JP2017072167A - Torque fluctuation suppression device, torque converter, and power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress peak of torque fluctuation of a rotary member in a wide rotational frequency range.SOLUTION: A device includes a mass body 20, a first centrifugal element 21 and a second centrifugal element 21, a first cam mechanism 221, and a second cam mechanism 222. The mass body 20 is rotatable with a rotor 12, and relatively rotatable to the rotor 12. Each of centrifugal elements 21 receives centrifugal force by rotation of the rotor 12 and the mass body 20. A first cam mechanism 221 receives the centrifugal force acting on the first centrifugal element 21, and converts the centrifugal force into first circumferential force in a direction to reduce relative displacement, when the relative displacement in the rotating direction occurs between the rotor 12 and the mass body 20. A second cam mechanism 222 receives centrifugal force acting on the second centrifugal element 21, and converts the centrifugal force into second circumferential force in a direction to reduce relative displacement when the relative displacement in the rotating direction occurs between the rotor 12 and the mass body 20.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a torque fluctuation suppressing device, and more particularly to a torque fluctuation suppressing device for suppressing torque fluctuation of a rotating body to which torque is input. The present invention also relates to a torque converter and a power transmission device including a torque fluctuation suppressing device.

  For example, a clutch device including a damper device and a torque converter are provided between an automobile engine and a transmission. Further, the torque converter is provided with a lockup device for mechanically transmitting torque at a predetermined rotational speed or more in order to reduce fuel consumption.

  Generally, the lock-up device has a clutch portion and a damper having a plurality of torsion springs. The clutch portion has a piston with a friction member that is pressed against the front cover by the action of hydraulic pressure. In the lock-up-on state, torque is transmitted from the front cover to the piston via the friction member, and further transmitted to the output side member via the plurality of torsion springs.

  In such a lock-up device, torque fluctuations (rotational speed fluctuations) are suppressed by a damper having a plurality of torsion springs.

  Further, in the lockup device disclosed in Patent Document 1, torque fluctuations are suppressed by providing a dynamic damper device including an inertia member. The dynamic damper device of Patent Document 1 is mounted on a plate that supports a torsion spring, a pair of inertia rings that are rotatable relative to the plate, and a plurality of coil springs provided between the plate and the inertia ring. And have.

Japanese Patent Laying-Open No. 2015-094424

  By providing the dynamic damper device of Patent Document 1 in the lockup device, it is possible to suppress the peak of torque fluctuation that occurs in a predetermined rotation speed range.

  In the conventional dynamic damper device including Patent Document 1, the peak of torque fluctuation in a predetermined rotation speed range can be suppressed. However, when the engine specifications change, the rotational speed range in which the peak of torque fluctuations changes accordingly. For this reason, it is necessary to change the inertial amount of inertia and the spring constant of the coil spring in accordance with changes in the engine specifications and the like, which may be difficult to cope with.

  An object of the present invention is to enable a peak of torque fluctuation to be suppressed in a relatively wide rotational speed range in an apparatus for suppressing torque fluctuation of a rotating member.

  (1) A torque fluctuation suppressing device according to the present invention is a device for suppressing torque fluctuation of a rotating body to which torque is input. The torque fluctuation suppressing device includes a mass body, a first centrifuge and a second centrifuge, a first cam mechanism, and a second cam mechanism. The mass body can be rotated together with the rotating body, and is disposed so as to be rotatable relative to the rotating body. The first centrifuge and the second centrifuge are arranged so as to receive a centrifugal force due to the rotation of the rotating body and the mass body. When the first cam mechanism receives a centrifugal force acting on the first centrifuge and a relative displacement in the rotational direction occurs between the rotating body and the mass body, the first cam mechanism converts the centrifugal force into the first direction in which the relative displacement is reduced. Convert to 1 circumferential force. When the second cam mechanism receives a centrifugal force acting on the second centrifuge and a relative displacement in the rotational direction occurs between the rotating body and the mass body, the second cam mechanism converts the centrifugal force into the first direction in which the relative displacement is reduced. Convert to 2 circumferential force.

  In this device, when torque is input to the rotating body, the rotating body and the mass body rotate. When there is no change in the torque input to the rotating body, there is no relative displacement in the rotating direction between the rotating body and the mass body, and the rotor rotates synchronously. On the other hand, when there is a fluctuation in the input torque, the mass body is arranged so as to be relatively rotatable with respect to the rotating body. In some cases, this displacement may be expressed as “rotational phase difference”).

  Here, when the rotating body and the mass body rotate, the first and second centrifuges receive a centrifugal force. When the first and second cam mechanisms are displaced relative to each other between the rotating body and the mass body, the centrifugal forces acting on the first and second centrifuges are converted into different first circumferential force and It converts into the 2nd circumferential direction force, and it operates so that the relative displacement between a rotary body and a mass body may be made small by this circumferential direction force. Torque fluctuations are suppressed by the operation of the first and second cam mechanisms.

  Here, since the centrifugal force acting on the first and second centrifuges is used as a force for suppressing the torque fluctuation, the characteristic for suppressing the torque fluctuation changes according to the rotational speed of the rotating body. . Further, by appropriately setting the characteristics of the first cam mechanism and the second cam mechanism, it is possible to appropriately set the characteristics for suppressing the torque fluctuation, for example, for an engine that performs cylinder deactivation. The peak of torque fluctuation in the region can be suppressed.

  (2) Preferably, the rotator has a first rotator disposed at the first axial position and a second rotator disposed at the second axial position. Further, the mass body has a first inertia ring disposed on the outer periphery or inner periphery of the first rotating body and a second inertia ring disposed on the outer periphery or inner periphery of the second rotating body. The first centrifuge is supported by the first rotating body or the first inertia ring so as to be movable in the radial direction, and the second centrifuge is supported by the second rotating body or the second inertia ring so as to be movable in the radial direction. Yes. Further, the first cam mechanism is disposed at the first axial position in the axial direction, and the second cam mechanism is disposed at the second axial position in the axial direction.

  Here, since the first inertia ring and the second inertia ring constituting the mass body are respectively arranged on the outer periphery or the inner periphery of the first rotary body and the second rotary body, the axial space of the apparatus is shortened. Can do.

  (3) Preferably, the 1st centrifuge is arrange | positioned in the circumferential direction 1st position in a rotary body or a mass body, and the 2nd centrifuge is arrange | positioned in the circumferential direction 2nd position in a rotary body or a mass body. The first cam mechanism is disposed at the first circumferential position, and the second cam mechanism is disposed at the second circumferential position.

  Here, since the first centrifuge and the second centrifuge are arranged at different circumferential positions, both centrifuges can be arranged on the same circumference, and the radial space of the apparatus can be reduced. The same applies to the first cam mechanism and the second cam mechanism.

  (4) Preferably, a mass body has the 1st inertia ring arrange | positioned on the outer periphery of a rotary body, and the 2nd inertia ring arrange | positioned further on the outer periphery of the 1st inertia ring. The first centrifuge is supported by the rotating body so as to be movable in the radial direction, and the second centrifuge is supported by the first inertia ring so as to be movable in the radial direction. Further, the first cam mechanism is disposed on the inner periphery of the first inertia ring on the outer periphery of the rotating body, and the second cam mechanism is disposed on the inner periphery of the second inertia ring on the outer periphery of the first inertia ring.

  Here, the first inertia ring is disposed on the outer periphery of the rotating body, and the second inertia ring is disposed further on the outer periphery of the first inertia ring. Therefore, the first and second inertia rings are disposed at the same position in the axial direction. it can. Therefore, the axial dimension of the apparatus can be shortened. The same applies to the first cam mechanism and the second cam mechanism.

  (5) Preferably, the second cam mechanism has an operation prohibiting mechanism that restricts the movement of the second centrifuge outward in the radial direction when the rotating body or the mass body is equal to or higher than a predetermined rotational speed. The centrifugal force acting on the second centrifuge is not converted into a circumferential force.

  (6) Preferably, the rotating body has a recess on the outer peripheral surface, and at least one of the first and second centrifuges is accommodated in the recess so as to be movable in the radial direction.

  In this case, since the centrifuge is accommodated in the recess of the rotating body, the axial dimension of the apparatus can be suppressed.

  (7) Preferably, the coefficient of friction between the centrifuge accommodated in the concave portion of the first and second centrifuges and the concave portion is 0.1 or less.

  (8) Preferably, a friction reducing member is disposed between the side surface of the centrifuge in the direction in which the centrifuge accommodated in the concave portion moves and the concave portion to reduce friction when the centrifuge moves. ing.

  (9) Preferably, the first cam mechanism and the second cam mechanism have a cam follower and a cam. Cam followers are provided in the first centrifuge and the second centrifuge. The cam is formed on the inner peripheral surface of the rotating body or mass body arranged on the outer peripheral side, and the cam follower contacts and the circumferential force changes according to the relative displacement amount in the rotational direction between the rotating body and the mass body. It has a shape that

  Here, the amount of relative displacement in the rotational direction between the rotating body and the mass body varies depending on the magnitude of torque variation of the rotating body. At this time, since the shape of the cam is set such that the circumferential force converted from the centrifugal force changes in accordance with the relative displacement, torque fluctuation can be more efficiently suppressed.

  (10) Preferably, at least one of the first centrifuge and the second centrifuge is arranged radially outside so that the cam follower and the cam are in contact with each other when the rotating body and the mass body are not rotated. And an urging member for urging the urging direction.

  Here, the cam follower provided in the centrifuge urged radially outward by the urging member is always brought into contact with the cam. For this reason, it is possible to eliminate noise when the cam follower moves away from the cam when the rotation is stopped, or when the cam follower contacts (collises) with the cam when the rotation starts.

  (11) Preferably, the mass body is formed in a continuous annular shape.

  (12) The torque converter according to the present invention is disposed between the engine and the transmission. The torque converter includes an input-side rotating body that receives torque from the engine, an output-side rotating body that outputs torque to the transmission, and a damper that is disposed between the input-side rotating body and the turbine. Any of the torque fluctuation suppression devices.

  (13) Preferably, the torque fluctuation suppressing device is arranged on the input side rotating body.

  (14) Preferably, the torque fluctuation suppressing device is disposed on the output side rotating body.

  (15) Preferably, the damper is provided between the first damper that receives torque from the input side rotating body, the second damper that outputs torque to the output side rotating body, and the first damper and the second damper. And an intermediate member. The torque fluctuation suppressing device is disposed on the intermediate member.

  (16) Preferably, the damper has a plurality of coil springs. Preferably, it further includes a float member that is rotatable relative to the input-side rotator and the output-side rotator, and supports a plurality of coil springs, and the torque fluctuation suppressing device is disposed on the float member.

  (17) A power transmission device according to the present invention includes a flywheel, a clutch device, and any of the torque fluctuation suppression devices described above. The flywheel includes a first inertial body that rotates about a rotation axis, a second inertial body that rotates about the rotation axis and is rotatable relative to the first inertial body, and a first inertial body and a second inertial body. And a damper disposed therebetween. The clutch device is provided on the second inertial body of the flywheel.

  (18) Preferably, the torque fluctuation suppressing device is disposed on the second inertial body.

  (19) Preferably, the torque fluctuation suppressing device is disposed on the first inertial body.

  (20) Preferably, the damper is provided between the first damper that receives torque from the first inertial body, the second damper that outputs torque to the second inertial body, and the first damper and the second damper. And an intermediate member. The torque fluctuation suppressing device is disposed on the intermediate member.

  In the present invention as described above, in the apparatus for suppressing the torque fluctuation of the rotating member, the peak of the torque fluctuation can be suppressed in a relatively wide rotational speed range.

The schematic diagram of the torque converter by one Embodiment of this invention. The front view of the 1st output side rotary body and torque fluctuation suppression apparatus of FIG. The figure equivalent to Drawing 2A of other embodiments. The front view of the 2nd output side rotary body and torque fluctuation suppression apparatus of FIG. The figure equivalent to FIG. 3A of other embodiment. FIG. 2B is an enlarged partial view of FIG. 2A. The figure for demonstrating the action | operation of a cam mechanism. The characteristic view which shows the relationship between a rotation speed and a torque fluctuation. The front view of the torque fluctuation suppression apparatus by 2nd Embodiment of this invention. FIG. 8 is a partial plan view of the apparatus shown in FIG. 7. The front view of the torque fluctuation suppression apparatus by 3rd Embodiment of this invention. The front view of the torque fluctuation suppression apparatus by 4th Embodiment of this invention. The front view of the torque fluctuation suppression apparatus by 5th Embodiment of this invention. The figure for demonstrating the action | operation of the cam mechanism by 5th Embodiment of this invention. The front view of the torque fluctuation suppression apparatus by 6th Embodiment of this invention. The figure equivalent to FIG. 1 which shows other embodiment of this invention. The figure equivalent to FIG. 4 which shows other embodiment of this invention. The schematic diagram which shows the application example 1 of this invention. The schematic diagram which shows the application example 2 of this invention. The schematic diagram which shows the application example 3 of this invention. The schematic diagram which shows the application example 4 of this invention. The schematic diagram which shows the application example 5 of this invention. The schematic diagram which shows the application example 6 of this invention. The schematic diagram which shows the application example 7 of this invention. The schematic diagram which shows the application example 8 of this invention. The schematic diagram which shows the application example 9 of this invention.

  FIG. 1 is a schematic diagram when a torque fluctuation suppressing device according to an embodiment of the present invention is mounted on a lock-up device of a torque converter. In FIG. 1, OO is the rotational axis of the torque converter.

[overall structure]
The torque converter 1 includes a front cover 2, a torque converter main body 3, a lockup device 4, and an output hub 5. Torque is input to the front cover 2 from the engine. The torque converter main body 3 includes an impeller 7 connected to the front cover 2, a turbine 8, and a stator (not shown). The turbine 8 is connected to the output hub 5, and an input shaft (not shown) of the transmission can be engaged with the inner peripheral portion of the output hub 5 by a spline.

[Lock-up device 4]
The lock-up device 4 has a clutch part, a piston that is operated by hydraulic pressure, and the like, and can take a lock-up on state and a lock-up off state. In the lock-up on state, the torque input to the front cover 2 is transmitted to the output hub 5 via the lock-up device 4 without passing through the torque converter body 3. On the other hand, in the lock-up off state, torque input to the front cover 2 is transmitted to the output hub 5 via the torque converter body 3.

  The lockup device 4 includes an input-side rotator 11, an output-side rotator 12, a damper 13, and a torque fluctuation suppressing device 14.

  The input-side rotator 11 includes a piston that is movable in the axial direction, and has a friction member 16 on a side surface on the front cover 2 side. When the friction member 16 is pressed against the front cover 2, torque is transmitted from the front cover 2 to the input side rotating body 11.

  The output-side rotator 12 includes a first hub (first rotator) 121 and a second hub (second rotator) 122 that are arranged to face each other in the axial direction. The first hub 121 is disposed so as to face the input side rotating body 11 in the axial direction, and is rotatable relative to the input side rotating body 11. Further, the first hub 121 and the second hub 122 are fixed to each other and rotate synchronously, and both are connected to the output hub 5.

  The damper 13 is disposed between the input side rotating body 11 and the first hub 121. The damper 13 has a plurality of torsion springs, and elastically connects the input side rotating body 11 and the first hub 121 in the rotational direction. The damper 13 transmits torque from the input side rotating body 11 to the first hub 121 and the second hub 122 and absorbs and attenuates torque fluctuations.

[Torque fluctuation suppressing device 14]
-First embodiment-
2A is a front view of the first hub 121 and the torque fluctuation suppressing device 14, and FIG. 3A is a front view of the second hub 122 and the torque fluctuation suppressing device 14. Moreover, a part of FIG. 2A is enlarged and shown in FIG. As shown in these drawings, the torque fluctuation suppressing device 14 includes a first inertia ring 201 and a second inertia ring 202 that constitute the mass body 20, a plurality of centrifuges 21, and four first cam mechanisms 221. Four second cam mechanisms 222 and a plurality of coil springs 23 are provided. The centrifuge 21, the first and second cam mechanisms 221, 222, and the coil spring 23 are arranged at equal intervals of 90 ° in the circumferential direction.

  2B and 3B, the coil springs 23 arranged on the inner peripheral side of each centrifuge 21 can be omitted. Similarly, in each example described below, the coil spring 23 may be provided or omitted.

  The first inertia ring 201 is a plate having a predetermined thickness formed in a continuous annular shape, and is arranged on the outer peripheral side of the first hub 121 with a predetermined gap in the radial direction. That is, the first inertia ring 201 is disposed at the same position as the first hub 121 in the axial direction. The first inertia ring 201 has the same rotation axis as the rotation axis of the first hub 121, can rotate with the first hub 121, and can rotate relative to the first hub 121.

  The second inertia ring 202 has the same configuration as the first inertia ring 201. That is, it is formed in a continuous annular shape, arranged on the outer peripheral side of the second hub 122 with a predetermined gap in the radial direction, and arranged at the same position in the axial direction as the second hub 122. The second inertia ring 202 has the same rotation axis as the rotation axis of the second hub 122, can rotate with the second hub 122, and can rotate relative to the second hub 122.

  The centrifuge 21 is disposed on the first hub 121 and the second hub 122, and can be moved in the radial direction by the centrifugal force generated by the rotation of the first hub 121 and the second hub 122. Hereinafter, the centrifuge provided in the first hub 121 will be described.

  As shown in an enlarged view in FIG. 4, the first hub 121 is provided with a recess 121 a on the outer peripheral surface. The recess 121a is formed in a rectangular shape on the outer peripheral surface of the first hub 121 so as to be recessed toward the center of rotation on the inner peripheral side. The centrifuge 21 is inserted into the recess 121a so as to be movable in the radial direction. The centrifuge 21 and the recess 121a are set so that the friction coefficient between the side surface of the centrifuge 21 and the recess 121a is 0.1 or less. The centrifuge 21 is a plate having substantially the same thickness as the first hub 121, and the outer peripheral surface 21a is formed in an arc shape. Further, the outer peripheral surface 21a of the centrifuge 21 is formed with a roller accommodating portion 21b that is recessed inward.

  As shown in FIG. 4, the first cam mechanism 221 includes a roller 25 as a cam follower and a cam 26 formed on the inner peripheral surface of the first inertia ring 201. The roller 25 is attached to the roller accommodating portion 21 b of the centrifuge 21 and is movable in the radial direction together with the centrifuge 21. The roller 25 may be rotatable or fixed in the roller accommodating portion 21b. The cam 26 is an arc-shaped surface with which the roller 25 abuts. When the first hub 121 and the first inertia ring 201 are relatively rotated within a predetermined angular range, the roller 25 moves along the cam 26. To do.

  Although details will be described later, when a rotational phase difference is generated between the first hub 121 and the first inertia ring 201 due to contact between the roller 25 and the cam 26, centrifugal force generated in the centrifuge 21 and the roller 25. Is converted into a circumferential force that reduces the rotational phase difference.

  The coil spring 23 is disposed between the bottom surface of the recess 12a and the inner peripheral surface of the centrifuge 21, and urges the centrifuge 21 to the outer peripheral side. Due to the urging force of the coil spring 23, the centrifuge 21 and the roller 25 are pressed against the cam 26 of the first inertia ring 201. Therefore, even when the centrifugal force is not acting on the centrifuge 21 with the first hub 121 not rotating, the roller 25 abuts against the cam 26.

  The second cam mechanism 222 is the same as the first cam mechanism 221 except for the shape of the cam 26.

[Operation of First Cam Mechanism 221]
The operation of the first cam mechanism 221 (suppression of torque fluctuation) will be described with reference to FIGS. 4 and 5. When the lockup is on, the torque transmitted to the front cover 2 is transmitted to the first hub 121 and the second hub 122 via the input side rotating body 11 and the damper 13.

  If there is no torque fluctuation during torque transmission, the first hub 121 and the first inertia ring 201 rotate in the state shown in FIG. That is, the roller 25 of the first cam mechanism 221 contacts the deepest position (circumferential center position) of the cam 26, and the rotational phase difference between the first hub 121 and the first inertia ring 201 is “0”. .

  As described above, the relative displacement in the rotational direction between the first hub 121 and the first inertia ring 201 is referred to as a “rotational phase difference”, which is shown in FIG. 4 and FIG. And the deviation between the center position of the roller 25 in the circumferential direction and the center position of the cam 26 in the circumferential direction.

  On the other hand, if torque fluctuation exists during torque transmission, a rotational phase difference ± θ occurs between the first hub 121 and the first inertia ring 201 as shown in FIGS. FIG. 5A shows a case where a rotational phase difference + θ occurs on the + R side, and FIG. 5B shows a case where a rotational phase difference −θ occurs on the −R side.

  As shown in FIG. 5A, when a rotational phase difference + θ occurs between the first hub 121 and the first inertia ring 201, the roller 25 of the first cam mechanism 221 moves relative to the cam 26. Accordingly, the left side of FIG. At this time, since the centrifugal force is acting on the centrifuge 21 and the roller 25, the reaction force received by the roller 25 from the cam 26 becomes the direction and magnitude of P0 in FIG. The reaction force P0 generates a first component force P1 in the circumferential direction and a second component force P2 in a direction that moves the centrifuge 21 and the roller 25 toward the center of rotation.

  The first component force P1 is a force that moves the first hub 121 to the right in FIG. 5A via the first cam mechanism 221. That is, a force in the direction of reducing the rotational phase difference between the first hub 121 and the first inertia ring 201 acts on the first hub 121. Further, the centrifuge 21 and the roller 25 are moved to the radially inner peripheral side against the urging force of the coil spring 23 by the second component force P2.

  FIG. 5B shows a case where a rotational phase difference −θ is generated between the first hub 121 and the first inertia ring 201, and the moving direction of the roller 25 of the first cam mechanism 221 and the reaction force P 0. The operation is the same except that the directions of the first component force P1 and the second component force P2 are different from those in FIG.

  As described above, when a rotational phase difference is generated between the first hub 121 and the first inertia ring 201 due to torque fluctuation, the first hub is caused by the centrifugal force acting on the centrifuge 21 and the action of the first cam mechanism 221. 121 receives a force (first component force P1) in a direction to reduce the rotational phase difference between the two. This force suppresses torque fluctuations.

  The force for suppressing the torque fluctuation described above varies depending on the centrifugal force, that is, the rotational speed of the first hub 121, and also varies depending on the rotational phase difference and the shape of the cam 26. Therefore, by appropriately setting the shape of the cam 26, the characteristics of the torque fluctuation suppressing device 14 can be made optimal characteristics according to the engine specifications and the like.

  For example, the shape of the cam 26 can be such that the first component force P1 changes linearly according to the rotational phase difference in the state where the same centrifugal force is acting. In addition, the shape of the cam 26 can be a shape in which the first component force P1 changes nonlinearly according to the rotational phase difference.

[Operation of Second Cam Mechanism 222]
The operation of the second cam mechanism 222 is basically the same as the operation of the first cam mechanism 221. The difference is the conversion characteristic from centrifugal force to circumferential force due to the difference in cam shape. That is, in the first cam mechanism 221, the cam 26 is formed with a relatively small radius of curvature. On the other hand, the cam of the second cam mechanism 222 is formed larger than the radius of curvature of the cam 26 of the first cam mechanism 221 as is apparent from FIGS. 3A and 3B. For this reason, in the first cam mechanism 221, when the centrifuge receives a centrifugal force, it is converted into a circumferential force by the first conversion characteristic, but in the second cam mechanism 222, a second different from the first conversion characteristic. With the conversion characteristic, centrifugal force is converted into circumferential force.

[Specifications of the first cam mechanism 221 and the second cam mechanism 222]
As described above, the first cam mechanism 221 has a first conversion characteristic, and the second cam mechanism 222 has a second conversion characteristic. Therefore, for example, when performing a two-cylinder deactivation in a four-cylinder engine, the first conversion characteristic suppresses torque fluctuation when the four cylinders are operating, and the second conversion characteristic causes only two cylinders to operate. It is possible to suppress the torque fluctuation during the operation.

  In the case of four cylinders, only the first cam mechanism 221 acts, torque fluctuation is suppressed by the first conversion characteristic, and the second cam mechanism 222 acts only as inertia. Conversely, in the case of two cylinders, only the second cam mechanism 222 acts, torque fluctuation is suppressed by the second conversion characteristics, and the first cam mechanism 221 acts only as inertia.

  More specifically, for example, when the engine speed is 1000 rpm, the anti-resonance frequency of the torque fluctuation suppressing device for four cylinders is 33.3 Hz, and the anti-resonance frequency of the torque fluctuation suppressing device for two cylinders is 16.7 Hz. is there. Therefore, the torque fluctuation is effectively suppressed at each anti-resonance point by the action of only one of the cam mechanisms.

[Example of characteristics]
FIG. 6 is a diagram illustrating an example of torque fluctuation suppression characteristics. The horizontal axis represents the rotational speed, and the vertical axis represents the torque fluctuation (rotational speed fluctuation). The characteristic Q1 is a case where a device for suppressing torque fluctuation is not provided, the characteristic Q2 is a case where a conventional dynamic damper device is provided, and the characteristic Q3 is a case where the torque fluctuation suppressing device 14 of the present embodiment is provided. Show.

  As is apparent from FIG. 6, in the device (characteristic Q2) provided with the conventional dynamic damper device, it is possible to suppress the torque fluctuation only in a specific rotational speed range. On the other hand, in the present embodiment (characteristic Q3), torque fluctuation can be suppressed in all the rotational speed ranges.

-Second Embodiment-
7 and 8 show a torque fluctuation suppressing device according to a second embodiment of the present invention. In FIG. 7, the first inertia ring 201 is partially broken. FIG. 8 is a partial plan view of FIG. Note that members that are the same as or correspond to those in the first embodiment are denoted by the same reference numerals even if the shapes and the like are different.

  The torque fluctuation suppressing device according to the second embodiment includes a first inertia ring 201, a second inertia ring 202, four centrifuges 21, two first cam mechanisms 221, and two second cam mechanisms. 222 and four coil springs 23. Each of the four centrifuges 21 and the cam mechanisms 221 and 222 is disposed at equal intervals of 90 ° in the circumferential direction. In the example shown in FIG. 7, the coil spring 23 is provided, but the coil spring 23 may be omitted as described above.

  The first inertia ring 201 and the second inertia ring 202 are plates that have a predetermined thickness and are formed in a continuous annular shape. It is arranged with a gap. As shown in FIG. 8, the first inertia ring 201 and the second inertia ring 202 are disposed so as to face each other in the axial direction, and both have the same rotation axis as the rotation axis of the output-side rotator 12 and output. It can rotate with the side rotator 12 and can rotate relative to the output side rotator 12.

  The centrifuge 21 is disposed on the output-side rotator 12 and is movable in the radial direction by a centrifugal force generated by the rotation of the output-side rotator 12. The relationship between the centrifuge 21 and the output-side rotator 12 and the configuration thereof are the same as those in the first embodiment. That is, a concave portion 12a is provided on the outer peripheral surface of the output side rotating body 12, and the centrifuge 21 is inserted into the concave portion 12a so as to be movable in the radial direction. The centrifuge 21 is a plate having substantially the same thickness as that of the output-side rotator 12, and a roller accommodating portion is formed on the outer peripheral surface.

  The first cam mechanism 221 has the same configuration as that of the first embodiment except for the number. That is, the two first cam mechanisms 221 are arranged at an interval of 180 ° in the circumferential direction, the roller 25 as a cam follower, the cam 26 formed on the inner peripheral surface of the first inertia ring 201, It is composed of The roller 25 is attached to the roller accommodating portion of the centrifuge 21 and is movable in the radial direction together with the centrifuge 21. The cam 26 is an arc-shaped surface with which the roller 25 abuts. When the output side rotating body 12 and the first inertia ring 201 are relatively rotated within a predetermined angle range, the roller 25 moves along the cam 26.

  The second cam mechanism 222 has the same configuration as that of the first embodiment except for the number. That is, the two second cam mechanisms 222 are arranged at an interval of 180 ° in the circumferential direction, the roller 25 as a cam follower, the cam 26 formed on the inner peripheral surface of the first inertia ring 201, It is composed of The first cam mechanism 221 is different from the first cam mechanism 221 only in the shape of the cam 26, and other configurations are the same as those of the first cam mechanism 221.

  In the inner peripheral surface of the first inertia ring 201, a groove 201a having a predetermined length in the circumferential direction is formed in a portion where the second cam mechanism 222 is disposed. The outer peripheral surface of the groove 201 a is formed in an arc shape centering on the rotation center of the output side rotating body 12 and the first inertia ring 201. Therefore, even if the roller 25 as a cam follower moves in the groove 201a, it does not function as a cam mechanism.

  A similar groove 202a is also formed on the inner peripheral surface of the second inertia ring 202, and even if the roller 25 moves in the groove 202a, it does not function as a cam mechanism.

[Operation of first and second cam mechanisms 221 and 222]
Regarding the operation of the first and second cam mechanisms 221 and 222 (torque fluctuation suppression), the basic operation is the same as that of the first embodiment except that the number and arrangement of the cam mechanisms are different from those of the first embodiment. . Also in the second embodiment, as in the first embodiment, the force for suppressing the torque fluctuation varies depending on the centrifugal force, that is, the rotational speed of the output side rotating body 12, and depends on the rotational phase difference and the shape of the cam 26. Also changes. Therefore, by appropriately setting the shape of the cam 26, the characteristics of the torque fluctuation suppressing device can be made optimal characteristics according to the engine specifications and the like.

  Further, for example, in the case of performing cylinder deactivation for two cylinders in a four-cylinder engine, the torque variation when the four cylinders are operating is caused by the first conversion characteristic of the first cam mechanism 221 as in the first embodiment. It is possible to suppress the torque fluctuation when only two cylinders are operating by the second conversion characteristic of the second cam mechanism 222.

-Third embodiment-
FIG. 9 shows a torque fluctuation suppressing device according to a third embodiment of the present invention. Note that members that are the same as or correspond to those in the first embodiment are denoted by the same reference numerals even if the shapes and the like are different.

  The torque fluctuation suppression device according to the third embodiment includes a first inertia ring 201 and a second inertia ring 202, four first centrifuges 211 and second centrifuges 212, and four first cam mechanisms 221, respectively. And four second cam mechanisms 222 and eight coil springs 23. Each of the four centrifuges 21 and the cam mechanisms 221 and 222 is disposed at equal intervals of 90 ° in the circumferential direction. Although the coil spring 23 is provided in the example shown in FIG. 9, the coil spring 23 may be omitted as described above.

  The first inertia ring 201 is a plate having a predetermined thickness formed in a continuous annular shape, and is arranged on the outer peripheral side of the output side rotary body 12 with a predetermined gap in the radial direction from the output side rotary body 12. Has been. The first inertia ring 201 has the same rotational axis as the rotational axis of the output-side rotator 12, can rotate with the output-side rotator 12, and can rotate relative to the output-side rotator 12.

  The second inertia ring 202 is a plate having a predetermined thickness formed in a continuous annular shape, and has a predetermined gap in the radial direction with the first inertia ring 201 further on the outer peripheral side of the first inertia ring 201. Has been placed. The second inertia ring 202 has the same rotation axis as the rotation axis of the output-side rotator 12 and the first inertia ring 201, can rotate together with the output-side rotator 12 and the first inertia ring 201, and the first inertia ring Rotating relative to 201 is possible.

  The first centrifuge 211 and the second centrifuge 212 are arranged in different locations, but have the same configuration and shape. The first centrifuge 211 is disposed on the output-side rotator 12 and is movable in the radial direction by a centrifugal force generated by the rotation of the output-side rotator 12. The second centrifuge 212 is disposed on the first inertia ring 201 and is movable in the radial direction by a centrifugal force generated by the rotation of the first inertia ring 201.

  The relationship between the centrifuges 211 and 212, the output-side rotator 12, and the first inertia ring 201 and the configuration thereof are the same as those in the first embodiment. That is, a recess 12a is provided on the outer peripheral surface of the output-side rotator 12, and the first centrifuge 211 is inserted into the recess 12a so as to be movable in the radial direction. Further, the first inertia ring 201 is formed with a recess 201a similar to the recess 12a of the output-side rotator 12, and a second centrifuge 212 is inserted into the recess 201a so as to be movable in the radial direction. Each centrifuge 211, 212 is a plate having substantially the same thickness as the output-side rotator 12, and a roller accommodating portion is formed on the outer peripheral surface.

  The first cam mechanism 221 has the same configuration as in the first embodiment. That is, the four first cam mechanisms 221 are arranged at intervals of 90 ° in the circumferential direction, and the rollers 25 as cam followers, the cams 26 formed on the inner peripheral surface of the first inertia ring 201, It is composed of The roller 25 is attached to the roller accommodating portion of the first centrifuge 21 and is movable in the radial direction together with the first centrifuge 21. The cam 26 is an arc-shaped surface with which the roller 25 abuts. When the output side rotating body 12 and the first inertia ring 201 are relatively rotated within a predetermined angle range, the roller 25 moves along the cam 26.

  The second cam mechanism 222 has the same configuration as the first cam mechanism 221 except where it is arranged. That is, the four second cam mechanisms 222 are arranged at intervals of 90 ° in the circumferential direction, the roller 25 as a cam follower, the cam 26 formed on the inner peripheral surface of the second inertia ring 202, It is composed of In addition, although the shape of the cam 26 of the 1st cam mechanism 221 and the 2nd cam mechanism 222 is the same, the radial direction position in which the cam 26 was formed differs.

[Operation of first and second cam mechanisms 221 and 222]
Regarding the operation of the first and second cam mechanisms 221 and 222 (torque fluctuation suppression), the basic operation is the same as in the first embodiment. The first cam mechanism 221 and the second cam mechanism 222 have the same shape of the cam 26, but the radial position where the second centrifuge 212 is arranged is the radial direction where the first centrifuge 211 is arranged. Greater than position. Therefore, when the rotation speed is the same, the centrifugal force acting on the roller 25 (cam follower: second centrifuge 212) of the second cam mechanism 212 is applied to the roller 25 (first centrifuge 211) of the first cam mechanism 211. Greater than the acting centrifugal force. Therefore, at the same rotation speed, the torque fluctuation suppressing force by the second cam mechanism 212 is larger than that by the first cam mechanism 211.

  Also in the third embodiment, as in the first embodiment, the force for suppressing the torque fluctuation varies depending on the centrifugal force, that is, the rotation speed of the output-side rotator 12, and the rotational phase difference and the cam 26 It varies depending on the shape. Therefore, by appropriately setting the shape of the cam 26, the characteristics of the torque fluctuation suppressing device can be made optimal characteristics according to the engine specifications and the like.

  For example, in the case of performing cylinder deactivation for two cylinders in a four-cylinder engine, as in the first embodiment, the first cam mechanism 221 suppresses torque fluctuation when the four cylinders are operating, and the second The cam mechanism 222 can suppress torque fluctuation when only two cylinders are operating.

-Fourth embodiment-
FIG. 10 shows a torque fluctuation suppressing device according to the fourth embodiment. Note that members that are the same as or correspond to those in the first embodiment are denoted by the same reference numerals even if the shapes and the like are different. In each of the above-described embodiments, the mass body is configured by a continuous annular member. In the fourth embodiment, the mass body is formed by a plurality of divided inertia bodies 201 and 202 arranged side by side in the circumferential direction. It is configured. The configurations of the other output side rotator 12, the centrifuge 21 and the like are the same as those of the other embodiments.

  In this embodiment, each mass body is constituted by two first inertia bodies 201 and second inertia bodies 202. The two first inertia bodies 201 are arranged to face each other with the rotation axis therebetween, and the two second inertia bodies 202 are similarly arranged to face each other with the rotation axis interposed therebetween. The first inertia body 201 and the second inertia body 202 are arranged at positions shifted by 90 °. A holding ring 203 for holding the inertia bodies 201 and 202 in the radial direction is provided on the outer peripheral side of the inertia bodies 201 and 202.

  A cam 26 having the same shape as the first inertia ring 201 of the first embodiment is formed on the inner peripheral surface of the first inertia body 201. A cam 26 having the same shape as the second inertia ring 202 of the first embodiment is formed on the inner peripheral surface of the second inertia body 202. The first cam mechanism 221 and the second cam mechanism 222 are constituted by a roller 25 as a cam follower provided on the outer peripheral surface of the centrifuge 21 and a cam 26 formed on the inner peripheral surfaces of the inertia bodies 201 and 202. And are configured.

  The operations of the first cam mechanism 221 and the second cam mechanism 222 are the same as those in the first embodiment except that the inertia amounts of the first and second inertia bodies 201 and 202 are small. Also according to the fourth embodiment, it is possible to obtain the same operational effects as the respective embodiments.

-Fifth embodiment-
FIG. 11 shows a torque fluctuation suppressing device according to the fifth embodiment. Note that members that are the same as or correspond to those in the first embodiment are denoted by the same reference numerals even if the shapes and the like are different. In the fifth embodiment, as in the fourth embodiment, two first cam mechanisms 221 and two second cam mechanisms 222 are arranged on the same circumference.

  The first cam mechanism 221 has the same configuration as the first cam mechanism 221 of the first embodiment. Further, the recess 12a is formed in the output-side rotator 12, and the configuration in which the centrifuge 21 is disposed so as to be movable in the radial direction in the recess 12a and the configuration of the centrifuge 21 are the same as those in the above embodiments. is there.

  The second cam mechanism 222 has the same configuration as the first cam mechanism 221 except that the operation prohibiting mechanism 27 is provided. That is, the second cam mechanism 222 has a roller 25 as a cam follower and a cam 26 formed on the inner peripheral surface of the inertia ring 20.

  The operation prohibiting mechanism 27 is disposed to face the rotation shaft. That is, of the four centrifuges 21, the movement of the two opposing centrifuges 21 in the radial direction is restricted, and the operation of the second cam mechanism 222 is restricted.

  As shown in an enlarged view in FIG. 12, the operation prohibiting mechanism 27 holds the pair of rotating members 281 and 282 and the pair of rotating members 281 and 282 in an operation allowable posture as shown in FIG. And torsion springs 29a and 29b. The pair of rotating members 281 and 282 are arranged so as to sandwich the centrifuge 21 in the circumferential direction. The pair of rotating members 281 and 282 are arranged symmetrically with respect to the centrifuge 21.

  One rotating member 281 is rotatably supported by a pin 30 fixed to the output side rotating body 12. That is, the rotation member 281 is rotatable around the pin 30 in parallel with the side surface of the output side rotating body 12. The rotating member 281 has a claw portion 281a on the centrifuge 21 side of the pin 30 and a weight portion 281b on the opposite side. The claw portion 281 a is formed to have a length that can contact the outer peripheral surface of the centrifuge 21. And the other rotation member 282 is also the same structure, and has the nail | claw part 282a and the weight part 282b.

  The pair of rotating members 281 and 282 are held in an allowable posture as shown in FIG. 12A when an external force (centrifugal force due to rotation) is not applied by the torsion springs 29a and 29b. That is, the claw portions 281a and 282a of the pair of rotating members 281 and 282 face the outer peripheral side, and the centrifuge 21 is freely movable in the radial direction.

  On the other hand, when the output-side rotator 12 reaches a predetermined number of revolutions or more, the centrifugal force acting on the weight portions 281b and 282b of the pair of rotating members 281 and 282 is changed to the centrifugal force acting on the centrifuge 21 and the torsion spring 29a. , 29b. In this case, as shown in FIG. 12B, the weight portions 281b and 282b of the pair of rotating members 281 and 282 move to the outer peripheral side, and the claw portions 281a and 282a move to the inner peripheral side. In such a state, the centrifuge 21 is prohibited from moving in the radial direction by the claw portions 281a and 282a. Therefore, the roller 25 as the cam follower provided in the centrifuge 21 cannot contact the cam 26, and the second cam mechanism 222 does not operate.

  As described above, in the fifth embodiment, when the output-side rotator 12 is lower than the predetermined rotational speed, both the first cam mechanism 221 and the second cam mechanism 222 operate. However, when the output-side rotator 12 reaches a predetermined number of revolutions or more, only the first cam mechanism 221 operates and the second cam mechanism 222 does not operate. Therefore, if the shapes of the cams 26 and the rotating members 281 and 282 of the two cam mechanisms 221 and 222 are appropriately set according to the engine specifications and the like, torque fluctuation can be effectively suppressed.

-Sixth Embodiment-
A sixth embodiment is shown in FIG. In the sixth embodiment, two first cam mechanisms 221 and two second cam mechanisms 222 are arranged on one output-side rotator 12 and one inertia ring 20. Since the configuration of each cam mechanism 221, 222 is the same as that of the first embodiment, it is omitted here. In the sixth embodiment, the characteristic for suppressing the torque fluctuation is a characteristic obtained by synthesizing the first cam mechanism 221 and the second cam mechanism 222 unlike the first embodiment.

[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) As shown in FIG. 14, the inertia ring constituting the torque fluctuation suppressing device may be connected to the turbine 8. In this case, the turbine 8 is not connected to the output hub 5. In this example, since the inertia ring is connected to the turbine 8 (more precisely, the turbine shell 8a), the turbine shell 8a also functions as an inertia (inertial body) together with the inertia ring.

  In the embodiment shown in FIG. 14, in the lock-up-off state, torque from the torque converter body 3 is transmitted from the torque fluctuation suppressing device 14 to the output-side rotating body 12 via the turbine 8 and is output to the output hub 5. Is output. At this time, it is difficult to transmit torque (not a fluctuating torque but a steady average torque) from the inertia ring to the output-side rotator 12 via the cam mechanism. For this reason, it is necessary to configure such that torque is transmitted using a spring, a mechanical stopper, or the like while ensuring the operating angle of the cam mechanism.

  (B) As shown in FIG. 15, a member that reduces friction such as a roller, a resin race, or a sheet may be disposed between the centrifuge 21 and the recess 12a.

[Application example]
When the torque fluctuation suppressing device as described above is applied to a torque converter or another power transmission device, various arrangements are possible. Below, a specific application example is demonstrated using the schematic diagram of a torque converter or another power transmission device. In the drawings showing the following examples, the cam mechanism is shown in a simplified manner, but the cam mechanism in each of the above-described embodiments can be applied to all the cam mechanisms.

  (1) FIG. 16 is a diagram schematically showing a torque converter. The torque converter includes an input-side rotating body 71, an output-side rotating body 72, and a damper provided between the rotating bodies 71 and 72. 73. The input-side rotator 71 includes members such as a front cover, a drive plate, and a piston. The output side rotating body 72 includes a driven plate and a turbine hub. The damper 73 includes a plurality of torsion springs.

  In the example shown in FIG. 16, a centrifuge is provided in any of the rotating members that constitute the input-side rotator 71, and a cam mechanism 74 that operates by utilizing the centrifugal force acting on the centrifuge is provided. It has been. About the cam mechanism 74, the structure similar to the structure shown by the said each embodiment is applicable.

  (2) The torque converter shown in FIG. 17 is provided with a centrifuge in any of the rotating members constituting the output-side rotator 72, and a cam mechanism that operates by utilizing the centrifugal force acting on the centrifuge. 74 is provided. About the cam mechanism 74, the structure similar to the structure shown by the said each embodiment is applicable.

  (3) The torque converter shown in FIG. 18 has another damper 75 and an intermediate member 76 provided between the two dampers 73 and 75 in addition to the configuration shown in FIGS. doing. The intermediate member 76 is relatively rotatable with the input-side rotator 71 and the output-side rotator 72, and causes the two dampers 73 and 75 to act in series.

  In the example shown in FIG. 18, the intermediate member 76 is provided with a centrifuge, and a cam mechanism 74 that operates using a centrifugal force acting on the centrifuge is provided. About the cam mechanism 74, the structure similar to the structure shown by the said each embodiment is applicable.

  (4) The torque converter shown in FIG. 19 has a float member 77. The float member 77 is a member for supporting the torsion spring constituting the damper 73, and is formed, for example, in an annular shape so as to cover the outer periphery and at least one side surface of the torsion spring. The float member 77 is relatively rotatable with the input-side rotator 71 and the output-side rotator 72, and rotates around the damper 73 by friction with the torsion spring of the damper 73. That is, the float member 77 also rotates.

  In the example shown in FIG. 19, the float member 77 is provided with a centrifuge 78, and a cam mechanism 74 that operates using centrifugal force acting on the centrifuge 78 is provided. About the cam mechanism 74, the structure similar to the structure shown by the said each embodiment is applicable.

  (5) FIG. 20 is a schematic diagram of a power transmission device having a flywheel 80 having two inertia bodies 81 and 82 and a clutch device 84. That is, the flywheel 80 disposed between the engine and the clutch device 84 includes a first inertial body 81, a second inertial body 82 disposed so as to be rotatable relative to the first inertial body 81, and two inertial bodies. And a damper 83 disposed between 81 and 82. The second inertia body 82 also includes a clutch cover that constitutes the clutch device 84.

  In the example shown in FIG. 20, a centrifuge is provided in one of the rotating members constituting the second inertial body 82, and a cam mechanism 85 that operates by utilizing the centrifugal force acting on the centrifuge is provided. ing. About the cam mechanism 85, the structure similar to the structure shown by the said each embodiment is applicable.

  (6) FIG. 21 is an example in which a centrifuge is provided on the first inertial body 81 in the same power transmission device as that of FIG. A cam mechanism 85 that operates using centrifugal force acting on the centrifuge is provided. About the cam mechanism 85, the structure similar to the structure shown by the said each embodiment is applicable.

  (7) In addition to the configuration shown in FIGS. 20 and 21, the power transmission device shown in FIG. 22 includes another damper 86 and an intermediate member 87 provided between the two dampers 83, 86. Have. The intermediate member 87 is rotatable relative to the first inertial body 81 and the second inertial body 82.

  In the example shown in FIG. 22, a centrifuge 88 is provided on the intermediate member 87, and a cam mechanism 85 that operates using a centrifugal force acting on the centrifuge 88 is provided. About the cam mechanism 85, the structure similar to the structure shown by the said each embodiment is applicable.

  (8) FIG. 23 is a schematic diagram of a power transmission device in which a clutch device is provided on one flywheel. The first inertial body 91 in FIG. 23 includes one flywheel and a clutch cover of the clutch device 92. In this example, a centrifuge is provided on any of the rotating members that constitute the first inertial body 91, and a cam mechanism 94 that operates using a centrifugal force acting on the centrifuge is provided. For the cam mechanism 94, the same configuration as that shown in each of the above embodiments can be applied.

  (9) FIG. 24 is an example in which a centrifuge 95 is provided on the output side of the clutch device 92 in the same power transmission device as FIG. A cam mechanism 94 is provided that operates by utilizing the centrifugal force acting on the centrifuge 95. For the cam mechanism 94, the same configuration as that shown in each of the above embodiments can be applied.

  (10) Although not shown in the drawings, the torque fluctuation suppressing device of the present invention may be disposed on any of the rotating members constituting the transmission, and further, the shaft (propeller shaft or drive) on the output side of the transmission (Shaft).

  (11) As another application example, the torque fluctuation suppressing device of the present invention may be further applied to a conventionally known dynamic damper device or a power transmission device provided with a pendulum type damper device.

DESCRIPTION OF SYMBOLS 1 Torque converter 11 Input side rotary body 12 Output side rotary body 121 1st hub 122 2nd hub 14 Torque fluctuation suppression apparatus 20 Inertia ring (mass body)
201 First inertia ring 202 Second inertia ring 21 Centrifuge 22 Cam mechanism 221 First cam mechanism 222 Second cam mechanism 23 Coil spring (biasing member)
25 Kolo (Cam Follower)
26 Cam 73, 75, 83, 86 Damper 76, 87 Intermediate member 77 Float member 80 Flywheel 81, 82, 91 Inertial body 84, 92 Clutch device

Claims (20)

A torque fluctuation suppressing device for suppressing torque fluctuation of a rotating body to which torque is input,
A mass body that is rotatable together with the rotating body and is arranged to be rotatable relative to the rotating body;
A first centrifuge and a second centrifuge arranged to receive a centrifugal force generated by the rotation of the rotating body and the mass body;
When a relative displacement in the rotational direction occurs between the rotating body and the mass body due to the centrifugal force acting on the first centrifuge, the centrifugal force is changed to the first in the direction in which the relative displacement is reduced. A first cam mechanism for converting to a circumferential force;
When a relative displacement in the rotational direction occurs between the rotating body and the mass body due to the centrifugal force acting on the second centrifuge, the centrifugal force is applied to the second in the direction in which the relative displacement is reduced. A second cam mechanism for converting to a circumferential force;
Torque fluctuation suppressing device comprising: The rotator includes a first rotator disposed at a first axial position, and a second rotator disposed at a second axial position.
The mass body includes a first inertia ring disposed on an outer periphery or an inner periphery of the first rotating body, and a second inertia ring disposed on an outer periphery or an inner periphery of the second rotating body,
The first centrifuge is supported by the first rotating body or the first inertia ring so as to be movable in a radial direction,
The second centrifuge is supported by the second rotating body or the inertia ring so as to be movable in a radial direction,
The first cam mechanism is disposed at the first axial position in the axial direction;
The second cam mechanism is disposed at the second axial position in the axial direction.
The torque fluctuation suppressing device according to claim 1. The first centrifuge is arranged at a first circumferential position in the rotating body or the mass body,
The second centrifuge is disposed at a second circumferential position in the rotating body or the mass body,
The first cam mechanism is disposed at the first circumferential position;
The second cam mechanism is disposed at the second position in the circumferential direction.
The torque fluctuation suppressing device according to claim 1. The mass body has a first inertia ring disposed on the outer periphery of the rotating body, and a second inertia ring disposed on the outer periphery of the first inertia ring,
The first centrifuge is supported by the rotating body so as to be movable in a radial direction,
The second centrifuge is supported by the first inertia ring so as to be movable in a radial direction,
The first cam mechanism is disposed on an outer periphery of the rotating body on an inner periphery of the first inertia ring;
The second cam mechanism is disposed on the outer periphery of the first inertia ring and on the inner periphery of the second inertia ring.
The torque fluctuation suppressing device according to claim 1.   The second cam mechanism has an operation prohibiting mechanism that restricts the movement of the second centrifuge outward in the radial direction when the rotating body or the mass body is equal to or higher than a predetermined number of rotations. The torque fluctuation suppressing device according to claim 1, wherein the centrifugal force acting on the second centrifuge is not converted into a circumferential force. The rotating body has a recess on the outer peripheral surface,
At least one of the first and second centrifuges is accommodated in the recess so as to be movable in the radial direction.
The torque fluctuation suppressing device according to any one of claims 1 to 5. Of the first and second centrifuges, the coefficient of friction between the centrifuge accommodated in the recess and the recess is 0.1 or less.
The torque fluctuation suppressing device according to claim 6.   Between the side surface of the centrifuge in the direction in which the centrifuge accommodated in the recess moves and the recess, a friction reducing member for reducing the friction when the centrifuge moves is disposed. The torque fluctuation suppressing device according to claim 7. The first cam mechanism and the second cam mechanism are:
Cam followers provided in the first centrifuge and the second centrifuge;
Formed on the inner peripheral surface of the rotating body or the mass body arranged on the outer peripheral side, the cam follower comes into contact with the circumferential direction according to the relative displacement amount in the rotational direction between the rotating body and the mass body A cam having a shape in which the force changes;
Having
The torque fluctuation suppressing device according to any one of claims 6 to 8.   At least one of the first centrifuge and the second centrifuge is arranged radially outside so that the cam and the cam follower are in contact with each other when the rotating body and the mass body are not rotated. The torque fluctuation suppressing device according to claim 9, further comprising a biasing member biasing toward the direction.   The torque fluctuation suppressing device according to any one of claims 1 to 10, wherein the mass body is formed in a continuous annular shape. A torque converter disposed between the engine and the transmission,
An input-side rotating body to which torque from the engine is input;
An output-side rotating body that outputs torque to the transmission;
A damper disposed between the input-side rotor and the turbine;
A torque fluctuation suppressing device according to any one of claims 1 to 11,
Torque converter with   The torque converter according to claim 12, wherein the torque fluctuation suppressing device is disposed on the input side rotating body.   The torque converter according to claim 12, wherein the torque fluctuation suppressing device is disposed on the output side rotating body. The damper is
A first damper to which torque is input from the input side rotating body;
A second damper that outputs torque to the output-side rotating body;
An intermediate member provided between the first damper and the second damper;
Have
The torque fluctuation suppressing device is disposed on the intermediate member,
The torque converter according to claim 12. The damper has a plurality of coil springs,
A float member that is relatively rotatable with respect to the input side rotating body and the output side rotating body, and that supports the plurality of coil springs;
The torque fluctuation suppressing device is disposed on the float member;
The torque converter according to claim 12. A first inertial body that rotates about a rotation axis; a second inertial body that rotates about the rotation axis and is rotatable relative to the first inertial body; and the first inertial body and the second inertial body. A flywheel having a damper disposed therebetween,
A clutch device provided in the second inertial body of the flywheel;
A torque fluctuation suppressing device according to any one of claims 1 to 11,
Power transmission device with   The power transmission device according to claim 17, wherein the torque fluctuation suppressing device is disposed in the second inertial body.   The power transmission device according to claim 17, wherein the torque fluctuation suppressing device is disposed in the first inertial body. The damper is
A first damper that receives torque from the first inertial body;
A second damper that outputs torque to the second inertial body;
An intermediate member provided between the first damper and the second damper;
Have
The torque fluctuation suppressing device is disposed on the intermediate member,
The power transmission device according to claim 17.

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