 4th Embodiment of this invention. The schematic diagram of 5th Embodiment of this invention. The schematic diagram of 6th Embodiment of this invention.

-First embodiment-
FIG. 1 is a partial sectional view of a torque converter 1 having a lockup device according to a first 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.

[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 side 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. The impeller hub 14.

The turbine 4 is disposed opposite to 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 disk portion 17a, a flange portion 17b, and a cylindrical portion 17c. The flange portion 17b is formed to extend further to the outer peripheral side from the end portion of the disc portion 17a on the turbine 4 side. The inner peripheral portion of the turbine shell 15 is fixed to the flange portion 17 b by a plurality of rivets 18. The cylindrical portion 17c is formed to extend from the inner peripheral end of the disc portion 17a to the front cover 2 side. An input shaft of a transmission (not shown) can be spline-engaged with the inner peripheral portion of the cylindrical portion 17c.

The stator 5 is a mechanism for rectifying the hydraulic oil 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.

[Overall Configuration of Lockup 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 24, a drive plate 25, an outer peripheral side torsion spring (first elastic member) 26, a float member 27, an intermediate member 28, an inner peripheral side torsion spring 29, and an output side rotating member. As a hub flange 30 and a dynamic vibration absorber 31. The piston 24 and the drive plate 25 constitute an input side rotating member.

[Piston 24]
The piston 24 is a disk-shaped plate and is disposed on the transmission side of the front cover 2. A cylindrical portion 24 a extending toward the turbine 4 is formed at the inner peripheral end of the piston 24. The tubular portion 24a is supported on the outer peripheral surface of the tubular portion 17c of the turbine hub 17 so as to be axially movable and relatively rotatable. A flat portion 24 b is formed on the outer peripheral portion of the piston 24. An annular friction material 33 is fixed to the surface of the flat portion 24b on the front cover 2 side. When the friction material 33 is pressed against the front cover 2, torque is transmitted from the front cover 2 to the piston 24. That is, the piston 24 and the friction material 33 constitute a clutch portion.

Note that a seal member 35 is attached to the outer peripheral surface of the cylindrical portion 17 c of the turbine hub 17, thereby sealing between the inner peripheral surface of the piston 24 and the turbine hub 17. Further, the axial movement of the piston 24 toward the turbine 4 is restricted by the tip of the cylindrical portion 24 a coming into contact with the side surface of the disc portion 17 a of the turbine hub 17.

[Drive plate 25]
The drive plate 25 is fixed to the side surface on the turbine 4 side in the outer peripheral portion of the piston 24. Specifically, the drive plate 25 is formed in a disk shape, and the inner peripheral portion 25 a is fixed to the transmission side surface of the piston 24 by a rivet 37. A plurality of engaging portions 25 b are formed on the outer peripheral portion of the drive plate 25. The engaging portion 25b is formed by bending the outer peripheral end portion of the drive plate 25 to the transmission side. The engaging portion 25 b is engaged with both ends of the outer peripheral side torsion spring 26 in the circumferential direction.

Further, a plurality of spring support portions 25c projecting toward the transmission side are formed at the radial intermediate portion of the drive plate 25. The plurality of spring support portions 25c are formed at predetermined intervals in the circumferential direction. Each spring support portion 25 c supports the inner peripheral side of the outer peripheral side torsion spring 26.

[Outer peripheral side torsion spring 26 and float member 27]
The plurality of outer peripheral torsion springs 26 are arc springs formed in an arc shape that swells to the outer peripheral side in a free state, that is, in a single state before being assembled to the lockup device 7.

The float member 27 is an annular plate member as shown in an enlarged view in FIG. The outer peripheral portion of the float member 27 is bent toward the front cover 2 to form a cylindrical portion 27a. The tubular portion 27a is formed with a plurality of spring accommodating portions 27b at predetermined intervals in the circumferential direction. The spring accommodating portion 27b is formed by bending the front end portion of the cylindrical portion 27a on the front cover 2 side toward the inner peripheral side. The outer periphery side torsion spring 26 is accommodated in the spring accommodating portion 27b.

The float member 27 is freely rotatable with respect to other members, that is, the drive plate 25, the intermediate member 28, and the hub flange 30. Further, since the spring accommodating portion 27 b and the outer peripheral side torsion spring 26 are not engaged with each other, the float member 27 does not rotate in synchronization with the outer peripheral side torsion spring 26.

On the other hand, when the outer peripheral side torsion spring 26 is compressed and deformed so as to expand to the outer peripheral side due to centrifugal force, the outer peripheral part of the outer peripheral side torsion spring 26 slides with the inner peripheral wall of the spring accommodating part 27b. In this case, frictional resistance is generated between the outer peripheral side torsion spring 26 and the float member 27, and the float member 27 is rotated with the outer peripheral side torsion spring 26.

[Intermediate member 28]
As shown in FIG. 3, the intermediate member 28 is a member that connects both the outer peripheral side torsion spring 26 and the inner peripheral side torsion spring 29 so as to act in series. The intermediate member 28 also has a function of holding the inner peripheral side torsion spring 29. The intermediate member 28 includes a first plate 41 and a second plate 42, and is rotatable relative to the drive plate 25 and the hub flange 30.

The first and

second plates

41 and 42 are annular and disk-shaped members disposed between the piston 24 and the turbine shell 15. The first plate 41 and the second plate 42 are arranged with a space in the axial direction. The first plate 41 is disposed on the front cover 2 side, and the second plate 42 is disposed on the turbine 4 side.

The outer peripheral portion of the first plate 41 and the radial intermediate portion of the second plate 42 are fixed to each other by a plurality of stop pins 43. Therefore, the 1st plate 41 and the 2nd plate 42 are connected so that relative rotation is impossible and it cannot move in the direction of an axis. Note that both end surfaces of the body portion of the stop pin 43 abut against the mutually opposing side surfaces of each

play

41, 42, thereby setting a predetermined distance between the first plate 41 and the second plate 42. .

The outer peripheral portion of the second plate 42 has a plurality of protruding portions 42 a that protrude further to the outer peripheral side than the outer peripheral portion of the first plate 41. The plurality of protrusions 42a are formed at predetermined intervals in the circumferential direction. The front end (outer peripheral end) of the protruding portion 42 a is bent toward the front cover 2, and a plurality of locking portions 42 b that contact the end surface of the outer peripheral torsion spring 26 are formed. One outer torsion spring 26 is arranged between the two locking portions 42b.

A stopper claw 25d formed at the tip of the spring support portion 25c of the drive plate 25 is disposed between two adjacent protruding portions 42a. Therefore, the drive plate 25 and the intermediate member 28 (second plate 42) can be rotated relative to each other within a range in which the stopper claw 25d can move in the rotational direction between two adjacent protruding portions 42a. In other words, relative rotation between the drive plate 25 and the intermediate member 28 is prohibited by the stopper claw 25d coming into contact with the protruding portion 42a.

Further, the first plate 41 and the second plate 42 are respectively formed with

windows

41c and 42c penetrating in the axial direction. The

window portions

41c and 42c 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. An inner peripheral side torsion spring 29 is arranged in the

window portions

41c and 42c of both the

plates

41 and 42. The inner circumferential side torsion spring 29 is supported at both ends in the circumferential direction and both sides in the radial direction by the

windows

41c and 42c. Further, the inner periphery side torsion spring 29 is restricted from projecting in the radial direction and the axial direction by the cut and raised portions of the

window portions

41c and 42c.

[Hub flange 30]
As shown in FIG. 3 and the like, the hub flange 30 is an annular and disk-shaped member, and an inner peripheral portion thereof is fixed to the flange portion 17 b of the turbine hub 17 by a rivet 18 together with the turbine shell 15. The hub flange 30 is disposed between the first plate 41 and the second plate 42 so as to be rotatable relative to the

plates

41 and 42 between the first plate 41 and the second plate 42. A window hole 30 a is formed in the outer peripheral portion of the hub flange 30 corresponding to the

window portions

41 c and 42 c of the first and

second plates

41 and 42. The window hole 30a is a hole penetrating in the axial direction, and an inner peripheral torsion spring 29 is disposed in the window hole 30a.

A plurality of notches 30 b are formed on the outer peripheral portion of the hub flange 30. A stop pin 43 passes through the notch 30b in the axial direction. Therefore, the intermediate member 28 and the hub flange 30 can rotate relative to each other within a range in which the stop pin 43 can move in the rotation direction in the notch 30b. In other words, relative rotation between the intermediate member 28 and the hub flange 30 is prohibited by the stop pin 43 coming into contact with the end face of the notch 30b.

[Positioning of Float Member 27]
As shown in an enlarged view in FIG. 4, a regulating portion 30 c that extends linearly from the portion fixed to the turbine shell 15 to the outer circumferential side is formed on the inner circumferential portion of the hub flange 30. A support member 45 that supports the float member 27 is provided between the inner peripheral portion of the hub flange 30 and the turbine shell 15. The support member 45 is fixed to the turbine shell 15 by the rivet 18 together with the hub flange 30. The support member 45 is an annular and disk-shaped member, and has a radial support portion 45a and an axial support portion 45b on the outer peripheral portion. The radial support portion 45a is formed in a cylindrical shape extending in the axial direction. The axial support portion 45b is formed to extend from the end portion of the radial support portion 45a to the outer peripheral side.

With such a configuration, the float member 27 is positioned in the radial direction by the radial support portion 45a of the support member 45, and is sandwiched between the restriction portion 30c of the hub flange 30 and the axial support portion 45b of the support member 45. Is positioned in the axial direction.

[Dynamic vibration absorber 31]
The dynamic vibration absorber 31 attenuates vibrations by moving relative to the float member 27 when the float member 27 rotates. As shown in FIGS. 2, 3, and 5, the dynamic vibration absorber 31 includes a plurality of pendulums 50, a holding plate 51, and a plurality of pins 52.

As shown in FIG. 5, which is a cross-sectional view taken along line VV of FIG. 1, the pendulum 50 has a fan shape formed so that the outer peripheral surface swells to the outer peripheral side. The pendulum 50 is formed with two grooves 50a arranged in the circumferential direction. The two grooves 50a are formed in line symmetry. Further, the two grooves 50a are formed in a substantially arc shape whose central portion is recessed toward the inner peripheral side.

The holding plate 51 is an annular and disk-shaped member, and a radially intermediate portion and an inner peripheral portion are fixed to the float member 27 by a plurality of

rivets

55 and 56, respectively. The outer rivet 55 is disposed between the adjacent pendulums 50 in the circumferential direction. A collar 58 made of an elastic member is attached to the outer peripheral surface of the rivet 55 on the outer peripheral side. When the end face 50b in the circumferential direction of the pendulum 50 is in contact with the collar 58, abnormal noise when the pendulum 50 is activated can be suppressed.

The float member 27 and the holding plate 51 are formed with a plurality of

grooves

27c and 51c arranged in the circumferential direction. In FIG. 5, only the groove 27c of the float member 27 is shown, and the groove 51c of the holding plate 51 does not appear. However, since these

grooves

27c and 51c have exactly the same shape, the groove 27c of the float member 27 will be described here.

The groove 27c is formed at a position corresponding to the position of the groove 50a of the pendulum 50 when the pendulum 50 is located at the neutral position. The two grooves 27c formed corresponding to each pendulum 50 are formed in line symmetry. Moreover, each groove | channel 27c is formed in the substantially circular arc shape where a center part swells to the outer peripheral side contrary to the groove | channel 50a of the pendulum 50. FIG.

As shown in FIG. 5, two pins 52 are assigned to each pendulum 50. The pin 52 has a large diameter part 52a and two small diameter parts 52b provided at both ends of the large diameter part 52a. The large diameter portion 52a of the pin 52 is inserted into the groove 50a of the pendulum 50 so as to be movable along the groove 50a. The small diameter portion 52b is inserted into the groove 27c of the float member 27 and the groove 51c of the holding plate 51 so as to be movable along the

grooves

27c and 51c.

Further, the axial distance between the float member 27 and the holding plate 51 is set by the axial length of the large diameter portion 52a of the pin 52. The axial length of the large diameter portion 52a is set slightly larger than the thickness (axial length) of the pendulum 50.

With the above configuration, the pendulum 50 can swing in the rotational direction with respect to the float member 27 and the holding plate 51.

[Operation]
First, the operation of the torque converter body 6 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 is increased and the input shaft reaches a constant rotational speed, the hydraulic oil between the front cover 2 and the piston 24 is drained, and the hydraulic oil is supplied to the turbine 24 side of the piston 24. Then, the piston 24 is moved to the front cover 2 side. As a result, the friction material 33 fixed to the piston 24 is pressed against the front cover 2, and the lockup device 7 is turned on.

In the clutch-on state as described above, torque is transmitted through the path of the front cover 2 → piston 24 → drive plate 25 → outer side torsion spring 26 → intermediate member 28 → inner side torsion spring 29 → hub flange 30 and turbine It is output to the transmission side via the hub 17.

The lockup device 7 transmits torque and absorbs and attenuates fluctuations in rotational speed input from the front cover 2. Specifically, when torsional vibration occurs in the lockup device 7, the outer peripheral side torsion spring 26 and the inner peripheral side torsion spring 29 are compressed in series between the drive plate 25 and the hub flange 30. The rotation speed fluctuation is attenuated by the operation of these torsion springs 26 and 29 and the frictional resistance (hysteresis torque) of each part.

[Operation of dynamic vibration absorber 31]
When the outer peripheral side torsion spring 26 is compressed, the circumferential central portion is deformed so as to expand radially outward. Further, the outer peripheral side torsion spring 26 tends to move radially outward due to the centrifugal force.

In the above situation, the outer peripheral portion of the outer peripheral side torsion spring 26 and the inner peripheral wall of the float member 27 slide, and a frictional resistance is generated between them. For this reason, the float member 27 is rotated in the same direction as the rotation direction of the outer periphery side torsion spring 26 by a rotation angle that is approximately ½ of the twist angle of the outer periphery side torsion spring 26.

On the other hand, since the dynamic vibration absorber 31 is attached to the float member 27, the pendulum 50 swings with respect to the float member 27 when the rotational speed fluctuates. At this time, since centrifugal force is acting on the pendulum 50, a force for returning to the center position in the circumferential direction acts on the pendulum 50. The action of the pendulum 50 can further suppress vibration.

Note that if the rotational speed fluctuation is large during the operation of the pendulum 50, the swing range of the pendulum 50 also becomes large. In this case, the end surface 50b in the circumferential direction of the pendulum 50 contacts the collar 58, and the swing range of the pendulum 50 is restricted.

FIG. 6 shows the effects of the above dynamic vibration absorber 31 in comparison with the conventional apparatus. In FIG. 6, the horizontal axis represents the engine speed, and the vertical axis represents the rotational speed fluctuation on the output side. And the characteristic C1 has shown the characteristic in the apparatus (for example, patent document 2) which attached the dynamic vibration absorber 31 to the intermediate member of the lockup apparatus, and the characteristic C2 has shown the characteristic of this embodiment. Note that both are characteristics when an irregular order appears on the input side.

As is clear from FIG. 6, in this embodiment, fluctuations in the conventional apparatus can be greatly suppressed, particularly in the low rotation speed range. Further, fluctuations in the conventional apparatus can be suppressed even in a relatively high rotational speed range. This is because the float member 27 is not engaged with the outer peripheral side torsion spring 26 and is rotatable relative to other members, and the vibration of the float member 27 is excluded from the vibration system.

-Second Embodiment-
FIG. 7 shows a schematic diagram of the second embodiment of the present invention. In the second embodiment, a float member 61 that supports the inner peripheral torsion spring 29 is provided, and the dynamic vibration absorber 31 is coupled to the float member 61. The other configurations of the dynamic vibration absorber 31 and the second embodiment are basically the same as those of the first embodiment.

-Third embodiment-
FIG. 8 shows a schematic diagram of the third embodiment of the present invention. In the first embodiment, the outer peripheral side torsion spring 26 and the inner peripheral side torsion spring 29 are provided, but in the third embodiment, only one of the torsion springs 64 is provided.

That is, in the third embodiment, one type of torsion spring 64 is provided between the piston 24 and the turbine 4 (specifically, the turbine hub 17). The torsion spring 64 is provided with a float member 65 having the same configuration as that of the first embodiment. Although the float member 65 is not engaged with the torsion spring 64, the float member 65 can be rotated with respect to the torsion spring 64 within a predetermined range by the frictional resistance between them as in the first embodiment.

The dynamic vibration absorber 31 is mounted on the float member 65, and the configuration thereof is the same as that of the first embodiment.

-Fourth embodiment-
FIG. 9 shows a schematic diagram of the fourth embodiment. In the fourth embodiment, an intermediate torsion spring 67 is provided in addition to the outer periphery side torsion spring 26 and the inner periphery side torsion spring 29. The float member 68 is provided so as to accommodate the intermediate torsion spring 67. Similarly to the above, the float member 68 is not engaged with the intermediate torsion spring 67 but can be rotated with respect to the intermediate torsion spring 67 within a predetermined range by the frictional resistance between them.

The dynamic vibration absorber 31 is mounted on the float member 68, and the configuration thereof is the same as in the other embodiments.

-Fifth embodiment-
FIG. 10 shows a schematic diagram of the fifth embodiment. In the fifth embodiment, in addition to the third embodiment of FIG. 8, a hysteresis torque generating mechanism 70 is further provided between the float member 65 and the output-side rotating member. Here, hysteresis torque is generated by the hysteresis torque generating mechanism 70 when the float member 65 is rotated around the torsion spring 64.

The hysteresis torque generating mechanism may be provided between the float member 65 and the input side member instead of between the float member 65 and the output side rotation member.

-Sixth Embodiment-
FIG. 11 shows a schematic diagram of the sixth embodiment. In the sixth embodiment, in addition to the third embodiment of FIG. 8, a stopper mechanism 72 is further provided between the float member 65 and the rotating member on the output side. The stopper mechanism 72 restricts the movement of the float member 65 in the rotation direction within a predetermined range.

Note that the stopper mechanism may be provided between the float member 65 and the input side rotating member.

[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 each of the embodiments described above, the present invention is applied to the lock-up device of the torque converter, but can be similarly applied to other power transmission devices.

(B) The configuration of the dynamic vibration absorber is not limited to the above-described embodiments, and various modifications are possible. For example, another mass body may be provided instead of the plurality of pendulums.

Industrial application fields

In the power transmission device of the present invention, the rotational speed fluctuation transmitted to the transmission can be more effectively suppressed by providing the float member with a rotational speed adaptive dynamic vibration absorber.

DESCRIPTION OF SYMBOLS 1 Torque converter 2 Front cover 4 Turbine 6 Torque converter main body 7 Lock-up device 24 Piston 25 Drive plate 26 Outer side torsion springs 27, 61, 65, 68 Float member 28 Intermediate member 29 Inner side torsion spring 30 Hub flange 31 Dynamic vibration absorption 50 pendulum

Claims

A power transmission device for transmitting power from an engine to a transmission,
An input-side rotating member to which power from the engine is input;
An output-side rotating member that outputs power to the transmission;
A first elastic member that connects the input side rotating member and the output side rotating member so as to be relatively rotatable;
A float member that is rotatable relative to the input side rotation member, the output side rotation member, and the first elastic member, and that slides relative to the first elastic member during rotation;
A rotational speed adaptive dynamic vibration absorber connected to the float member and having a mass body that moves relative to the float member when the float member rotates;
Power transmission device with
The power transmission device according to claim 1, wherein the mass body of the dynamic vibration absorber is a plurality of pendulum members.
The first elastic member is a coil spring extending in a rotation direction;
The float member is capable of contacting an outer peripheral portion of the coil spring, and restricts radial movement of the coil spring;
The power transmission device according to claim 1 or 2.
The power transmission device according to claim 3, wherein the coil spring is an arc spring that extends in an arc shape in a rotational direction in a free state.
5. The apparatus according to claim 1, further comprising a second and / or third elastic member arranged in series with the first elastic member on at least one of the input side and the output side of the first elastic member. Power transmission device.
The apparatus further comprises a friction generating mechanism that is disposed between at least one of the float member and the input side rotating member and between the float member and the output side rotating member and generates a frictional resistance therebetween. The power transmission device according to any one of 1 to 5.
The power transmission device according to any one of claims 1 to 6, further comprising a stopper mechanism for restricting movement of the float member in a rotation direction within a predetermined range.
A lockup device that is disposed between a front cover and a torque converter main body connected to a member on an engine side, and that directly transmits power from the front cover to a turbine of the torque converter main body,
A clutch portion for transmitting power from the front cover;
An output flange coupled to the turbine;
A plurality of elastic members for transmitting power from the clutch portion to the output flange;
A float that is rotatable relative to the clutch portion, the output flange, and the plurality of elastic members, that slides with the plurality of elastic members during rotation, and that restricts radial movement of the plurality of elastic members. Members,
A rotational speed adaptive dynamic vibration absorber connected to the float member and having a mass body that moves relative to the float member when the float member rotates;
Torque converter lockup device with