JP2018076911A - damper - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a damper which can be further downsized, for example, in an axial direction.SOLUTION: A damper comprises: a first rotary element including a first end wall; a second rotary element including a second end wall which is arranged at only one of rotating shafts with respect to the first end wall; an elastic member which elongates and contracts in a peripheral direction according to relative rotation between the first rotary element and the second rotary element; and a third rotary element having an annular intermediate wall which is sandwiched between the first end wall and the second end wall, and a plurality of first inclined faces which are provided on the intermediate wall at intervals in the peripheral direction, and are formed along an oblique direction between the peripheral direction and the axial direction. One of the first end wall and the second end wall has a plurality of second inclined faces which are provided at intervals in the peripheral direction, located between the two first inclined faces, and formed along the oblique direction. Friction resistance torque is generated between the other of the first end wall and the second end wall, and the intermediate wall, accompanied by slides or the engagement of the first inclined faces and the second inclined faces.SELECTED DRAWING: Figure 2

Description

  The present invention relates 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, the first rotating element is provided with two walls facing each other in the axial direction. A second rotating element having a first inclined surface (wedge) and a friction element having a second inclined surface (wedge) facing the first inclined surface are disposed between the two walls. And by sliding or engaging the first inclined surface and the second inclined surface, between the first rotating element and the second rotating element and between the first rotating element and the friction element. There is known a damper configured to generate a resistance torque therebetween (for example, Patent Document 1).

Japanese Patent No. 4874995

  However, in the above prior art, the second rotating element and the friction element are sandwiched in the axial direction by the two walls of the first rotating element. For this reason, there is a problem that the damper is easily increased in size in the axial direction by the two walls.

  Then, one of the subjects of this invention is obtaining the damper which can be reduced in size by an axial direction, for example.

  The damper of the present invention rotates around the rotation axis, includes a first rotation element including a first end wall intersecting the rotation axis, rotates around the rotation axis, intersects the rotation axis, and A second rotating element including a second end wall provided on only one of the rotating shafts with respect to the end wall, and interposed between the first rotating element and the second rotating element, An elastic member that elastically expands and contracts in the circumferential direction of the rotating shaft in response to relative rotation between the first rotating element and the second rotating element; An annular intermediate wall that intersects the axis and is sandwiched between the first end wall and the second end wall, and is provided on the intermediate wall with a spacing in the circumferential direction, A third rotating element having a plurality of first inclined surfaces along an oblique direction between the axial direction, and the first end wall and One of the second end walls is provided with an interval in the circumferential direction and has a plurality of second inclined surfaces located between the two first inclined surfaces and along the oblique direction. As the first inclined surface and the second inclined surface slide or engage, friction occurs between the other of the first end wall and the second end wall and the intermediate wall. Resistance torque is generated.

  In the damper, when the first inclined surface provided in the intermediate wall and the second inclined surface provided in the first end wall and the second end wall slide or engage with each other. A structure in which a frictional resistance torque is generated between the other of the first end wall and the second end wall and the intermediate wall can be configured without being sandwiched between two walls of one rotating element. Therefore, for example, the axial length of the damper can be further shortened.

  In addition, the damper includes, for example, a first peripheral wall protruding in the axial direction from the peripheral edge of the first end wall toward the second end wall, and the peripheral edge of the second end wall. A second peripheral wall protruding in the axial direction toward the first end wall. Therefore, according to such a damper, for example, the first peripheral wall or the second peripheral wall is compared with a configuration in which the first peripheral wall and the second peripheral wall constituting the gap overlap in the radial direction and protrude in the same direction. The length of the peripheral wall, and thus the length of the damper in the axial direction can be made shorter.

  Further, in the damper, for example, provided in one of the first peripheral wall and the second peripheral wall, a radial gap of the rotating shaft between the first peripheral wall and the second peripheral wall is provided. A first sealing member for sealing is provided. Therefore, according to such a damper, for example, the leakage of the lubricating oil from the radial gap is easily suppressed by the first seal member that seals the radial gap.

  In the damper, for example, a third peripheral wall projecting in the axial direction from one to the other of the first end wall and the second end wall, the first end wall, and the first end wall A second seal member that seals the gap in the axial direction between the other end wall of the second end wall and the tip of the third peripheral wall. Therefore, according to such a damper, for example, the leakage of the lubricating oil from the axial gap is easily suppressed by the second seal member that seals the axial gap.

FIG. 1 is a schematic and exemplary cross-sectional view orthogonal to the rotation center of the damper according to the embodiment. 2 is a cross-sectional view taken along the line II-II in FIG. FIG. 3 is a schematic and exemplary perspective view of a part of the third rotating element of the embodiment. FIG. 4 is a schematic and exemplary perspective view of a part of the second rotating element of the embodiment. Drawing 5 is a side view seen from the diameter direction of the 2nd rotation element of the embodiment, and the 3rd rotation element, and is the mimetic diagram which extended the annular shape in the shape of a straight line. FIG. 6 is a cross-sectional view of the damper of the first modification at the same position as FIG. FIG. 7 is a cross-sectional view of the damper of the second modified example at the same position as FIG.

  Hereinafter, exemplary embodiments of the present invention are disclosed. The configuration of the embodiment shown below, and the operation and result (effect) brought about by the configuration are examples. The present invention can be realized by configurations other than those disclosed in the following embodiments. According to the present invention, it is possible to obtain at least one of various effects (including derivative effects) obtained by the configuration.

  In each figure, directions are shown for convenience. An arrow X indicates the axial direction (backward, first direction) of the rotation center Ax. Hereinafter, the axial direction of the rotation center Ax is simply referred to as the axial direction, the radial direction of the rotation center Ax is simply referred to as the radial direction, and the circumferential direction of the rotation center Ax is simply referred to as the circumferential direction. Further, regarding the axial direction, the left side in FIG. 2 is referred to as the front side, and the right side in FIG. The rotation center Ax is an example of a rotation axis.

(Outline of configuration and function of damper 100)
1 is a cross-sectional view orthogonal to the rotation center Ax of the damper 100, and FIG. 2 is a cross-sectional view taken along the line II-II in FIG. 1 is a cross-sectional view taken along the line II of FIG.

  The damper 100 is, for example, a flywheel damper, and is provided between an engine as a drive source and a clutch, and reduces rotational fluctuation (torque fluctuation). The damper 100 can reduce rotational fluctuation by the moment of inertia and the elastic expansion and contraction of the elastic member.

  The damper 100 includes a drive plate 10, a driven plate 20, and a coil spring 30. The rotation (torque) of the drive source is transmitted to a drive target such as a wheel via the drive plate 10 and the driven plate 20.

  The coil spring 30 is elastically compressed according to the relative angle difference between the drive plate 10 and the driven plate 20. When the drive plate 10 is twisted in one of the rotational directions relative to the driven plate 20, the coil spring 30 is twisted in the other direction (when returning). It releases by elastically stretching. In addition, when the drive plate 10 is twisted in the other direction of rotation relative to the driven plate 20, the coil spring 30 is twisted (returns) to the energy stored by being elastically compressed. In this case, it is released by elastically stretching. 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 an example of a first rotating element, the driven plate 20 is an example of a second rotating element, and the coil spring 30 is an example of an elastic member.

  The damper 100 also includes a friction plate 40. When a relative rotation occurs between the drive plate 10 and the driven plate 20, the friction plate 40 frictions between at least one of the drive plate 10 and the driven plate 20 in accordance with the relative rotation. To do. A resistance torque based on the frictional resistance acts on the drive plate 10 and the driven plate 20. By the friction between the friction plate 40 and at least one of the drive plate 10 and the driven plate 20, the kinetic energy corresponding to the relative rotation can be converted into heat energy. The friction plate 40 is an example of a third rotating element.

(Detailed configuration of damper 100)
The drive plate 10 and the driven plate 20 shown in FIGS. 1 and 2 are arranged in the axial direction so as to be rotatable around the rotation center Ax.

  As shown in FIG. 2, the drive plate 10 has 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 has a disk shape that spreads across the rotation center Ax. The peripheral wall 11b has a cylindrical shape protruding rearward from the peripheral edge (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 has a disk shape that spreads across the rotation center Ax. The peripheral wall 12b has a cylindrical shape protruding rearward from the peripheral edge (outer edge) of the rear wall 12a. The rear end portion of the peripheral wall 11b of the front plate 11 and the peripheral edge of the back plate 12 are joined together by welding, screwing, or the like, whereby the front plate 11 and the back plate 12 are fixed and integrated. The rear wall 12a is an example of a first end wall, and the peripheral wall 12b is an example of a first peripheral wall.

  As shown in FIG. 2, the coil spring 30 is accommodated between the front plate 11 and the back plate 12. The coil spring 30 is arranged in a posture in which the winding center is substantially along the circumferential direction. A gap between the front plate 11 and the back plate 12 extends along the circumferential direction, and a plurality of coil springs 30 are arranged in series in the gap. A sheet member 31 is provided between two coil springs 30 adjacent to each other in the circumferential direction. 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. Further, the sheet member 31 is provided with a recess 31a and a protrusion (not shown). The coil spring 30 is held and guided by the recess 31a and the protrusion. The sheet member 31 can also be referred to as a retainer.

  As shown in FIG. 1, the back plate 12 is provided with a protrusion 12c. The protrusion 12 c protrudes forward so as to approach the front plate 11. Further, the front wall 11 a of the front plate 11 is provided with a protrusion (not shown) that faces the protrusion 12 c. The protrusion protrudes rearward so as to approach the back plate 12. The protrusions of the front plate 11 and the protrusion 12 c of the back plate 12 that face each other in the axial direction function as a pressing portion 32 that applies a force to the coil spring 30 and receives a force from the coil spring 30. The pressing portions 32 are arranged at a plurality of locations at regular intervals in the circumferential direction, for example, at two locations at intervals of 180 ° in the present embodiment. A row in which the coil springs 30 and the sheet members 31 are alternately arranged along the circumferential direction is disposed between the pressing portion 32 and another pressing portion 32. The sheet member 31 is also disposed between the coil spring 30 and the pressing portion 32.

  As shown in FIG. 2, the driven plate 20 includes a center plate 21 and a cover plate 22.

  As shown in FIG. 1, the center plate 21 has a center wall 21a and a protrusion 21b. The central wall 21a has a disk shape that spreads across the rotation center Ax. The protrusion 21b protrudes radially outward from the peripheral edge (outer edge) of the central wall 21a. The protrusion 21 b functions as a pressing portion 33 that applies force to the coil spring 30 and receives force from the coil spring 30.

  The pressing portions 33 are arranged at a plurality of locations at regular intervals in the circumferential direction. For example, in the present embodiment, the pressing portions 33 are arranged at two locations at intervals of 180 °. A row in which the coil springs 30 and the sheet members 31 are alternately arranged along the circumferential direction is arranged between the pressing portion 33 and another pressing portion 33. The sheet member 31 is also disposed between the coil spring 30 and the pressing portion 33.

  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. ing. Moreover, the press part 32 and the press part 33 are comprised so that it may not contact mutually. For example, in the present embodiment, gaps are provided in the axial direction between the protrusions of the front plate 11 and the tips of the protrusions 12c of the back plate 12 and the protrusions 21b.

  As shown in FIG. 2, the cover plate 22 has a rear wall 22a, an annular wall 22b, and a peripheral wall 22c. The rear wall 22a is configured in a mortar shape. The annular wall 22b extends radially outward from the peripheral edge (outer edge) of the rear wall 22a, and has an annular shape and a plate shape. The peripheral wall 22c has a cylindrical shape protruding forward from the peripheral edge (outer edge) of the ring wall 22b. The annular wall 22b is an example of a second end wall, and the peripheral wall 22c is an example of a second peripheral wall.

  As shown in FIG. 2, the rear surface of the center plate 21 and the front surface of the cover plate 22 are joined by welding, screwing, or the like at a position radially inward from the coil spring 30 and the seat member 31. Thereby, the center plate 21 and the cover plate 22 are fixed and integrated.

  As shown in FIG. 2, the friction plate 40 is disposed between the back plate 12 and the cover plate 22. The friction plate 40 has an annular and plate shape that spreads across the rotation center Ax. The friction plate 40 is positioned by the peripheral wall 22c in the radial direction.

  3 is a perspective view of a part of the friction plate 40, FIG. 4 is a perspective view of a part of the cover plate 22, and FIG. 5 is a side view of the friction plate 40 and the cover plate 22 as viewed from the radial direction. FIG. 3 is a schematic view in which an annular friction plate 40 is linearly extended.

  As shown in FIGS. 3 and 5, the friction plate 40 has a base portion 41 and a protrusion 42. The base portion 41 has an annular shape and a plate shape. The base portion 41 is located between the rear wall 12 a of the back plate 12 and the annular wall 22 b of the cover plate 22. The protrusion 42 protrudes from the base portion 41 in the axial direction. In the present embodiment, a plurality of protrusions 42 having the same shape are arranged on the surface 41a on the rear side (right side in FIG. 2) of the base portion 41 at intervals along the circumferential direction. The plurality of protrusions 42 are arranged at equal intervals. The surface 41a intersects (orthogonally) the axial direction. A surface 41b opposite to the surface 41a of the base portion 41 is flat (planar). The base part 41 is an example of an intermediate wall.

  One side surface and the other side surface of the protrusion 42 in the circumferential direction are inclined surfaces 42a extending along the circumferential direction. The inclined surface 42a is positioned adjacent to the top portion 42b of the protrusion 42 in the circumferential direction, and is configured to be farther in the axial direction as it is farther from the top portion 42b in the circumferential direction. In other words, from the surface 41a of the base part 41, the taper-shaped protrusion 42 having the inclined surfaces 42a provided on one and the other in the circumferential direction protrudes. The inclined surface 42a extends in oblique directions Icw and Iccw between the circumferential direction (tangential direction) and the rear. In addition, the bus line of the inclined surface 42a is along the radial direction. The inclined surface 42a is an example of a first inclined surface.

  One rotating element of the drive plate 10 and the driven plate 20, for example, in the present embodiment, the driven plate 20 is provided with a protrusion 52 that faces the protrusion 42 of the friction plate 40. Specifically, as shown in FIGS. 2, 4, and 5, a protrusion 52 is provided on the annular wall 22 b of the cover plate 22 that is a part of the driven plate 20. The annular wall 22b is a base portion 51 on which a protrusion 52 is provided. The protrusion 52 protrudes from the base portion 51 in the axial direction. In the present embodiment, a plurality of protrusions 52 having the same shape are arranged on the front surface 51a of the base portion 51 (left side in FIG. 2) at intervals along the circumferential direction. The plurality of protrusions 52 are arranged at equal intervals. The surface 51a intersects (orthogonally) the axial direction.

  One side surface and the other side surface of the protrusion 52 in the circumferential direction are inclined surfaces 52a extending along the circumferential direction. The inclined surface 52a is positioned adjacent to the top portion 52b of the protrusion 52 in the circumferential direction, and is configured to be farther in the axial direction as it is farther from the top portion 52b in the circumferential direction. In other words, from the surface 51a of the base part 51, the taper-shaped protrusion 52 which has the inclined surface 52a provided in one and the other of the circumferential direction protrudes. The inclined surface 52a extends in oblique directions Iccw and Icw between the circumferential direction (tangential direction) and the rear. The bus bar of the inclined surface 52a is along the radial direction. The inclined surface 52a is an example of a second inclined surface.

  Here, the diameter of the circumferential row where the protrusions 52 are provided is the same as the diameter of the circumferential row where the protrusions 42 are provided. The number of protrusions 52 is the same as the number of protrusions 42. The interval between the arcs (angles) where the plurality of protrusions 52 are arranged is the same as the interval between the arcs (angles) where the plurality of protrusions 42 are arranged. In addition, each of the protrusions 52 is positioned between the two protrusions 42. In a state where there is no relative angle difference between the drive plate 10 and the driven plate 20, the protrusion 52 is positioned at an intermediate position between the two protrusions 42 as shown by P 0 in FIG.

  Further, the other of the drive plate 10 and the driven plate 20, for example, in this embodiment, the drive plate 10 is provided with a sliding surface 53 facing the surface 41b of the friction plate 40 as shown in FIG. Yes. Specifically, the rear surface 12 d of the back plate 12 that is a part of the drive plate 10 is a sliding surface 53. The sliding surface 53 intersects (perpendicular to) the axial direction and is flat (planar). Between the sliding surface 53 and the surface 41b, a thin friction material 54 spreading in a direction intersecting (orthogonal) with the axial direction may be interposed. In that case, the friction material 54 may be bonded to the surface 41b or the sliding surface 53 by adhesion or the like. The surface 41b may be referred to as a first sliding surface, and the sliding surface 53 may be referred to as a second sliding surface.

  2, the peripheral wall 12b of the back plate 12 of the drive plate 10 and the peripheral wall 22c of the cover plate 22 of the driven plate 20 have a diameter via a cylindrical clearance C (radial gap). Adjacent to each other, aligned in the radial direction, and overlapped in the radial direction. That is, the cylindrical inner surface of the peripheral wall 12b and the cylindrical outer surface of the peripheral wall 22c face each other through the clearance C.

  The clearance C is covered with a ring-shaped seal member 60 attached to the peripheral wall 12b. The seal member 60 suppresses the leakage of the lubricating oil in the clearance C. That is, the seal member 60 seals the clearance C. The seal member 60 is, for example, a packing made of an elastic material such as an elastomer. The seal member 60 is an example of a first seal member.

(Operation of coil spring 30)
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, so that the drive plate 10 moves to the driven plate 20. Suppresses transmission of torque fluctuations (rotational fluctuations).

(Operation of friction plate 40)
Further, in the above-described configuration, when the drive plate 10 and the driven plate 20 rotate relatively according to the magnitude of engine-induced torque fluctuation (rotational fluctuation) generated in the drive plate 10, as shown in FIG. The inclined surface 42a of the protrusion 42 of the friction plate 40 and the inclined surface 52a of the protrusion 52 provided on the cover plate 22 of the driven plate 20 are in contact with each other. In this state, when the drive plate 10 and the driven plate 20 further rotate relative to each other, the protrusion 52 further moves to the left in FIG. 5 with respect to the protrusion 42, and the inclined surface 52a rises above the inclined surface 42a, that is, the protrusion 52 moves away from the base portion 41 of the friction plate 40 in the axial direction, and the inclined surface 42a and the inclined surface 52a are engaged with each other. Here, since the cover plate 22 is an elastic material such as a metal material, when the inclined surface 52a is pushed by the inclined surface 42a, the cover plate 22 moves to the state in which the ring wall 22b moves rearward in FIG. Elastically deforms. In this case, a forward repulsive force accompanying the elastic deformation of the cover plate 22 is applied to the inclined surface 42a and the inclined surface 52a, and a frictional force is generated when the inclined surface 42a and the inclined surface 52a slide, Thereby, resistance torque between the drive plate 10 and the driven plate 20 is generated, and torque fluctuation (rotational fluctuation) is reduced.

  In the present embodiment, the friction plate 40 is not fixed to the back plate 12, and the surface 41b of the friction plate 40 and the sliding surface 53 are slidable in the circumferential direction. Therefore, as described above, when the drive plate 10 and the driven plate 20 further rotate relative to each other in a state where the forward repulsive force due to the elastic deformation of the cover plate 22 is applied to the surface 41b and the sliding surface 53. In addition, sliding friction is generated between the surface 41b and the sliding surface 53, whereby a resistance torque is generated between the drive plate 10 and the driven plate 20, and energy is consumed by the sliding friction to change the torque ( (Rotational fluctuation) is reduced.

(Configuration for clearance C)
The peripheral wall 12b of the back plate 12 and the peripheral wall 22c of the cover plate 22 constitute a cylindrical clearance C (gap) extending in the axial direction. Thereby, the leakage of the lubricating oil from between the back plate 12 and the cover plate 22 is suppressed.

  The peripheral wall 12 b of the back plate 12 protrudes rearward from the rear wall 12 a of the back plate 12, and the peripheral wall 22 c of the cover plate 22 protrudes forward from the annular wall 22 b of the cover plate 22. Thereby, compared with the structure which the surrounding wall 12b and the surrounding wall 22c which comprise the clearance C overlap in radial direction, and protruded in the same direction, the length of the surrounding wall 12b or the surrounding wall 22c can be shortened.

  The radially inner end of the cover plate 22 is fixed to the center plate 21. The peripheral wall 22c protrudes forward from the peripheral edge (outer edge) of the ring wall 22b, and the front end (front end) of the peripheral wall 22c is a free end. Therefore, when the annular wall 22b moves rearward along with the sliding of the inclined surface 42a and the inclined surface 52a, the cover plate 22 is elastically deformed so as to incline in the clockwise direction in FIG. The tip moves radially outward and approaches the peripheral wall 12b of the back plate 12. Therefore, according to such a structure, the clearance C between the surrounding wall 22c and the surrounding wall 12b becomes narrow, and the sealing performance of the lubricating oil in the clearance C improves.

  As described above, in the damper 100 of the present embodiment, the base portion 41 (intermediate wall) of the friction plate 40 (third rotation element) is located behind the drive plate 10 (first rotation element) (first rotation element). A rear wall 12a (first end wall) that is an end wall in the direction of (2), and an annular wall 22b that is located behind the rear wall 12a and is the rear end wall of the driven plate 20 (second rotating element). The second end wall). That is, the annular wall 22b of the driven plate 20 is provided only on one side (front side) in the axial direction with respect to the rear wall 12a of the drive plate 10. According to such a configuration, when the inclined surface 42a provided on the base portion 41 and the inclined surface 52a provided on the annular wall 22b slide or engage with each other, the surface 41b and the sliding surface 53 The frictional force between them increases, and as a result, a resistance torque is generated between the drive plate 10 and the driven plate 20. According to such a configuration, for example, compared to a configuration in which the components of the friction plate 40 and the driven plate 20 are sandwiched between the two components of the drive plate 10, the axial length of the damper 100 is increased. It can be made shorter. Further, for example, since the number of parts is reduced, it is possible to reduce manufacturing effort and cost.

  Further, as in the prior art, the second rotating element and the friction element are sandwiched between the two walls of the first rotating element, and the inclined surface provided in the second rotating element and the friction element are provided. In the configuration in which the inclined surfaces slide and engage with each other, when the engagement state of these two inclined surfaces is to be released, the second rotating element and the friction element having the inclined surfaces include: Frictional force acts in the same rotational direction from the two walls of the first rotating element. Therefore, in the configuration of the prior art, there is a problem that it is difficult to release the engagement state of the two inclined surfaces. In this regard, according to the present embodiment, a frictional force is applied only from the drive plate 10 to the base portion 41 provided with the inclined surface 42a, and a frictional force is applied to the driven plate 20 having the inclined surface 52a from the drive plate 10. Since it does not act, when attempting to disengage the inclined surfaces 42a, 52a, the engine torque fluctuation from the drive plate 10 acts as a disengagement force. It can be said that the state is easily released.

  In the damper 100 of the present embodiment, the peripheral wall 12b (first peripheral wall) of the back plate 12 and the peripheral wall 22c (second peripheral wall) of the cover plate 22 have a cylindrical clearance C extending in the axial direction. It is composed. According to such a configuration, for example, the lubricating oil is difficult to leak from between the back plate 12 and the cover plate 22.

  Further, in the damper 100 of the present embodiment, the peripheral wall 12b (first peripheral wall) of the back plate 12 protrudes rearward from the rear wall 12a (first end wall) of the back plate 12, and the peripheral wall 22c ( The second peripheral wall) protrudes forward from the annular wall 22b (second end wall) of the cover plate 22. According to such a configuration, for example, compared to a configuration in which the peripheral wall 12b and the peripheral wall 22c constituting the clearance C overlap in the radial direction and protrude in the same direction, the axial length of the peripheral wall 12b or the peripheral wall 22c, As a result, the axial length of the damper 100 can be further shortened.

  Further, in the damper 100 of the present embodiment, the peripheral wall 12b (first peripheral wall) of the back plate 12 has a clearance C (gap) radially outward from the peripheral wall 22c (second peripheral wall) of the cover plate 22. The peripheral wall 22c protrudes forward from the ring wall 22b (second end wall), and the tip (front end) of the peripheral wall 22c is a free end. According to such a configuration, when the annular wall 22b receives a backward force by sliding between the inclined surface 42a and the inclined surface 52a, the cover fixed to the center plate 21 at the radially inner end. The plate 22 is elastically deformed so that the front end of the peripheral wall 22c approaches the peripheral wall 12b. Therefore, for example, the clearance C between the peripheral wall 22c and the peripheral wall 12b is narrowed, and the sealing performance of the lubricating oil in the clearance C is improved.

  Further, in the damper 100 of the present embodiment, the radial clearance C is covered by the seal member 60 (first seal member) attached to the peripheral wall 12b. According to such a configuration, for example, leakage of lubricating oil from the clearance C is suppressed.

(First modification)
FIG. 6 is a cross-sectional view of the damper 100A of the first modified example at the same position as FIG. The damper 100A of the modified example shown in FIG. 6 also has the same configuration as the damper 100 of the above embodiment, and the same effect based on the same configuration can be obtained. The same code | symbol is provided to the same structure and the overlapping description is abbreviate | omitted.

  However, as shown in FIG. 6, in this modification, the drive plate 10, not the driven plate 20, is provided with a protrusion 52 that faces the protrusion 42 of the friction plate 40. Specifically, as shown in FIG. 6, a protrusion 52 is provided on the rear wall 12 a of the back plate 12 that is a part of the drive plate 10. The rear wall 12a is a base portion 51 on which a protrusion 52 is provided. The protrusion 52 protrudes from the base portion 51 in the axial direction. In the present modification, a plurality of protrusions 52 having the same shape are arranged on the surface 51a on the rear side (right side in FIG. 6) of the base portion 51 at intervals along the circumferential direction. The plurality of protrusions 52 are arranged at equal intervals. The surface 51a intersects (orthogonally) the axial direction.

  The friction plate 40 is disposed in a posture opposite to that in the front and rear directions of the above embodiment. That is, a plurality of protrusions 42 (not shown in FIG. 6) having the same shape are arranged on the front surface 41a (left side in FIG. 6) of the base portion 41 with a gap in the circumferential direction. The plurality of protrusions 42 are arranged at equal intervals.

  The driven plate 20 is provided with a sliding surface 53 facing the surface 41 b of the friction plate 40. Specifically, as shown in FIG. 6, the front surface 22 d of the cover plate 22 that is a part of the driven plate 20 is a sliding surface 53. The sliding surface 53 intersects (perpendicular to) the axial direction and is flat (planar). Also by such a modification, the same effect as the said embodiment is acquired.

(Second modification)
FIG. 7 is a cross-sectional view of the damper 100 of the above embodiment at the same position as FIG. The damper 100B of the modified example shown in FIG. 7 also has the same configuration as the dampers 100 and 100A of the above-described embodiments and modified examples, and the same effect based on the similar configuration is obtained. The same code | symbol is provided to the same structure and the overlapping description is abbreviate | omitted.

  However, as shown in FIG. 7, in this modification, the back plate 12 of the drive plate 10 does not have the peripheral wall 12b (see FIG. 6). A clearance C (a gap in the axial direction) between the rear wall 12a of the back plate 12 and the tip of the peripheral wall 22c of the driven plate 20 is sealed by a ring-shaped seal member 60 attached to the peripheral wall 22c. Has been. Even with such a configuration, leakage of the lubricating oil from the clearance C is suppressed. Further, in the present modification, the damper 100B can be configured to be lighter because there is no peripheral wall 12b. The peripheral wall 22c is an example of a third peripheral wall, and the seal member 60 is an example of a second seal member.

  As mentioned above, although embodiment of this invention was illustrated, the said embodiment is an example and is not intending limiting the range of invention. The embodiment 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 example can be partially exchanged. In addition, the specifications (structure, type, direction, shape, size, length, width, height, number, arrangement, position, etc.) of each configuration and shape can be changed as appropriate. For example, the present invention can be applied to a damper other than the flywheel damper. The third rotating element may be fixed to one of the first rotating element and the second rotating element that does not have an inclined surface (projection). Moreover, the sealing member should just be attached to one of the two members which comprise clearance. Further, even in the configuration in which the peripheral wall 22c is positioned with a gap outward in the radial direction of the peripheral wall 12b, the clearance between the peripheral wall 12b and the peripheral wall 22c (radial The gap) can be sealed.

  DESCRIPTION OF SYMBOLS 10 ... Drive plate (1st rotation element), 12a ... Back wall (1st end wall), 12b ... Peripheral wall (1st surrounding wall), 20 ... Driven plate (2nd rotation element), 22b ... Ring wall (Second end wall), 22c ... peripheral wall (second peripheral wall, third peripheral wall), 30 ... coil spring (elastic member), 40 ... friction plate (third rotating element), 41 ... base portion (intermediate) Wall), 42a ... inclined surface (first inclined surface), 51 ... base portion, 52a ... inclined surface (second inclined surface), 60 ... seal member (first seal member, second seal member), 100, 100A ... damper, Ax ... center of rotation, C ... clearance (gap), Icw, Iccw ... diagonal direction, X ... rearward in the axial direction (first direction).

Claims (4)

A first rotating element that rotates about a rotation axis and includes a first end wall intersecting the rotation axis;
A second rotating element that rotates about the rotation axis and includes a second end wall that intersects the rotation axis and that is provided on only one of the rotation axes with respect to the first end wall;
A circumferential direction of the rotating shaft according to relative rotation between the first rotating element and the second rotating element interposed between the first rotating element and the second rotating element An elastic member that elastically expands and contracts,
An annular intermediate wall that rotates about the rotation axis, intersects the rotation axis, and is sandwiched between the first end wall and the second end wall, and spaced apart in the circumferential direction. A plurality of first inclined surfaces provided on the intermediate wall along an oblique direction between the circumferential direction and the axial direction, and a third rotating element,
With
One of the first end wall and the second end wall is provided with a gap in the circumferential direction, and is positioned between two first inclined surfaces and extends in the oblique direction. Having a second inclined surface;
Friction resistance torque between the other of the first end wall and the second end wall and the intermediate wall as the first inclined surface and the second inclined surface slide or engage with each other. A damper occurs. A first peripheral wall projecting in the axial direction from the peripheral edge of the first end wall toward the second end wall;
A second peripheral wall protruding in the axial direction from the peripheral edge of the second end wall toward the first end wall;
The damper according to claim 1, comprising:   A first seal member that is provided on one of the first peripheral wall and the second peripheral wall and seals a radial clearance of the rotation shaft between the first peripheral wall and the second peripheral wall; The damper according to claim 2 provided. A third peripheral wall protruding in the axial direction from one to the other of the first end wall and the second end wall;
A second seal member that seals the gap in the axial direction between the other of the first end wall and the second end wall and the tip of the third peripheral wall;
The damper according to claim 1, comprising:

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