JP2019019885A - damper - Google Patents

Abstract

To provide a damper which can be easily returned to an original position from a position at which a rotary element generates friction force, for example.SOLUTION: A damper according to one embodiment includes: a first rotary element (20); a second rotary element (10); a third rotary element (80); a protrusion (83) protruding from the third rotary element (80) and having a tilt surface (83b); and a turning body (94) having a rolling part (95) which is supported by the first rotary element (20) and can roll on the tilt surface (83b), and a lock part (96) which restricts rolling of the rolling part (95) in a first rolling direction (Dp2) on the tilt surface (83b) when the first rotary element (20) is rotated in a first rotation direction (Dp1) with respect to the second rotary element (10) and allows rolling of the rolling part (95) in a second rolling direction (Dn2) on the tilt surface (83b) when the first rotary element (20) is rotated in a second rotation direction (Dn1) with respect to the second rotary element (10).SELECTED DRAWING: Figure 4

Description

  Embodiments described herein relate generally to a damper.

  Conventionally, in a damper that alleviates rotational fluctuation between a first rotating element on the input side and a second rotating element on the output side, two surfaces facing the first rotating element in the axial direction are provided. A damper is known in which a second rotating element having an inclined surface and a friction element also having an inclined surface are arranged between two surfaces. The damper generates an axial force by sliding the inclined surfaces on each other, the relative rotation of the first and second rotating elements, and the first rotating element and the friction element. A frictional force (torque) that prevents relative rotation is provided (for example, Patent Document 1).

Special table 2008-528880 gazette

  However, in the above-described conventional technology, the first rotating element is formed with two surfaces on which the second rotating element and the friction element are disposed, so that the damper is likely to be enlarged in the axial direction. When one of the two surfaces is removed, the generated axial force pushes the first rotating element, the second rotating element, and the friction element away from each other, and the inclined surfaces exceed the desired range. May slide on each other. In this case, the maximum static frictional force between the inclined surfaces increases, and the first rotating element, the second rotating element, and the friction element are prevented from returning to their original positions.

  Accordingly, the present invention has been made in view of the above, and provides a damper that can easily return from a position where a rotating element generates a frictional force to an original position.

  As an example, the damper according to the embodiment of the present invention can rotate around the first rotation axis with respect to the first rotation element and the first rotation element that can rotate around the first rotation axis. A second rotating element, and positioned between the first rotating element and the second rotating element in a circumferential direction of the first rotating shaft, the first rotating element and the second rotating element; A first elastic member that elastically expands and contracts in the circumferential direction according to relative rotation with the first rotation element and the second rotation element in the axial direction of the first rotation axis A third rotating element positioned between and rotatable about the first rotating axis with respect to the first rotating element and the second rotating element; and from the third rotating element to the first rotating element Projecting toward the rotating element and moving in the first direction of rotation about the first axis of rotation. And a convex portion having an inclined surface approaching the rotating element, and supported by the first rotating element so as to be rotatable about a second rotating shaft that intersects the first rotating shaft, and is rotated on the inclined surface. A movable rolling portion and the second rotation on the inclined surface when the first rotating element rotates in the first rotating direction with respect to the second rotating element. Limiting rolling in a first rolling direction about an axis, the first rotating element rotates in a second rotating direction opposite to the first rotating direction relative to the second rotating element A rotating body having a lock portion that allows the rolling portion to roll in a second rolling direction opposite to the first rolling direction on the inclined surface. When the first rotating element rotates in the first rotating direction with respect to the second rotating element, the lock portion is restrained from rolling. Has been the rolling unit, presses the third rotating element by pressing said inclined surface to said second rotational element. Therefore, as an example, when the first rotating element rotates (returns) in the second rotating direction with respect to the second rotating element from the state in which the rolling part presses the inclined surface, the rolling part rolls. Possible, resulting in less rolling resistance. Therefore, the first to third rotating elements can easily return to the original position from the position where the frictional force is generated between the second rotating element and the third rotating element.

  For example, in the damper, one of the first rotating element and the second rotating element is rotated from the other rotating element of the first rotating element and the second rotating element in the axial direction. And a stopper for restricting separation from each other. Therefore, as an example, the first rotating element that supports the rotating body and the third rotating element having the convex portion are restricted from relatively rotating beyond a predetermined angle, and the rolling unit and The frictional resistance generated with the inclined surface is limited within a predetermined range. Therefore, the first to third rotating elements can easily return to the original position from the position where the frictional force is generated between the second rotating element and the third rotating element.

  In the damper, as an example, when the first rotation element rotates in the first rotation direction with respect to the second rotation element, the lock portion is arranged on the inclined surface. Rolling in the first rolling direction contacts the stopper and restricts rolling of the rolling part on the inclined surface in the first rolling direction. By contacting the part, the one rotating element is restricted from being separated from the other rotating element in the axial direction. Therefore, as an example, it is not necessary to provide a stopper at a position different from the lock portion, and the structure of the damper can be simplified.

  In the damper, as an example, when the first rotation element rotates in the first rotation direction with respect to the second rotation element, the lock portion is arranged on the inclined surface. By rolling in the first rolling direction, it comes into contact with another member and restricts rolling of the rolling part on the inclined surface in the first rolling direction. Therefore, as an example, the rolling of the rolling part in the first rolling direction of the rolling part on the inclined surface can be limited without a part such as a ratchet.

  In the damper, as an example, the lock portion includes a first position that allows the rolling portion to roll in the second rolling direction, and the rolling portion is in the second rolling direction. And the second position that restricts rolling to the second rotation axis is rotatable about the second rotation axis, and the rotating body moves the lock portion in the second position to the first position. A second elastic member that urges toward. Therefore, as an example, the lock unit is configured such that when the first rotation element rotates in the second rotation direction with respect to the second rotation element, the rolling unit rotates in the second rolling direction on the inclined surface. It is kept in a state that allows it to move. Therefore, the first to third rotating elements can easily return to the original position from the position where the frictional force is generated between the second rotating element and the third rotating element.

FIG. 1 is a cross-sectional view orthogonal to the rotation center of the damper according to the first embodiment. 2 is a cross-sectional view of the damper according to the first embodiment taken along line F2-F2 of FIG. FIG. 3 is a perspective view showing a part of the friction plate of the first embodiment. FIG. 4 is a cross-sectional view showing a part of the damper according to the first embodiment from the radial direction. FIG. 5 is a cross-sectional view illustrating a part of the damper in a state where the convex portion and the roller are in contact with each other according to the first embodiment from the radial direction. FIG. 6 is a cross-sectional view showing a part of the damper from the radial direction in a state where the stopper of the first embodiment is in contact with the rotation stopper. FIG. 7 is a cross-sectional view showing a part of the damper from the radial direction in a state where the driven plate of the first embodiment returns to the drive plate. FIG. 8 is a cross-sectional view showing a part of the damper according to the second embodiment from the radial direction. FIG. 9 is a cross-sectional view showing a part of the damper from the radial direction in a state where the stopper of the second embodiment is in contact with the cover plate. FIG. 10 is a cross-sectional view illustrating a part of the damper according to the third embodiment.

(First embodiment)
The first embodiment will be described below with reference to FIGS. 1 to 7. In the present specification, a plurality of expressions may be described for the constituent elements according to the embodiment and the description of the elements. The constituent elements and descriptions in which a plurality of expressions are made may be other expressions that are not described. Further, the constituent elements and descriptions that are not expressed in a plurality may be expressed in other ways that are not described.

  FIG. 1 is a cross-sectional view orthogonal to the rotation center Ax1 of the damper 100 according to the first embodiment. FIG. 2 is a sectional view showing the damper 100 of the first embodiment along the line F2-F2 of FIG. 1 is a cross-sectional view taken along line F1-F1 of FIG.

  The damper 100 is a flywheel damper that is mounted on a vehicle such as a four-wheeled vehicle and is provided between an engine as a drive source and a clutch. As shown in FIG. 2, the damper 100 includes a drive plate 10, a driven plate 20, a plurality of coil springs 30, a clutch disk 40, a pressure plate 50, a clutch cover 60, and a diaphragm spring 70. In the present embodiment, the drive plate 10 is an example of a second rotating element. The driven plate 20 is an example of a first rotating element. The coil spring 30 is an example of a first elastic member.

  The drive plate 10, the driven plate 20, the clutch disk 40, the pressure plate 50, and the clutch cover 60 are arranged in the axial direction so as to be rotatable around the rotation center Ax1. The rotation center Ax1 is an example of a first rotation axis.

  Hereinafter, the direction along the rotation center Ax1 is referred to as the axial direction of the rotation center Ax1, or simply the axial direction, and the direction orthogonal to the rotation center Ax1 is referred to as the radial direction of the rotation center Ax1, or simply the radial direction, and around the rotation center Ax1. The direction of rotation is referred to as the circumferential direction of the rotation center Ax1, or simply the circumferential direction. For further convenience, one axial direction indicated by the arrow X is referred to as the front, and the opposite direction of the arrow X is referred to as the rear. The front and rear designations in the present specification do not limit the position and orientation of each element in the vehicle, for example.

  The rotation (torque) of the drive source is transmitted to a drive target such as a wheel via the drive plate 10, the driven plate 20, the coil spring 30, and the clutch disk 40. The damper 100 attenuates rotation fluctuation (torque fluctuation) when transmitting rotation.

  For example, the damper 100 attenuates rotational fluctuations by the moment of inertia of the damper 100 and the elastic expansion and contraction of the coil spring 30. The coil spring 30 is elastically compressed according to the relative angle difference between the drive plate 10 and the driven plate 20.

  The coil spring 30 stores energy by being elastically compressed when the drive plate 10 is twisted in one of the rotational directions with respect to the driven plate 20. When the drive plate 10 is twisted (returned) to the other rotational direction with respect to the driven plate 20, the coil spring 30 releases the stored energy by elastically extending. Due to such elastic expansion and contraction of the coil spring 30, transmission of torque fluctuation (rotational fluctuation) from the drive plate 10 to the driven plate 20 is suppressed.

  The drive plate 10 is connected to a crankshaft 101 of the engine, for example. The drive plate 10 may be connected to other components such as a motor. The drive plate 10 includes a front plate 11 and a back plate 12.

  The front plate 11 has a front wall 11a and a peripheral wall 11b. The front wall 11a is formed in a substantially disk shape extending in the radial direction. The peripheral wall 11b is formed in a substantially cylindrical shape protruding rearward from the outer edge of the front wall 11a.

  The back plate 12 has a rear wall 12a and a convex wall 12b. The rear wall 12a is formed in a substantially disk shape spreading in the radial direction. The convex wall 12b is formed in a substantially cylindrical shape protruding rearward at a position spaced radially inward from the outer edge of the rear wall 12a.

  The rear end portion of the peripheral wall 11b of the front plate 11 and the outer edge of the back plate 12 are joined by welding or screwing, for example. As a result, the front plate 11 and the back plate 12 are fixed to each other and can rotate integrally around the rotation center Ax1.

  A space S extending in the circumferential direction is provided between the front wall 11 a of the front plate 11 and the rear wall 12 a of the back plate 12. The peripheral wall 11b of the front plate 11 covers the space S from the outside in the radial direction. The coil spring 30 is accommodated in the space S.

  As shown in FIG. 1, the coil spring 30 is disposed in the space S in a posture in which the winding center is substantially along the circumferential direction. A plurality of coil springs 30 are arranged in series in the space S. Further, a plurality of sheet members 31 are arranged in the space S. The sheet member 31 may also be referred to as a retainer.

  The back plate 12 is provided with a protrusion 12c. The protrusion 12c protrudes from the rear wall 12a toward the front plate 11, for example. Further, the front plate 11 is provided with a protrusion facing the protrusion 12c. The protrusion protrudes from the front wall 11a toward the back plate 12, for example.

  The drive plate 10 includes a plurality of pressing portions 32 that apply force to the coil spring 30 and receive force from the coil spring 30. The pressing portion 32 includes a protrusion of the front plate 11 and a protrusion 12 c of the back plate 12 that are axially opposed to each other. The pressing portions 32 are arranged at a plurality of locations at regular intervals in the circumferential direction. For example, the pressing parts 32 are arranged at intervals of 180 °.

  A plurality of coil springs 30 and a plurality of sheet members 31 are alternately arranged in the circumferential direction between the pressing portion 32 and the other pressing portion 32. The sheet member 31 is disposed between the two coil springs 30 adjacent in the circumferential direction and between the coil spring 30 and the pressing portion 32.

  The sheet member 31 is supported by the drive plate 10 or the driven plate 20 so as to be movable in the circumferential direction. The sheet member 31 is provided with a recess 31a. The recess 31a holds and guides the coil spring 30. For example, the sheet member 31 may be provided with a protrusion that holds and guides the coil spring 30.

  The driven plate 20 can rotate about the rotation center Ax1 with respect to the drive plate 10. As shown in FIG. 2, the driven plate 20 includes a center plate 21, a cover plate 22, and a flywheel 23.

  As shown in FIG. 1, the center plate 21 has a central wall 21a and a plurality of protrusions 21b. The central wall 21a is formed in a substantially disk shape that extends in the radial direction. The protrusion 21b protrudes radially outward from the outer edge of the central wall 21a. At least a part of the protrusion 21b is disposed in the space S.

  The driven plate 20 includes a plurality of pressing portions 33 that apply force to the coil spring 30 and receive force from the coil spring 30. The pressing part 33 includes a protrusion 21b. The pressing portions 33 are arranged at a plurality of locations at regular intervals in the circumferential direction. For example, the pressing portions 33 are arranged at intervals of 180 °.

  The pressing portion 32 of the drive plate 10 and the pressing portion 33 of the driven plate 20 are arranged so as to overlap in the axial direction in a state where there is no relative angular difference (= 0 °) between the drive plate 10 and the driven plate 20. Is done. Further, the pressing portion 32 and the pressing portion 33 are separated from each other. For example, a gap is provided in the axial direction between the projection of the front plate 11 and the projection 12 c of the back plate 12 and the projection 21 b of the center plate 21.

  By arranging the pressing portion 33 as described above, the plurality of coil springs 30 and the plurality of sheet members 31 are also positioned between the pressing portion 33 and the other pressing portions 33. The sheet member 31 is disposed between the two coil springs 30 adjacent in the circumferential direction and between the coil spring 30 and the pressing portion 33.

  The coil spring 30 and the sheet member 31 are located between the pressing portion 32 of the drive plate 10 and the pressing portion 33 of the driven plate 20 in the circumferential direction. When the drive plate 10 is twisted in one direction of rotation with respect to the driven plate 20, the pressing portion 32 of the drive plate 10 approaches the pressing portion 33 of the driven plate 20 and compresses the coil spring 30. Further, when the drive plate 10 is twisted (returned) in the rotational direction with respect to the driven plate 20, the pressing portion 32 moves away from the pressing portion 33 and extends the coil spring 30. In this manner, the coil spring 30 is elastically compressed and extended (expanded / contracted) in the circumferential direction in accordance with the relative rotation of the drive plate 10 and the driven plate 20.

  The coil spring 30 is elastically expanded and contracted between the drive plate 10 and the driven plate 20 according to the magnitude of torque fluctuation (rotational fluctuation) of the drive plate 10. The coil spring 30 suppresses transmission of torque fluctuation (rotational fluctuation) from the drive plate 10 to the driven plate 20 by the expansion and contraction.

  As shown in FIG. 2, the cover plate 22 is located between the center plate 21 and the flywheel 23 in the axial direction. The cover plate 22 has a rear wall 22a and an annular wall 22b. The rear wall 22a is formed in a substantially funnel shape (conical frustum shape) having a smaller diameter toward the front. The annular wall 22b is formed in a substantially annular shape extending radially outward from the outer edge of the rear wall 22a.

  The flywheel 23 has a rear wall 23a and an annular wall 23b. The rear wall 23a is formed in a substantially funnel shape with a smaller diameter toward the front. The annular wall 23b is formed in a substantially annular shape extending radially outward from the outer edge of the rear wall 23a. In the axial direction, the annular wall 23 b is thicker than the annular wall 22 b of the cover plate 22.

  The center wall 21 a of the center plate 21, the rear wall 22 a of the cover plate 22, and the rear wall 23 a of the flywheel 23 are joined together by bolts 24 at positions spaced radially inward from the coil spring 30 and the seat member 31. The Thereby, the center plate 21, the cover plate 22, and the flywheel 23 are fixed to each other and can rotate integrally. The center plate 21, the cover plate 22, and the flywheel 23 may be joined by other means such as welding.

  The flywheel 23 is supported on the crankshaft 101 by a bearing 25, for example. For this reason, the driven plate 20 can rotate around the rotation center Ax1 with respect to the drive plate 10 connected to the crankshaft 101.

  The clutch disk 40 is connected to an input shaft of the transmission, for example. The clutch disk 40 may be connected to other components. The clutch disk 40 is located between the annular wall 23 b of the flywheel 23 and the pressure plate 50.

  The clutch cover 60 is attached to the flywheel 23 and covers the clutch disc 40 and the pressure plate 50. The diaphragm spring 70 is supported by the clutch cover 60 and urges the pressure plate 50 toward the flywheel 23. The pressure plate 50 pushes the clutch disk 40.

  The pressure plate 50 presses the clutch disc 40 against the flywheel 23. Thereby, the driven plate 20 and the clutch disk 40 connected to the input shaft can transmit rotation to each other. The clutch disk 40 suppresses transmission of torque fluctuation (rotational fluctuation) from the flywheel 23 to the input shaft by, for example, elastic expansion and contraction of the damper spring 41.

  The damper 100 further includes a friction plate 80. The friction plate 80 is an example of a third rotating element. When relative rotation occurs between the drive plate 10 and the driven plate 20, the friction plate 80 moves between at least one of the drive plate 10 and the driven plate 20 according to the relative rotation. Causes friction. At this time, a resistance torque based on the frictional resistance acts on the drive plate 10 and the driven plate 20. Due to the friction between the friction plate 80 and at least one of the drive plate 10 and the driven plate 20, the kinetic energy corresponding to the relative rotation is converted into thermal energy, and the rotational fluctuation is attenuated.

  The friction plate 80 is disposed between the rear wall 12 a of the back plate 12 and the annular wall 22 b of the cover plate 22. The friction plate 80 is formed in a substantially annular shape extending in the radial direction. For example, the friction plate 80 is positioned in the radial direction by the convex wall 12b.

  FIG. 3 is a perspective view showing a part of the friction plate 80 of the first embodiment. FIG. 4 is a cross-sectional view showing a part of the damper 100 of the first embodiment from the radial direction. In FIG. 4 and FIGS. 5 to 7 described later, the back plate 12, the cover plate 22, and the friction plate 80 are schematically shown in a linearly stretched state. The friction plate 80 includes a base portion 81 and a friction material 82.

  As shown in FIG. 3, the base part 81 is formed in a substantially annular shape extending in the circumferential direction. As shown in FIG. 4, the base portion 81 is located between the rear wall 12 a of the back plate 12 and the annular wall 22 b of the cover plate 22 in the axial direction.

  The base part 81 has a first surface 81a and a second surface 81b. The first surface 81a is a substantially flat surface facing rearward in the axial direction. The first surface 81 a faces the annular wall 22 b of the cover plate 22. The second surface 81b is a substantially flat surface located on the opposite side of the first surface 81a and facing forward in the axial direction. The second surface 81b faces the rear wall 12a of the back plate 12.

  The friction material 82 is formed in a substantially annular shape extending in the radial direction. In the axial direction, the friction material 82 is thinner than the base portion 81. The friction material 82 is joined to the second surface 81b of the base portion 81 by, for example, adhesion. In other words, the friction material 82 is located between the base portion 81 and the rear wall 12a of the back plate 12.

  A plurality of convex portions 83 are provided on the friction plate 80. The base portion 81 and the plurality of convex portions 83 are provided integrally. The plurality of convex portions 83 may be separate parts from the base portion 81 of the friction plate 80. The base part 81 and the convex part 83 are made of a metal such as iron, for example.

  The convex portion 83 projects in the axial direction from the first surface 81 a of the base portion 81. In the present embodiment, the convex portion 83 protrudes from the base portion 81 toward the cover plate 22. In the present embodiment, a plurality of convex portions 83 having the same shape are arranged at intervals in the circumferential direction. The plurality of convex portions 83 are arranged at equal intervals in the circumferential direction.

  The plurality of convex portions 83 each have an end portion 83a and two inclined surfaces 83b. The end portion 83 a is an end portion of the convex portion 83 in the axial direction and faces the annular wall 22 b of the cover plate 22.

  The two inclined surfaces 83b are adjacent to the end 83a in the circumferential direction. The inclined surface 83b extends closer to the cover plate 22 as it is closer to the end 83a in the circumferential direction. According to another expression, the two inclined surfaces 83b extend so as to approach each other in the circumferential direction as they approach the end 83a in the axial direction. In this manner, the convex portion 83 is formed in a tapered shape that tapers toward the cover plate 22. The two inclined surfaces 83b extend in oblique directions Icw and Iccw between the circumferential direction (tangential direction) and the rear. The bus bar of the inclined surface 83b is along the radial direction.

  The friction plate 80 further has a sliding surface 86. In the present embodiment, the sliding surface 86 of the friction plate 80 is provided on the friction material 82 and faces the rear wall 12 a of the back plate 12. When the friction material 82 is not provided on the friction plate 80, the sliding surface 86 is provided on the second surface 81 b of the base portion 81.

  A plurality of openings 91 and a plurality of support portions 92 are provided in one rotating element of the drive plate 10 and the driven plate 20. In the present embodiment, the opening 91 and the support portion 92 are provided in the cover plate 22 of the driven plate 20 that is an example of the first rotating element.

  The opening 91 is provided in the annular wall 22b of the cover plate 22 and penetrates the annular wall 22b in the axial direction. In the present embodiment, the opening 91 is a notch opened outward in the radial direction of the annular wall 22b, but may be a hole closed in the radial direction.

  The support portion 92 is formed in a substantially cylindrical shape, and protrudes radially outward from the edge of the annular wall 22b that defines the opening 91. For this reason, the support portion 92 is disposed inside the opening 91. In the present embodiment, a plurality of openings 91 and a plurality of support portions 92 having the same shape are arranged at intervals in the circumferential direction. The plurality of openings 91 and the plurality of support portions 92 are arranged at equal intervals in the circumferential direction.

  Each of the plurality of support portions 92 extends along a central axis Ax2 that intersects the rotation center Ax1. The center axis Ax2 is an example of a second rotation axis. In the present embodiment, the center axis Ax2 is orthogonal to the rotation center Ax1 and is equal to the radial direction of the rotation center Ax1. The central axis Ax2 may extend in a direction that obliquely intersects the rotation center Ax1 forward or backward, for example. Center axes Ax2 of the plurality of support portions 92 are arranged at equal intervals in the circumferential direction and extend radially from the rotation center Ax1.

  The damper 100 further includes a plurality of rotating bodies 94. Each of the rotating bodies 94 includes a roller 95, a rotation stopper 96, and two leaf springs 97. The roller 95 is an example of a rolling part. The rotation stopper 96 is an example of a lock portion. The leaf spring 97 is an example of a second elastic member.

  The roller 95 is formed in a substantially cylindrical shape, and the support portion 92 is passed through the inside. Thereby, the rotating body 94 is supported by the support portion 92 of the driven plate 20 so as to be rotatable about the central axis Ax2.

  The rotation stopper 96 protrudes from the roller 95, for example, in a direction orthogonal to the central axis Ax2. The rotation stopper 96 may protrude from the roller 95 in the other direction. For example, the rotation stopper 96 protrudes toward the flywheel 23 and is separated from the flywheel 23 in a state where there is no relative angular difference between the drive plate 10 and the driven plate 20. The rotation stopper 96 is disposed on the opposite side of the friction plate 80 with respect to the annular wall 22 b of the cover plate 22.

  The rotation stopper 96 can rotate about the central axis Ax2 integrally with the roller 95. The distance between the rotation stopper 96 and the flywheel 23 changes as the rotation stopper 96 rotates about the central axis Ax2.

  The leaf spring 97 is attached to the roller 95 or the rotation stopper 96, for example. A roller 95 and a rotation stopper 96 are disposed between the two leaf springs 97. In the present embodiment, at least one of the two leaf springs 97 contacts the flywheel 23 in a state where there is no relative angular difference between the drive plate 10 and the driven plate 20. The two leaf springs 97 may be separated from the flywheel 23 in a state where there is no relative angular difference between the drive plate 10 and the driven plate 20.

  The plurality of rotating bodies 94 are arranged at equal intervals in the circumferential direction by being supported by the plurality of support portions 92. The plurality of rotating bodies 94 have the same shape. The diameter of the row of the rotating bodies 94 arranged in the circumferential direction (the average of the diameter of the radially inner end and the diameter of the radially outer end of the rotating body 94) is the convex 83 arranged in the circumferential direction. This is substantially the same as the diameter of the row (the average of the inner and outer diameters of the protrusion 83). The number of rotating bodies 94 is the same as the number of convex portions 83. The circumferential interval (angle) at which the plurality of rotating bodies 94 are arranged is substantially the same as the circumferential interval (angle) at which the plurality of convex portions 83 are arranged.

  The plurality of convex portions 83 and the plurality of rotating bodies 94 are alternately arranged in the circumferential direction. In other words, each of the rotating bodies 94 is located between the two convex portions 83. For example, two rotating bodies 94 may be disposed between the two convex portions 83. In a state where there is no relative angle difference between the drive plate 10 and the driven plate 20, the rotating body 94 is located at an intermediate position P 0 between the two convex portions 83.

  At the intermediate position P <b> 0, the two convex portions 83 are separated from the rotating body 94 located between the two convex portions 83 in the circumferential direction. At the intermediate position P0, the interval between the convex portion 83 and the rotating body 94 is uniform.

  A sliding surface 98 is provided on the other rotating element of the drive plate 10 and the driven plate 20. In the present embodiment, the sliding surface 98 is provided on the rear wall 12 a of the back plate 12 of the drive plate 10. The sliding surface 98 of the back plate 12 is formed substantially flat and faces rearward in the axial direction. The sliding surface 98 faces the sliding surface 86 of the friction plate 80.

  A stopper 99 is provided on the flywheel 23. The stopper 99 is, for example, an annular surface that is provided on the annular wall 23b of the flywheel 23 and extends in the radial direction. That is, the stopper 99 is located on the opposite side of the friction plate 80 with respect to the annular wall 22b. In other words, the annular wall 22 b is located between the stopper 99 and the friction plate 80. The roller 95 supported by the support portion 92 of the annular wall 22b, the convex portion 83 of the friction plate 80, and the stopper 99 are provided at substantially the same position in the radial direction. The stopper 99 is provided on the flywheel 23 to rotate integrally with the driven plate 20.

  The stopper 99 faces the annular wall 22b and the rotating body 94 and is separated from the annular wall 22b. Further, in a state where there is no relative angle difference between the drive plate 10 and the driven plate 20, the stopper 99 is separated from the rotation stop 96 of the rotating body 94.

  Hereinafter, with reference to FIG. 4 to FIG. 6, an example of the attenuation of the rotational fluctuation by the friction plate 80 will be described. FIG. 5 is a cross-sectional view illustrating a part of the damper 100 in a state where the convex portion 83 and the roller 95 of the first embodiment are in contact with each other from the radial direction. FIG. 6 is a cross-sectional view showing a part of the damper 100 in a state where the stopper 99 of the first embodiment is in contact with the rotation stopper 96 from the radial direction.

  In the damper 100, the drive plate 10 and the driven plate 20 relatively rotate according to the magnitude of engine-induced torque fluctuation (rotational fluctuation) generated in the drive plate 10. At this time, the driven plate 20 and the friction plate 80 rotate relatively in a direction in which the roller 95 of the rotating body 94 and the inclined surface 83b of the convex portion 83 approach each other.

  For example, the driven plate 20 rotates in the left direction (forward rotation direction) Dp <b> 1 in FIG. 5 with respect to the drive plate 10 and the friction plate 80. The forward rotation direction Dp1 is one direction around the rotation center Ax1, and is an example of a first rotation direction. Thereby, as shown in FIG. 5, the inclined surface 83 b of the convex portion 83 of the friction plate 80 and the roller 95 of the rotating body 94 supported by the driven plate 20 come into contact with each other. The inclined surface 83b with which the roller 95 comes into contact is inclined in a direction approaching the annular wall 22b of the cover plate 22 of the driven plate 20 toward the normal rotation direction Dp1.

  When the inclined surface 83b and the roller 95 are in contact with each other, the driven plate 20 further rotates in the normal rotation direction Dp1 with respect to the drive plate 10, so that the roller 95 further moves in the normal rotation direction Dp1 with respect to the convex portion 83. To do. At this time, the roller 95 rolls in one direction Dp2 around the central axis Ax2 on the inclined surface 83b due to friction between the roller 95 and the inclined surface 83b. The one direction Dp2 is an example of a first rolling direction.

  When the roller 95 rolls in one direction Dp2 around the central axis Ax2, the distance between the rotation stopper 96 and the stopper 99 of the flywheel 23 decreases. In other words, the rotation stopper 96 approaches the stopper 99.

  As the distance between the rotation stopper 96 and the stopper 99 decreases, one of the two leaf springs 97 of the rotating body 94 comes into contact with the stopper 99 and is elastically deformed. The other of the two leaf springs 97 is separated from the stopper 99.

  As shown in FIG. 6, when the relative rotation (twist) between the drive plate 10 and the driven plate 20 reaches a predetermined angle, the rotation stopper 96 that rolls together with the roller 95 contacts the stopper 99. In other words, when the driven plate 20 rotates in the normal rotation direction Dp1 with respect to the drive plate 10, the detent 96 is caused by the roller 95 rolling on the inclined surface 83b in one direction Dp2 around the central axis Ax2. , Contacts the stopper 99. The stopper 99 is an example of another member. The rotation stopper 96 is in contact with the stopper 99, thereby restricting rolling in one direction Dp2 around the central axis Ax2 of the roller 95 on the inclined surface 83b. As described above, the rotation stopper 96 limits the rolling (rotation, swinging) of the roller 95 within a predetermined range.

  Further, the stopper 99 is in contact with the rotation stopper 96, thereby supporting the annular wall 22 b provided with the support portion 92 in the axial direction and restricting the cover plate 22 from being separated from the drive plate 10 in the axial direction. Therefore, the convex portion 83 and the roller 95 whose rolling is restricted are fixed in the circumferential direction, and the inclined surface 83b and the roller 95 are engaged with each other.

  When the driven plate 20 further rotates in the normal rotation direction Dp1 with respect to the drive plate 10 while the roller 95 is rolling on the inclined surface 83b until the rotation is restricted by the rotation stop 96, the roller 95 is moved to the convex portion 83. To further move in the forward direction Dp1. For example, the roller 95 tends to move so as to move up the inclined surface 83b.

  More specifically, when the driven plate 20 rotates in the normal rotation direction Dp1 with respect to the drive plate 10, the roller 95 rolls on the inclined surface 83b and applies a circumferential force to the inclined surface 83b. The circumferential force is decomposed into a force along the inclined surface 83b and a force Fo1 orthogonal to the inclined surface 83b. The cover plate 22 is made of an elastic material such as metal. For this reason, the cover plate 22 can be elastically deformed so that the ring wall 22b moves backward by being pushed by the force Fo1. According to another expression, when the roller 95 rolls on the inclined surface 83b, the rotating body 94 and the cover plate 22 and the base portion 81 of the friction plate 80 can be separated from each other in the axial direction.

  As a result, a forward repulsive force Fo2 due to the elastic deformation of the cover plate 22 is applied to the inclined surface 83b and the roller 95. A frictional force Fr1 is generated between the inclined surface 83b and the roller 95 by the repulsive force Fo2 and the force Fo1.

  When the roller 95 rolls on the inclined surface 83b, the frictional force Fr1 is rolling resistance. However, when the rolling in the one direction Dp2 around the central axis Ax2 of the roller 95 reaches a predetermined angle, the rotation stopper 96 restricts the rolling of the roller 95 as described above. When the rolling of the roller 95 is restricted, the frictional force Fr1 becomes a frictional force generated by sliding and becomes larger than the rolling resistance. The frictional force Fr1 generates a resistance torque between the drive plate 10 and the driven plate 20, and torque fluctuation (rotational fluctuation) is reduced.

  The friction plate 80 is not fixed to the back plate 12 and can rotate about the rotation center Ax1 with respect to the drive plate 10 and the driven plate 20. For this reason, the sliding surface 86 of the friction plate 80 and the sliding surface 98 of the back plate 12 can slide in the circumferential direction.

  As described above, when the inclined surface 83b and the roller 95 are in contact with each other and the drive plate 10 and the driven plate 20 further rotate relative to each other, the roller 95 further moves in the normal rotation direction Dp1 with respect to the convex portion 83. To do. At this time, the convex portion 83 tends to move with respect to the roller 95 so that the inclined surface 83 b goes up the roller 95. That is, the friction plate 80 is pressed against the rear wall 12a of the back plate 12 by the force Fo1. As described above, the driven plate 20 rotates in the normal rotation direction Dp1 with respect to the drive plate 10, so that the roller 95 whose rolling is restricted by the rotation stopper 96 presses the inclined surface 83 b to slide the friction plate 80. 86 is pressed against the sliding surface 98 of the rear wall 12a.

  Further, the repulsive force Fo <b> 2 of the cover plate 22 described above is applied to the sliding surface 86 and the sliding surface 98. When the repulsive force Fo2 and the force Fo1 are applied to the sliding surfaces 86 and 98 and the drive plate 10 and the driven plate 20 are further rotated relative to each other, the sliding surface 86 and the sliding surface 98 are interposed between each other. A frictional force Fr2 is generated.

  As described above, the drive plate 10 and the driven plate 20 relatively rotate, so that the frictional force (hysteresis torque) Fr1 is generated between the inclined surface 83b and the roller 95 and between the sliding surfaces 86 and 98. , Fr2. Due to the frictional forces Fr1 and Fr2, resistance torque is generated between the drive plate 10 and the driven plate 20, energy is consumed by friction, and torque fluctuation (rotational fluctuation) is reduced.

  FIG. 7 is a cross-sectional view showing a part of the damper 100 in a state where the driven plate 20 of the first embodiment returns to the drive plate 10 from the radial direction. Due to the rotational fluctuation, the driven plate 20 repeatedly rotates relative to the drive plate 10 in the forward rotation direction Dp1 shown in FIGS. 5 and 6 and the reverse rotation direction Dn1 shown in FIG. The reverse rotation direction Dn1 is a direction opposite to the normal rotation direction Dp1, and is an example of a second rotation direction.

  As shown in FIG. 7, the driven plate 20 rotates in the reverse rotation direction Dn1 with respect to the drive plate 10 and the friction plate 80 in a state where the roller 95 contacts the inclined surface 83b and the stopper 99 contacts the rotation stopper 96. (Return). In other words, the friction plate 80 and the driven plate 20 rotate relatively in the direction in which the inclined surface 83b and the roller 95 move away from each other. Also at this time, frictional forces Fr1 and Fr2 are generated between the inclined surface 83b and the roller 95 and between the sliding surfaces 86 and 98 by the repulsive force Fo2, for example.

  The detent 96 restricts the roller 95 from rolling on the inclined surface 83b in one direction Dp2 around the central axis Ax2, but the roller 95 rolls on the inclined surface 83b in the reverse direction Dn2 around the central axis Ax2. It is permissible to do. The reverse direction Dn2 is a direction opposite to the one direction Dp2, and is an example of a second rolling direction. For this reason, when the driven plate 20 rotates in the reverse direction Dn1 with respect to the drive plate 10, the roller 95 rolls in the reverse direction Dn2 around the central axis Ax2 on the inclined surface 83b. At this time, the frictional force Fr1 generated between the roller 95 and the inclined surface 83b becomes rolling resistance, and becomes smaller than the frictional force Fr1 generated by sliding between the roller 95 and the inclined surface 83b whose rolling is restricted.

  Further, the repulsive force Fo2 is proportional to the amount of elastic deformation of the cover plate 22. However, in the present embodiment, the stopper 99 limits the elastic deformation of the cover plate 22 to a certain range. For this reason, the repulsive force Fo2 and the frictional force (friction resistance) Fr1 generated by the repulsive force Fo2 are limited to a certain range. As described above, even if the torque in the reverse rotation direction Dn1 is relatively small, the roller 95 can move down the inclined surface 83b.

  The roller 95 rolls in the reverse direction Dn2 around the central axis Ax2 on the inclined surface 83b. Further, the deformed leaf spring 97 biases the roller 95 in the reverse direction Dn2 around the central axis Ax2 by a restoring force. In this manner, the leaf spring 97 biases the roller 95 that has rolled in one direction Dp2 around the central axis Ax2 in the reverse direction Dn2 around the central axis Ax2 until the rotation stop 96 restricts the rotation. When the roller 95 rolls in the reverse direction Dn2, the rotation stopper 96 is separated from the stopper 99 of the flywheel 23.

  As shown in FIG. 4, the rotation stopper 96 has a first position P1 that allows the roller 95 to roll in the reverse direction Dn2 around the central axis Ax2 when the roller 95 rolls, and the roller 95 It can rotate around the central axis Ax2 to a second position P2 that restricts rolling in the reverse direction Dn2 around the central axis Ax2. In the first position P <b> 1, the rotation stopper 96 is separated from the stopper 99. In the second position P2, the rotation stopper 96 contacts the stopper 99.

  For example, when the roller 95 rolls in the reverse direction Dn2 around the central axis Ax2 due to inertia, the rotation stopper 96 may rotate to the second position P2. At this time, one of the two leaf springs 97 of the rotating body 94 comes into contact with the stopper 99 and elastically deforms. The leaf spring 97 that is elastically deformed urges the rotation stopper 96 at the second position P2 toward the first position P1 by a repulsive force. As described above, the rotation stopper 96 allows the roller 95 to roll in the reverse direction Dn2 around the central axis Ax2 on the inclined surface 83b when the driven plate 20 rotates in the reverse rotation direction Dn1 with respect to the drive plate 10. The state is returned to the state by the leaf spring 97.

  In the damper 100 according to the first embodiment described above, the detent 96 of the rotating body 94 is such that the roller 95 is on the inclined surface 83b when the driven plate 20 rotates in the normal rotation direction Dp1 with respect to the drive plate 10. Is restricted to roll in one direction Dp2 around the central axis Ax2, and when the driven plate 20 rotates in the reverse direction Dn1 with respect to the drive plate 10, the roller 95 rolls in the reverse direction Dn2 on the inclined surface 83b. Allow to do. When the driven plate 20 rotates in the normal rotation direction Dp1 with respect to the drive plate 10, the roller 95 whose rolling is restricted by the rotation stop 96 presses the friction plate 80 against the drive plate 10 by pressing the inclined surface 83b. That is, the roller 95 generates a larger frictional resistance when the driven plate 20 rotates in the forward rotation direction Dp1 with respect to the drive plate 10, but the driven plate 20 rotates in the reverse rotation direction Dn1 with respect to the drive plate 10. In some cases, a smaller rolling resistance is produced. Therefore, when the driven plate 20 rotates (returns) in the reverse rotation direction Dn1 with respect to the drive plate 10 from the state in which the roller 95 presses the inclined surface 83b, the roller 95 can roll and has a rolling resistance smaller than the frictional resistance. Produce. Accordingly, since the resistance generated between the roller 95 and the inclined surface 83b is kept low, the drive plate 10, the driven plate 20, and the friction plate 80 are separated from the roller 95 from the state in which the roller 95 and the inclined surface 83b are in contact with each other. The inclined surface 83b can be relatively rotated in a direction away from each other. Therefore, the drive plate 10, the driven plate 20, and the friction plate 80 are moved from the position where the frictional force Fr2 is generated between the friction plate 80 and the drive plate 10 to the original position where the rotating body 94 is located at the intermediate position P0. It can be easily restored.

  When the driven plate 20 rotates in the normal rotation direction Dp1 with respect to the drive plate 10, the roller 95 presses the inclined surface 83b, and the driven plate 20, the drive plate 10, and the friction plate 80 try to be separated from each other. However, the stopper 99 restricts one rotating element of the driven plate 20 and the drive plate 10 from being separated from the other rotating element in the axial direction. For this reason, the driven plate 20 that supports the rotating body 94 and the friction plate 80 having the convex portion 83 are restricted from rotating relative to each other beyond a predetermined angle, and the gap between the roller 95 and the inclined surface 83b is limited. The frictional resistance generated at is limited within a predetermined range. Since the resistance generated between the roller 95 and the inclined surface 83b is kept low, the drive plate 10, the driven plate 20, and the friction plate 80 are separated from the state in which the roller 95 and the inclined surface 83b are in contact with each other. 83b can rotate relative to each other in a direction away from each other. Therefore, the drive plate 10, the driven plate 20, and the friction plate 80 can easily return to the original positions from the position where the friction force Fr <b> 2 is generated between the drive plate 10 and the friction plate 80.

  When the driven plate 20 rotates in the normal rotation direction Dp1 with respect to the drive plate 10, the rotation stopper 96 comes into contact with the stopper 99 when the roller 95 rolls in one direction Dp2 on the inclined surface 83b. The rolling of the roller 95 in one direction Dp2 on 83b is limited. Thereby, the rotation stop 96 can restrict | limit rolling of the roller 95 in one direction Dp2 on the inclined surface 83b, without components, such as a ratchet. Further, the stopper 99 restricts the driven plate 20 from being separated from the drive plate 10 in the axial direction by contacting the detent 96. Thereby, it is not necessary to provide the stopper 99 at a position different from the rotation stopper 96, and the structure of the damper 100 can be simplified.

  The rotation stopper 96 has a first position P1 that allows the roller 95 to roll in the reverse direction Dn2 around the central axis Ax2, and a second position P2 that restricts the roller 95 from rolling in the reverse direction Dn2. In addition, it can be rotated around the central axis Ax2. The leaf spring 97 urges the detent 96 at the second position P2 toward the first position P1. Accordingly, the rotation stopper 96 is maintained in a state that allows the roller 95 to roll in the reverse direction Dn2 on the inclined surface 83b when the driven plate 20 rotates in the reverse direction Dn1 with respect to the drive plate 10. . Therefore, when the driven plate 20 rotates in the reverse direction Dn1 with respect to the drive plate 10 from the state in which the roller 95 pushes the inclined surface 83b, the roller 95 can roll and a rolling resistance smaller than the frictional resistance is generated. Since the resistance generated between the roller 95 and the inclined surface 83b is kept low, the drive plate 10, the driven plate 20, and the friction plate 80 are separated from the state in which the roller 95 and the inclined surface 83b are in contact with each other. 83b can rotate relative to each other in a direction away from each other. Therefore, the drive plate 10, the driven plate 20, and the friction plate 80 can easily return to the original positions from the position where the friction force Fr <b> 2 is generated between the drive plate 10 and the friction plate 80.

  As described above, the roller 95 can roll when the driven plate 20 and the friction plate 80 rotate in the reverse direction Dn2. Generally, lubrication with grease is performed to stabilize the frictional resistance, but in this embodiment, a small rolling resistance can be stably obtained without lubrication. Therefore, the roller 95 can be used in a dry environment without lubrication. The roller 95 may be lubricated with grease, for example.

(Second Embodiment)
Hereinafter, the second embodiment will be described with reference to FIGS. 8 and 9. In the following description of the plurality of embodiments, components having the same functions as the components already described are denoted by the same reference numerals as those described above, and further description may be omitted. . In addition, a plurality of components to which the same reference numerals are attached do not necessarily have the same functions and properties, and may have different functions and properties according to each embodiment.

  FIG. 8 is a cross-sectional view showing a part of the damper 100 according to the second embodiment from the radial direction. FIG. 9 is a cross-sectional view showing a part of the damper 100 in a state where the stopper 99 of the second embodiment is in contact with the cover plate 22 from the radial direction. 8 and 9, the back plate 12, the cover plate 22, and the friction plate 80 are schematically shown in a state of being straightened. The friction plate 80 includes a base portion 81 and a friction material 82.

  As shown in FIG. 8, in the second embodiment, the leaf spring 97 is provided not on the rotating body 94 but on the annular wall 22 b of the cover plate 22. The leaf spring 97 may be provided at another position such as the rotating body 94. An opening 91 is located between the two leaf springs 97 in the circumferential direction. Further, a detent 96 is located between the two leaf springs 97 in the direction of rotation around the central axis Ax2. At least one of the two leaf springs 97 always contacts the rotation stopper 96. Thereby, for example, when the rotating body 94 is located at the intermediate position P0, the rotation stopper 96 is maintained at a predetermined position. The rotation stopper 96 may be separated from the leaf spring 97.

  In the second embodiment, the stopper 99 protrudes from the ring wall 23 b of the flywheel 23 toward the ring wall 22 b of the cover plate 22. The stopper 99 is located, for example, on the radially inner side or the radially outer side of the rotating body 94. In a state where there is no relative angle difference between the drive plate 10 and the driven plate 20, the stopper 99 is separated from the annular wall 22b.

  As shown in FIG. 9, as in the first embodiment, the driven plate 20 further rotates in the normal rotation direction Dp1 with respect to the drive plate 10 while the inclined surface 83b and the roller 95 are in contact with each other. 95 further moves in the forward rotation direction Dp1 with respect to the convex portion 83. At this time, the roller 95 rolls in one direction Dp2 around the central axis Ax2 on the inclined surface 83b due to friction between the roller 95 and the inclined surface 83b.

  When the roller 95 rolls in one direction Dp2 around the central axis Ax2, the distance between the rotation stopper 96 and the annular wall 22b of the cover plate 22 decreases. In other words, the rotation stopper 96 approaches the annular wall 22b. By reducing the distance between the rotation stopper 96 and the ring wall 22b, the leaf spring 97 provided on the ring wall 22b is pushed by the rotation stopper 96 and is elastically deformed.

  When the relative rotation (twist) between the drive plate 10 and the driven plate 20 reaches a predetermined angle, the rotation stopper 96 that rolls integrally with the roller 95 is supported by the annular wall 22b via the leaf spring 97. In other words, when the driven plate 20 rotates in the normal rotation direction Dp1 with respect to the drive plate 10, the detent 96 is caused by the roller 95 rolling on the inclined surface 83b in one direction Dp2 around the central axis Ax2. , Supported by the ring wall 22b. The rotation stopper 96 is supported by the ring wall 22b, thereby restricting rolling in one direction Dp2 around the central axis Ax2 of the roller 95 on the inclined surface 83b. Thus, the rotation stopper 96 restricts the rolling of the roller 95 within a predetermined range.

  When the driven plate 20 further rotates in the normal rotation direction Dp1 with respect to the drive plate 10 while the roller 95 is rolling on the inclined surface 83b until the rotation is restricted by the rotation stop 96, the roller 95 is moved to the convex portion 83. Further in the forward rotation direction Dp1. At this time, the roller 95 moves so as to go up the inclined surface 83b.

  The circumferential force that the roller 95 moving in the forward rotation direction Dp1 acts on the inclined surface 83b generates a force Fo1 orthogonal to the inclined surface 83b. The cover plate 22 is pushed by the force Fo1 and elastically deforms so that the annular wall 22b moves rearward. According to another expression, when the roller 95 slides on the inclined surface 83b, the rotating body 94 and the cover plate 22 and the base portion 81 of the friction plate 80 are separated from each other in the axial direction.

  As a result, a forward repulsive force Fo2 due to the elastic deformation of the cover plate 22 is applied to the inclined surface 83b and the roller 95. A frictional force Fr1 is generated between the inclined surface 83b and the roller 95 by the repulsive force Fo2 and the force Fo1.

  When the roller 95 rolls on the inclined surface 83b, the frictional force Fr1 is rolling resistance. On the other hand, when the rolling of the roller 95 is restricted, the frictional force Fr1 becomes a frictional force generated by sliding and becomes larger than the rolling resistance. The frictional force Fr1 generates a resistance torque between the drive plate 10 and the driven plate 20, and torque fluctuation (rotational fluctuation) is reduced.

  When the relative rotation (twist) between the drive plate 10 and the driven plate 20 reaches a predetermined angle, the annular wall 22b of the cover plate 22 that is axially separated from the friction plate 80 contacts the stopper 99. The stopper 99 restricts the cover plate 22 from being separated from the drive plate 10 in the axial direction by supporting the annular wall 22b in the axial direction. For this reason, the convex part 83 and the roller 95 are fixed to the circumferential direction, and the inclined surface 83b and the roller 95 mutually engage.

  As described above, when the drive plate 10 and the driven plate 20 are further rotated in a state where the inclined surface 83b and the roller 95 are in contact with each other, the convex portion 83 has the inclined surface 83b rises above the roller 95 with respect to the roller 95. To move. The roller 95 whose rolling is restricted by the rotation stopper 96 presses the inclined surface 83b to press the sliding surface 86 of the friction plate 80 against the sliding surface 98 of the rear wall 12a. In addition to this, a repulsive force Fo2 is also applied, and a frictional force Fr2 is generated between the sliding surface 86 and the sliding surface 98.

  As described above, the drive plate 10 and the driven plate 20 relatively rotate, so that the frictional force (hysteresis torque) Fr1 is generated between the inclined surface 83b and the roller 95 and between the sliding surfaces 86 and 98. , Fr2. Due to the frictional forces Fr1 and Fr2, resistance torque is generated between the drive plate 10 and the driven plate 20, energy is consumed by friction, and torque fluctuation (rotational fluctuation) is reduced.

  The driven plate 20 rotates (returns) in the reverse direction Dn1 of FIG. 8 with respect to the drive plate 10 and the friction plate 80 with the roller 95 in contact with the inclined surface 83b and the cover plate 22 supporting the rotation stopper 96. . Thereby, the roller 95 rolls in the reverse direction Dn2 around the central axis Ax2 on the inclined surface 83b. At this time, the frictional force Fr1 generated between the roller 95 and the inclined surface 83b becomes rolling resistance, and becomes smaller than the frictional force Fr1 generated by sliding between the roller 95 and the inclined surface 83b whose rotation is restricted. Therefore, even if the torque in the reverse rotation direction Dn1 is relatively small, the roller 95 can move down the inclined surface 83b.

  The roller 95 rolls in the reverse direction Dn2 around the central axis Ax2 on the inclined surface 83b. Further, the deformed leaf spring 97 biases the roller 95 in the reverse direction Dn2 around the central axis Ax2 by a restoring force. As the roller 95 rolls in the reverse direction Dn <b> 2, the rotation stopper 96 is separated from the annular wall 22 b of the cover plate 22.

  As in the second embodiment described above, the stopper 99 may limit the driven plate 20 from being separated from the drive plate 10 in the axial direction by supporting the driven plate 20. Further, the rotation stopper 96 may be supported by the driven plate 20 to restrict the roller 95 from rolling in one direction Dp2 around the central axis Ax2 on the inclined surface 83b.

(Third embodiment)
The third embodiment will be described below with reference to FIG. FIG. 10 is a cross-sectional view showing a part of the damper 100 according to the third embodiment. As shown in FIG. 10, in the third embodiment, the plurality of rotating bodies 94 are provided on the drive plate 10.

  In the third embodiment, the support portion 92 is provided on the rear wall 12 a of the back plate 12 of the drive plate 10. The roller 95 of the rotating body 94 is supported by the support portion 92 so as to be rotatable around the central axis Ax2. That is, in the third embodiment, the drive plate 10 is an example of a first rotating element, and the driven plate 20 is an example of a second rotating element.

  On the other hand, in the third embodiment, the friction plate 80 is positioned in the radial direction by a cylindrical convex wall 23 c provided on the flywheel 23. The convex wall 23c protrudes forward from the annular wall 23b. The convex portion 83 of the friction plate 80 projects in the axial direction from the second surface 81 b of the base portion 81 toward the rear wall 12 a of the back plate 12.

  In the third embodiment, the stopper 99 is provided on the rear wall 12 a of the back plate 12 and rotates integrally with the drive plate 10. The stopper 99 faces the rotating body 94. The sliding surface 98 is provided on the annular wall 23 b of the flywheel 23. The friction material 82 is located between the base portion 81 and the sliding surface 98 of the annular wall 23b.

  As in the first and third embodiments described above, the rotating body 94 may be provided on either the drive plate 10 or the driven plate 20. The convex portion 83 protrudes from the base portion 81 of the friction plate 80 toward one of the drive plate 10 and the driven plate 20 provided with the rotating body 94.

  As mentioned above, although embodiment of this invention was illustrated, the said embodiment and modification are examples to the last, Comprising: It is not intending limiting the range of invention. The above-described embodiments and modifications can be implemented in various other forms, and various omissions, replacements, combinations, and changes can be made without departing from the scope of the invention. In addition, the configuration and shape of each embodiment and each modification may be partially exchanged.

  DESCRIPTION OF SYMBOLS 10 ... Drive plate (2nd rotation element, 1st rotation element), 20 ... Driven plate (1st rotation element, 2nd rotation element), 30 ... Coil spring (1st elastic member), 80 ... Friction plate (third rotation element), 83 ... convex part, 83b ... inclined surface, 94 ... rotating body, 95 ... roller (rolling part), 96 ... detent (lock part), 97 ... leaf spring (second Elastic member), 99 ... stopper, 100 ... damper, Ax1 ... rotation center (first rotation axis), Ax2 ... center axis (second rotation axis), Dp1 ... forward rotation direction (first rotation direction), Dp2 ... one direction (first rolling direction), Dn1 ... reverse rotation direction (second rotation direction), Dn2 ... reverse direction (second rolling direction), P1 ... first position, P2 ... second position.

Claims (5)

A first rotating element rotatable around a first axis of rotation;
A second rotating element rotatable about the first axis of rotation with respect to the first rotating element;
Positioned between the first rotating element and the second rotating element in the circumferential direction of the first rotating shaft, for relative rotation between the first rotating element and the second rotating element. And a first elastic member that elastically expands and contracts in the circumferential direction in response.
Located between the first rotating element and the second rotating element in the axial direction of the first rotating shaft, the first rotating element and the second rotating element with respect to the first rotating element. A third rotating element rotatable about the rotation axis;
A convex portion that protrudes from the third rotating element toward the first rotating element and has an inclined surface that approaches the first rotating element toward the first rotating direction around the first rotating shaft; ,
A rolling part supported by the first rotating element so as to be rotatable around a second rotating axis intersecting the first rotating axis and capable of rolling on the inclined surface; and the first rotating element The rolling portion rolls in the first rolling direction around the second rotation axis on the inclined surface when rotating in the first rotating direction with respect to the second rotating element. And when the first rotating element rotates in a second rotating direction opposite to the first rotating direction with respect to the second rotating element, the rolling part is A rotating body having a lock portion that allows rolling in a second rolling direction opposite to the first rolling direction;
Comprising
When the first rotation element rotates in the first rotation direction with respect to the second rotation element, the rolling part whose rolling is restricted by the lock part pushes the inclined surface and Pressing a third rotating element against the second rotating element;
damper.   Limiting that one rotating element of the first rotating element and the second rotating element is spaced apart from the other rotating element of the first rotating element and the second rotating element in the axial direction. The damper according to claim 1, further comprising a stopper. When the first rotating element rotates in the first rotating direction with respect to the second rotating element, the rolling unit moves the first rolling direction on the inclined surface when the first rotating element rotates in the first rotating direction. In contact with the stopper to limit rolling in the first rolling direction of the rolling part on the inclined surface,
The stopper restricts the one rotating element from being separated from the other rotating element in the axial direction by contacting the lock portion.
The damper according to claim 2.   When the first rotating element rotates in the first rotating direction with respect to the second rotating element, the rolling unit moves the first rolling direction on the inclined surface when the first rotating element rotates in the first rotating direction. The damper according to claim 1 which contacts other members by rolling to limit the rolling of the rolling part on the inclined surface in the first rolling direction. The lock part restricts the rolling part from rolling in the second rolling direction, and the first position allowing the rolling part to roll in the second rolling direction. Is pivotable about the second rotational axis to a second position
The rotating body includes a second elastic member that urges the lock portion at the second position toward the first position.
The damper according to claim 3 or 4.

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