Rotating devices and power transmission devices

Abstract

To provide a rotation capable of smoothly moving a centrifugal element in a radial direction.SOLUTION: A rotation device 10 includes a first rotating body 2, a centrifugal element 4, and a falling prevention mechanism 9. The first rotating body 2 is rotatably arranged. The centrifugal element 4 is supported to be movable in a radial direction with respect to the first rotating body 2. The falling prevention mechanism 9 prevents falling of the centrifugal element 4.SELECTED DRAWING: Figure 7

Description

[Technical Field]

[0001] The present invention relates to a rotating device and a power transmission device. [Background technology]

[0002] A rotating device is known in which a centrifugal element is attached to a rotatable first rotor. This rotating device functions by smoothly moving the centrifugal element in the radial direction. One example of such a rotating device is a torque fluctuation suppression device.

[0003] For example, in the torque fluctuation suppressing device described in Patent Document 1, a flange plate and a mass body are provided so as to be rotatable relative to each other. A centrifugal element is attached to the flange plate. The centrifugal element moves radially due to the action of centrifugal force, thereby reducing the rotational phase difference between the flange plate and the mass body. As a result, torque fluctuation is suppressed. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Patent Application Publication No. 2018-132161 Summary of the Invention [Problem to be solved by the invention]

[0005] In the torque fluctuation suppressing device described above, it is desirable that the centrifugal element moves smoothly in order to prevent a deterioration in its function.

[0006] Therefore, an object of the present invention is to provide a rotating device in which the centrifugal element can move smoothly in the radial direction. [Means for solving the problem]

[0007] A rotation device according to a first aspect of the present invention includes a first rotor, a centrifugal element, and a tilt prevention mechanism. The first rotor is rotatably arranged. The centrifugal element is supported so as to be movable in a radial direction relative to the first rotor. The tilt prevention mechanism prevents the centrifugal element from tilting.

[0008] According to this configuration, the fall prevention mechanism can prevent the centrifugal element from falling over, which can prevent the centrifugal element from falling over and interfering with an adjacent member, thereby allowing the centrifugal element to move smoothly in the radial direction.

[0009] Preferably, the rotation device further includes a support member. The support member supports the centrifugal element from the radially outer side when the centrifugal element moves radially outward. The anti-tip mechanism is configured to restrict axial movement of the centrifugal element relative to the support member. With this configuration, the support member can stably support the centrifugal element, preventing the centrifugal element from tipping over due to unstable support.

[0010] Preferably, the tipping prevention mechanism includes a groove and a protrusion. The groove is formed on one of the support member and the centrifugal element. The protrusion is formed on the other of the support member and the centrifugal element. The protrusion is disposed in the groove.

[0011] Preferably, the tipping prevention mechanism has an abutment surface and a guide surface. The abutment surface faces radially outward. The guide surface faces radially inward and faces the abutment surface. The abutment surface is formed on the centrifugal element. In the axial direction, the guide surface is recessed so as to gradually become deeper toward its center. With this configuration, the guide surface allows the centrifugal element to maintain a stable posture. This prevents the centrifugal element from tipping over.

[0012] Preferably, the contact surface protrudes in the axial direction so as to gradually increase in height toward the center thereof.

[0013] Preferably, the anti-tip mechanism has an abutment surface and a guide surface. The abutment surface faces radially inward. The guide surface faces radially outward and faces the abutment surface. The guide surface is formed on the centrifugal element. In the axial direction, the guide surface is recessed so as to gradually become deeper toward its center. With this configuration, the guide surface allows the centrifugal element to maintain a stable posture. This prevents the centrifugal element from tipping over.

[0014] Preferably, the contact surface protrudes in the axial direction so as to gradually increase in height toward the center thereof.

[0015] Preferably, the centrifugal element has a first abutment surface and a second abutment surface. The first abutment surface and the second abutment surface are arranged at an interval in the axial direction. The first abutment surface and the second abutment surface abut against the first rotor. The tipping prevention mechanism is constituted by the first abutment surface and the second abutment surface. With this configuration, the centrifugal element abuts against the first rotor at two points, the first abutment surface and the second abutment surface, so that the attitude of the centrifugal element is stable and tipping of the centrifugal element can be prevented.

[0016] Preferably, the rotation device further includes a second rotating body, the second rotating body being rotatable together with the first rotating body and being arranged to be rotatable relative to the first rotating body.

[0017] Preferably, the rotation device further includes a second rotor, the second rotor being rotatable together with the first rotor and being rotatable relative to the first rotor, and the tip-over prevention mechanism includes a sliding member disposed between the centrifugal element and the second rotor.

[0018] Preferably, the sliding member is annular and extends in the circumferential direction.

[0019] Preferably, the sliding member is curved so as to become thinner towards the outer and inner circumferential edges.

[0020] Preferably, the rotation device further includes a second rotor, the second rotor being rotatable together with the first rotor and being rotatable relative to the first rotor, and the tipping prevention mechanism includes an elastic member disposed between the centrifugal element and the second rotor.

[0021] Preferably, the second rotor has a first plate and a second plate spaced apart in the axial direction. The centrifugal element is disposed between the first plate and the second plate. The elastic member has a first elastic member and a second elastic member. The first elastic member is disposed between the first plate and the centrifugal element. The second elastic member is disposed between the second plate and the centrifugal element.

[0022] Preferably, the rotation device further includes a cam mechanism that receives centrifugal force acting on the centrifugal element and converts the centrifugal force into a circumferential force in a direction that reduces the rotational phase difference between the first rotor and the second rotor.

[0023] Preferably, the cam mechanism has a cam surface and a cam follower. The cam surface is formed on the centrifugal element. The cam follower abuts against the cam surface and transmits force between the centrifugal element and the second rotor.

[0024] Preferably, the cam follower rolls on the cam surface.

[0025] Preferably, the centrifugal element has a first through hole that penetrates the centrifugal element in the axial direction, and the cam surface is defined by an inner wall surface of the first through hole.

[0026] Preferably, the cam follower is rotatably attached to the second rotor.

[0027] Preferably, the second rotation body The second through hole has a second through hole, and the cam follower rolls on the inner wall surface of the second through hole.

[0028] Preferably, the cam follower has a small diameter portion and a large diameter portion. The small diameter portion abuts against the inner wall surface of the second through hole. The large diameter portion abuts against the centrifugal element. The large diameter portion has an outer diameter that gradually increases toward the center in the thickness direction of the large diameter portion. With this configuration, even if the cam follower is tilted, the contact state between the cam follower and the centrifugal element does not change significantly.

[0029] Preferably, the centrifugal element is configured to rotate on its own axis when moving radially.

[0030] Preferably, the rotating device further includes a first rolling member. The first rotating body has a first guide surface and a second guide surface facing in the circumferential direction. The first rolling member is disposed between the first guide surface and the centrifugal element. The first rolling member is configured to roll on the first guide surface due to the rotation of the centrifugal element.

[0031] Preferably, the centrifugal element is configured to roll on the second guide surface.

[0032] A power transmission device according to a second aspect of the present invention includes an input member, an output member, and any one of the above rotation devices. Torque is transmitted to the output member from the input member. [Effects of the Invention]

[0033] According to the present invention, the centrifugal element can move smoothly in the radial direction. [Brief explanation of the drawings]

[0034] [Figure 1] Schematic diagram of a torque converter. [Figure 2] FIG. 2 is a front view of the torque fluctuation suppressing device according to the first embodiment with the first plate removed. [Figure 3] Cross-sectional view of line III-III in Figure 2. [Figure 4] 1 is an enlarged front view of a torque fluctuation suppressing device according to a first embodiment. [Figure 5] 1 is a front view of a torque fluctuation suppressing device according to a first embodiment. [Figure 6] FIG. 2 is an enlarged cross-sectional view showing the tipping prevention mechanism according to the first embodiment. [Figure 7] FIG. 2 is an enlarged cross-sectional view showing the tipping prevention mechanism according to the first embodiment. [Figure 8] FIG. 10 is a schematic diagram showing the positional relationship between a centrifugal element, a cam follower, and an inertia ring when no torque fluctuation is input. [Figure 9] FIG. 4 is a schematic diagram showing the positional relationship between a centrifugal element, a cam follower, and an inertia ring when torque fluctuation is input. [Figure 10] 4 is a graph showing an example of characteristics of a torque fluctuation suppressing device. [Figure 11] FIG. 10 is a front view of a torque fluctuation suppressing device according to a second embodiment with the first plate removed. [Figure 12] Cross-sectional view of line XII-XII in Figure 11. [Figure 13] FIG. 10 is a front view of a torque fluctuation suppressing device according to a second embodiment. [Figure 14] FIG. 10 is an enlarged front view of a torque fluctuation suppressing device according to a second embodiment. [Figure 15] FIG. 10 is an enlarged front view of a torque fluctuation suppressing device according to a second embodiment. [Figure 16] FIG. 4 is a schematic diagram showing the positional relationship between a centrifugal element, a cam follower, an inertia ring, and a first rolling member when no torque fluctuation is input. [Figure 17] FIG. 4 is a schematic diagram showing the positional relationship between a centrifugal element, a cam follower, an inertia ring, and a first rolling member when torque fluctuation is input. [Figure 18] FIG. 10 is an enlarged cross-sectional view showing a tipping prevention mechanism according to a second embodiment. [Figure 19] FIG. [Figure 20] FIG. 10 is an enlarged cross-sectional view of a torque fluctuation suppressing device according to a modified example. [Figure 21] FIG. 10 is a top view of a torque fluctuation suppressing device according to a modified example. [Figure 22] FIG. 10 is an enlarged cross-sectional view of a torque fluctuation suppressing device according to a modified example. [Figure 23] FIG. 10 is an enlarged cross-sectional view of a torque fluctuation suppressing device according to a modified example. [Figure 24] FIG. 10 is an enlarged cross-sectional view of a torque fluctuation suppressing device according to a modified example. DETAILED DESCRIPTION OF THE INVENTION

[0035] A torque fluctuation suppressing device (an example of a rotation device) and a torque converter (an example of a power transmission device) according to each embodiment will be described below with reference to the drawings. In the following description, the axial direction refers to the direction in which the rotation axis O of the torque fluctuation suppressing device extends. The circumferential direction refers to the circumferential direction of a circle centered on the rotation axis O, and the radial direction refers to the radial direction of the circle centered on the rotation axis O. The circumferential direction does not have to completely coincide with the circumferential direction of the circle centered on the rotation axis O, and for example, in FIG. 4, the radial direction also includes the left-right direction based on the centrifugal element. The radial direction does not have to completely coincide with the diameter direction of the circle centered on the rotation axis O, and for example, in FIG. 4, the radial direction also includes the up-down direction based on the centrifugal element.

[0036] First embodiment The torque fluctuation suppressing device according to the first embodiment will be described below. First, a torque converter to which the torque fluctuation suppressing device according to the first embodiment is attached will be described. [Overall configuration] Fig. 1 is a schematic diagram of a torque converter. As shown in Fig. 1, a torque converter 100 has a front cover 11, a torque converter main body 12, a lockup device 13, and an output hub 14 (an example of an output member). Torque is input to the front cover 11 from the engine. The torque converter main body 12 has an impeller 121 connected to the front cover 11, a turbine 122, and a stator (not shown). The turbine 122 is connected to the output hub 14. An input shaft of a transmission (not shown) is spline-fitted to the output hub 14.

[0037] [Lockup device 13] The lockup device 13 has a clutch unit, a piston that is operated by hydraulic pressure, etc., and can be in a lockup on state and a lockup off state. In the lockup on state, torque input to the front cover 11 is transmitted to the output hub 14 via the lockup device 13 without passing through the torque converter main body 12. On the other hand, in the lockup off state, torque input to the front cover 11 is transmitted to the output hub 14 via the torque converter main body 12.

[0038] The lockup device 13 includes an input side rotor 131 (an example of an input member), a damper 132, and the torque fluctuation suppressing device 10.

[0039] The input side rotor 131 includes a piston that is movable in the axial direction, and a friction member 133 is fixed to the side surface on the front cover 11 side. When the friction member 133 is pressed against the front cover 11, torque is transmitted from the front cover 11 to the input side rotor 131.

[0040] The damper 132 is disposed between the input rotor 131 and the flange plate 2, which will be described later. The damper 132 has a plurality of torsion springs, and elastically connects the input rotor 131 and the flange plate 2 in the circumferential direction. The damper 132 transmits torque from the input rotor 131 to the flange plate 2, and also absorbs and attenuates torque fluctuations.

[0041] [Torque fluctuation suppression device 10] Fig. 2 is a front view of the torque fluctuation suppressing device 10, and Fig. 3 is a cross-sectional view taken along line III-III in Fig. 2. Note that the first plate 3a has been removed in Fig. 2, and the output hub 14 has been attached in Fig. 3. In each figure, unless otherwise noted, the torque fluctuation suppressing device 10 is rotating, and the centrifugal element 4 is moving radially outward.

[0042] As shown in Figures 2 and 3, the torque fluctuation suppression device 10 has a flange plate 2 (an example of a first rotating body), an inertia ring 3 (an example of a second rotating body), a centrifugal element 4, a cam mechanism 6, and a tipping prevention mechanism 9.

[0043] <Flange plate 2> The flange plate 2 is rotatably arranged. The flange plate 2 is arranged axially opposite the input rotation body 131. The flange plate 2 is rotatable relative to the input rotation body 131. The flange plate 2 is connected to the output hub 14. That is, the flange plate 2 rotates integrally with the output hub 14. The flange plate 2 and the output hub 14 may be configured as a single member.

[0044] The flange plate 2 is an annular plate. The flange plate 2 can be thicker than the first plate 3a and the second plate 3b, which will be described later. The flange plate 2 has a plurality of mounting holes 211 at its inner peripheral end. The flange plate 2 is attached to the output hub 14 using these mounting holes 211.

[0045] The flange plate 2 has a plurality of accommodating portions 24. In this embodiment, the flange plate 2 has six accommodating portions 24. The plurality of accommodating portions 24 are arranged at intervals in the circumferential direction. Each accommodating portion 24 opens radially outward. The accommodating portions 24 have a predetermined depth.

[0046] Fig. 4 is an enlarged view of the torque fluctuation suppressing device 10. As shown in Fig. 4, the accommodation portion 24 has a first guide surface 241, a second guide surface 242, and a bottom surface 243. The first guide surface 241, the second guide surface 242, and the bottom surface 243 form the inner wall surfaces of the accommodation portion 24.

[0047] The first guide surface 241 and the second guide surface 242 face in the circumferential direction (left-right direction in FIG. 4). The first guide surface 241 and the second guide surface 242 face the centrifugal element 4. When the centrifugal element 4 is not present, the first guide surface 241 and the second guide surface 242 face each other. The first guide surface 241 and the second guide surface 242 extend approximately parallel to each other. The first and second guide surfaces 241, 242 are flat surfaces.

[0048] The bottom surface 243 connects the first guide surface 241 and the second guide surface 242. The bottom surface 243 has a substantially arcuate shape when viewed from the front (axial direction). The bottom surface 243 faces radially outward. The bottom surface 243 faces the outer circumferential surface of the centrifugal element 4.

[0049] <Inertia Ring 3> As shown in Figures 3 and 5, the inertia ring 3 is formed in an annular shape. The inertia ring 3 extends continuously in an annular shape. The inertia ring 3 functions as a mass body of the torque fluctuation suppressing device 10. The inertia ring 3 is rotatable together with the flange plate 2 and is rotatable relative to the flange plate 2. The rotation axis of the inertia ring 3 is the same as the rotation axis of the flange plate 2.

[0050] The inertia ring 3 is disposed axially at a distance from the flange plate 2. The inertia ring 3 is also disposed axially at a distance from the centrifugal element 4.

[0051] The inertia ring 3 has a first plate 3a and a second plate 3b. The first plate 3a and the second plate 3b are arranged to sandwich the flange plate 2 in the axial direction.

[0052] The first plate 3a and the second plate 3b are arranged with a predetermined gap in the axial direction relative to the flange plate 2. The inner peripheral ends of the first plate 3a and the second plate 3b are in contact with the flange plate 2. A sliding plate may be interposed between the inner peripheral ends of the first plate 3a and the second plate 3b and the flange plate 2. The sliding plate has a smaller coefficient of friction than the first plate 3a, the second plate 3b and the flange plate 2.

[0053] The inner peripheral surface of the second plate 3b is arranged so as to be able to abut against the outer peripheral surface of the flange portion 14a of the output hub 14. In this way, the inertia ring 3 is supported by the output hub 14 in the radial direction.

[0054] The first plate 3a and the second plate 3b are fixed to each other by a plurality of rivets 35. Therefore, the first plate 3a and the second plate 3b cannot move relative to each other in the axial, radial, and circumferential directions. In other words, the first plate 3a and the second plate 3b rotate integrally with each other.

[0055] As shown in Fig. 5, the first plate 3a has a plurality of second through holes 36. The second through holes 36 are arranged in the circumferential direction. The second through holes 36 extend in the axial direction. The second through holes 36 penetrate the first plate 3a in the axial direction. The diameter of the second through holes 36 is larger than the diameter of a small diameter portion 622 of a cam follower 62, which will be described later. The diameter of the second through holes 36 is also smaller than the large diameter portion 621 of the cam follower 62.

[0056] Similar to the first plate 3a, the second plate 3b has a plurality of second through holes 36. The second through holes 36 formed in the first plate 3a and the second through holes 36 formed in the second plate 3b are formed at the same positions in the circumferential and radial directions.

[0057] As shown in FIG. 2, a plurality of inertia blocks 38 are disposed between the first plate 3a and the second plate 3b. The plurality of inertia blocks 38 are disposed at intervals from one another in the circumferential direction. For example, the inertia blocks 38 and the centrifugal elements 4 are disposed alternately in the circumferential direction. The inertia blocks 38 are fixed to the first plate 3a and the second plate 3b. Specifically, the inertia blocks 38 are fixed to the first plate 3a and the second plate 3b by rivets 35. The inertia blocks 38 are thicker than the centrifugal elements 4.

[0058] <Centrifugal element 4> The centrifugal element 4 is supported so as to be movable in the radial direction relative to the flange plate 2. More specifically, the centrifugal element 4 is disposed in the housing portion 24 of the flange plate 2. The centrifugal element 4 is configured to receive centrifugal force due to the rotation of the flange plate 2. The centrifugal element 4 is movable in the radial direction within the housing portion 24. The centrifugal element 4 is configured to rotate on its axis when moving in the radial direction. In this embodiment, the entire centrifugal element 4 rotates on its axis. The axial movement of the centrifugal element 4 is restricted by an anti-tip mechanism 9, which will be described later.

[0059] As shown in Fig. 4, the centrifugal element 4 is disk-shaped and has a first through-hole 41 in the center. That is, the centrifugal element 4 is cylindrical. The centrifugal element 4 is thicker than the flange plate 2. The centrifugal element 4 can be formed from a single member.

[0060] The centrifugal element 4 is configured to roll on the inner wall surface of the storage section 24. Specifically, when moving in the radial direction, the centrifugal element 4 rolls on the inner wall surface of the storage section 24. The centrifugal element 4 rolls on first and second guide surfaces 241 and 242 of the inner wall surface.

[0061] For example, when the inertia ring 3 rotates clockwise relative to the flange plate 2, the centrifugal element 4 rolls on the first guide surface 241. Conversely, when the inertia ring 3 rotates counterclockwise relative to the flange plate 2, the centrifugal element 4 rolls on the second guide surface 242.

[0062] Of the outer peripheral surface of the centrifugal element 4, a surface that comes into rolling contact with the first guide surface 241 when the centrifugal element 4 rolls is referred to as a first contact surface 42a. Also, of the outer peripheral surface of the centrifugal element 4, a surface that comes into rolling contact with the second guide surface 242 when the centrifugal element 4 rolls is referred to as a second contact surface 42b. The first and second contact surfaces 42a and 42b are arc-shaped when viewed in the axial direction.

[0063] The distance between the first guide surface 241 and the second guide surface 242 is preferably the same as or slightly larger than the diameter of the centrifugal element 4. If the distance between the first guide surface 241 and the second guide surface 242 is slightly larger than the diameter of the centrifugal element 4, when the first contact surface 42a rolls on the first guide surface 241, the second contact surface 42b does not come into sliding contact with the second guide surface 242. Furthermore, when the second contact surface 42b rolls on the second guide surface 242, the first contact surface 42a does not come into sliding contact with the first guide surface 241.

[0064] The first through hole 41 extends in the axial direction. The first through hole 41 passes through the centrifugal element 4 in the axial direction. The diameter of the first through hole 41 is larger than the diameter of the cam follower 62. More specifically, the diameter of the first through hole 41 is larger than the diameter of the large diameter portion 621 of the cam follower 62. A part of the inner wall surface that defines this first through hole 41 constitutes the cam surface 61.

[0065] <Cam mechanism 6> The cam mechanism 6 is configured to receive the centrifugal force acting on the centrifugal element 4 and convert the centrifugal force into a circumferential force in a direction that reduces the rotational phase difference between the flange plate 2 and the inertia ring 3. The cam mechanism 6 functions when a rotational phase difference occurs between the flange plate 2 and the inertia ring 3.

[0066] The cam mechanism 6 has a cam surface 61 and a cam follower (an example of a support member) 62. The cam surface 61 is formed on the centrifugal element 4. Specifically, the cam surface 61 is part of the inner wall surface of the first through-hole 41 of the centrifugal element 4. The cam surface 61 is a surface against which the cam follower 62 abuts, and is arc-shaped when viewed in the axial direction. The cam surface 61 faces radially outward.

[0067] The cam follower 62 abuts against the cam surface 61. The cam follower 62 is configured to transmit force between the centrifugal element 4 and the inertia ring 3. Specifically, the cam follower 62 extends through the first through hole 41 and each of the second through holes 36. The cam follower 62 is attached to the inertia ring 3 so as to be rotatable about its axis.

[0068] The cam follower 62 rolls on the cam surface 61 of the first through hole 41. The cam follower 62 also rolls on the inner wall surface of the second through hole 36. The cam follower 62 abuts against a surface of the inner wall surface of the second through hole 36 that faces radially inward. In other words, the cam follower 62 is sandwiched between the cam surface 61 and the inner wall surface of the second through hole 36.

[0069] More specifically, the cam follower 62 abuts against the cam surface 61 on the radially inner side, and against the inner wall surface of the second through hole 36 on the radially outer side. This positions the cam follower 62. Furthermore, because the cam follower 62 is sandwiched between the cam surface 61 and the inner wall surface of the second through hole 36 in this manner, the cam follower 62 transmits force between the centrifugal element 4 and the inertia ring 3.

[0070] The cam follower 62 is configured as a cylindrical roller. In other words, the cam follower 62 is not a bearing. The cam follower 62 has a large diameter portion 621 and a pair of small diameter portions 622. The large diameter portion 621 and the small diameter portion 622 are centered. The large diameter portion 621 has a larger diameter than the small diameter portion 622. The large diameter portion 621 has a smaller diameter than the first through hole 41 and a larger diameter than the second through hole 36. The large diameter portion 621 rolls on the cam surface 61.

[0071] Each small diameter portion 622 protrudes from the large diameter portion 621 on both sides in the axial direction. The small diameter portion 622 rolls on the inner wall surface of the second through hole 36. The small diameter portion 622 has a smaller diameter than the second through hole 36. The cam follower 62 can be formed from a single member. That is, the large diameter portion 621 and the pair of small diameter portions 622 of the cam follower 62 are formed from a single member. The cam follower 62 may be cylindrical and have a constant diameter. The cam follower 62 may also be cylindrical.

[0072] When a rotational phase difference occurs between the flange plate 2 and the inertia ring 3 due to contact between the cam follower 62 and the cam surface 61, and between the cam follower 62 and the inner wall surface of the second through hole 36, the centrifugal force generated in the centrifugal element 4 is converted into a circumferential force that reduces the rotational phase difference.

[0073] The cam follower 62 also has the function of supporting the centrifugal element 4 from the radially outer side when the centrifugal element 4 moves radially outward.

[0074] <Tilt prevention mechanism> As shown in Fig. 3, the tilt prevention mechanism 9 is configured to prevent the centrifugal element 4 from tilting. The tilt of the centrifugal element 4 means that the in-plane direction of the centrifugal element 4 is inclined with respect to a plane perpendicular to the rotation axis O. When the centrifugal element 4 is not tilted, the in-plane direction of the centrifugal element 4 extends substantially parallel to the plane perpendicular to the rotation axis O.

[0075] The tipping prevention mechanism 9 is configured to restrict the centrifugal element 4 from moving in the axial direction relative to the cam follower 62. Specifically, as shown in Fig. 6, the tipping prevention mechanism 9 has a groove 901 and a protrusion 902. Note that Fig. 6 is an enlarged cross-sectional view of only the portion related to the tipping prevention mechanism 9.

[0076] The groove 901 is formed on the inner wall surface of the first through hole 41 of the centrifugal element 4. More specifically, the groove 901 is formed on the cam surface 61 of the centrifugal element 4. The groove 901 is disposed in the axial center of the cam surface 61. The groove 901 extends annularly along the inner wall surface of the first through hole 41.

[0077] The protrusion 902 is formed on the outer peripheral surface of the cam follower 62. More specifically, the protrusion 902 is formed on the outer peripheral surface of the large diameter portion 621 of the cam follower 62. The protrusion 902 is disposed in the axial center on the outer peripheral surface of the large diameter portion 621. The protrusion 902 extends in an annular shape along the outer peripheral surface of the large diameter portion 621.

[0078] The protrusion 902 is disposed in the groove 901. Note that the tip surface of the protrusion 902 does not contact the bottom surface of the groove 901, but may do so. In this way, the protrusion 902 formed on the cam follower 62 and the groove 901 formed on the centrifugal element 4 are engaged with each other, so the centrifugal element 4 does not move in the axial direction relative to the cam follower 62. Therefore, the centrifugal element 4 is supported by the cam follower 62 in a stable state. As a result, the centrifugal element 4 can be prevented from falling over.

[0079] 7, the groove 901 may be formed in the cam follower 62, and the protrusion 902 may be formed in the centrifugal element 4. When the axial dimension of the protrusion 902 is large like the protrusion 902 in FIG. 7, the tip surface of the protrusion 902 may be in contact with the groove 901. The tip surface of the protrusion 902 may then form the cam surface 61.

[0080] <Stopper mechanism> As shown in Fig. 4, the torque fluctuation suppressing device 10 further includes a stopper mechanism 8. The stopper mechanism 8 restricts the relative rotation angle range between the flange plate 2 and the inertia ring 3. The stopper mechanism 8 has a protrusion 81 and a recess 82.

[0081] The protrusion 81 protrudes radially inward from the inertia block 38. The recess 82 is formed on the outer peripheral surface of the flange plate 2. The protrusion 81 is disposed within the recess 82. The protrusion 81 abuts against the end face of the recess 82, thereby restricting the relative rotation angle range between the flange plate 2 and the inertia ring 3.

[0082] [Operation of the torque fluctuation suppression device 10] The operation of the torque fluctuation suppressing device 10 will be described with reference to FIGS.

[0083] When the lock-up is on, the torque transmitted to the front cover 11 is transmitted to the flange plate 2 via the input side rotor 131 and the damper 132 .

[0084] If there is no torque fluctuation during torque transmission, the flange plate 2 and inertia ring 3 rotate in the state shown in Figure 8. In this state, the cam follower 62 of the cam mechanism 6 abuts against the radially innermost position (the central position in the circumferential direction) of the cam surface 61. Also, in this state, the rotational phase difference between the flange plate 2 and the inertia ring 3 is "0".

[0085] As described above, the amount of relative displacement in the circumferential direction between the flange plate 2 and the inertia ring 3 is called the "rotational phase difference." In Figures 8 and 9, this indicates the deviation between the central positions of the centrifugal element 4 and the cam surface 61 in the circumferential direction and the central position of the second through hole 36.

[0086] Here, if torque fluctuations occur during torque transmission, a rotational phase difference θ occurs between the flange plate 2 and the inertia ring 3, as shown in FIG.

[0087] As shown in Fig. 9, when a rotational phase difference θ occurs between the flange plate 2 and the inertia ring 3, the cam follower 62 of the cam mechanism 6 moves from the position shown in Fig. 8 to the position shown in Fig. 9. At this time, the cam follower 62 moves relatively to the left while rolling on the cam surface 61. The cam follower 62 also rolls on the inner wall surface of the second through hole 36. More specifically, the large diameter portion 621 of the cam follower 62 rolls on the cam surface 61, and the small diameter portion 622 of the cam follower 62 rolls on the inner wall surface of the second through hole 36. The cam follower 62 rotates counterclockwise.

[0088] As the cam follower 62 moves to the left, the cam follower 62 presses the centrifugal element 4 radially inward (toward the lower side in FIGS. 8 and 9) via the cam surface 61, causing the centrifugal element 4 to move radially inward. As a result, the centrifugal element 4 moves from the position shown in FIG. 8 to the position shown in FIG. 9. At this time, the centrifugal element 4 rolls on the second guide surface 242. The centrifugal element 4 rotates clockwise on its axis.

[0089] Since centrifugal force acts on the centrifugal element 4 that has moved to the position shown in Figure 9, the centrifugal element 4 moves radially outward (toward the upper side in Figure 9). More specifically, the centrifugal element 4 rolls on the second guide surface 242 and moves radially outward. The centrifugal element 4 rotates counterclockwise.

[0090] Furthermore, the cam surface 61 formed on the centrifugal element 4 presses the inertia ring 3 to the right in FIG. 9 via the cam follower 62, causing the inertia ring 3 to move to the right in FIG. 9. At this time, the large diameter portion 621 of the cam follower 62 rolls on the cam surface 61, and the small diameter portion 622 of the cam follower 62 rolls on the inner wall surface of the second through hole 36. The cam follower 62 rotates clockwise. As a result, the state returns to that shown in FIG. 8.

[0091] When a rotational phase difference occurs in the opposite direction, the cam follower 62 moves relatively to the right in Figure 9 along the cam surface 61, but the operating principle is the same. At this time, the centrifugal element 4 rolls on the first guide surface 241.

[0092] As described above, when a rotational phase difference occurs between the flange plate 2 and the inertia ring 3 due to torque fluctuations, the flange plate 2 receives a circumferential force that reduces the rotational phase difference between them due to the centrifugal force acting on the centrifugal element 4 and the action of the cam mechanism 6. This force suppresses the torque fluctuations. Note that force is transmitted between the centrifugal element 4 and the inertia ring 3 via the cam follower 62.

[0093] The force that suppresses the torque fluctuations described above varies depending on the centrifugal force, i.e., the rotational speed of the flange plate 2, and also on the rotational phase difference and the shape of the cam surface 61. Therefore, by appropriately setting the shape of the cam surface 61, the characteristics of the torque fluctuation suppression device 10 can be optimized according to the engine specifications, etc.

[0094] Furthermore, the centrifugal element 4 moves in the radial direction by rolling on the first guide surface 241 or the second guide surface 242. Therefore, the centrifugal element 4 can move in the radial direction more smoothly than if it were to slide on the first guide surface 241 or the second guide surface 242. Furthermore, the cam follower 62 rolls on the cam surface 61 and the inner wall surface of the second through hole 36. Therefore, force can be transmitted more smoothly between the centrifugal element 4 and the inertia ring 3.

[0095] [Example of characteristics] 10 is a diagram showing an example of the characteristics of the torque fluctuation suppressing device 10. The horizontal axis represents the rotation speed, and the vertical axis represents torque fluctuation (rotational speed fluctuation). Characteristic Q1 represents the case where no device for suppressing torque fluctuation is provided, characteristic Q2 represents the case where a conventional dynamic damper device without a cam mechanism is provided, and characteristic Q3 represents the case where the torque fluctuation suppressing device 10 of this embodiment is provided.

[0096] As is clear from Fig. 10, the device provided with the dynamic damper device without a cam mechanism (characteristic Q2) can suppress torque fluctuations only in a specific rotation speed range, whereas the present embodiment with the cam mechanism 6 (characteristic Q3) can suppress torque fluctuations in all rotation speed ranges.

[0097] Second embodiment Next, a torque fluctuation suppression device 10 according to a second embodiment will be described. The following description will focus on the differences from the torque fluctuation suppression device 10 according to the first embodiment. The same components as those in the torque fluctuation suppression device 10 according to the first embodiment will be assigned the same reference numerals and description thereof will be omitted.

[0098] Fig. 11 is a front view of the torque fluctuation suppressing device 10, and Fig. 12 is a cross-sectional view taken along line XII-XII in Fig. 11. In Fig. 11, the first plate 3a has been removed.

[0099] As shown in Figures 11 and 12, the torque fluctuation suppression device 10 of the second embodiment has a first rolling member 5, a sliding member 15, and a pair of spacers 16, which are not included in the torque fluctuation suppression device 10 of the first embodiment.

[0100] The flange plate 2 has an inner circumferential portion 21, an outer circumferential portion 22, and a connecting portion 23. The inner circumferential portion 21 has a plurality of mounting holes 211. The mounting holes 211 are used to mount the inner circumferential portion 21 of the flange plate 2 to the output hub 14. The inner circumferential portion 21 is disposed outside the housing space, which will be described later.

[0101] 12, the outer peripheral portion 22 is accommodated in an accommodation space, which will be described later. The outer peripheral portion 22 is positioned in a different axial direction from the inner peripheral portion 21. Specifically, the outer peripheral portion 22 is disposed on a first axial side (the left side in FIG. 12) relative to the inner peripheral portion 21.

[0102] The connecting portion 23 connects the outer circumferential portion 22 and the inner circumferential portion 21. More specifically, the connecting portion 23 connects the outer circumferential end of the inner circumferential portion 21 and the inner circumferential end of the outer circumferential portion 22. The connecting portion 23 extends in the axial direction. The connecting portion 23 is cylindrical.

[0103] The flange plate 2 has a first support surface 25. More specifically, the connecting portion 23 has the first support surface 25. The inner peripheral surface of the connecting portion 23 constitutes the first support surface 25. The first support surface 25 faces radially inward. The first support surface 25 is annular. When viewed in the axial direction, the first support surface 25 has a circular shape.

[0104] The first plate 3a has a first annular portion 31a and a first cylindrical portion 32a. The first annular portion 31a is annular. The first annular portion 31a is disposed on a first axial side relative to the flange plate 2. The first annular portion 31a is disposed axially at a distance from the flange plate 2.

[0105] The first cylindrical portion 32a extends in the axial direction from the inner circumferential end of the first annular portion 31a toward the second plate 3b. That is, the first cylindrical portion 32a extends from the inner circumferential end of the first annular portion 31a toward the second side in the axial direction.

[0106] The first cylindrical portion 32a is disposed radially inward of the connecting portion 23. The first cylindrical portion 32a has a second support surface 33. Specifically, the outer peripheral surface of the first cylindrical portion 32a forms the second support surface 33.

[0107] The second support surface 33 faces radially outward. The second support surface 33 is configured to be supported by the first support surface 25. More specifically, the second support surface 33 is configured to be supported by the first support surface 25 via the sliding member 15. In this embodiment, a gap is formed between the second support surface 33 and the sliding member 15. When the inertia ring 3 moves in the radial direction, the second support surface 33 abuts against the sliding member 15. Note that there does not need to be a gap between the second support surface 33 and the sliding member 15.

[0108] The second plate 3b has a second annular portion 31b and a second cylindrical portion 32b. The second annular portion 31b is annular. The second annular portion 31b is disposed on a second axial side relative to the flange plate 2. The second annular portion 31b is disposed axially at a distance from the flange plate 2.

[0109] The second annular portion 31b is disposed axially apart from the first annular portion 31a. The second annular portion 31b is disposed on a second axial side relative to the first annular portion 31a. The outer peripheral portion 22 of the flange plate 2 is disposed axially between the first annular portion 31a and the second annular portion 31b.

[0110] The second cylindrical portion 32b extends in the axial direction from the outer peripheral end of the second annular portion 31b toward the first plate 3a. That is, the second cylindrical portion 32b extends from the outer peripheral end of the second annular portion 31b toward the first side in the axial direction.

[0111] The second cylindrical portion 32b is disposed radially outward from the outer peripheral portion 22 of the flange plate 2. The inner peripheral surface of the second cylindrical portion 32b faces the outer peripheral surface of the outer peripheral portion 22 of the flange plate 2. In the radial direction, the outer peripheral portion 22 of the flange plate 2 is disposed between the first cylindrical portion 32a and the second cylindrical portion 32b. In addition, the outer peripheral portion 22 of the flange plate 2 is disposed between the first annular portion 31a and the second annular portion 31b in the axial direction. In this way, the first plate 3a and the second plate 3b form an accommodation space that accommodates the outer peripheral portion 22 of the flange plate 2.

[0112] A first gap G1 is formed between the outer peripheral end of the first annular portion 31a and the tip end of the second cylindrical portion 32b. That is, the outer peripheral surface of the first annular portion 31a is not in contact with the inner peripheral surface of the second cylindrical portion 32b, but is spaced apart. This first gap G1 may be formed along the entire circumference, or only partially. Note that the outer peripheral surface of the first annular portion 31a may be in contact with the inner peripheral surface of the second cylindrical portion 32b, and the first gap G1 may not be formed.

[0113] A second gap G2 is formed between the inner peripheral end of the second annular portion 31b and the tip end of the first cylindrical portion 32a. That is, the inner peripheral surface of the second annular portion 31b is First cylindrical portion 32aThe second gap G2 is not in contact with the outer peripheral surface of the flange plate 2, but is spaced apart from it. This second gap G2 is formed around the entire circumference, but may be formed only on a portion of the circumference. The connecting portion 23 of the flange plate 2 connects the inner peripheral portion 21 and the outer peripheral portion 22 via this second gap G2.

[0114] 13, the first plate 3a has a plurality of restriction grooves 37. More specifically, the first annular portion 31a has a plurality of restriction grooves 37. The restriction grooves 37 are arranged in the circumferential direction. The restriction grooves 37 are formed in an arc shape that bulges outward in the radial direction.

[0115] Similar to the first plate 3a, the second plate 3b has a plurality of restriction grooves 37. The restriction grooves 37 formed in the first plate 3a and the restriction grooves 37 formed in the second plate 3b are formed at the same positions in the circumferential and radial directions.

[0116] 11 and 12, the sliding member 15 is disposed between the first support surface 25 and the second support surface 33. More specifically, the sliding member 15 is attached to the first support surface 25. The sliding member 15 is formed in an annular shape. The sliding member 15 is press-fitted into the connecting portion 23. The flange plate 2 has a greater plate thickness than the first plate 3a and the second plate 3b.

[0117] The sliding member 15 is made of a material having a lower coefficient of friction than the flange plate 2. The sliding member 15 is also made of a material having a lower coefficient of friction than the inertia ring 3. For example, the sliding member 15 can be made of resin, and more specifically, can be made of polytetrafluoroethylene (PTFE), polyether ether ketone (PEEK), thermoplastic polyimide (TPI), or the like.

[0118] The second support surface 33 is configured to be supported by the first support surface 25 via the sliding member 15 .

[0119] The center of gravity of the inertia ring 3, as viewed in the radial direction, overlaps with the first support surface 25 and also with the second support surface 33. Note that, when the second support surface 33 is supported by the first support surface 25 via the sliding member 15 as in this embodiment, the center of gravity of the inertia ring 3 overlaps with all of the first support surface 25, the second support surface 33, and the sliding member 15, as viewed in the radial direction.

[0120] The pair of spacers 16 are arranged in the axial direction between the flange plate 2 and the inertia ring 3. Specifically, one spacer 16 is arranged between the outer circumferential portion 22 and the first plate 3a, and the other spacer 16 is arranged between the outer circumferential portion 22 and the second plate 3b.

[0121] The spacer 16 is annular. The spacer 16 may be fixed to the flange plate 2 or may be fixed to the inertia ring 3. The spacer 16 is made of a material with a lower coefficient of friction than the flange plate 2 or the inertia ring 3. Specifically, the spacer 16 may be made of resin, and more specifically, the spacer 16 may be made of polytetrafluoroethylene (PTFE), polyether ether ketone (PEEK), thermoplastic polyimide (TPI), or the like.

[0122] As shown in FIG. 14 , the centrifugal element 4 is in contact with the second guide surface 242 and the first rolling member 5. Therefore, the movement of the centrifugal element 4 in the circumferential direction is restricted. On the other hand, the centrifugal element 4 is movable in the radial direction. When moving in the radial direction, the centrifugal element 4 rolls on the second guide surface 242 of the accommodating portion 24. When moving in the radial direction, the centrifugal element 4 rolls on the first guide surface 241 via the first rolling member 5. That is, the centrifugal element 4 rolls on the outer circumferential surface of the first rolling member 5.

[0123] Of the outer peripheral surface of the centrifugal element 4, a surface that comes into rolling contact with the outer peripheral surface of the first rolling member 5 when the centrifugal element 4 rolls is defined as a first contact surface 42a.

[0124] The first rolling member 5 is disposed between the first guide surface 241 and the centrifugal element 4. More specifically, the first rolling member 5 is sandwiched between the first guide surface 241 and the centrifugal element 4. The first rolling member 5 is in contact with the first guide surface 241 and the centrifugal element 4.

[0125] The center of the first rolling member 5 is located radially inward of the center of the centrifugal element 4. The first rolling member 5 is configured as a cylindrical roller. In other words, the first rolling member 5 is not a bearing.

[0126] The first rolling member 5 has a large diameter portion 51 and a pair of small diameter portions 52. The large diameter portion 51 and the small diameter portion 52 are centered. The large diameter portion 51 has a larger diameter than the small diameter portion 52. The diameter of the large diameter portion 51 is larger than the width of the restriction groove 37. Therefore, the first rolling member 5 is supported in the axial direction by the first plate 3a and the second plate 3b.

[0127] Each small diameter portion 52 protrudes from the large diameter portion 51 on both sides in the axial direction. The diameter of the small diameter portion 52 is smaller than the width of the restriction groove 37. The small diameter portion 52 is disposed within the restriction groove 37 of the inertia ring 3. A predetermined gap is provided between the small diameter portion 52 and the inner wall surface of the restriction groove 37, allowing the small diameter portion 52 to move smoothly within the restriction groove 37. Because the small diameter portion 52 is disposed within the restriction groove 37 in this manner, radial movement of the first rolling member 5 when stopped can be restricted. In other words, the first rolling member 5 is supported by the restriction groove 37.

[0128] The first rolling member 5 can be formed from a single member. That is, the large diameter portion 51 and the pair of small diameter portions 52 of the first rolling member 5 are formed from a single member. The first rolling member 5 may be cylindrical with a constant diameter. The first rolling member 5 may also be cylindrical.

[0129] The first rolling member 5 is configured to roll on the first guide surface 241 due to the rotation of the rotor 4. That is, when the rotor 4 rotates, the first rolling member 5 also rotates. Note that the rotation direction of the rotor 4 is opposite to the rotation direction of the first rolling member 5. Then, the first rolling member 5 rolls on the first guide surface 241 by rotating. Specifically, the large-diameter portion 51 of the first rolling member 5 rolls on the first guide surface 241.

[0130] When there is no relative displacement in the rotation direction (rotation phase difference) between the flange plate 2 and the inertia ring 3, as shown in FIG. 13, the small-diameter portion 52 is located approximately at the center in the longitudinal direction (circumferential direction) of the regulation groove 37. When a rotation phase difference occurs between the flange plate 2 and the inertia ring 3, the small-diameter portion 52 moves along the regulation groove 37.

[0131] As shown in FIG. 15, the distance H between the first guide surface 241 and the second guide surface 242 is smaller than the sum of the diameter D1 of the rotor 4 and the diameter D2 of the first rolling member 5. That is, the formula H < D1 + D2 holds. Thereby, during the operation of the torque fluctuation suppression device 10, the rotor 4 is always in contact with the second guide surface 242 and the first rolling member 5.

[0132] Since the diameter D2 of the first rolling member 5 is larger than the gap between the outer peripheral surface of the rotor 4 and the first guide surface 241, the first rolling member 5 is restricted from protruding radially outward.

[0133] When the cam follower 62 of the cam mechanism 6 moves from the position shown in FIG. 16 to the position shown in FIG. 17, as the rotor 4 rotates clockwise, the first rolling member 5 rotates counterclockwise. Then, the first rolling member 5 rolls on the first guide surface 241 and moves radially inward.

[0134] Also, when the cam follower 62 returns from the position shown in FIG. 17 to the position shown in FIG. 16, as the rotor 4 rotates counterclockwise, the first rolling member 5 rotates clockwise. Then, it rolls on the first guide surface 241 and moves radially outward.

[0135] 18, in this embodiment, the tipping prevention mechanism 9 has a contact surface 91 and a guide surface 92 instead of a groove 901 and a protrusion 902. The contact surface 91 is formed on the centrifugal element 4. In this embodiment, the contact surface 91 is formed by the cam surface 61 of the centrifugal element 4. The contact surface 91 faces radially outward.

[0136] The contact surface 91 protrudes radially outward. In the axial direction, the contact surface 91 protrudes so as to gradually increase in height toward its center. The contact surface 91 has an arc-shaped cross section. The contact surface 91 bulges radially outward.

[0137] The centrifugal element 4 is configured so that the inner diameter of the centrifugal element 4 is smallest at the center in the thickness direction of the centrifugal element 4. The inner diameter of the centrifugal element 4 gradually decreases toward the center in the thickness direction of the centrifugal element 4.

[0138] The guide surface 92 faces radially inward. The guide surface 92 faces the abutment surface 91. When the torque fluctuation suppressing device 10 is in operation, the guide surface 92 abuts against the cam surface 61 of the centrifugal element 4. The guide surface 92 is formed on the cam follower 62. More specifically, the guide surface 92 is formed by the outer peripheral surface of the cam follower 62. More specifically, the guide surface 92 is formed by the outer peripheral surface of the large diameter portion 621 of the cam follower 62.

[0139] The guide surface 92 is recessed radially outward. In the axial direction, the guide surface 92 is recessed so as to gradually become deeper toward its center. The cross section of the guide surface 92 is arc-shaped. The guide surface 92 is recessed radially outward. The radius of curvature of this guide surface 92 is larger than the radius of curvature of the abutment surface 91.

[0140] Large diameter portion 621 is configured so that the outer diameter of large diameter portion 621 is smallest at the center in the thickness direction of large diameter portion 621 of cam follower 62. The outer diameter of large diameter portion 621 gradually decreases toward the center in the thickness direction of large diameter portion 621.

[0141] Since the guide surface 92 is formed in this manner, the centrifugal element 4, which abuts against the guide surface 92 via the abutment surface 91, maintains its posture, thereby preventing the centrifugal element 4 from falling over.

[0142] [Variations] The present invention is not limited to the above-described embodiments, and various modifications and alterations are possible without departing from the scope of the present invention.

[0143] <Variation 1> In each of the above embodiments, a torque fluctuation suppression device has been described as an example of a rotation device, but the rotation device may be something other than a torque fluctuation suppression device, such as a clutch device or a damper device.

[0144] <Variation 2> In the above-described embodiments, the flange plate 2 is illustrated as an example of the first rotating body, but the first rotating body is not limited to this. For example, when the torque fluctuation suppressing device is attached to a torque converter as in the above-described embodiments, the front cover 11 or the input rotating body 131 of the torque converter 100 may be the first rotating body.

[0145] <Variation 3> In each of the above embodiments, the torque fluctuation suppressing device 10 is attached to the torque converter 100, but the torque fluctuation suppressing device 10 can also be attached to other power transmission devices such as a clutch device.

[0146] For example, as shown in FIG. 19 , the torque fluctuation suppressing device 10 can be attached to a damper device 101. This damper device 101 is mounted on, for example, a hybrid vehicle. The damper device 101 includes an input member 141, an output member 142, a damper 143, and the torque fluctuation suppressing device 10. Torque from a drive source is input to the input member 141. The damper 143 is disposed between the input member 141 and the output member 142. The torque from the input member 141 is transmitted to the output member 142 via the damper 143. The torque fluctuation suppressing device 10 is attached to, for example, the output member 142.

[0147] <Variation 4> In the second embodiment, the contact surface 91 is formed on the centrifugal element 4, and the guide surface 92 is formed on the cam follower 62. However, the configuration of the tipping prevention mechanism 9 is not limited to this. For example, as shown in FIG. 20 , the contact surface 91 may be formed on the cam follower 62. In this case, the contact surface 91 faces radially inward. In the axial direction, the contact surface 91 gradually becomes higher toward its center.

[0148] Alternatively, the guide surface 92 may be formed on the centrifugal element 4. The guide surface 92 faces radially outward. In the axial direction, the guide surface 92 is recessed so as to become gradually deeper toward the center thereof.

[0149] <Variation 5> The configuration of the tipping prevention mechanism 9 is not limited to the configuration of each of the above-described embodiments. For example, as shown in Fig. 21 , the tipping prevention mechanism 9 can be configured by a first contact surface 93 and a second contact surface 94 provided on the centrifugal element 4. Note that in Fig. 21 , the inertia block 38 and the rivet 35 are omitted for ease of illustration.

[0150] The first contact surface 93 and the second contact surface 94 are formed by the outer peripheral surface of the centrifugal element 4. The first contact surface 93 and the second contact surface 94 are arranged with a gap between them in the axial direction. A groove 43 is formed in the outer peripheral surface of the centrifugal element 4. The groove 43 is formed in the center in the thickness direction of the centrifugal element 4. The groove 43 extends in an annular shape along the outer peripheral surface of the centrifugal element 4. The first contact surface 93 and the second contact surface 94 are arranged so as to sandwich the groove 43 in the axial direction.

[0151] The first abutment surface 93 and the second abutment surface 94 abut against the flange plate 2. The flange plate 2 has a main body 26 and a plurality of abutment portions 27. The abutment portions 27 are plate-shaped and extend from the main body 26 in the axial and radial directions. The first abutment surface 93 and the second abutment surface 94 abut against the abutment portions 27. Note that the dimension of the abutment portions 27 in the axial direction is larger than the dimension of the centrifugal element 4. A second guide surface 242 is formed on the abutment portions 27. That is, the first abutment surface 93 and the second abutment surface 94 abut against the second guide surface 242.

[0152] The first rolling member 5 also has a third abutment surface 95 and a fourth abutment surface 96. The third abutment surface 95 and the fourth abutment surface 96 are formed by the outer circumferential surface of the first rolling member 5. The third abutment surface 95 and the fourth abutment surface 96 are arranged at an interval from each other in the axial direction. A groove 53 is formed in the outer circumferential surface of the first rolling member 5. The groove 53 is formed in the central portion in the thickness direction of the first rolling member 5. The groove 53 extends in an annular shape along the outer circumferential surface of the first rolling member 5. The third abutment surface 95 and the fourth abutment surface 96 are arranged so as to sandwich the groove 53 in the axial direction.

[0153] The third abutment surface 95 and the fourth abutment surface 96 abut against the abutment portion 27. A first guide surface 241 is formed on the abutment portion 27 with which the third abutment surface 95 and the fourth abutment surface 96 abut. That is, the third abutment surface 95 and the fourth abutment surface 96 abut against the first guide surface 241.

[0154] The third contact surface 95 and the fourth contact surface 96 also contact the centrifugal element 4. More specifically, the third contact surface 95 contacts the first contact surface 93. The fourth contact surface 96 contacts the second contact surface 94.

[0155] As shown in FIG. 22, the outer diameter of the large diameter portion 621 of the cam follower 62 may gradually increase toward the center in the thickness direction of the large diameter portion 621.

[0156] <Variation 6> The tipping prevention mechanism 9 may have other configurations. For example, as shown in Fig. 23, the tipping prevention mechanism 9 may be configured by a first sliding member 99a and a second sliding member 99b. The first sliding member 99a and the second sliding member 99b are disposed between the centrifugal element 4 and the inertia ring 3. In detail, the first sliding member 99a is disposed between the centrifugal element 4 and the first plate 3a, and the second sliding member 99b is disposed between the centrifugal element 4 and the second plate 3b.

[0157] The first sliding member 99a is fixed to the first plate 3a, and the second sliding member 99b is fixed to the second plate 3b. The first sliding member 99a and the second sliding member 99b are annular and extend in the circumferential direction. The first sliding member 99a and the second sliding member 99b are curved so as to become thinner toward the outer and inner peripheral edges.

[0158] The first sliding member 99a and the second sliding member 99b can be made of resin, and more specifically, can be made of polytetrafluoroethylene (PTFE), polyether ether ketone (PEEK), thermoplastic polyimide (TPI), or the like.

[0159] <Variation 7> 24, the tipping prevention mechanism 9 may be configured with a first elastic member 99c and a second elastic member 99d. The first elastic member 99c and the second elastic member 99d are arranged between the centrifugal element 4 and the inertia ring 3. In detail, the first elastic member 99c is arranged between the centrifugal element 4 and the first plate 3a, and the second elastic member 99d is arranged between the centrifugal element 4 and the second plate 3b.

[0160] The first elastic member 99c is fixed to the first plate 3a, and the second elastic member 99d is fixed to the second plate 3b. The first elastic member 99c and the second elastic member 99d are annular and extend in the circumferential direction. The first elastic member 99c and the second elastic member 99d are configured to urge the centrifugal element 4 back to its original position when the centrifugal element 4 falls toward the first elastic member 99c. The first elastic member 99c and the second elastic member 99d may be, for example, a wave spring. [Explanation of symbols]

[0161] 2: Flange plate 241: First guide surface 242: Second guide surface 3: Inertia ring 3a: First plate 3b: Second plate 36: Second through hole 4: Centrifugal element 41: First through hole 5: First rolling member 6: Cam mechanism 61: Cam surface 62: Cam follower 9: Anti-fall mechanism 91: Contact surface 92: Guide surface 93: 1st contact surface 94:Second contact surface 99c: First elastic member 99d: Second elastic member 901: Groove 902: Protrusion 10: Torque fluctuation suppression device 15: Sliding member 100: Torque converter 141: Input member 142: Output member

Claims

1. a rotatably disposed first rotor; a centrifugal element supported so as to be movable in a radial direction relative to the first rotor; a fall prevention mechanism that prevents the centrifugal element from falling; a second rotating body that is rotatable together with the first rotating body and that is arranged so as to be rotatable relative to the first rotating body; a cam mechanism that receives centrifugal force acting on the centrifugal element and converts the centrifugal force into a circumferential force in a direction that reduces a rotational phase difference between the first rotor and the second rotor; Equipped with The cam mechanism a cam surface formed on the centrifugal element; a cam follower that contacts the cam surface and transmits force between the centrifugal element and the second rotor; having Rotating device.

2. a support member that supports the centrifugal element from the radially outer side when the centrifugal element moves radially outward; The anti-tilt mechanism is configured to restrict axial movement of the centrifugal element relative to the support member. The rotating device according to claim 1 .

3. The tipping prevention mechanism includes a groove formed in one of the support member and the centrifugal element, and a protrusion formed in the other of the support member and the centrifugal element and disposed in the groove. The rotating device according to claim 2 .

4. the tipping prevention mechanism has a contact surface facing radially outward and a guide surface facing radially inward and opposing the contact surface, the contact surface is formed on the centrifugal element, In the axial direction, the guide surface is recessed so as to become gradually deeper toward the center thereof. The rotating device according to claim 1 .

5. In the axial direction, the abutment surface protrudes so as to gradually increase in height toward the center thereof. The rotating device according to claim 4.

6. the tipping prevention mechanism has a contact surface facing radially inward and a guide surface facing radially outward and opposing the contact surface, The guide surface is formed on the centrifugal element, In the axial direction, the guide surface is recessed so as to become gradually deeper toward the center thereof. The rotating device according to claim 1 .

7. In the axial direction, the abutment surface protrudes so as to gradually increase in height toward the center thereof. The rotating device according to claim 6.

8. The centrifugal element has a first abutment surface and a second abutment surface that are spaced apart from each other in the axial direction, the first contact surface and the second contact surface contact the first rotating body, The fall prevention mechanism is configured by the first contact surface and the second contact surface. The rotating device according to claim 1 .

9. The tip-over prevention mechanism has a sliding member disposed between the centrifugal element and the second rotating body. The rotating device according to claim 1 .

10. The sliding member is annular and extends in the circumferential direction. The rotation device according to claim 9.

11. The sliding member is curved so as to become thinner toward the outer peripheral edge and the inner peripheral edge. A rotating device according to claim 9 or 10.

12. The tip-over prevention mechanism has an elastic member disposed between the centrifugal element and the second rotating body. The rotating device according to claim 1 .

13. the second rotor has a first plate and a second plate spaced apart in the axial direction, the centrifugal element is disposed between the first plate and the second plate, The elastic member includes a first elastic member disposed between the first plate and the centrifugal element, and a second elastic member disposed between the second plate and the centrifugal element. The rotating device of claim 12.

14. The cam follower rolls on the cam surface. A rotating device according to any one of claims 1 to 13.

15. The centrifugal element has a first through hole that penetrates in the axial direction, the cam surface is formed by an inner wall surface of the first through hole, A rotating device according to any one of claims 1 to 14.

16. The cam follower is rotatably attached to the second rotor. A rotating device according to any one of claims 1 to 15.

17. the second rotor has a second through hole, The cam follower rolls on an inner wall surface of the second through hole. A rotating device according to any one of claims 1 to 16.

18. the cam follower has a small diameter portion that contacts an inner wall surface of the second through hole and a large diameter portion that contacts the centrifugal element, The large diameter portion has an outer diameter that gradually increases toward the center in the thickness direction of the large diameter portion.

18. The rotation device of claim 17.

19. The centrifugal element is configured to rotate on its own axis when moving in a radial direction. A rotating device according to any one of claims 1 to 17.

20. Further comprising a first rolling member; the first rotor has a first guide surface and a second guide surface facing in a circumferential direction, the first rolling member is disposed between the first guide surface and the centrifugal element and configured to roll on the first guide surface by rotation of the centrifugal element.

20. The rotation device of claim 19.

21. The centrifugal element is configured to roll on the second guide surface.

21. The rotation device of claim 20.

22. An input member; an output member to which torque is transmitted from the input member; A rotation device according to any one of claims 1 to 21; A power transmission device comprising:

23. A rotatably arranged first rotating body; a centrifugal element supported so as to be movable in a radial direction relative to the first rotor; a fall prevention mechanism that prevents the centrifugal element from falling; Equipped with The centrifugal element has a first abutment surface and a second abutment surface that are spaced apart from each other in the axial direction, the first contact surface and the second contact surface contact the first rotating body, The fall prevention mechanism is configured by the first contact surface and the second contact surface. Rotating device.

24. A rotatably arranged first rotating body; a centrifugal element supported so as to be movable in a radial direction relative to the first rotor; a fall prevention mechanism that prevents the centrifugal element from falling; a second rotating body that is rotatable together with the first rotating body and that is arranged so as to be rotatable relative to the first rotating body; Equipped with the tipping prevention mechanism has a sliding member disposed between the centrifugal element and the second rotor; Rotating device.

25. A rotatably arranged first rotating body; a centrifugal element supported so as to be movable in a radial direction relative to the first rotor; a fall prevention mechanism that prevents the centrifugal element from falling; a second rotating body that is rotatable together with the first rotating body and that is arranged so as to be rotatable relative to the first rotating body; Equipped with the fall prevention mechanism has an elastic member disposed between the centrifugal element and the second rotor; Rotating device.

26. A rotatably arranged first rotating body; a centrifugal element supported so as to be movable in a radial direction relative to the first rotor; a fall prevention mechanism that prevents the centrifugal element from falling; a first rolling member; Equipped with The centrifugal element is configured to rotate on its own axis when moving in a radial direction, the first rotor has a first guide surface and a second guide surface facing in a circumferential direction, the first rolling member is disposed between the first guide surface and the centrifugal element and configured to roll on the first guide surface by rotation of the centrifugal element. Rotating device.

Images