JP2019019857A - 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 (100) according to one embodiment includes a first rotary element (20), a second rotary element (10), a third rotary element (80), a first protrusion (91) protruding from the first rotary element (20) and having a first tilt surface (91b), a second protrusion (83) protruding from the third rotary element (80) and having a second tilt surface (83b), and a stopper (97) integrally rotated with the one rotary element (20) and abutted to the one rotary element (20) in an axial direction so as to restrict separation of the one rotary element (20) from the other rotary element (10) in the axial direction. The second protrusion (83) presses the third rotary element (80) onto the second rotary element (10) with the second tilt surface (83b) pressed onto the first tilt surface (91b).SELECTED DRAWING: Figure 5

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, and the relative rotation of the first and second rotating elements and the relative of the first rotating element and the friction element. A frictional force (torque) that prevents normal 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, a damper according to an embodiment of the present invention includes a first rotating element that can rotate around a rotation axis, and a second rotating element that can rotate around the rotation axis with respect to the first rotating element. , Located between the first rotating element and the second rotating element in the circumferential direction of the rotating shaft, and according to relative rotation of the first rotating element and the second rotating element An elastic member that elastically expands and contracts in the circumferential direction, and is positioned between the first rotating element and the second rotating element in the axial direction of the rotating shaft, and the first rotating element and the second rotating element A third rotating element that is rotatable about the rotation axis with respect to the rotating element, and projects from the first rotating element toward the third rotating element, arranged in the circumferential direction, and in the axial direction A first end and a portion closer to the first end in the circumferential direction. A plurality of first convex portions each having a first inclined surface close to the third rotating element; and protruding from the third rotating element toward the first rotating element and arranged in the circumferential direction. A plurality of second protrusions each having a second end portion in the axial direction and a second inclined surface closer to the first rotation element as it is closer to the second end portion in the circumferential direction. And the first rotating element and the second rotating element rotate together with one rotating element and abut against the one rotating element in the axial direction so that the one rotating element becomes the first rotating element. A stopper that restricts the rotation of the first rotation element and the second rotation element from the other rotation element in the axial direction, and the plurality of second protrusions includes the first inclined surface. And the second inclined surface in a direction in which the second inclined surface approaches each other. Wherein the first rotating element rotates relative, since the second inclined surface is pushed to the first inclined surface is pressed against the third rotating element to the second rotating element. Therefore, as an example, the first rotating element having the first convex portion and the third rotating element having the second convex portion are restricted from relatively rotating beyond a predetermined angle. The Thereby, the frictional resistance generated between the first inclined surface and the second inclined surface is limited within a predetermined range, and the first rotating element and the third rotating element are the first inclined surface. The first inclined surface and the second inclined surface can be relatively rotated in a direction in which the first inclined surface and the second inclined surface are separated from each other. Therefore, the third rotating element can easily return to the original position from the position where the first rotating element generates a frictional force with the second rotating element.

  In the above damper, as an example, the third rotating element is configured such that the third rotating element and the first rotating element are relative to each other in a direction in which the first inclined surface and the second inclined surface approach each other. A contact surface that is pressed against the second rotating element by the plurality of second convex portions by rotating the first, and the friction coefficient of the second inclined surface is larger than the friction coefficient of the contact surface Low. Therefore, as an example, the frictional resistance generated between the first inclined surface and the second inclined surface is reduced, and the first rotating element and the third rotating element are the first inclined surface and the first inclined surface. The first inclined surface and the second inclined surface can be rotated relative to each other from the state in which the two inclined surfaces are in contact with each other. Therefore, the third rotating element can easily return to the original position from the position where the first rotating element generates a frictional force with the second rotating element.

  In the damper, as an example, the third rotating element and the plurality of second convex portions are integrally provided. Therefore, as an example, when the third rotating element and the first rotating element rotate relatively in the direction in which the first inclined surface and the second inclined surface approach each other, Damage to the second convex portion is suppressed.

  In the damper, as an example, the one rotating element is separated from the stopper by a first position, and the stopper is brought into contact with the stopper in the axial direction, and from the other rotating element than the first position. The third rotation element and the plurality of second convex portions are movable in a direction in which the first inclined surface and the second inclined surface approach each other. When the third rotation element and the first rotation element rotate relatively, the one rotation element is pushed from the first position to the second position. Therefore, as an example, the frictional force generated between the third rotating element and the second rotating element is changed by the movement of one rotating element, and the damper can attenuate the rotational fluctuation more smoothly.

  In the damper, as an example, the stopper comes into contact with a region where the first convex portion and the second convex portion are provided in the radial direction of the rotating shaft among the one rotating element. The one rotating element is restricted from being separated from the other rotating element in the axial direction. Therefore, as an example, bending of one rotating element is suppressed.

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 perspective view showing a part of the cover plate of the first embodiment. FIG. 5 is a cross-sectional view showing a part of the damper according to the first embodiment from the radial direction. FIG. 6 is a cross-sectional view showing a part of the damper in a state where the convex portions of the first embodiment are in contact with each other from the radial direction. FIG. 7 is a cross-sectional view illustrating a part of the damper in a state where the stopper according to the first embodiment is in contact with the cover plate from the radial direction. FIG. 8 is a cross-sectional view showing a part of the damper from the radial direction in a state where the drive plate of the first embodiment returns to the driven plate. FIG. 9 is a cross-sectional view showing a part of the damper according to the second embodiment.

(First embodiment)
The first embodiment will be described below with reference to FIGS. 1 to 8. 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 Ax 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 an 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 Ax. The rotation center Ax is an example of a rotation axis.

  Hereinafter, the direction along the rotation center Ax is referred to as the axial direction of the rotation center Ax, or simply the axial direction, and the direction orthogonal to the rotation center Ax is referred to as the radial direction of the rotation center Ax, or simply the radial direction, around the rotation center Ax. The direction of rotation is referred to as the circumferential direction of the rotation center Ax, 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 peripheral wall 12b. The rear wall 12a is formed in a substantially disk shape spreading in the radial direction. The peripheral wall 12b is formed in a substantially cylindrical shape protruding rearward 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 Ax.

  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 around the rotation center Ax 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 includes a rear wall 22a, an annular wall 22b, and a peripheral wall 22c. 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 peripheral wall 22c is formed in a substantially cylindrical shape protruding forward from the outer edge of the ring wall 22b.

  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 of the rotation center Ax, 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 by bolts 24 at positions spaced radially inward from the coil spring 30 and the seat member 31. Is done. 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. Therefore, the driven plate 20 can rotate around the rotation center Ax 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 peripheral wall 22c.

  FIG. 3 is a perspective view showing a part of the friction plate 80 of the first embodiment. FIG. 4 is a perspective view showing a part of the cover plate 22 of the first embodiment. FIG. 5 is a cross-sectional view showing a part of the damper 100 of the first embodiment from the radial direction. In FIG. 5 and FIGS. 6 to 8 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. 5, 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 convex portion 83 is an example of a second convex portion. 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 83a is an example of a second end. The inclined surface 83b is an example of a second inclined surface. The end portion 83 a is an end portion of the convex portion 83 in the axial direction and faces 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. The sliding surface 86 is an example of a contact surface. In the present embodiment, the sliding surface 86 of the friction plate 80 is provided on the friction material 82 and faces 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.

  The friction coefficient of the inclined surface 83 b of the convex portion 83 is lower than the friction coefficient of the sliding surface 86. For example, the friction coefficient of the material of the friction material 82 is higher than the friction coefficient of iron which is the material of the convex portion 83. The friction coefficient of the inclined surface 83b of the convex portion 83 may be lower than the friction coefficient of the sliding surface 86 by performing surface treatment or film formation on at least one of the inclined surface 83b and the sliding surface 86. .

  A plurality of convex portions 91 are provided on one rotating element of the drive plate 10 and the driven plate 20. The convex portion 91 is an example of a first convex portion. In this embodiment, the convex part 91 is provided in the driven plate 20 which is an example of a 1st rotation element.

  The convex portion 91 protrudes in the axial direction from the annular wall 22 b of the cover plate 22 which is a part of the driven plate 20 toward the base portion 81 of the friction plate 80. In the present embodiment, a plurality of convex portions 91 having the same shape are arranged at intervals in the circumferential direction. The plurality of convex portions 91 are arranged at equal intervals in the circumferential direction.

  The plurality of convex portions 91 each have an end portion 91a and two inclined surfaces 91b. The end portion 91a is an example of a first end portion. The inclined surface 91b is an example of a first inclined surface. The end portion 91 a is an end portion of the convex portion 91 in the axial direction and faces the base portion 81.

  The two inclined surfaces 91b are adjacent to the end portion 91a in the circumferential direction. The inclined surface 91b extends closer to the base portion 81 as it is closer to the end portion 91a in the circumferential direction. According to another expression, the two inclined surfaces 91b extend so as to approach each other in the circumferential direction as they approach the end portion 91a. Thus, the convex part 91 is formed in a taper shape that tapers toward the base part 81. The two inclined surfaces 91b extend in oblique directions Iccw and Icw between the circumferential direction (tangential direction) and the rear. The bus bar of the inclined surface 91b is along the radial direction.

  The diameter of the row of the convex portions 91 arranged in the circumferential direction (average of the inner diameter and the outer diameter of the convex portion 91) is the diameter of the row of the convex portions 83 arranged in the circumferential direction (the inner diameter and the outer diameter of the convex portion 83). And the average). The number of convex portions 91 is the same as the number of convex portions 83. The circumferential interval (angle) at which the plurality of convex portions 91 are arranged is substantially the same as the circumferential interval (angle) at which the plurality of convex portions 83 are arranged.

  The plurality of protrusions 83 and the plurality of protrusions 91 are alternately arranged in the circumferential direction. In other words, each of the convex portions 91 is located 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 convex portion 91 is located at an intermediate position P 0 between the two convex portions 83.

  At the intermediate position P0, the two convex portions 83 are separated from the convex portion 91 located between the two convex portions 83 in the circumferential direction. At the intermediate position P0, the distance between the convex portion 83 and the convex portion 91 is equal.

  A sliding surface 95 is provided on the other rotating element of the drive plate 10 and the driven plate 20. In the present embodiment, the sliding surface 95 is provided on the rear wall 12 a of the back plate 12 of the drive plate 10. The sliding surface 95 of the back plate 12 is substantially flat and faces rearward in the axial direction. The sliding surface 95 faces the sliding surface 86 of the friction plate 80.

  As shown in FIG. 2, a stopper 97 is provided on the flywheel 23. The stopper 97 is, for example, a protrusion that protrudes from the ring wall 23 b of the flywheel 23 toward the ring wall 22 b of the cover plate 22. That is, the stopper 97 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 97 and the friction plate 80. The convex portion 91 of the annular wall 22b, the convex portion 83 of the friction plate 80, and the stopper 97 are provided at substantially the same position in the radial direction. In a state where there is no relative angle difference between the drive plate 10 and the driven plate 20, the stopper 97 is separated from the annular wall 22b.

  The stopper 97 is provided on the flywheel 23 to rotate integrally with the driven plate 20. That is, in this embodiment, the driven plate 20 is an example of one rotating element.

  Hereinafter, with reference to FIG. 5 to FIG. 7, an example of the attenuation of rotational fluctuations by the friction plate 80 will be described. FIG. 6 is a cross-sectional view showing a part of the damper 100 in a state where the convex portion 83 and the convex portion 91 of the first embodiment are in contact with each other from the radial direction. FIG. 7 is a cross-sectional view showing a part of the damper 100 in a state in which the stopper 97 of the first embodiment is in contact with the cover plate 22 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 inclined surface 91b of the convex portion 91 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) D <b> 1 in FIG. 6 with respect to the drive plate 10 and the friction plate 80. Thereby, as shown in FIG. 6, the inclined surface 83 b of the convex portion 83 of the friction plate 80 and the inclined surface 91 b of the convex portion 91 of the driven plate 20 come into contact with each other.

  With the inclined surfaces 83b and 91b in contact with each other, the drive plate 10 and the driven plate 20 further rotate relative to each other, whereby the convex portion 91 further moves in the normal rotation direction D1 with respect to the convex portion 83. The convex portion 91 moves so that the inclined surface 91b rises above the inclined surface 83b.

  More specifically, when the driven plate 20 rotates in the normal rotation direction D1 with respect to the drive plate 10, the inclined surface 91b applies a circumferential force to the inclined surface 83b. The circumferential force is decomposed into a force along the inclined surfaces 83b and 91b and a force Fo1 orthogonal to the inclined surfaces 83b and 91b. The cover plate 22 is made of an elastic material such as metal. For this reason, 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 inclined surface 91b slides on the inclined surface 83b, the convex portion 91 and the cover plate 22 and the base portion 81 of the friction plate 80 are separated from each other in the axial direction.

  Thereby, the repulsive force Fo2 to the front accompanying the elastic deformation of the cover plate 22 is applied to the inclined surface 83b and the inclined surface 91b. The repulsive force Fo2 and the force Fo1 generate a frictional force Fr1 when the inclined surface 83b and the inclined surface 91b slide. 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 around the rotation center Ax with respect to the drive plate 10 and the driven plate 20. Therefore, the sliding surface 86 of the friction plate 80 and the sliding surface 95 of the back plate 12 can slide in the circumferential direction.

  As described above, when the drive plate 10 and the driven plate 20 are further rotated with the inclined surfaces 83b and 91b in contact with each other, the convex portion 91 further moves in the normal rotation direction D1 with respect to the convex portion 83. At this time, the convex part 83 moves with respect to the convex part 91 so that the inclined surface 83b goes up the inclined surface 91b. 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 convex portion 83 is configured so that the friction plate 80 and the driven plate 20 are relatively rotated in the direction in which the inclined surfaces 83b and 91b approach each other, and the inclined surface 83b is pushed by the inclined surface 91b. The sliding surface 86 is pressed against the sliding surface 95 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 95. When the repulsive force Fo2 and the force Fo1 are applied to the sliding surfaces 86 and 95 and the drive plate 10 and the driven plate 20 further rotate relative to each other, the sliding surface 86 and the sliding surface 95 are interposed between them. A frictional force Fr2 is generated.

  As described above, the drive plate 10 and the driven plate 20 relatively rotate, so that frictional force (hysteresis torque) Fr1, between the inclined surfaces 83b and 91b and between the sliding surfaces 86 and 95 is obtained. Fr2 is generated. 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.

  As shown in FIG. 7, when the relative rotation (twist) between the drive plate 10 and the driven plate 20 reaches a predetermined angle, the ring wall 22 b of the cover plate 22 that is axially separated from the friction plate 80 is brought into contact with the stopper 97. Abut. The stopper 97 abuts on the region of the annular wall 22b where the convex portions 83 and 91 are provided in the radial direction. In other words, the stopper 97 is an annular region extending in the circumferential direction and located between at least the radially inner end and the radially outer end of each of the convex portions 83 and 91 in the annular wall 22b. Abut.

  The stopper 97 is in contact with the annular wall 22b in the axial direction, thereby supporting the annular wall 22b in the axial direction and restricting the cover plate 22 from being separated from the drive plate 10 in the axial direction. For this reason, the convex part 83 and the convex part 91 are fixed to the circumferential direction, and the inclined surface 83b and the inclined surface 91b mutually engage.

  As shown in FIG. 5, when there is no relative angle difference between the drive plate 10 and the driven plate 20, the ring wall 22b of the cover plate 22 of the driven plate 20 is at the first position P1 in the axial direction. To position. When the convex portion 91 is located at the intermediate position P0, the cover plate 22 is located at the first position P1. The cover plate 22 is separated from the stopper 97 at the first position P1.

  As shown in FIG. 7, 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 of the driven plate 20 Located at position P2. In the second position P2, the annular wall 22b of the cover plate 22 is in contact with the stopper 97 and is farther from the rear wall 12a of the back plate 12 of the drive plate 10 than in the first position P1.

  The friction plate 80 pushes the cover plate 22 from the first position P1 to the second position P2 by the relative rotation of the friction plate 80 and the driven plate 20 in the direction in which the inclined surfaces 83b and 91b approach each other. Thereby, the cover plate 22 moves in the axial direction from the first position P1 to the second position P2.

  FIG. 8 is a cross-sectional view showing a part of the damper 100 in a state where the drive plate 10 of the first embodiment returns to the driven plate 20 from the radial direction. Due to the rotational fluctuation, the drive plate 10 and the driven plate 20 repeatedly rotate relative to each other in the forward rotation direction D1 shown in FIGS. 6 and 7 and the reverse rotation direction D2 shown in FIG.

  As shown in FIG. 8, for example, the driven plate 20 rotates (returns) in the reverse rotation direction D2 with respect to the drive plate 10 and the friction plate 80 in a state where the cover plate 22 is positioned at the second position P2. In other words, the friction plate 80 and the driven plate 20 relatively rotate in the direction in which the inclined surfaces 83b and 91b move away from each other. Also at this time, frictional forces Fr1 and Fr2 are generated between the inclined surfaces 83b and 91b and between the sliding surfaces 86 and 95 by the repulsive force Fo2.

  The repulsive force Fo2 is proportional to the amount of elastic deformation of the cover plate 22. However, in the present embodiment, the stopper 97 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.

  Further, since the friction coefficient of the inclined surface 83b of the convex portion 83 is lower than the friction coefficient of the sliding surface 86, when the driven plate 20 rotates in the reverse rotation direction D2 with respect to the drive plate 10, the inclined surfaces 83b and 91b The generated frictional force Fr1 is reduced. As described above, even if the torque in the reverse rotation direction D2 is relatively small, the convex portion 91 can move so that the inclined surface 91b moves down the inclined surface 83b. As the inclined surfaces 83b and 91b slide, the cover plate 22 returns from the second position P2 to the first position P1 in the axial direction.

  In the damper 100 according to the first embodiment described above, when the friction plate 80 and the driven plate 20 relatively rotate in the direction in which the inclined surface 91b and the inclined surface 83b approach each other, the plurality of convex portions 83 are A force Fo1 is generated in a direction in which the friction plate 80 is pressed against the drive plate 10. The force Fo1 tends to separate the driven plate 20 from the drive plate 10 in the axial direction. However, the stopper 97 is in contact with the driven plate 20 in the axial direction, thereby limiting the driven plate 20 from being separated from the drive plate 10 in the axial direction. For this reason, the driven plate 20 having the convex portion 91 and the friction plate 80 having the convex portion 83 are restricted from rotating relatively beyond a predetermined angle. Thus, the frictional force Fr1 generated between the inclined surface 91b and the inclined surface 83b is limited within a predetermined range, and the driven plate 20 and the friction plate 80 are in a state where the inclined surface 91b and the inclined surface 83b are in contact with each other. Therefore, the inclined surface 91b and the inclined surface 83b can be relatively rotated in the reverse rotation direction D2 away from each other. Therefore, the friction plate 80 and the driven plate 20 change from the state in which the frictional forces Fr1 and Fr2 are generated between the drive plate 10, the driven plate 20, and the friction plate 80 to the state in which the convex portion 91 is located at the intermediate position P0. It can be easily restored.

  The friction coefficient of the inclined surface 83 b is lower than the friction coefficient of the sliding surface 86. As a result, the frictional force Fr1 generated between the inclined surface 91b and the inclined surface 83b is reduced, and the driven plate 20 and the friction plate 80 are moved from the state where the inclined surface 91b and the inclined surface 83b are in contact with each other. And the inclined surface 83b can rotate relative to each other in the reverse rotation direction D2. Therefore, the friction plate 80 and the driven plate 20 change from the state in which the frictional forces Fr1 and Fr2 are generated between the drive plate 10, the driven plate 20, and the friction plate 80 to the state in which the convex portion 91 is located at the intermediate position P0. It can be easily restored.

  When the friction plate 80 and the driven plate 20 are relatively rotated in a direction in which the inclined surface 91b and the inclined surface 83b approach each other, the convex portion 83 and the convex portion 91 come into contact with each other. Since the friction plate 80 and the plurality of convex portions 83 are provided integrally, the friction plate 80 and the convex portions 83 are prevented from being damaged by the contact.

  The driven plate 20 is movable to a first position P1 that is separated from the stopper 97, and a second position P2 that is in axial contact with the stopper 97 and that is farther from the drive plate 10 than the first position P1. It is. When the friction plate 80 and the driven plate 20 rotate relatively in the forward rotation direction D1 in which the inclined surface 91b and the inclined surface 83b approach each other, the forces Fo1 and Fo2 with which the inclined surface 91b and the inclined surface 83b are pressed are frictional. The plate 80 is pressed against the drive plate 10. However, when the driven plate 20 is located between the first position P1 and the second position P2, the force Fo1 is reduced by the movement of the driven plate 20 from the first position P1 to the second position P2. The Therefore, the frictional force Fr2 generated between the friction plate 80 and the drive plate 10 when the driven plate 20 is located between the first position P1 and the second position P2 is caused by the driven plate 20 being the second position. Is smaller than the frictional force Fr2 generated between the friction plate 80 and the drive plate 10 in the case of the position P2. As described above, the frictional force Fr2 generated between the friction plate 80 and the drive plate 10 changes, so that the damper 100 can attenuate the rotational fluctuation more smoothly.

  For example, when the position where the stopper 97 contacts the driven plate 20 and the position where the protrusions 83 and 91 are provided are displaced in the radial direction, the force by which the protrusion 91 presses the friction plate 80 against the drive plate 10 is There is a possibility that the driven plate 20 bends with the portion in contact with the stopper 97 as a fulcrum. However, in the present embodiment, the stopper 97 abuts the region of the driven plate 20 where the convex portions 83 and 91 are provided in the radial direction, so that the driven plate 20 is separated from the drive plate 10 in the axial direction. Limit. Thereby, it is suppressed that the driven plate 20 bends.

(Second Embodiment)
Hereinafter, the second embodiment will be described with reference to FIG. In the following description of the embodiment, components having the same functions as those 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. 9 is a cross-sectional view showing a part of the damper 100 according to the second embodiment. As shown in FIG. 9, in the second embodiment, the plurality of convex portions 91 are provided on the drive plate 10. That is, in the second 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.

  The convex portion 91 protrudes in the axial direction from the rear wall 12 a of the back plate 12 of the drive plate 10 toward the base portion 81 of the friction plate 80. On the other hand, 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.

  As in the first embodiment, the stopper 97 is provided on the flywheel 23 and rotates integrally with the driven plate 20. That is, also in the second embodiment, the driven plate 20 is an example of one rotating element.

  In the second embodiment, the sliding surface 95 is provided on the annular wall 22 b of the cover plate 22 of the driven plate 20. The friction material 82 is located between the base portion 81 and the sliding surface 95 of the annular wall 22b.

  As in the first and second embodiments described above, the convex portion 91 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 convex portion 91.

  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 (elastic member), 80 ... Friction plate ( (Third rotation element), 83 ... convex portion (second convex portion), 83a ... end portion (second end portion), 83b ... inclined surface (second inclined surface), 86 ... sliding surface (contact) Surface), 91 ... convex portion (first convex portion), 91a ... end portion (first end portion), 91b ... inclined surface (first inclined surface), 97 ... stopper, 100 ... damper, Ax ... rotation Center (rotation axis), P1... First position, P2.

Claims (5)

A first rotating element rotatable around a rotation axis;
A second rotating element rotatable about the rotation axis with respect to the first rotating element;
It is located between the first rotating element and the second rotating element in the circumferential direction of the rotating shaft, and according to the relative rotation of the first rotating element and the second rotating element, An elastic member that elastically expands and contracts in the circumferential direction;
It is located between the first rotating element and the second rotating element in the axial direction of the rotating shaft, and can rotate around the rotating axis with respect to the first rotating element and the second rotating element. A third rotating element,
Projecting from the first rotating element toward the third rotating element, arranged in the circumferential direction, and the closer to the first end in the circumferential direction, the closer to the first end in the circumferential direction, A plurality of first convex portions each having a first inclined surface close to the third rotating element;
Projecting from the third rotating element toward the first rotating element, arranged in the circumferential direction, the second end in the axial direction, and the closer to the second end in the circumferential direction, A plurality of second convex portions each having a second inclined surface close to the first rotating element;
The first rotating element and the second rotating element rotate integrally with one rotating element, and the one rotating element comes into contact with the one rotating element in the axial direction, so that the one rotating element becomes the first rotating element. A stopper for limiting the axial separation from the other rotating element of the element and the second rotating element;
Comprising
In the plurality of second convex portions, the third rotating element and the first rotating element relatively rotate in a direction in which the first inclined surface and the second inclined surface approach each other, The second inclined surface is pressed against the first inclined surface by pressing the third rotating element against the second rotating element;
damper. The third rotating element rotates relative to the third rotating element and the first rotating element in a direction in which the first inclined surface and the second inclined surface approach each other. A contact surface pressed against the second rotating element by a plurality of second convex portions,
A friction coefficient of the second inclined surface is lower than a friction coefficient of the contact surface;
The damper according to claim 1.   The damper according to claim 2, wherein the third rotating element and the plurality of second convex portions are integrally provided. The one rotational element is separated from the stopper by a first position, and the stopper is in contact with the stopper in the axial direction, and the second position is farther from the other rotational element than the first position; Can be moved to
The third rotating element and the plurality of second convex portions include the third rotating element and the first rotating element in a direction in which the first inclined surface and the second inclined surface approach each other. The one rotation element is pushed from the first position to the second position.
The damper according to claim 1.   The stopper is in contact with a region where the first convex portion and the second convex portion are provided in the radial direction of the rotating shaft among the one rotating element, so that the one rotating element is The damper according to claim 1, wherein the damper is limited from being separated from the other rotating element in the axial direction.

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