JP2019065901A - Torque variation suppression device and torque converter - Google Patents

Abstract

To suppress the viscous resistance of fluid received by centrifugal elements, and to obtain desired vibration attenuation performance, in a torque variation suppression device having the centrifugal elements and cam mechanisms.SOLUTION: This device comprises an inertia ring 20, a plurality of centrifugal elements 21 and a plurality of cam mechanisms 22. The inertia ring 20 is arranged so as to be relatively rotatable with respect to a hub flange 12. A plurality of the centrifugal elements 21 are arranged so as to be movable in a radial direction in the fluid by receiving centrifugal forces by the rotation of the hub flange 12 and the inertia ring 20, and have communication grooves 21d, 21e for reducing viscous resistance generated by the fluid at movement in the radial direction. When relative displacement in a rotation direction is generated between the hub flange 12 and the inertia ring 20, a plurality of the cam mechanisms 22 receive the centrifugal forces acting on the centrifugal elements 21, and convert the centrifugal forces to circumferential forces in a direction in which the relative displacement becomes small.SELECTED DRAWING: Figure 2

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 which rotates around a rotation shaft and receives torque. The present invention also relates to a torque converter provided with a torque fluctuation suppressor.

  For example, a clutch device including a damper device and a torque converter are provided between an engine and a transmission of an automobile. 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.

  Patent Document 1 discloses a lockup device provided with a torque fluctuation suppression device. The torque fluctuation suppressing device of Patent Document 1 includes inertia, a plurality of centrifuges, and a plurality of cam mechanisms. The inertia ring is rotatable relative to the hub flange to which torque is transmitted, and the centrifuge receives centrifugal force by the rotation of the hub flange and the inertia ring. The cam mechanism has a cam formed on the surface of the centrifuge and a cam follower in contact with the cam.

  In the device of this patent document 1, when a shift in the rotational direction occurs between the hub flange and the inertia ring due to torque fluctuation, the cam mechanism operates in response to the centrifugal force acting on the centrifugal member, causing the centrifugal member to The acting centrifugal force is converted into a circumferential force in the direction in which the deviation between the hub flange and the inertia ring is reduced. The circumferential force suppresses torque fluctuations.

JP, 2017-53467, A

  In the torque fluctuation suppressing device of Patent Document 1, the centrifuge reciprocates in the radial direction in the housing space surrounded by the hub flange and the inertia ring. Here, in the case where the torque fluctuation suppressing device is applied to a lockup device of a torque converter, a working fluid is present in a space that accommodates a centrifuge. Therefore, when the centrifuge moves, the centrifuge receives viscosity resistance of fluid. If the centrifuge receives viscous resistance, it will be difficult to move and the vibration damping effect of the device will be lost.

  An object of the present invention is to suppress the viscous resistance of fluid received by a centrifuge and obtain desired vibration damping performance in a torque fluctuation suppressor having a centrifuge and a cam mechanism.

  (1) The torque fluctuation suppressing device according to the present invention is a device that suppresses torque fluctuation of a rotating body to which torque is input. The torque fluctuation suppressor includes a mass body, a plurality of centrifuges, and a plurality of cam mechanisms. The mass is rotatable with the rotating body, and is disposed so as to be rotatable relative to the rotating body. The plurality of centrifuges are disposed radially movably in the fluid under centrifugal force generated by the rotation of the rotating body and the mass body, and a viscous drag reduction portion for reducing viscous drag due to fluid when moving in the radial direction. Have. The plurality of cam mechanisms receive a centrifugal force acting on the centrifuge, and when a relative displacement occurs in the rotational direction between the rotating body and the mass body, the centrifugal force is reduced in the circumferential direction in which the relative displacement decreases. Convert to 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 rotational direction between the rotating body and the mass body. On the other hand, if there is a fluctuation in the torque to be input, the mass body is disposed so as to be rotatable relative to the rotating body, so depending on the degree of the torque fluctuation, the relative displacement in the rotational direction 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. Then, when relative displacement in the rotational direction occurs between the rotating body and the mass body, the cam mechanism converts the centrifugal force acting on the centrifuge into circumferential force. This circumferential force acts to reduce the relative displacement between the rotor and the mass. The operation of such a cam mechanism suppresses torque fluctuation.

  Here, since the centrifugal force acting on the centrifuge is used as a force for suppressing the torque fluctuation, the characteristic of suppressing the torque fluctuation changes in accordance with the number of rotations of the rotating body. Further, for example, the characteristic of suppressing the torque fluctuation can be appropriately set by the shape of the cam or the like, and the peak of the torque fluctuation in a wider rotation speed region can be suppressed.

  In addition, here, the centrifuge is provided with a viscous drag reduction portion such as a groove extending in the radial direction, for example. As a result, when the centrifuge is moved in the radial direction, the viscous drag due to the fluid to the centrifuge is reduced, and desired vibration damping performance can be obtained.

  (2) Preferably, the viscous drag reduction portion causes fluid to flow between the outer peripheral side and the inner peripheral side of the centrifugal separator.

  Here, since the fluid flows on the outer peripheral side and the inner peripheral side of the centrifuge through the viscous drag reduction portion, the viscosity resistance when the centrifuge moves in the radial direction is reduced, and the centrifuge can be moved smoothly. it can.

  (3) Preferably, the viscous drag reduction portion is a groove which is formed on at least one side surface of the centrifugal shaft in the rotation axis direction and extends in the radial direction.

  (4) Preferably, the radially extending groove is a groove whose width extends toward at least one of radially inward and outward.

  In this case, the fluid on the outer peripheral side or the inner peripheral side of the centrifuge easily flows into the groove of the centrifuge. This further reduces the viscous drag on the centrifuge.

  (5) Preferably, the viscous drag reduction portion is a hole which penetrates the centrifuge in the radial direction.

  (6) Preferably, the viscous drag reduction portion is a region in which the thickness in the rotational axis direction is thinner than the other portion formed at at least one end in the radial direction of the centrifugal separator.

  In this case, the fluid can easily flow through the thin region formed at one end of the centrifuge. For this reason, the viscous resistance to the centrifuge is reduced as described above.

  (7) Preferably, the thickness of the rotating shaft direction is gradually reduced from the central portion side in the radial direction to at least one side of the outer peripheral side and the inner peripheral side in the radial direction. This is an area where the thickness of one end of the

  (8) Preferably, the viscous drag reduction portion is a region formed in a curved surface shape at a corner portion of at least one end in the radial direction of the centrifugal separator.

  Here, a wider gap is secured between the wall of the space for accommodating the centrifuge and the curved corner portion of the centrifuge as compared to the others. Fluid flows between the outer peripheral side and the inner peripheral side of the centrifugal separator through the wide gap. Thus, the viscous drag on the centrifuge is reduced.

  (9) Preferably, the viscous drag reduction portion causes fluid to flow between one side and the other side in the circumferential direction of the centrifuge.

  In this case, the viscous drag between the wall of the space containing the centrifuge and the side of the centrifuge is reduced.

  (10) Preferably, it further comprises a plurality of regulating mechanisms which allow the operation of the centrifuge by the cam mechanism and regulate the radial movement of the centrifuge.

  Here, when the rotation of the rotating body is stopped, the centrifuge located at the upper side may fall downward, and the centrifuge may collide with another member to generate a tapping noise. Then, if the viscosity resistance to the centrifuge is reduced by the viscosity resistance reduction unit, the centrifuge may drop vigorously and the hitting noise may increase.

  Therefore, it is preferable to provide a restriction mechanism that restricts the radial movement of the centrifuge while permitting the operation of the centrifuge by the cam mechanism by means of the restriction mechanism. In this case, it is possible to prevent the hitting sound from being generated when the centrifugal separator collides with another member such as a rotating body at the time of rotation stop or the like. Further, even in the case where the centrifuge and the other member collide, it is possible to suppress the hitting sound at the time of the collision.

  (11) Preferably, the rotating body has a plurality of accommodating portions that accommodates the centrifugal element in a radially movable manner, and the regulating mechanism regulates that the inner circumferential surface of the centrifugal element abuts on the bottom surface of the accommodating portion .

  (12) Preferably, the cam mechanism has a cam provided on one of the mass body and the centrifuge, and a cam follower provided on the other of the mass body and the centrifuge and moving along the cam.

  Here, the amount of relative displacement in the rotational direction between the rotating body and the mass body varies depending on the magnitude of the torque variation of the rotating body. At this time, by setting the shape of the cam so that the circumferential force converted from the centrifugal force changes in accordance with the relative displacement amount, it is possible to suppress the torque fluctuation more efficiently.

  (13) Preferably, the mass body includes a first inertia ring and a second inertia ring disposed opposite to each other with the rotating body interposed therebetween, and a pin for connecting the first inertia ring and the second inertia ring so as not to be relatively rotatable. ,have. The centrifuge is disposed on the outer peripheral portion of the rotating body and on the inner peripheral side of the pin in the axial direction between the first inertia ring and the second inertia ring. The cam follower is a cylindrical roller having a hole through which a pin passes in the axial direction. The cam is formed on the centrifugal element and is in contact with the cam follower, and has a shape such that circumferential force changes according to the relative displacement amount in the rotational direction between the rotating body and the mass body.

  Here, the cam follower is mounted using a pin that connects the first inertia ring and the second inertia ring. This simplifies the configuration of the cam mechanism.

  (14) The torque converter according to the present invention is disposed between the engine and the transmission. The torque converter includes any one of the above-described input rotors to which torque from the engine is input, a hub flange for outputting torque to the transmission, and a damper disposed between the input rotor and the turbine. And a torque fluctuation suppressing device.

  (15) A power transmission device according to the present invention includes a flywheel, a clutch device, and any one of the torque fluctuation suppressing devices described above. The flywheel includes a first inertia body rotating about a rotation axis, a second inertia body rotating relative to the first inertia body rotating about the rotation axis, a first inertia body, and a second inertia body. And a damper disposed therebetween. The clutch device is provided on the second inertia body of the flywheel.

  According to the present invention as described above, in the torque fluctuation suppressing apparatus having a centrifuge and a cam mechanism, it is possible to suppress the viscous resistance of the fluid received by the centrifuge and obtain desired vibration damping performance.

FIG. 2 is a schematic view of a torque converter according to an embodiment of the present invention. The front partial view of the hub flange of FIG. 1, and a torque fluctuation control apparatus. Arrow A figure of FIG. FIG. 3 is an external perspective view of a portion shown in FIG. 2; The figure for demonstrating the action | operation of a cam mechanism. The figure for demonstrating the action | operation of a cam mechanism. The characteristic view which shows the relationship between rotation speed and torque fluctuation. The figure corresponding to FIG. 2 which shows the modification of a viscous drag reduction part. The figure corresponding to FIG. 3 which shows the modification of a viscous drag reduction part. The figure corresponding to FIG. 2 which shows another modification of a viscous drag reduction part. The figure corresponding to FIG. 2 which shows another modification of a viscous drag reduction part. The figure corresponding to FIG. 3 which shows another modification of a viscous drag reduction part. The figure corresponding to FIG. 3 which shows another modification of a viscous drag reduction part. 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 view of a torque fluctuation suppressing apparatus according to an embodiment of the present invention mounted on a lockup device of a torque converter. In FIG. 1, OO is a rotational axis of the torque converter.

[overall structure]
The torque converter 1 has 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 has 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 by splines on the inner periphery of the output hub 5.

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

  The lockup device 4 includes an input-side rotating body 11, a hub flange 12 (rotating body), a damper 13, and a torque fluctuation suppressing device 14.

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

  The hub flange 12 is disposed to axially face the input side rotating body 11 and is rotatable relative to the input side rotating body 11. The hub flange 12 is connected to the output hub 5.

  The damper 13 is disposed between the input side rotating body 11 and the hub flange 12. The damper 13 has a plurality of torsion springs, and elastically connects the input side rotation body 11 and the hub flange 12 in the rotational direction. The damper 13 transmits torque from the input side rotating body 11 to the hub flange 12 and absorbs and damps torque fluctuation.

[Torque fluctuation suppressor 14]
FIG. 2 is a front view of the hub flange 12 and the torque fluctuation suppressor 14. Note that FIG. 2 shows one (front side) of the inertia ring removed. 3 is a view as seen from the direction A of FIG. 2, and FIG. 4 is an external perspective view of FIG. Although the hub flange 12 and a part of the torque fluctuation suppressing device 14 are shown in the drawings after FIG. 2, as a whole, the parts shown in each drawing are provided at equal angular intervals at four places in the circumferential direction. There is.

  The torque fluctuation suppressing device 14 regulates the first inertia ring 201 and the second inertia ring 202, which constitute the inertia ring 20 (mass), the four centrifugal elements 21, the four cam mechanisms 22, and the four restrictions. And a mechanism 23.

<First and second inertia rings 201, 202>
The first and second inertia rings 201 and 202 are plates having a predetermined thickness formed in a continuous annular shape, and both sides of the hub flange 12 in the axial direction of the hub flange 12 as shown in FIG. Are arranged with a predetermined gap. That is, the hub flange 12 and the first and second inertia rings 201 and 202 are arranged in line in the axial direction. The first and second inertia rings 201 and 202 have the same rotation axis as the rotation axis of the hub flange 12, are rotatable with the hub flange 12, and are rotatable relative to the hub flange 12.

  In the first and second inertia rings 201 and 202, holes 201a and 202a penetrating in the axial direction are formed. The first inertia ring 201 and the second inertia ring 202 are fixed by rivets 24 passing through the holes 201a and 202a. Therefore, the first inertia ring 201 can not move in the axial direction, the radial direction, and the rotational direction with respect to the second inertia ring 202.

<Hub flange 12>
The hub flange 12 is formed in a disk shape, and the inner peripheral portion is connected to the output hub 5 as described above. At the outer peripheral portion of the hub flange 12, four protrusions 121 further protruding outward and having a predetermined width in the circumferential direction are formed. At a central portion in the circumferential direction of the protrusion 121, a recess 121a (housing portion) having a predetermined width is formed. The recess 121 a is formed to open to the outer peripheral side, and has a predetermined depth.

<Centrifuge 21>
The centrifugal element 21 is disposed in the recess 121 a of the hub flange 12 and can be moved in the radial direction by the centrifugal force caused by the rotation of the hub flange 12. The centrifugal element 21 is formed to extend in the circumferential direction, and has grooves 21a and 21b at both ends in the circumferential direction. The width of the grooves 21a and 21b is larger than the thickness of the hub flange 12, and the hub flange 12 is inserted in a part of the grooves 21a and 21b.

  The outer peripheral surface 21 c of the centrifugal element 21 is formed in an arc shape recessed toward the inner peripheral side, and functions as a cam 31 as described later.

  Two rollers 26a and 26b are disposed in the grooves 21a and 21b at both ends of the centrifuge 21, respectively. Each roller 26a, 26b is rotatably mounted around a pin 27 provided penetrating the grooves 21a, 21b in the rotational axis direction. And each roller 26a, 26b can contact | abut in the side surface of the recessed part 121a, and can roll.

  Further, as shown in FIGS. 2 to 4, flow grooves 21 d and 21 e (viscous resistance reduction portions) penetrating in the radial direction are formed on both side surfaces of the centrifugal element 21 in the rotational axis direction. The respective flow grooves 21d and 21e are formed at positions separated by the same distance from the center of the circumferential direction of the centrifuge 21 to one side and the other side. Further, the width of each of the flow grooves 21d and 21e is wider as it goes from the center in the radial direction to the outer peripheral side and the inner peripheral side. For this reason, it is possible for the hydraulic oil on the outer peripheral side and the inner peripheral side of the centrifugal element 21 to move smoothly in the radial direction through the flow grooves 21d and 21e.

<Cam mechanism 22>
The cam mechanism 22 includes a cylindrical roller 30 as a cam follower, and a cam 31 which is an outer peripheral surface 21 c of the centrifugal element 21. The roller 30 is fitted on the outer periphery of the body of the rivet 24. That is, the roller 30 is supported by the rivet 24. In addition, although it is preferable that the roller 30 is rotatably mounted with respect to the rivet 24, it may be non-rotatable. The cam 31 is an arc-shaped surface on which the roller 30 abuts, and when the hub flange 12 and the first and second inertia rings 201 and 202 relatively rotate within a predetermined angle range, the roller 30 is engaged with the cam 31 Move along.

  Although the details will be described later, when the rotational phase difference is generated between the hub flange 12 and the first and second inertia rings 201 and 202 due to the contact between the roller 30 and the cam 31, the centrifugal produced in the centrifuge 21 The force is converted to a circumferential force such that the rotational phase difference is reduced.

<Regulatory mechanism 23>
The restricting mechanism 23 allows the cam mechanism 22 to operate the centrifuge 21 and restricts the radial movement of the centrifuge 21. The regulating mechanism 23 has a pin (regulating shaft) 231 and a groove (regulating groove) 232.

  The pin 231 is provided to penetrate the centrifuge 21 in the rotation axis direction. More specifically, the pin 231 is provided at the central portion in the longitudinal direction (circumferential direction) of the centrifuge 21 so as to extend along the rotation axis. Further, the groove 232 is formed in the same position and in the same shape in each of the first inertia ring 201 and the second inertia ring 202. The groove 232 is formed in a circular arc shape convex on the outer peripheral side, and the pin 231 is inserted into the groove 232. A predetermined gap is provided between the pin 231 and the groove 232, and the pin 231 can move smoothly in the groove 232.

  Further, when there is no relative displacement in rotational direction (rotational phase difference) between the hub flange 12 and the first and second inertia rings 201 and 202, as shown in FIG. It is located at the center in the longitudinal direction (circumferential direction). When the rotational phase difference occurs between the hub flange 12 and the two inertia rings 201 and 202, the centrifugal force of the centrifugal mechanism 21 is moved by the operation of the cam mechanism 22. The pin 231 moves along the groove 232 as the centrifuge 21 operates. However, the shape of the groove 232 is set such that the inner peripheral surface of the centrifugal element 21 does not abut on the bottom surface of the recess 121 a of the hub flange 12 wherever the pin 231 is positioned in the groove 232.

[Operation of cam mechanism 22]
The operation of the cam mechanism 22 (suppression of the torque fluctuation) will be described with reference to FIGS. 2, 5 and 6. In the following description, the first and second inertia rings 201 and 202 may be simply referred to as “inertia ring 20”.

  When lockup is on, the torque transmitted to the front cover 2 is transmitted to the hub flange 12 via the input side rotating body 11 and the damper 13.

  When there is no torque fluctuation at the time of torque transmission, the hub flange 12 and the inertia ring 20 rotate in the state as shown in FIG. In this state, the roller 30 of the cam mechanism 22 abuts on the innermost circumferential position (center position in the circumferential direction) of the cam 31 and the rotational phase difference between the hub flange 12 and the inertia ring 20 is "0". .

  As described above, although the relative displacement between the hub flange 12 and the inertia ring 20 in the rotational direction is referred to as “rotational phase difference”, in FIGS. 21 shows a deviation between a central position in the circumferential direction of the cam 21 and the cam 31 and a central position of the roller 30.

  Here, if torque fluctuation is present during transmission of torque, a rotational phase difference occurs between the hub flange 12 and the inertia ring 20 as shown in FIGS. 5 and 6. FIG. 5 shows the case where the rotational phase difference + θ1 (for example, 5 degrees) occurs on the + R side, and FIG. 6 similarly shows the case where the rotational phase difference + θ2 (for example, 10 degrees) occurs on the + R side.

  As shown in FIG. 5, when a rotational phase difference + θ 1 occurs between the hub flange 12 and the inertia ring 20, the roller 30 of the cam mechanism 22 moves relatively to the left in FIG. 5 along the cam 31. Do. At this time, since the centrifugal force acts on the centrifuge 21, the reaction force that the cam 31 formed on the centrifuge 21 receives from the roller 30 has the direction and the 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 the direction in which the centrifugal element 21 is moved toward the inner circumferential side.

  The first component force P1 is a force that moves the hub flange 12 in the left direction in FIG. 5 via the cam mechanism 22 and the centrifugal element 21. That is, a force in the direction of reducing the rotational phase difference between the hub flange 12 and the inertia ring 20 acts on the hub flange 12. Further, the centrifugal force is moved to the inner circumferential side against the centrifugal force by the second component force P2.

  When the rotational phase difference occurs in the reverse direction, the roller 30 moves relatively to the right in FIG. 5 along the cam 31, but the operating principle is the same.

  As described above, when a rotational phase difference occurs between the hub flange 12 and the inertia ring 20 due to torque fluctuation, the hub flange 12 rotates both of the hub flange 12 due to the centrifugal force acting on the centrifugal element 21 and the action of the cam mechanism 22. The force (first component force P1) in the direction to reduce the phase difference is received. This force suppresses torque fluctuation.

  The force for suppressing the above torque fluctuation changes with the centrifugal force, that is, the rotation speed of the hub flange 12, and also changes with the rotation phase difference and the shape of the cam 31. Therefore, by appropriately setting the shape of the cam 31, the characteristic of the torque fluctuation suppressing device 14 can be made the optimum characteristic according to the engine specification and the like.

  For example, the shape of the cam 31 can be made such that the first component force P1 linearly changes in accordance with the rotational phase difference in a state where the same centrifugal force is applied. Further, the shape of the cam 31 can be a shape in which the first component force P1 changes nonlinearly in accordance with the rotational phase difference.

  As described above, the centrifuge 21 moves in the radial direction to suppress torque fluctuation. Here, during operation, the working oil is accumulated in the recess 121 a of the hub flange 12. For this reason, when the centrifugal element 21 moves in the radial direction in the recess 121 a, the hydraulic oil flows between the outer circumferential side and the inner circumferential side of the centrifugal element 21. If the gap between the side surface of the centrifuge 21 (the surface of the end surface along the rotation axis direction) and the side surface of the inertia ring 20 which is the wall surface of the recess 121a is small, the working oil passing through this gap Viscosity resistance increases. If the centrifuge 21 can not move smoothly due to this viscous resistance, the torque fluctuation suppressing effect of the device is lost.

  Therefore, in this embodiment, the flow grooves 21 d and 21 e are formed on both side surfaces of the centrifuge 21 in the rotation axis direction. The hydraulic oil can smoothly flow between the outer peripheral side and the inner peripheral side of the centrifugal element 21 through the flow grooves 21d and 21e, and the viscosity resistance to the centrifugal element 21 can be reduced.

[Regulation of movement of the centrifuge 21]
For example, when the engine is stopped and the rotation of the hub flange 12 is stopped, the centrifuge 21 positioned above among the plurality of centrifuges 21 falls downward. Here, as described above, the flow grooves 21 d and 21 e are formed in the centrifuge 21, and the viscous resistance to the centrifuge 21 is small. For this reason, the centrifuge 21 located at the upper side will drop vigorously. However, since the movement of the centrifugal element 21 is restricted by the restriction mechanism 23, it is possible to prevent the hitting of the centrifugal element 21 against the bottom surface of the recess 121a.

  More specifically, first, during operation of the cam mechanism 22, the centrifuge 21 is not restricted in movement by the restriction mechanism 23. That is, the pin 231 provided on the centrifuge 21 can move smoothly along the groove 232, and the radial movement of the centrifuge 21 is not restricted.

  On the other hand, when the rotation of the hub flange 12 and the inertia ring 20 is stopped and immediately after the hub flange 12 and the inertia ring 20 start rotating, the radial movement of the centrifuge 21 is restricted by the restriction mechanism 23.

  That is, although the centrifugal element 21 positioned at the upper side among the four centrifugal elements 21 falls in the inner circumferential direction (downward), as shown in FIG. 6, the pin 231 fixed to the centrifugal element 21 is a groove 232 The centrifuge 21 is restricted from moving further inward (downward) from the position shown in FIG. For this reason, the inner peripheral surface of the centrifugal element 21 does not collide with the bottom surface of the recess 121a, and it is possible to avoid striking sound when the rotation is stopped.

  In addition, assuming that the restriction mechanism 23 is not provided, the centrifugal element 21 located at the upper side at the time of the rotation stop is falling to a position in contact with the bottom surface of the concave portion 121a. In this case, a relatively wide gap is present between the cam 31 which is the outer peripheral surface of the centrifugal element 21 and the roller 30. In this state, when the hub flange 12 and the inertia ring 20 start to rotate, the centrifugal element 21 moves to the outer peripheral side, collides with the roller 30, and a striking sound is generated.

  However, since the restriction mechanism 23 is provided here, as shown in FIG. 6, even when the rotation is stopped and the centrifuge 21 is most dropped to the inner peripheral side (downward), as shown in FIG. The outer peripheral surface and the roller 30 abut on each other or have only a minute gap. Therefore, even if the rotation is started from this state and the centrifugal member 21 moves to the outer peripheral side, the hitting noise can be suppressed even if the hitting noise does not occur or is generated.

[Example of characteristics]
FIG. 7 is a diagram showing an example of the torque fluctuation suppression characteristic. The horizontal axis is the rotational speed, and the vertical axis is the torque fluctuation (rotational speed fluctuation). In the case where the characteristic Q1 is not provided with a device for suppressing torque fluctuation, the characteristic Q2 is provided in the torque fluctuation suppressing device 14 of the present embodiment when a conventional dynamic damper device without a cam mechanism is provided. Shows the case where is provided.

  As apparent from FIG. 7, in the apparatus (characteristic Q2) provided with the dynamic damper device without the cam mechanism, it is possible to suppress the torque fluctuation only in the specific rotational speed range. On the other hand, in the present embodiment (characteristic Q3) having the cam mechanism 22, it is possible to suppress the torque fluctuation in all the rotational speed regions.

[Other embodiments]
The present invention is not limited to the embodiments as described above, and various changes or modifications are possible without departing from the scope of the present invention.

  (A) In the above-described embodiment, the flow grooves 21d and 21e are formed on both side surfaces of the centrifuge 21, but the grooves may be formed on only one of the side surfaces.

  (B) As the viscous drag reducing portion, the flow passage penetrating in the radial direction is formed in the above embodiment, but various configurations can be considered as the viscous drag reducing portion. In the example shown in FIG. 8 and FIG. 9, flow holes 21 f and 21 g penetrating in the radial direction in the centrifugal element 21 are formed as the viscous resistance reduction portion. The flow holes 21 f and 21 g are formed at the same distance from the center of the circumferential direction of the centrifuge 21 by one and the same distance. Also with such a configuration, the hydraulic oil on the outer peripheral side and the inner peripheral side of the centrifugal separator 21 can smoothly move in the radial direction through the flow holes 21 f and 21 g. Therefore, the viscous drag on the centrifuge 21 is reduced.

  (C) In the example shown in FIG. 10, outer peripheral grooves 21h and 21i and inner peripheral grooves 21j and 21k are formed on both side surfaces of the centrifugal element 21 in the rotation axis direction as a viscous resistance reduction portion. As in the embodiments described above, the grooves 21h and 21j on one side and the grooves 21i and 21k on the other side are formed symmetrically in FIG. Each groove may be formed only on one side of the centrifuge 21.

  Here, although the outer circumferential grooves 21h and 21i and the inner circumferential grooves 21j and 21k are not in communication with each other, these grooves reduce the viscous resistance to the centrifuge 21. Therefore, the centrifuge 21 can move smoothly in the radial direction.

  (D) In the example shown in FIG. 11, circumferential grooves 21m extending in the circumferential direction are formed on both side surfaces of the centrifugal element 21 in the rotation axis direction as a viscous drag reduction portion. The circumferential groove 21m penetrates from one end surface of the centrifugal element 21 in the circumferential direction to the other end surface. The circumferential groove 21m may be formed on only one side of the centrifugal separator 21.

  The circumferential groove 21m facilitates the flow of hydraulic oil between one side and the other side in the circumferential direction of the centrifuge 21. For this reason, the viscous drag on the centrifuge 21 is reduced, and the movement of the centrifuge 21 becomes smooth.

  In addition to the grooves or holes in the radial direction in the above-described embodiments, the grooves in the circumferential direction in FIG. 11 may be formed, and in this case, the viscous resistance to the centrifuge 21 is further reduced.

  (E) In the example shown in FIG. 12, portions 21n having a smaller thickness than the other portions are formed at both end portions on the inner peripheral side of the centrifuge 21 as a viscous resistance reduction portion. More specifically, both ends on the inner peripheral side of the centrifugal separator 21 are formed so that the thickness in the direction of the rotation axis is gradually reduced from the center to the inner peripheral end in the circumferential direction. By forming the thin portion 21 n, the viscosity resistance to the centrifuge 21 is reduced, and the centrifuge 21 can be smoothly moved in the working oil. In addition, you may form the same viscous-resistance reduction part in the both ends of the outer peripheral side of the centrifuge 21. FIG.

  (F) In the example shown in FIG. 13, the corner portions 21 o at both ends in the radial direction of the centrifuge 21 are formed in a curved surface shape. By forming the corner portion in a curved shape, the gap between the corner portion 21 o and each of the inertia rings 201 and 202 is wider than other portions. That is, the viscous resistance with respect to the centrifugal element 21 is reduced by the curved corner portion 21 o, and the corner portion 21 o functions as a viscous drag reduction portion.

  (G) In the above embodiment, the inertia ring is formed of a continuous annular member, but a plurality of divided inertia bodies may be arranged in the circumferential direction. In this case, in order to hold a plurality of inertia bodies, it is necessary to provide a holding member such as an annular holding ring or the like on the outer peripheral side of the inertia body.

  (H) In the embodiment described above, the guide roller has the outer peripheral roller and the inner peripheral roller, but the guide roller may be configured by one roller. In addition, one roller is provided on each side in the circumferential direction of the centrifuge, and one roller is provided between the inner circumferential surface of the centrifuge and the bottom of the recess, and a total of three rollers constitute a guide roller. May be

  (I) In the above embodiment, the guide roller is disposed as the support portion, but another member such as a resin race or a sheet for reducing friction may be disposed. In this case, the member for reducing friction is pressed by the biasing member against the recess of the centrifuge or the hub flange. Also, so-called roller bearings may be used as the guide rollers. In this case, the friction between the recess of the centrifuge or the hub flange and the outer periphery of the roller bearing can be further reduced.

  (J) In the embodiment described above, the recess that opens to the outer peripheral side is provided as the housing portion for housing the centrifugal element, but the housing portion may be an opening whose outer peripheral side is closed. The shape or the like is not limited as long as the shape can be accommodated movably.

[Example of application]
When the above torque fluctuation suppressing device is applied to a torque converter or another power transmission device, various arrangements are possible. Hereinafter, specific application examples will be described using schematic diagrams of a torque converter and other power transmission devices.

  (1) FIG. 14 is a view schematically showing a torque converter, and the torque converter includes an input side rotating body 41, a hub flange 42, and a damper 43 provided between both rotating bodies 41 and 42. ,have. The input side rotating body 41 includes members such as a front cover, a drive plate, and a piston. The hub flange 42 includes a driven plate and a turbine hub. The damper 43 includes a plurality of torsion springs.

  In the example shown in FIG. 14, a centrifuge is provided on any of the rotating members constituting the input side rotating body 41, and a cam mechanism or the like 44 operated by utilizing centrifugal force acting on the centrifuge is provided. It is provided. The same configuration as the configuration shown in each of the embodiments can be applied to the cam mechanism 44 and the like.

  (2) In the torque converter shown in FIG. 15, a centrifuge is provided on any of the rotating members constituting the hub flange 42, and a cam mechanism etc. that operates using the centrifugal force acting on this centrifuge 44 Is provided. The same configuration as the configuration shown in each of the embodiments can be applied to the cam mechanism 44 and the like.

  (3) The torque converter shown in FIG. 16 has another damper 45 and an intermediate member 46 provided between the two dampers 43 and 45 in addition to the configuration shown in FIGS. 14 and 15. doing. The intermediate member 46 is rotatable relative to the input side rotation body 41 and the hub flange 42, and causes the two dampers 43 and 45 to act in series.

  In the example shown in FIG. 16, a centrifuge is provided on the intermediate member 46, and a cam mechanism or the like 44 that operates using centrifugal force acting on the centrifuge is provided. The same configuration as the configuration shown in each of the embodiments can be applied to the cam mechanism 44 and the like.

  (4) The torque converter shown in FIG. 17 has the float member 47. The float member 47 is a member for supporting the torsion spring constituting the damper 43, and is formed, for example, in an annular shape, and is disposed so as to cover the outer periphery and at least one side surface of the torsion spring. In addition, the float member 47 is rotatable relative to the input-side rotating body 41 and the hub flange 42 and rotates with the damper 43 due to the friction between the damper 43 and the torsion spring. That is, the float member 47 also rotates.

  In the example shown in FIG. 17, the float member 47 is provided with a centrifugal member 48, and a cam mechanism or the like 44 operated by utilizing the centrifugal force acting on the centrifugal member 48 is provided. The same configuration as the configuration shown in each of the embodiments can be applied to the cam mechanism 44 and the like.

  (5) FIG. 18 is a schematic view of a power transmission system having a flywheel 50 having two inertia bodies 51 and 52 and a clutch device 54. As shown in FIG. That is, the flywheel 50 disposed between the engine and the clutch device 54 includes a first inertial body 51, a second inertial body 52 disposed rotatably relative to the first inertial body 51, and two inertial bodies. And a damper 53 disposed between 51 and 52. The second inertial body 52 also includes a clutch cover that constitutes the clutch device 54.

  In the example shown in FIG. 18, a centrifuge is provided on any of the rotating members constituting the second inertia body 52, and a cam mechanism or the like 55 which operates using centrifugal force acting on the centrifuge is provided. It is done. The same configuration as the configuration shown in each of the embodiments can be applied to the cam mechanism etc. 55.

  (6) FIG. 19 shows an example in which the first inertia body 51 is provided with a centrifuge in the same power transmission device as FIG. A cam mechanism or the like 55 is provided which operates using the centrifugal force acting on the centrifuge. The same configuration as the configuration shown in each of the embodiments can be applied to the cam mechanism etc. 55.

  (7) The power transmission device shown in FIG. 20 has another damper 56 and an intermediate member 57 provided between the two dampers 53 and 56 in addition to the configuration shown in FIGS. Have. The intermediate member 57 is rotatable relative to the first inertial body 51 and the second inertial body 52.

  In the example shown in FIG. 20, the intermediate member 57 is provided with a centrifugal member 58, and a cam mechanism or the like 55 which operates using centrifugal force acting on the centrifugal member 58 is provided. The same configuration as the configuration shown in each of the embodiments can be applied to the cam mechanism etc. 55.

  (8) FIG. 21 is a schematic view of a power transmission device in which a clutch device is provided on one flywheel. The first inertia body 61 of FIG. 21 includes one flywheel and a clutch cover of the clutch device 62. In this example, a centrifuge is provided on any of the rotating members constituting the first inertia body 61, and a cam mechanism or the like 64 that operates using the centrifugal force acting on the centrifuge is provided. The same configuration as the configuration shown in each of the embodiments can be applied to the cam mechanism 64 and the like.

  (9) FIG. 22 shows an example in which a centrifugal member 65 is provided on the output side of the clutch device 62 in the same power transmission device as in FIG. Further, a cam mechanism or the like 64 is provided which operates by utilizing the centrifugal force acting on the centrifuge 65. The same configuration as the configuration shown in each of the embodiments can be applied to the cam mechanism 64 and the like.

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

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

1 Torque Converter 11 Input Rotor 12 Hub Flange (Rotor)
121a recessed part (accommodating part)
14 Torque fluctuation suppressor 20, 201, 202 Inertial ring (mass)
21 Centrifuge 21d, 21e Flow groove (viscous drag reduction part)
21f, 21g Flow hole (viscous drag reduction part)
21h, 21i Outer peripheral groove (viscous drag reduction part)
21j, 21k inner circumferential groove (viscous drag reduction part)
21 m circumferential groove (viscous drag reduction section)
21n thin part (viscous drag reduction part)
21o Curved corner (viscous drag reduction)
22 cam mechanism 23 regulating mechanism 30 roller (cam follower)
31 cam

Claims (15)

A torque fluctuation suppressor that suppresses torque fluctuation of a rotating body to which torque is input,
A mass body that is rotatable with the rotating body and is disposed so as to be rotatable relative to the rotating body;
The rotary body and a plurality of viscous drag reduction portions are disposed radially movable in the fluid under centrifugal force by rotation of the mass body, and have viscous drag reduction portions for reducing viscous drag due to fluid when moving radially. With a centrifuge
When a relative displacement in the rotational direction occurs between the rotating body and the mass body by receiving a centrifugal force acting on the centrifugal element, the centrifugal force is a circumferential force in the direction in which the relative displacement is reduced. Multiple cam mechanisms to convert
Torque fluctuation suppressor equipped.   The torque fluctuation control device according to claim 1, wherein the viscous drag reduction unit causes fluid to flow between the outer circumferential side and the inner circumferential side of the centrifugal separator.   The torque fluctuation suppressing device according to claim 1, wherein the viscous drag reduction portion is a groove formed in at least one side surface in the rotation axis direction of the centrifuge and extending in a radial direction.   The torque fluctuation suppressing device according to claim 3, wherein the radially extending groove is a groove whose width extends toward at least one of radially inward and outward.   The torque fluctuation control device according to claim 2, wherein the viscous drag reduction portion is a hole penetrating the centrifugal element in a radial direction.   The torque fluctuation suppressing device according to claim 2, wherein the viscous drag reduction portion is a region in which a thickness in a rotation axis direction is thinner than another portion formed in at least one end portion in a radial direction of the centrifugal separator. The thickness of the centrifuge in the direction of the rotation axis is gradually reduced from the central portion side in the radial direction to at least one of the outer peripheral side and the inner peripheral side.
The viscous drag reduction unit is a region in which the thickness of one end of the centrifuge is thin.
The torque fluctuation control device according to claim 6.   The torque fluctuation suppressing device according to claim 2, wherein the viscous drag reduction portion is a region formed in a curved surface shape at a corner portion of at least one end in the radial direction of the centrifugal separator.   The torque fluctuation suppressing device according to claim 1, wherein the viscous drag reduction unit causes fluid to flow between one side and the other side in the circumferential direction of the centrifugal separator.   The torque fluctuation suppressing device according to any one of claims 1 to 9, further comprising: a plurality of restriction mechanisms which allow the operation of the centrifuge by the cam mechanism and restrict the radial movement of the centrifuge. The rotating body has a plurality of accommodating portions that accommodate the centrifugal element so as to be movable in the radial direction,
The regulation mechanism regulates that the inner circumferential surface of the centrifugal separator abuts on the bottom surface of the housing.
The torque fluctuation suppressing device according to claim 10. The cam mechanism is
A cam provided on one of the mass body and the centrifuge;
And a cam follower provided on the other of the mass body and the centrifuge and moving along the cam.
The torque fluctuation control device according to any one of claims 1 to 11. The mass body includes a first inertia ring and a second inertia ring disposed opposite to each other with the rotating body interposed therebetween, and a pin for connecting the first inertia ring and the second inertia ring so as not to be relatively rotatable. Have
The centrifugal separator is disposed on an outer peripheral portion of the rotating body and on an inner peripheral side of the pin, in an axial direction between the first inertia ring and the second inertia ring.
The cam follower is a cylindrical roller having a hole through which the pin passes in the axial direction.
The cam is formed on the centrifugal element and is in contact with the cam follower, and has a shape such that the circumferential force changes according to the relative displacement amount in the rotational direction between the rotating body and the mass body ,
A torque fluctuation suppressor according to claim 12. 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 turbine;
The torque fluctuation suppressing device according to any one of claims 1 to 13.
With torque converter. A first inertial body that rotates about a rotational axis, a second inertial body that rotates relative to the first inertial body that rotates about the rotational axis, a first inertial body, and a second inertial body A flywheel having a damper disposed therebetween;
A clutch device provided on the second inertial body of the flywheel;
The torque fluctuation suppressing device according to any one of claims 1 to 13.
Power transmission device.

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