JP6577823B2 - Torque fluctuation suppressing device, torque converter, and power transmission device - Google Patents

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. This lockup device is provided with a damper including a plurality of torsion springs.

  More specifically, the lockup device generally includes 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

  In the conventional dynamic damper device including Patent Document 1, it is possible to suppress the peak of torque fluctuation that occurs in a predetermined rotational speed range.

  However, in order to arrange the inertia ring and the coil spring constituting the dynamic damper device, an axial space is required. In the device of Patent Document 1, the dynamic damper device is arranged in a dead space, so that the entire device can be made relatively compact. However, in some cases, the provision of a dynamic damper device may lead to an increase in the size of the device in the axial direction.

  In addition, in the conventional dynamic damper device including Patent Document 1, it is possible to suppress the peak of torque fluctuation in a predetermined rotation speed range. It is necessary to change the spring constant, which may be difficult to cope with.

  An object of the present invention is to enable a device for suppressing torque fluctuation of a rotating member to suppress a peak of torque fluctuation in a relatively wide rotational speed range without increasing the axial space of the entire apparatus. It is in.

  (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 centrifuge, and a 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 centrifuge is arranged to receive a centrifugal force due to the rotation of the rotating body and the mass body. The cam mechanism receives a centrifugal force acting on the centrifuge, and when a relative displacement in the rotational direction occurs between the rotating body and the mass body, the centrifugal force is converted into a circumferential force in a direction in which the relative displacement is reduced. In addition to the conversion, when a torque fluctuation of a predetermined magnitude or more is input to the rotating body, the mass body is freely rotated with respect to the rotating body.

  In this device, when torque is input to the rotating body, the rotating body and the mass body are rotated by the operation of the cam mechanism. 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 centrifuge receives a centrifugal force. The cam mechanism converts the centrifugal force acting on the centrifuge into a circumferential force when a relative displacement occurs between the rotating body and the mass body due to the centrifugal force acting on the centrifuge. It operates to reduce the relative displacement between the rotating body and the mass body by the circumferential force. Torque fluctuation is suppressed by the operation of the cam mechanism. Further, when a torque fluctuation of a predetermined magnitude or more is input to the rotating body, the mass body freely rotates in the direction in which relative displacement occurs with respect to the rotating body.

  Here, since the apparatus is constituted by the mass body, the centrifuge, and the cam mechanism, these members can be arranged side by side in the radial direction with respect to the rotating body, and the axial space can be reduced. Is possible. In addition, since the centrifugal force acting on the centrifuge is used to suppress torque fluctuations, the characteristics that suppress torque fluctuations change according to the rotational speed of the rotating body, and the specifications of the cam mechanism are changed. By doing so, it is possible to change the characteristic for suppressing torque fluctuation, and to suppress the peak of torque fluctuation in a wider rotational speed range. Furthermore, the cam mechanism freely rotates the mass body in the direction in which the relative displacement occurs when a torque fluctuation of a predetermined magnitude or more is input to the rotating body, so that an excessive force acts on the cam mechanism. Can be prevented. For this reason, the strength of the cam mechanism can be set to an appropriate strength to avoid an increase in the cost of the cam mechanism and to avoid damage to the cam mechanism.

  (2) Preferably, when the torque fluctuation is equal to or less than a predetermined fluctuation value, the cam mechanism converts the centrifugal force into a circumferential force in a direction in which the relative displacement is reduced, and the torque fluctuation exceeds the predetermined fluctuation value. In the case, the mass body is freely rotated with respect to the rotating body.

  (3) Preferably, the cam mechanism rotates the rotating body and the mass body in synchronization when the torque fluctuation is smaller than a predetermined fluctuation value.

  (4) Preferably, the mass body is arrange | positioned at the outer periphery or inner periphery of a rotary body. In this case, since the rotating body and the mass body are arranged side by side in the radial direction, the axial space can be reduced.

  (5) Preferably, the rotary body or mass body arranged on the inner peripheral side has a recess on the outer peripheral surface. The centrifuge is accommodated in the recess so as to be movable in the radial direction. Also in this case, the axial space of the apparatus can be reduced as described above.

  (6) Preferably, the coefficient of friction between the centrifuge and the concave portion of the rotating body or the mass body is 0.1 or less.

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

  (8) Preferably, the cam mechanism includes a cam follower provided on the centrifuge and a cam. 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 amount of relative displacement 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.

  (9) Preferably, it further includes a biasing member that is disposed in the recess and biases the centrifuge radially outward so that the cam follower abuts the cam in a state where the rotating body and the mass body are not rotating. Yes.

  Here, the centrifuge is always brought into contact with the cam by the biasing member. For this reason, it is possible to eliminate the sound when the centrifuge separates from the cam when the rotation is stopped or when the centrifuge contacts (collises) with the cam when the rotation starts.

  (10) Preferably, the cam follower is a roller disposed on the outer peripheral surface of the centrifuge.

  (11) Preferably, the cam follower is a protrusion formed integrally with the centrifuge on the outer peripheral surface of the centrifuge.

  (12) Preferably, the cam mechanism includes a cam follower formed on an inner peripheral surface of a rotating body or a mass body arranged on the outer peripheral side, and a cam. The cam has an outer peripheral surface that abuts on the cam follower, is provided on the centrifuge, and has a shape in which the circumferential force changes according to the amount of relative displacement in the rotational direction between the rotating body and the mass body.

  (13) Preferably, the rotating body or mass body arranged on the outer peripheral side has a recess on the inner peripheral surface. The centrifuge is accommodated in the recess so as to be movable in the radial direction. Preferably, the cam mechanism includes a cam follower provided on the centrifuge and a cam. The cam is formed on the inner peripheral surface of the rotating body or mass body arranged on the inner peripheral side, and the cam follower comes into contact therewith and a circumferential force is generated according to the relative displacement amount in the rotational direction between the rotating body and the mass body. It has a shape that changes.

  (14) 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.

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

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

  (17) 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.

  (18) 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.

  (19) 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.

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

  (21) Preferably, the torque fluctuation suppressing device is arranged on the first inertial body.

  (22) 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 axial space can be particularly reduced, and 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 output side rotary body and torque fluctuation suppression apparatus of FIG. The figure equivalent to Drawing 2A of other embodiments. FIG. 2B is an enlarged partial view of FIG. 2A. The figure for demonstrating the action | operation of a cam mechanism. The figure for demonstrating the action | operation of a cam mechanism when excessive torque fluctuation | variation is input. The characteristic view which shows the relationship between a rotation speed and a torque fluctuation. The figure equivalent to FIG. 3 of the modification 1 of a cam mechanism. The figure equivalent to FIG. 3 of the modification 2 of a cam mechanism. The figure equivalent to FIG. 3 of the modification 3 of a cam mechanism. The figure equivalent to FIG. 3 of the modification 4 of a cam mechanism. The figure equivalent to FIG. 3 which shows other embodiment of this invention. The figure equivalent to FIG. 1 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 is disposed so as to face the input-side rotator 11 in the axial direction, and is rotatable relative to the input-side rotator 11. The output side rotating body 12 is connected to the output hub 5.

  The damper 13 is disposed between the input side rotating body 11 and the output side rotating body 12. The damper 13 has a plurality of torsion springs, and elastically connects the input side rotating body 11 and the output side rotating body 12 in the rotation direction. The damper 13 transmits torque from the input-side rotator 11 to the output-side rotator 12, and absorbs and attenuates torque fluctuations.

[Torque fluctuation suppressing device 14]
FIG. 2A is a front view of the output side rotating body 12 and the torque fluctuation suppressing device 14. As shown in FIG. 2A, the torque fluctuation suppression device 14 includes an inertia ring 20, four centrifuges 21, four cam mechanisms 22, and four coil springs 23. Each of the four centrifuges 21, the cam mechanism 22, and the coil springs 23 are arranged at equal intervals of 90 ° in the circumferential direction. As will be described later, the cam mechanism 22 includes a cam follower 25 and a cam 26, but the cams 26 are formed at a total of eight positions at equal angular intervals with respect to the four cam followers 25.

  In addition, as shown to FIG. 2B, it is also possible to abbreviate | omit the coil spring 23 arrange | positioned at the inner peripheral side of the centrifuge 21. FIG. Similarly, in each example described below, the coil spring 23 may be provided or omitted.

  The inertia ring 20 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 rotating body 12 with a predetermined gap in the radial direction. That is, the inertia ring 20 is disposed at the same position as the output side rotating body 12 in the axial direction. The inertia ring 20 has the same rotation axis as that 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 centrifuge 21 is disposed on the output-side rotator 12 and is movable radially outward by a centrifugal force generated by the rotation of the output-side rotator 12. More specifically, as shown in an enlarged view in FIG. 3, the output-side rotating body 12 is provided with a recess 12 a on the outer peripheral surface. The recess 12a is formed in a rectangular shape on the outer peripheral surface of the output-side rotating body 12 so as to be recessed toward the center of rotation on the inner peripheral side. The centrifuge 21 is inserted into the recess 12a so as to be movable in the radial direction. The centrifuge 21 and the recess 12a are set so that the friction coefficient between the side surface of the centrifuge 21 and the recess 12a is 0.1 or less. The centrifuge 21 is a plate having substantially the same thickness as that of the output-side rotator 12, 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. 3, the cam mechanism 22 includes a roller 25 as a cam follower and a cam 26 formed on the inner peripheral surface of the inertia ring 20. 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 output side rotating body 12 and the inertia ring 20 are relatively rotated within a predetermined angular range, the roller 25 moves along the cam 26.

  Although details will be described later, when a rotational phase difference is generated between the output-side rotating body 12 and the inertia ring 20 due to torque fluctuation, the centrifugal force generated in the centrifuge 21 and the roller 25 due to the contact between the roller 25 and the cam 26. The force is converted into a circumferential force that reduces the rotational phase difference. Further, when the torque fluctuation is a fluctuation value exceeding a predetermined value, the inertia ring 20 freely rotates in the direction in which the rotation phase difference is generated with respect to the output side rotating body 12.

  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 inertia ring 20. Therefore, even when the output side rotating body 12 is not rotating and the centrifugal force is not acting on the centrifuge 21, the roller 25 contacts the cam 26.

[Operation of cam mechanism 22]
Operation of the cam mechanism 22 (torque fluctuation suppression) will be described with reference to FIGS. 3 and 4. When the lockup is on, the torque transmitted to the front cover 2 is transmitted to the output-side rotator 12 via the input-side rotator 11 and the damper 13.

  When there is no torque fluctuation during torque transmission, the output side rotating body 12 and the inertia ring 20 rotate in the state shown in FIG. That is, the roller 25 of the cam mechanism 22 abuts on the deepest position (circumferential center position) of the cam 26, and the rotational phase difference between the output side rotating body 12 and the inertia ring 20 is “0”.

  As described above, the relative displacement in the rotation direction between the output-side rotator 12 and the inertia ring 20 is referred to as “rotational phase difference”. In FIGS. 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 is shown.

  On the other hand, when torque fluctuation occurs during torque transmission, a rotational phase difference ± θ is generated between the output-side rotator 12 and the inertia ring 20, as shown in FIGS. FIG. 4A shows a case where a rotational phase difference + θ occurs on the + R side, and FIG. 4B shows a case where a rotational phase difference −θ occurs on the −R side.

  As shown in FIG. 4A, when a rotational phase difference + θ occurs between the output-side rotator 12 and the inertia ring 20, the roller 25 of the cam mechanism 22 is relatively illustrated along the cam 26. Move to the left side of 4. At this time, since the centrifugal force acts 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 output-side rotating body 12 to the right in FIG. 4A via the cam mechanism 22. That is, a force in the direction of reducing the rotational phase difference between the output side rotating body 12 and the inertia ring 20 acts on the output side rotating body 12. 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. 4B shows a case where a rotational phase difference −θ is generated between the output side rotator 12 and the inertia ring 20. The moving direction of the roller 25 of the cam mechanism 22, the reaction force P 0, The operation is the same except that the directions of the 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 output-side rotating body 12 and the inertia ring 20 due to torque fluctuation, the output-side rotating body 12 is caused by the centrifugal force acting on the centrifuge 21 and the action of the cam mechanism 22. , A force (first component force P1) in a direction to reduce the rotational phase difference between the two is received. This force suppresses torque fluctuations.

  The force that suppresses the torque fluctuation described above varies depending on the centrifugal force, that is, the rotational speed of the output-side rotator 12, and also varies depending on the rotational phase difference and the shape of the cam. 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.

  When the torque fluctuation further increases and exceeds a predetermined fluctuation value, the cam 26 of the inertia ring 20 passes through the roller 25 as shown in FIG. That is, when an excessive torque fluctuation exceeding a predetermined fluctuation value is input to the output-side rotator 12, the cam mechanism 22 causes the inertia ring 20 to move in a direction in which a relative displacement has occurred with respect to the output-side rotator 12. Rotate freely. In FIG. 5, the inertia ring 20 rotates in the −R direction, and the cam 26 that has been operating as the cam mechanism is moving away from the roller 25.

  Thereafter, the roller 25 is fitted into the next cam 26 (the cam 26 formed in the clockwise direction in FIG. 5). If the torque fluctuation at that time is equal to or less than a predetermined fluctuation value, the cam mechanism 22 operates normally as described with reference to FIG. 4, and the torque fluctuation is suppressed. If the torque fluctuation exceeds a predetermined fluctuation value, the inertia ring 20 further rotates in the −R direction as described above.

  As described above, when an excessive torque fluctuation is input, the cam 26 of the inertia ring 20 exceeds the roller 25, and the inertia ring 20 freely rotates in the direction in which the relative displacement occurs with respect to the output side rotating body 12. To do. For this reason, excessive force does not act on the cam mechanism 22, and damage to the cam mechanism 22 can be avoided. Further, it is not necessary to design the cam mechanism 22 so as to withstand excessive torque fluctuations, and the manufacturing cost of the cam mechanism 22 can be reduced.

[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.

[Modification of Cam Mechanism 22]
(Modification 1)
In the embodiment shown in FIG. 7, a friction reducing member 30 such as a bearing, a roller, a resin race, and a sheet is disposed between the centrifuge 21 and the side surface (circumferential end surface) of the recess 12 a. By disposing such a friction reducing member 30, when the centrifuge 21 moves, it can move more smoothly.

(Modification 2)
In the embodiment shown in FIG. 8, the shape of the centrifuge and the inertia ring is different from that of the above embodiment. That is, the outer peripheral surface 31a of the centrifuge 31 is formed in an arc shape that is recessed toward the inner peripheral side. This outer peripheral surface 31a functions as a cam. On the other hand, on the inner peripheral surface of the inertia ring 40, a roller accommodating portion 40a that accommodates the roller 25 as a cam follower is formed. The roller 25 is in contact with the outer peripheral surface 31a as a cam.

  In this embodiment, the roller 25 as the cam follower of the cam mechanism 32 is disposed on the inertia ring 40, and the other configurations and operations are the same as those of the above embodiment except that the cam 31a is provided on the centrifuge 31. is there.

(Modification 3)
FIG. 9 shows an example in which the cam follower of the cam mechanism is formed integrally with the centrifuge. That is, a semicircular protrusion 41 a that protrudes to the outer peripheral side is formed on the outer peripheral surface of the centrifuge 41. The protrusion 41a functions as a cam follower, contacts the cam 26 formed on the inertia ring 20, and operates in the same manner as in the above embodiment.

(Modification 4)
FIG. 10 shows an example in which a centrifuge is arranged on the inertia ring side and a cam mechanism is arranged on the inner peripheral surface of the output side rotating body. A rectangular recess 50a is formed on the inner peripheral surface of the inertia ring 50, and a centrifuge 51 is disposed in the recess 50a so as to be movable in the radial direction. In addition, a tension spring 53 is provided between the centrifuge 51 and the bottom surface of the recess 50a to draw the centrifuge 51 to the outer peripheral side.

  On the other hand, the cam mechanism 52 includes a roller 55 as a cam follower provided at the tip (inner peripheral end) of the centrifuge 51 and a cam 56 formed on the inner peripheral surface of the output-side rotating body 57. . The shape of the cam 56 is the same as that in the above embodiment. The roller 55 is always in contact with the cam 56 by the biasing force of the tension spring 53.

  In this embodiment, when the inertia ring 50 rotates together with the output-side rotator 57, the centrifuge 51 generates a centrifugal force toward the outer peripheral side. The roller 55 is pressed against the cam 56 by this centrifugal force. The operation when torque fluctuation occurs is the same as in the above 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) The positional relationship between the output side rotator and the inertia ring is not limited to the above embodiment. For example, as shown in FIG. 11, the output side rotating body 60 may be disposed on the outer peripheral side and the inertia ring 61 may be disposed on the inner peripheral side, contrary to the above embodiment. Other configurations such as the cam mechanism 22 are the same as those in the above embodiment.

  (B) As shown in FIG. 12, the inertia ring constituting the torque fluctuation suppressing device 14 may be connected to the turbine 8. In this case, the turbine 8 is not connected to the output hub 5. In this case, 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. 12, in the lockup-off state, torque from the torque converter main 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 the torque is transmitted using a spring, a mechanical stopper, or the like while ensuring the operating angle of the cam mechanism.

  (C) In the above embodiment, the cam mechanism is operated when the torque fluctuation is equal to or smaller than the predetermined fluctuation value. However, when the fluctuation value of the torque fluctuation is very small, as in the case where there is no torque fluctuation, It is also possible to make specifications so that the cam mechanism is not operated.

[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.

  (1) FIG. 13 is a diagram schematically showing a torque converter. The torque converter includes an input-side rotator 71, an output-side rotator 72, and a damper provided between the rotators 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. 13, a centrifuge is provided in one of the input side rotators 71, 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.

  (2) The torque converter shown in FIG. 14 is provided with a centrifuge in one of the output side rotators 72, and a cam mechanism 74 that operates by utilizing the centrifugal force acting on the centrifuge. Yes. 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. 15 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. is 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. 15, 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. 16 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. 16, the float member 77 is provided with a centrifuge 78, and a cam mechanism 74 that operates using a 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. 17 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. 17, a centrifuge is provided in any of the rotating members that constitute the second inertial body 82, and a cam mechanism 85 that operates using 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. 18 is an example in which a centrifuge is provided on the first inertial body 81 in the same power transmission device as that in 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. 17 and 18, the power transmission device shown in FIG. 19 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. 19, the intermediate member 87 is provided with a centrifuge 88, and a cam mechanism 85 that operates by utilizing 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. 20 is a schematic diagram of a power transmission device in which a clutch device is provided on one flywheel. The first inertia body 91 of FIG. 20 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. 21 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 12, 57, 60 Output side rotary body 14 Torque fluctuation suppression apparatus 20, 40, 50, 61 Inertial (mass body)
21, 31, 41, 51, 78, 88, 95 Centrifuge 22, 32, 74, 85, 94 Cam mechanism 23 Coil spring (biasing member)
25 Rollers 26, 31a Cam 30 Thrust member 65 Inertia body 66 Holding ring 71 Input side rotating body 72 Output side rotating body 73, 75, 83, 86 Damper 76, 87 Intermediate member 77 Float member 80 Flywheel 81, 91 First inertia Body 82 Second inertial body 84, 92 Clutch device

Claims (23)

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 centrifuge arranged to receive a centrifugal force due to 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 centrifuge, the centrifugal force is converted into a circumferential force in a direction in which the relative displacement is reduced. And a cam mechanism that freely rotates the mass body relative to the rotating body when a torque fluctuation of a predetermined magnitude or more is input to the rotating body.
Torque fluctuation suppressing device comprising: The cam mechanism is
When the torque fluctuation is equal to or less than a predetermined fluctuation value, the centrifugal force is converted into a circumferential force in a direction in which the relative displacement is reduced,
When the torque fluctuation exceeds the predetermined fluctuation value, the mass body is freely rotated with respect to the rotating body,
The torque fluctuation suppressing device according to claim 1.   The torque variation suppressing device according to claim 2, wherein the cam mechanism rotates the rotating body and the mass body in synchronization when the torque variation is smaller than the predetermined variation value.   The torque fluctuation suppressing device according to any one of claims 1 to 3, wherein the mass body is disposed on an outer periphery or an inner periphery of the rotating body. The rotating body or mass body arranged on the inner peripheral side has a recess on the outer peripheral surface,
The centrifuge is accommodated in the recess so as to be movable in the radial direction.
The torque fluctuation suppressing device according to claim 4.   The torque fluctuation suppression device according to claim 5, wherein a friction coefficient between the centrifuge and the concave portion of the rotating body or the mass body is 0.1 or less.   A friction reducing member for reducing friction when the centrifuge moves is disposed between a side surface of the centrifuge in a direction in which the centrifuge moves and a concave portion of the rotating body or mass body. The torque fluctuation suppressing device according to claim 5 or 6. The cam mechanism is
A cam follower provided in the 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 5 to 7.   And a biasing member that is disposed in the recess and biases the centrifuge radially outward so that the cam follower abuts the cam in a state where the rotating body and the mass body are not rotating. The torque fluctuation suppressing device according to claim 8.   The torque fluctuation suppressing device according to claim 8 or 9, wherein the cam follower is a roller disposed on an outer peripheral surface of the centrifuge.   The torque fluctuation suppression device according to claim 8 or 9, wherein the cam follower is a protrusion formed integrally with the centrifuge on an outer peripheral surface of the centrifuge. The cam mechanism is
A cam follower formed on an inner peripheral surface of the rotating body or the mass body arranged on the outer peripheral side;
An outer peripheral surface abuts on the cam follower, is provided on the centrifuge, and has a shape such that the circumferential force changes according to the amount of relative displacement in the rotational direction between the rotating body and the mass body. When,
Having
The torque fluctuation suppressing device according to any one of claims 5 to 7. The rotating body or mass body arranged on the outer peripheral side has a recess on the inner peripheral surface,
The centrifuge is accommodated in the recess so as to be movable in the radial direction,
The cam mechanism is
A cam follower provided in the centrifuge;
It is formed on the inner peripheral surface of the rotating body or the mass body arranged on the inner peripheral side, and the cam follower comes into contact with the circumference according to the amount of relative displacement in the rotational direction between the rotating body and the mass body. A cam having a shape in which the directional force changes,
Having
The torque fluctuation suppressing device according to claim 4.   The cam mechanism is
  A roller held immovable in the circumferential direction with respect to the mass body;
  The outer circumferential surface of the centrifuge is formed in a circular arc shape that is recessed toward the inner circumferential side, abuts on the roller, and the circumferential force depends on the amount of relative displacement in the rotational direction between the rotating body and the mass body. A cam having a changing shape;
Having
The torque fluctuation suppressing device according to claim 1. 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 rotating body and the output side rotating body;
The torque fluctuation suppressing device according to any one of claims 1 to 14 ,
Torque converter with The torque converter according to claim 15 , wherein the torque fluctuation suppressing device is disposed on the input side rotating body. The torque converter according to claim 15 , 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 15 . 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 15 . 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;
The torque fluctuation suppressing device according to any one of claims 1 to 14 ,
Power transmission device with The power transmission device according to claim 20 , wherein the torque fluctuation suppressing device is disposed in the second inertial body. The power transmission device according to claim 20 , 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 20 .

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