JP2019056446A - Torque fluctuation suppression device, torque converter and power transmission device - Google Patents

Abstract

To acquire stable torsional characteristics even in the case where a centrifugal element is inclined, in a torque fluctuation suppression device having the centrifugal element for forming a cam.SOLUTION: This device includes an inertia ring 20, a plurality of centrifugal elements 21, a plurality of cam mechanisms 22 and a plurality of support parts 23. The inertia ring 20 can rotate relatively with respect to a hub flange 12. The centrifugal element 21 is movable in the radial direction. The cam mechanism 22 has a cam 31 and a cam follower 30, and by receiving a centrifugal force of the centrifugal element 31, when a rotational phase difference occurs between the hub flange 12 and the inertia ring 20, it converts the centrifugal force into a circumferential direction force in the direction in which the rotational phase difference becomes smaller. The support part 23 supports the centrifugal element 21 so as to move in the radial direction. A neutral time contact point Cn between the cam 31 and the cam follower 30 is located further inside radially than a steady point D.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 that rotates around a rotating shaft and receives torque. 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. 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 including a torque fluctuation suppressing device. The torque fluctuation suppressing device of Patent Document 1 includes inertia ring, 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 a 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 that contacts the cam.

  In the device of Patent Document 1, when a rotational direction shift occurs between the hub flange and the inertia ring due to torque fluctuation, the cam mechanism is activated by the centrifugal force acting on the centrifuge, The acting centrifugal force is converted into a circumferential force in a direction in which the deviation between the hub flange and the inertia ring is reduced. This circumferential force suppresses torque fluctuations.

JP 2017-53467 A

  In the torque fluctuation suppression device of Patent Document 1, a plurality of recesses that are opened radially outward are formed in the outer peripheral portion of the hub flange, and a centrifuge is accommodated in these recesses so as to be movable in the radial direction. In such a configuration, a gap is generated between both sides of the centrifuge in the circumferential direction and the side walls of the recesses facing the both sides. Due to the structure, this gap cannot be eliminated.

  The clearance between the centrifuge and the recess as described above causes the centrifuge to tilt during operation of the apparatus. If the centrifuge is tilted, the shape of the cam formed on the outer peripheral surface of the centrifuge will deviate from the designed shape, and the desired torsional characteristics (relative rotation angle between the hub flange and inertia ring, hub flange and inertia, The characteristic indicating the relationship with the transmission torque with the ring is not obtained. In addition, since the timing at which the centrifuge tilts varies depending on the frequency of torque fluctuation, there is a problem that the torsional characteristics vary.

  An object of the present invention is to obtain a stable torsional characteristic in a torque fluctuation suppressing device having a centrifuge and a cam mechanism even when the centrifuge forming the cam is inclined.

  (1) A 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 suppressing device includes a mass body, a plurality of centrifuges, a plurality of cam mechanisms, and a plurality of support portions. 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 plurality of centrifuges are movable in the radial direction under the centrifugal force generated by the rotation of the rotating body and the mass body. The plurality of cam mechanisms have a cam formed on the outer peripheral surface of the centrifuge and a cam follower that moves along the cam, receives a centrifugal force acting on the centrifuge, and rotates between the rotating body and the mass body. When a relative displacement occurs in, centrifugal force is converted into a circumferential force in a direction in which the relative displacement is reduced. The plurality of support portions are provided on the rotating body or the mass body and can support the centrifuge so as to be movable in the radial direction. The first side portion and the first side portion in the direction in which the centrifuge cam extends are opposite to the first side portion. It can contact | abut to a 2nd side part.

  The neutral contact point between the cam and the cam follower when there is no relative displacement in the rotational direction between the rotating body and the mass body is the first contact point at which the first side of the centrifuge contacts the support portion and the centrifugal contact point. The second side portion of the child is located radially inward from the straight line connecting the second contact point that contacts the support portion.

  In this device, when torque is input to the rotating body, the rotating body and the mass body rotate. When there is no change in the torque input to the rotating body, there is no relative displacement in the rotating direction between the rotating body and the mass body. 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. 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. When the relative displacement in the rotation direction occurs between the rotating body and the mass body, the cam mechanism converts the centrifugal force acting on the centrifuge into a circumferential force. This circumferential force acts to reduce the relative displacement between the rotating body and the mass body. Torque fluctuation is suppressed by the operation of the cam mechanism.

  Here, since the centrifugal force acting on the centrifuge is used as a force for suppressing the torque fluctuation, the characteristic for suppressing the torque fluctuation changes according to the rotational speed of the rotating body. Further, for example, the characteristics for suppressing torque fluctuation can be appropriately set depending on the shape of the cam and the like, and the peak of torque fluctuation in a wider rotational speed range can be suppressed.

  Here, the neutral contact point between the cam and the cam follower is located radially inward from the straight line connecting the first contact point and the second contact point of the centrifuge. In this case, compared to the conventional structure (see FIG. 9 of Patent Document 1), the center of the cam (for example, an arc) can be brought closer to a straight line connecting the first contact point and the second contact point. For this reason, even if the centrifuge is tilted, the degree of change in the shape of the cam formed on the outer peripheral surface of the centrifuge becomes small. Therefore, instability of torsional characteristics can be suppressed.

  (2) Preferably, the centrifuge has a first outer peripheral side contact portion and a first inner peripheral side contact portion, and a second outer peripheral side contact portion and a second inner peripheral side contact portion. Yes. The first outer peripheral contact portion and the first inner peripheral contact portion are provided on the first side portion and can contact the support portion. The second outer peripheral contact portion and the second inner peripheral contact portion are provided on the second side portion and can contact the support portion. In this case, the neutral contact point includes a first outer peripheral contact point where the first outer peripheral contact portion contacts the support portion and a second inner peripheral contact point where the second inner peripheral contact portion contacts the support portion. A straight line connecting the contact points, a first inner peripheral contact point at which the first inner peripheral contact part contacts the support part, and a first outer contact point at which the second outer contact part contacts the support part. Are located radially inward from the fixed point that is the intersection of the straight line connecting the two.

  Also in this case, as described above, even when the centrifuge is tilted, the degree of change in the shape of the cam formed on the outer peripheral surface of the centrifuge is reduced, and instability of torsional characteristics can be suppressed.

  (3) Preferably, the cam is formed in an arc shape recessed inward in the radial direction, and the arc center of the cam is located on a fixed point. In this case, the cam shape does not change even if the centrifuge is tilted.

  (4) Preferably, the rotating body has a plurality of concave portions that open radially outward on the outer peripheral surface, and a centrifuge is accommodated in the concave portions. Preferably, the first outer peripheral side contact portion, the first inner peripheral side contact portion, the second outer peripheral side contact portion, and the second inner peripheral side contact portion of the centrifuge each have a concave portion on the outer peripheral surface. It is a guide roller that can come into contact with the side wall.

  (5) Preferably, the rotating body has a plurality of concave portions that open radially outward on the outer peripheral surface, and a centrifuge is accommodated in the concave portions. Preferably, the support portion includes a first outer peripheral roller and a first inner peripheral roller that are rotatably mounted on the first side wall of the recess, and a second outer periphery that is rotatably mounted on the second side wall of the recess. A side roller and a second inner peripheral roller. The first outer peripheral side roller can contact the first outer peripheral side contact portion of the centrifuge. The first inner peripheral side roller can contact the first inner peripheral side contact portion of the centrifuge. The second outer peripheral side roller can contact the second outer peripheral side contact portion of the centrifuge. The second inner peripheral side roller can contact the second inner peripheral side contact portion of the centrifuge.

  (6) Preferably, the mass body includes a first inertia ring and a second inertia ring arranged to face each other with the rotating body interposed therebetween, and a pin that connects the first inertia ring and the second inertia ring so as not to be relatively rotatable. ,have. The centrifuge is arranged between the first inertia ring and the second inertia ring in the axial direction on the outer peripheral portion of the rotating body and on the inner peripheral side of the pin. The cam follower is a cylindrical roller having a hole through which a pin penetrates in the axial direction. The cam is formed in the centrifuge and contacts the cam follower, and has a shape in which the 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 connecting the first inertia ring and the second inertia ring. This simplifies the configuration of the cam mechanism.

  (7) The torque converter according to the present invention is disposed between the engine and the transmission. This torque converter includes an input-side rotator to which torque from the engine is input, a hub flange that outputs torque to the transmission, a damper disposed between the input-side rotator and the turbine, A torque fluctuation suppressing device.

  (8) The 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 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.

  In the present invention as described above, in a torque fluctuation suppressing device having a centrifuge and a cam mechanism, stable torsional characteristics can be obtained even when the centrifuge forming the cam is tilted.

The schematic diagram of the torque converter by a 1st embodiment of the present invention. FIG. 2 is a front partial view of the hub flange and torque fluctuation suppressing device of FIG. 1. FIG. 3 is an arrow A view of FIG. 2. The figure for demonstrating the action | operation of a cam mechanism. The figure corresponding to FIG. 2 for demonstrating the subject of a conventional apparatus. The figure corresponding to FIG. 2 for demonstrating the subject of a conventional apparatus. The characteristic view which shows the relationship between a rotation speed and a torque fluctuation. The figure corresponding to FIG. 2 of 2nd Embodiment of this invention. The figure corresponding to FIG. 2 of 3rd Embodiment of this invention. The figure corresponding to FIG. 2 of 3rd 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.

-First embodiment-
FIG. 1 is a schematic diagram when the torque fluctuation suppressing device according to the first 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 rotating body 11, a hub flange 12 (rotating body), 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 a friction member 16 is fixed to 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 hub flange 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 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 rotating 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 attenuates torque fluctuations.

[Torque fluctuation suppressing device 14]
FIG. 2 is a front view of the hub flange 12 and the torque fluctuation suppressing device 14. Note that FIG. 2 shows one (near side) inertia ring removed. FIG. 3 is a view of FIG. 2 viewed from the A direction. 2 and the subsequent drawings show a part of the hub flange 12 and the torque fluctuation suppressing device 14, but as a whole, the portions shown in each figure are provided at equal angular intervals at four locations in the circumferential direction. Yes.

  The torque fluctuation suppressing device 14 includes a first inertia ring 201 and a second inertia ring 202 that constitute an inertia ring 20 as a mass body, four centrifuges 21, four cam mechanisms 22, and a plurality of support portions. 23.

<First and second inertia rings 201, 202>
The first and second inertia rings 201 and 202 are plates each having a predetermined thickness formed in a continuous annular shape, and as shown in FIG. 3, both axial sides of the hub flange 12 sandwich the hub flange 12. Are arranged with a predetermined gap. That is, the hub flange 12 and the first and second inertia rings 201 and 202 are arranged side by side 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, can rotate together with the hub flange 12, and can rotate relative to the hub flange 12.

  The first and second inertia rings 201 and 202 are formed with holes 201a and 202a penetrating in the axial direction. And the 1st inertia ring 201 and the 2nd inertia ring 202 are being fixed by the rivet 203 which penetrates those holes 201a and 202a. Therefore, the first inertia ring 201 cannot move in the axial direction, the radial direction, and the rotation direction with respect to the second inertia ring 202.

<Hub flange 12>
The hub flange 12 is formed in a disc shape, and the inner peripheral portion is connected to the output hub 5 as described above. Four protrusions 121 are formed on the outer peripheral portion of the hub flange 12 so as to protrude further to the outer peripheral side and have a predetermined width in the circumferential direction. A concave portion 122 having a predetermined width is formed at the central portion of the protrusion 121 in the circumferential direction. The concave portion 122 is formed so as to open outward in the radial direction, and has a predetermined depth.

<Centrifuge 21 and support 23>
The centrifuge 21 is disposed in the recess 122 of the hub flange 12 and can move in the radial direction by the centrifugal force generated by the rotation of the hub flange 12. The centrifuge 21 is formed to extend in the circumferential direction, and has grooves 21 a and 21 b at both ends in the circumferential direction. The widths of the grooves 21a and 21b are larger than the thickness of the hub flange 12, and the hub flange 12 is inserted into a part of the grooves 21a and 21b.

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

  The centrifuge 21 includes a first guide roller 26a and a second guide roller 26b, and a pin 27 that rotatably supports the guide rollers 26a and 26b.

  The first guide roller 26 a and the second guide roller 26 b are disposed in the grooves 21 a and 21 b at both ends of the centrifuge 21. The first guide roller 26a includes a first outer peripheral roller 26oa (first outer peripheral contact portion) and a first inner peripheral roller 26ia (first inner peripheral) disposed on the inner peripheral side of the first outer peripheral roller 26oa. Side abutting portion). The second guide roller 26b includes a second outer peripheral roller 26ob (second outer peripheral contact portion) and a second inner peripheral roller 26ib (second second) disposed on the inner peripheral side of the second outer peripheral roller 26ob. Inner peripheral side contact portion). The first outer circumference side roller 26oa and the second outer circumference side roller 26ob are arranged to face each other, and the first inner circumference side roller 26ia and the second inner circumference side roller 26ib are arranged to face each other.

  The first outer peripheral side roller 26oa and the second inner peripheral side roller 26ia are capable of rolling while abutting against the first side wall 122a of the concave portion 122, and the second outer peripheral side roller 26ob and the second inner peripheral side roller 26ib are formed in the concave portion 122. It can roll in contact with the second side wall 122b on the opposite side. That is, the first side wall 122a and the second side wall 122b of the recess 122 function as a support portion 23 that supports the centrifuge 21 so as to be movable in the radial direction.

  The pin 27 is provided through the grooves 21 a and 21 b of the centrifuge 21 in the direction of the rotation axis. Both ends of the pin 27 are fixed to the centrifuge 21.

<Cam mechanism 22>
The cam mechanism 22 includes a cylindrical roller 30 as a cam follower and a cam 31 that is an outer peripheral surface 21 c of the centrifuge 21.

  The roller 30 is fitted on the outer periphery of the body portion of the rivet 203. That is, the roller 30 is supported by the rivet 203. The roller 30 is preferably mounted so as to be rotatable with respect to the rivet 203, but may not be rotatable.

  The cam 31 is an arcuate surface with which the roller 30 abuts. When the hub flange 12 and the first and second inertia rings 201 and 202 rotate relative to each other within a predetermined angular range, the roller 30 is connected to the cam 31. Move along. In this embodiment, the cam 31 is formed in an arc shape with a radius r centered on the point Z in FIG.

  Further, the neutral contact point Cn between the cam 31 and the roller 30 in a state where there is no relative displacement (rotation phase difference) in the rotational direction between the hub flange 12 and the inertia ring 20 is as follows. It is located radially inward from the fixed point D.

  Note that the fixed point D is a point where the position does not change even if the position of the centrifuge 21 is changed by tilting in the recess 122, and is defined by the intersection of the straight line L1 and the straight line L2 shown in FIG. The The straight line L1 includes a first outer peripheral contact point C1o where the first outer peripheral roller 26oa contacts the first side wall 122a, and a second inner peripheral contact point C2i where the second inner peripheral roller 26ib contacts the second side wall 122b. Is a straight line connecting The straight line L2 includes a first inner peripheral contact point C1i at which the first inner peripheral roller 26ia contacts the first side wall 122a, and a second outer peripheral contact point C2o at which the second outer peripheral roller 26ob contacts the second side wall 122b. Is a straight line connecting In this embodiment, the arc center Z of the cam 31 and the fixed point D are separated by a distance h.

  Although details will be described later, when the rotation 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 force generated in the centrifuge 21 is generated. The force is converted into a circumferential force that reduces the rotational phase difference.

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

  When the 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.

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

  As described above, the relative displacement amount in the rotational direction between the hub flange 12 and the inertia ring 20 is referred to as “rotational phase difference”. In FIG. 2 and FIG. The deviation between the center position of 31 in the circumferential direction and the center position of the roller 30 is shown.

  Here, if torque fluctuation exists during torque transmission, a rotational phase difference θ occurs between the hub flange 12 and the inertia ring 20 as shown in FIG. FIG. 4 shows a case where a rotational phase difference + θ1 (for example, 5 degrees) occurs on the + R side.

  As shown in FIG. 4, when a rotational phase difference + θ1 occurs between the hub flange 12 and the inertia ring 20, the roller 30 of the cam mechanism 22 moves relative to the left side in FIG. 4 along the cam 31. To do. At this time, since centrifugal force is applied to the centrifuge 21, the reaction force received from the roller 30 by the cam 31 formed on the centrifuge 21 is in 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 toward the inner periphery.

  The first component force P1 is a force that moves the hub flange 12 in the left direction in FIG. 4 via the cam mechanism 22 and the centrifuge 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. Moreover, the centrifuge 21 is moved to the inner peripheral side against the centrifugal force by the second component force P2.

  When a rotational phase difference occurs in the opposite direction, the roller 30 moves relative to the right side of FIG. 4 along the cam 31, but the operating principle is the same.

  As described above, when a rotational phase difference is generated between the hub flange 12 and the inertia ring 20 due to torque fluctuation, the hub flange 12 is rotated by the centrifugal force acting on the centrifuge 21 and the cam mechanism 22. A force in the direction of decreasing the phase difference (first component force P1) is received. This force suppresses torque fluctuations.

  The force for suppressing the torque fluctuation described above varies depending on the centrifugal force, that is, the rotational speed of the hub flange 12, and also varies depending on the rotational phase difference and the shape of the cam 31. Therefore, by setting the shape of the cam 31 as appropriate, the characteristics of the torque fluctuation suppressing device 14 can be optimized according to engine specifications and the like.

  For example, the shape of the cam 31 can be made 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 31 can be a shape in which the first component force P1 changes nonlinearly according to the rotational phase difference.

  Here, there is a gap between the first and second guide rollers 26a and 26b on both sides of the centrifuge 21 and the corresponding first and second side walls 122a and 122b. Therefore, during the operation of the cam mechanism 22, the centrifuge 21 is tilted when two of the four contact points C1o, C1i, C2o, and C2i contact each other. In this case, the center of inclination of the centrifuge 21 is a fixed point D, which is at a position deviated from the arc center Z of the cam 31. For this reason, when the centrifuge 21 tilts and the posture changes, the cam shape at the neutral contact point Cn changes from the designed cam shape (state shown in FIG. 2). For this reason, desired torsional characteristics cannot be obtained.

  5A and 5B show the above problem with reference to a conventional configuration. That is, as shown in FIGS. 5A and 5B, there is a gap (backlash) between the guide rollers 26 ′ on both sides of the centrifuge 21 ′ and the corresponding side wall of the recess of the hub flange 12 ′. In such a state, during operation, as shown in FIG. 5B, only two guide rollers 26 ′ on the inner peripheral side on one side and guide rollers 26 ′ on the outer peripheral side on the other side touch the side wall. In contact, the centrifuge 21 'tilts. As a result, the position of the cam follower 30 ′ is also shifted, and desired torsional characteristics cannot be obtained.

  As will be described later, if the arc center Z of the cam 31 coincides with the fixed point D, that is, if the distance h in FIG. 2 is set to “0”, the cam shape does not change even if the centrifuge 21 is tilted.

  However, in order to make the device compact in consideration of the shape of the centrifuge 21 and the like, it may be difficult to make the arc center Z of the cam 31 coincide with the fixed point D.

  Here, in this type of conventional device, the neutral contact point is set radially outward from the fixed point. Since the arc center of the cam is naturally positioned radially outward from the neutral contact point, the distance between the fixed point and the arc center of the cam becomes longer in the conventional device.

  Therefore, in this embodiment, the neutral contact point Cn is arranged on the radially inner side with respect to the fixed point D. By positioning the neutral contact point Cn more radially inward, the arc center Z of the cam 31 is also positioned radially inward. Therefore, the distance h shown in FIG. 2 is shorter than that of the conventional device. Since the distance h and the degree of change in the shape of the cam 31 are approximately proportional, when the distance h is shortened as in this embodiment, the change in the cam shape due to the inclination of the centrifuge 21 is also reduced. For this reason, the torsional characteristics of the cam mechanism 22 are more stable than those of the conventional device.

[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). When the characteristic Q1 is not provided with a device for suppressing torque fluctuation, the characteristic Q2 is provided with a conventional dynamic damper device having no cam mechanism, and the characteristic Q3 is indicated by the torque fluctuation suppressing device 14 of the present embodiment. The case where is provided is shown.

  As is apparent from FIG. 6, in the device (characteristic Q2) provided with the dynamic damper device that does not have the cam mechanism, the torque fluctuation can be suppressed only in the specific rotation speed range. On the other hand, in the present embodiment having the cam mechanism 22 (characteristic Q3), torque fluctuations can be suppressed in all the rotational speed ranges.

-Second Embodiment-
FIG. 7 shows a part of the torque fluctuation suppressing device according to the second embodiment of the present invention, and is a schematic view corresponding to FIG. 2 of the first embodiment. In FIG. 7, as in FIG. 2, the front side inertia ring 201 in the drawing is removed. Further, the same or corresponding members as those in the first embodiment are indicated by the same reference numerals.

  The torque fluctuation suppression device according to the second embodiment has the same basic configuration as that of the first embodiment, such as the operation of the cam mechanism 22, but the configuration of the centrifuge 21 and the support portion 23 is different from that of the first embodiment. Yes.

  The support portion 23 shown in FIG. 7 has a guide roller 36 b that is rotatably supported on the side wall 122 b of the recess 122. The guide roller 36b includes an outer peripheral side roller 36ob, and an inner peripheral side roller 36ib disposed on the inner peripheral side of the outer peripheral side roller 36ob. FIG. 7 shows only one guide roller 26b, but the other side has the same configuration.

  Both the outer peripheral side roller 36ob and the inner peripheral side roller 36ib are in contact with one side surface 21d in the circumferential direction of the centrifuge 21 and can roll. Accordingly, the centrifuge 21 has, on the side surface 21d, an outer peripheral side contact portion that can contact the outer peripheral side roller 36ob and an inner peripheral side contact portion that can contact the inner peripheral side roller 36ib. . That is, the outer peripheral side roller 36ob and the inner peripheral side roller 36ib function as a support portion 23 that supports the centrifuge 21 so as to be movable in the radial direction.

  The fixed point D in the second embodiment is defined by the intersection of the straight line L1 and the straight line L2 shown in FIG. The straight line L1 is a contact point where the outer peripheral roller on one side and the end surface on one side of the centrifuge 21 are in contact, and a contact point where the inner peripheral roller 36ib on the other side and the other end surface of the centrifuge 21 are in contact. Is a straight line connecting The straight line L2 is a straight line connecting a contact point where the inner peripheral roller on one side and the end surface on one side of the centrifuge 21 are in contact with a contact point where the outer roller 36ob and the end surface on the other side of the centrifuge 21 are in contact. It is.

  Also in the second embodiment as described above, the cam shape is set so that the neutral contact point Cn is located on the radially inward side of the fixed point D as in the first embodiment. Therefore, the distance between the arc center (not shown) of the cam and the fixed point D is shortened, and the torsional characteristics of the cam mechanism 22 are stabilized as compared with the conventional device.

-Third embodiment-
8A and 8B show a part of the torque fluctuation suppressing device according to the third embodiment of the present invention, and are schematic views corresponding to FIG. 2 of the first embodiment. 8A and 8B, the inertia ring 201 on the near side in the figure is removed as in FIG. Further, the same or corresponding members as those in the first embodiment are indicated by the same reference numerals.

  The torque fluctuation suppressing device of the third embodiment is the same as that of the first embodiment in the basic configuration such as the operation of the cam mechanism 22, but the positional relationship between the cam 31 and the fixed point D is different from that of the first embodiment. ing.

  That is, in the third embodiment, the arc center Z of the cam 31 and the fixed point D are set at the same position, and the distance h in FIG. 2 is set to “0”.

  In the third embodiment, as shown in FIG. 8B, the shape of the cam 31 does not change even when the centrifuge 21 is tilted. For this reason, in the apparatus of the third embodiment, the cam mechanism 22 can always obtain desired torsional characteristics.

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

  (A) In the above embodiment, the cam is formed by an arc having a constant curvature, but the cam may be formed by a curve composed of a plurality of curvatures. Even in such a case, if the cam is set so that the neutral contact point is positioned radially inward of the fixed point, the torsional characteristics of the cam mechanism are stabilized.

  (B) The number of guide rollers is not limited to the above embodiment. For example, one guide roller is provided on each side of the centrifuge in the circumferential direction, and one guide roller is provided between the inner peripheral surface of the centrifuge and the bottom surface of the recess. You may make it guide the movement of a child.

  In this case, the neutral contact point has a diameter larger than the straight line connecting the contact point where the guide roller on one side contacts the side wall of the recess and the contact point where the other side guide roller contacts the side wall of the recess. If the cam is set so as to be located inward in the direction, the torsional characteristics of the cam mechanism are stabilized.

  (C) A so-called roller bearing may be used as the guide roller. In this case, friction between the recess of the centrifuge or the hub flange and the outer periphery of the roller bearing can be further reduced.

  (D) In the above embodiment, the centrifuge is provided on the hub flange, but may be provided on the inertia ring.

[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. 9 is a diagram schematically showing a torque converter. The torque converter includes an input side rotating body 41, a hub flange 42, and a damper 43 provided between these members 41, 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. 9, a centrifuge is provided in any of the rotating members constituting the input-side rotator 41, and a cam mechanism and a support unit that operate using centrifugal force acting on the centrifuge A mechanism 44 is provided. About the cam mechanism and the support part 44, the structure similar to the structure shown by said each embodiment is applicable.

  (2) The torque converter shown in FIG. 10 is provided with a centrifuge in any one of the rotating members constituting the hub flange 42, and a cam mechanism and a support that operate using centrifugal force acting on the centrifuge. A mechanism 44 including a portion is provided. About the cam mechanism and the support part 44, the structure similar to the structure shown by said each embodiment is applicable.

  (3) The torque converter shown in FIG. 11 has another damper 45 and an intermediate member 46 provided between the two dampers 43, 45 in addition to the configurations shown in FIGS. doing. The intermediate member 46 is rotatable relative to the input side rotating 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. 11, the intermediate member 46 is provided with a centrifuge, and a mechanism 44 including a cam mechanism and a support portion that operates using a centrifugal force acting on the centrifuge is provided. About the cam mechanism and the support part 44, the structure similar to the structure shown by said each embodiment is applicable.

  (4) The torque converter shown in FIG. 12 has a 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 so as to cover the outer periphery and at least one side surface of the torsion spring. Further, the float member 47 is rotatable relative to the input side rotating body 41 and the hub flange 42, and rotates around the damper 43 by friction with the torsion spring of the damper 43. That is, the float member 47 also rotates.

  In the example shown in FIG. 12, the float member 47 is provided with a centrifuge 48, and a mechanism 44 including a cam mechanism and a support portion that operates by utilizing the centrifugal force acting on the centrifuge 48 is provided. Yes. About the cam mechanism and the support part 44, the structure similar to the structure shown by said each embodiment is applicable.

  (5) FIG. 13 is a schematic diagram of a power transmission device having a flywheel 50 having two inertia bodies 51, 52 and a clutch device 54. 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 so as to be rotatable relative to the first inertial body 51, and two inertial bodies. And a damper 53 disposed between 51 and 52. The second inertia body 52 also includes a clutch cover that constitutes the clutch device 54.

  In the example shown in FIG. 13, a centrifuge is provided in one of the rotating members that constitute the second inertial body 52, and a cam mechanism and a support portion that operate using centrifugal force acting on the centrifuge are provided. A including mechanism 55 is provided. About the cam mechanism and the support part 55, the structure similar to the structure shown by said each embodiment is applicable.

  (6) FIG. 14 is an example in which a centrifuge is provided in the first inertial body 51 in the same power transmission device as that in FIG. And the mechanism 55 containing the cam mechanism and support part which operate | move using the centrifugal force which acts on this centrifuge is provided. About the cam mechanism and the support part 55, the structure similar to the structure shown by said each embodiment is applicable.

  (7) In addition to the configuration shown in FIGS. 13 and 14, the power transmission device shown in FIG. 15 includes another damper 56 and an intermediate member 57 provided between the two dampers 53, 56. 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. 15, the intermediate member 57 is provided with a centrifuge 58, and a mechanism 55 including a cam mechanism and a support portion that operates by using centrifugal force acting on the centrifuge 58 is provided. . About the cam mechanism and the support part 55, the structure similar to the structure shown by said each embodiment is applicable.

  (8) FIG. 16 is a schematic diagram of a power transmission device in which a clutch device is provided on one flywheel. The first inertia body 61 in FIG. 16 includes one flywheel and a clutch cover of the clutch device 62. In this example, a centrifuge is provided in any of the rotating members that constitute the first inertial body 61, and a mechanism 64 including a cam mechanism and a support portion that operates using centrifugal force acting on the centrifuge is provided. Is provided. About the cam mechanism and the support part 64, the structure similar to the structure shown by said each embodiment is applicable.

  (9) FIG. 17 is an example in which a centrifuge 65 is provided on the output side of the clutch device 62 in the same power transmission device as FIG. And the mechanism 64 containing the cam mechanism and support part which operate | move using the centrifugal force which acts on this centrifuge 65 is provided. About the cam mechanism and the support part 64, the structure similar to the structure shown by said each embodiment is applicable.

  (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.

1 Torque Converter 11 Input Side Rotating Body 12 Hub Flange (Rotating Body)
122 recessed portion 122a first side wall (supporting portion)
122b 2nd side wall (support part)
14 Torque fluctuation suppression device 20, 201, 202 Inertia ring (mass body)
21, 58, 65 Centrifuge 22 Cam mechanism 23 Support portion 26oa First outer peripheral side roller (first outer peripheral side contact portion)
26ia 1st inner circumference side roller (1st inner circumference side contact part)
26ob 2nd outer peripheral side roller (2nd outer peripheral side contact part)
26ib 2nd inner peripheral side roller (2nd inner peripheral side contact part)
30 Kolo (Cam Follower)
31 Cam Cn Neutral contact point D Fixed point Z Cam arc center

Claims (8)

A torque fluctuation suppressing device that suppresses 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 plurality of centrifuges that are movable in the radial direction under the centrifugal force generated by the rotation of the rotating body and the mass body;
The cam has a cam formed on the outer peripheral surface of the centrifuge and a cam follower that moves along the cam, receives a centrifugal force acting on the centrifuge, and in a rotational direction between the rotating body and the mass body. A plurality of cam mechanisms that convert the centrifugal force into a circumferential force in a direction that reduces the relative displacement when a relative displacement occurs;
The centrifuge is provided on the rotating body or the mass body and can support the centrifuge so as to be movable in a radial direction, and is opposite to the first side and the first side in a direction in which the cam of the centrifuge extends. A plurality of support portions capable of contacting the second side portion;
With
When there is no relative displacement in the rotational direction between the rotating body and the mass body, the neutral contact point between the cam and the cam follower is a first contact point where the first side of the centrifuge contacts the support part. The contact and the second side portion of the centrifuge are located radially inward from a straight line connecting the second contact point that contacts the support portion,
Torque fluctuation suppression device. The centrifuge is
A first outer peripheral contact portion and a first inner peripheral contact portion provided on the first side portion and capable of contacting the support portion;
A second outer peripheral contact portion and a second inner peripheral contact portion provided on the second side portion and capable of contacting the support portion;
Have
The neutral contact point is
A first outer peripheral contact point where the first outer peripheral contact portion contacts the support portion is connected to a second inner peripheral contact point where the second inner peripheral contact portion contacts the support portion. A straight line,
A first inner peripheral contact point where the first inner peripheral contact portion contacts the support portion and a first outer peripheral contact point where the second outer peripheral contact portion contacts the support portion are connected. A straight line,
It is located radially inward from the fixed point that is the intersection of
The torque fluctuation suppressing device according to claim 1. The cam is formed in an arc shape recessed inward in the radial direction,
The arc center of the cam is located on the fixed point,
The torque fluctuation suppressing device according to claim 2. The rotating body has a plurality of recesses that open radially outward on an outer peripheral surface, and the centrifuge is accommodated in the recesses,
The first outer peripheral side abutting portion, the first inner peripheral side abutting portion, the second outer peripheral side abutting portion, and the second inner peripheral side abutting portion of the centrifuge each have an outer peripheral surface that contacts the side wall of the recess. This is a guide roller that can be touched.
The torque fluctuation suppressing device according to claim 2 or 3. The rotating body has a plurality of recesses that open radially outward on an outer peripheral surface, and the centrifuge is accommodated in the recesses,
The support part is
The first outer side roller that is rotatably attached to the first side wall of the recess and is capable of contacting the first outer peripheral side contact portion of the centrifuge and the first inner peripheral side contact portion of the centrifuge. A first inner side roller that can be contacted;
A second outer side roller that is rotatably attached to the second side wall of the recess and is capable of contacting the second outer peripheral side contact portion of the centrifuge, and the second inner peripheral side contact portion of the centrifuge. A second inner peripheral roller that can be contacted;
have,
The torque fluctuation suppressing device according to claim 2 or 3. The mass body includes a first inertia ring and a second inertia ring arranged to face each other with the rotating body interposed therebetween, and a pin that connects the first inertia ring and the second inertia ring so as not to be relatively rotatable. Have
The centrifuge is arranged between the first inertia ring and the second inertia ring in the axial direction on the outer peripheral portion of the rotating body and on the inner peripheral side of the pin.
The cam follower is a cylindrical roller having a hole through which the pin penetrates in the axial direction.
The cam is formed on the centrifuge and abuts on 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. ,
The torque fluctuation suppressing device according to any one of claims 1 to 5. A torque converter disposed between the engine and the transmission,
An input-side rotating body to which torque from the engine is input;
An output-side rotating body that outputs torque to the transmission;
A damper disposed between the input-side rotor and the turbine;
A torque fluctuation suppressing device according to any one of claims 1 to 5;
Torque converter with A first inertial body that rotates about a rotation axis; a second inertial body that rotates about the rotation axis and is rotatable relative to the first inertial body; and the first inertial body and the second inertial body. A flywheel having a damper disposed therebetween,
A clutch device provided in the second inertial body of the flywheel;
A torque fluctuation suppressing device according to any one of claims 1 to 5;
Power transmission device with

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