JP2019049306A - damper - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a damper having a new structure improved more efficiently by utilizing a structure having vibration paths in parallel. A damper of the present invention is interposed between a first rotating element, a second rotating element, and a first rotating element and a second rotating element, and elastically expands and contracts in a circumferential direction of a rotation center. A first elastic element, the first elastic element and the first elastic element arranged in the radial direction of the center of rotation, and the first elastic element and the second elastic element interposed in parallel with the first elastic element to elastically expand and contract in the circumferential direction. Two elastic elements and an intermediate mass element provided at an intermediate position in the circumferential direction of the first elastic element, and the first elastic element and the second elastic element are associated with the twisting of the first rotating element and the second rotating element. One state in which one of them is elastically compressed and the other is not elastically compressed, and the torsion angle between the first rotating element and the second rotating element is larger than that in the first state, and the first elastic element and the second elastic element A second state in which both of the elements are elastically compressed. [Selection diagram] Figure 10

Description

  The present invention relates to a damper.

  Conventionally, a damper having two parallel vibration paths capable of suppressing a torque fluctuation is known between an input element and an output element (Patent Document 1).

Japanese Patent Application Publication No. 2012-506006

  In this type of damper, by utilizing the configuration in which vibration paths are provided in parallel, for example, noise and vibration can be reduced, and the range of rotational speeds at which torque fluctuations can be suppressed can be improved more efficiently. It would be significant if it were possible to obtain a fixed damper.

  Therefore, one of the problems of the present invention is to obtain a damper with a novel configuration, which is improved more efficiently by using, for example, a configuration in which vibration paths are provided in parallel.

  The damper of the present invention is interposed between a first rotating element rotatable around the rotation center, a second rotating element rotatable around the rotation center, and the first rotating element and the second rotating element. A first elastic element that elastically extends and contracts in the circumferential direction of the rotation center, a radial direction of the first elastic element and the rotation center, and the space between the first rotation element and the second rotation element A second elastic element which is elastically extended and contracted in the circumferential direction and is disposed parallel to the first elastic element; and an intermediate mass element provided at an intermediate position in the circumferential direction of the first elastic element; A first state in which one of the first elastic element and the second elastic element is elastically compressed and the other is not elastically compressed due to the twisting of the first rotating element and the second rotating element; The twist angle between the first rotation element and the second rotation element is larger than in one state. Ku both the first elastomeric element and the second elastomeric element has a second state of being elastically compressed, the.

  In the damper described above, it is possible to set a lower rate of change in torsional torque per unit angle when the torsion angle is relatively small (first state). Therefore, according to the damper, for example, when vibration occurs in the circumferential direction, it is possible to further reduce the torque acting between two members having a gap (backlash) in the circumferential direction. Therefore, the resonance point of the damper can be moved to a lower rotational speed. Thereby, the torque fluctuation can be suppressed in a wider range of the rotational speed, and sound and vibration can be further reduced. Further, according to the above configuration, since the first elastic element and the second elastic element are aligned in the radial direction, the size of the damper in the axial direction can be further reduced.

  In the damper, for example, in the first state, the first elastic element is not elastically compressed and the second elastic element is elastically compressed. According to such a configuration, for example, the damper exhibits the characteristic in the first state to have the dynamic damper including the first elastic element and the intermediate mass element. In this case, it is possible to lower the rotational speed of the antiresonance point in a state where the twist angle is small. Therefore, according to such a configuration, for example, in the case where the transfer torque becomes larger as the rotational speed becomes higher, it is possible to suppress the torque fluctuation in a wider range of the rotational speed.

  Further, in the damper, for example, a unit of a twist angle between the first elastic element and the second elastic element of a torsion torque of the first rotating element and the second rotating element by expansion and contraction of the first elastic element. The rate of change per angle is smaller than the rate of change per unit angle of the twist angle of the torsional torque due to the expansion and contraction of the second elastic element. According to such a configuration, for example, by the lighter intermediate mass element, it is possible to obtain the effect of suppressing the torque fluctuation at the rotation speed of the antiresonance point.

  Further, in the damper, for example, the intermediate mass element is disposed between the first rotation element and the second rotation element in the axial direction of the rotation center. According to such a configuration, for example, the radial size at the portion including the intermediate mass element of the damper can be made smaller.

FIG. 1 is an exemplary and schematic cross-sectional view of the damper of the embodiment, and is an II cross-sectional view in FIG. FIG. 2 is an exemplary schematic rear view showing an internal configuration of the damper of the embodiment. FIG. 3 is an exemplary schematic view showing a schematic configuration of the damper of the embodiment expanded in the circumferential direction, and showing a state in which the damper is twisted by a predetermined angle from the set state. FIG. 4 is a graph showing an example of the correlation between the rotational speed and the torque fluctuation in the state of FIG. 3 of the damper of the embodiment. FIG. 5 is an exemplary schematic view showing the schematic configuration of the damper of the embodiment expanded in the circumferential direction, and showing a set state without twist. FIG. 6 is a graph showing an example of the correlation between the rotational speed and the torque fluctuation in the state of FIG. 5 of the damper of the embodiment. FIG. 7 is an exemplary and schematic rear view showing the internal configuration of the damper of the embodiment, showing a state in which the set state is twisted by a predetermined angle. FIG. 8 is an exemplary schematic rear view of a set state of a part of the damper of the embodiment. FIG. 9 is an exemplary and schematic rear view in a state where a predetermined angle is twisted from a set state of a part of the damper of the embodiment. FIG. 10 is a graph showing an example of the rate of change per unit angle of torsion torque in the torsion state of the damper of the embodiment.

  In the following, exemplary embodiments of the present invention are disclosed. The configurations of the embodiments and modifications thereof described below and the operations and results (effects) provided by the configurations are examples. The present invention can be realized by configurations other than the configurations disclosed in the following embodiments and modifications. Further, according to the present invention, it is possible to obtain at least one of various effects (including derivative effects) obtained by the configuration.

  In the following description, for convenience, the side closer to the engine (not shown) (left side in FIG. 1) is referred to as the front, and the side farther from the engine (right side in FIG. 1) is referred to as the rear. The front and rear in the following description do not necessarily coincide with the front and rear in the on-vehicle state.

  Also, in the following, 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.

  1 is a cross-sectional view of the damper 10, FIG. 2 is a rear view showing an internal configuration of the damper 10, and FIG. 3 is a schematic view showing a schematic configuration of the damper 10 expanded in the circumferential direction. FIG. 1 is a cross-sectional view of the damper 10 taken along line I-I of FIG. Moreover, FIG. 2 is the figure which looked at the damper 10 from the right side of FIG. 1 in the state from which the driven plate 30, the intermediate plate 40, and the rear plate 22b were removed. In FIG. 3, the arrow R indicates radially outward, and the arrow C indicates the circumferential direction and the counterclockwise direction in FIG. FIG. 3 is a view showing a state in which the drive plate 20 is rotated counterclockwise by a predetermined angle δ with respect to the driven plate 30 (a state in which the damper 10 is twisted by a predetermined angle δ from the set state).

  As shown in FIGS. 1 and 3, the damper 10 includes a drive plate 20, a driven plate 30, and an intermediate plate 40. The drive plate 20 is an example of a first rotation element (input rotation element), and the driven plate 30 is a second rotation element (example of an output rotation element).

  As shown in FIG. 3, in the damper 10, two torque transmission paths (a power transmission path, a rotation transmission path) are provided in parallel between the drive plate 20 and the driven plate 30. One is a path transmitted through the two inner coil springs 61 and 62 arranged in series, which will be hereinafter referred to as a first transmission path. The other is a path transmitted through the outer coil spring 50, which is hereinafter referred to as a second transmission path. An intermediate plate 40 is provided between the inner coil spring 61 and the inner coil spring 62. The intermediate plate 40 is provided with a weight member 42 (FIG. 1). The inner coil springs 61 and 62 are an example of a first elastic element, and the outer coil spring 50 is an example of a second elastic element. The intermediate plate 40 and the weight member 42 are an example of an intermediate mass element.

  FIG. 4 is a graph showing the correlation between the rotational speed of the damper 10 and the torque fluctuation in the state of FIG. The rotation speed N2 is a resonance point of the second transmission path including the outer coil spring 50, and the rotation speed N1 is an anti-resonance point of the damper 10. At the antiresonance point, the phase of the vibration in the first transmission path and the phase of the vibration in the second transmission path are opposite to each other, so that the torque fluctuation is suppressed. Therefore, by configuring the damper 10 so that the range of use of the rotational speed of the engine is a rotational speed near and higher than the rotational speed N1, the damper 10 has the characteristics shown by the broken line in FIG. It is possible to suppress torque fluctuation in a wider range of rotational speed.

  As shown in FIG. 1, the drive plate 20 has a front plate 21 and a rear plate 22.

  The front plate 21 has a front wall 21a, a peripheral wall 21b, and a flange 21c. The shape of the front wall 21a is a plate shape intersecting the rotation center Ax, and a ring shape centered on the rotation center Ax. The shape of the peripheral wall 21b is cylindrical. The circumferential wall 21b extends axially rearward from the peripheral edge of the front wall 21a. The shape of the flange 21c is a plate shape intersecting the rotation center Ax, and is a ring shape centered on the rotation center Ax. The flange 21 c extends radially outward from the axially rearward end of the peripheral wall 21 b.

  The rear plate 22 has a rear wall 22a. The shape of the rear wall 22a is a plate shape intersecting the rotation center Ax, and is a ring shape centered on the rotation center Ax. The rear wall 22a is axially separated from the front wall 21a.

  The flange 21c of the front plate 21 and the peripheral portion of the rear wall 22a of the rear plate 22 are joined by welding or the like, whereby the front plate 21 and the rear plate 22 are integrated. The rear wall 22a may also be referred to as an inward flange because it extends radially inward from the circumferential wall 21b. The front plate 21 and the rear plate 22 may be integrated not by welding but by a connecting tool such as a rivet or a bolt and a nut.

  As shown in FIGS. 1 and 2, at the peripheral portion of the drive plate 20, a housing portion 20 a (storage chamber) for housing the outer coil spring 50 is provided. The housing portion 20 a is configured by the front plate 21 and the rear plate 22 being partially separated in the axial direction, and extends in an arc shape along the circumferential direction.

  Grease (not shown) is contained in the housing portion 20a. Here, as shown in the upper side of FIG. 1, the radially outward end of the housing portion 20 a is closed by the peripheral wall 21 b and the rear plate 22. Further, the radially inward opening of the housing portion 20a is narrowed by the narrowed portion 20b curved so that the front plate 21 and the rear plate 22 approach each other in the axial direction and the center plate 31 passing through the narrowed portion 20b. There is. Further, as shown in the lower side of FIG. 1, both ends in the circumferential direction of the housing portion 20a are (the outer pressing portion 21d of the front plate 21), (the outer pressing portion 22c of the rear plate 22), and the center plate 31 (the Is covered by the outer pressing portion 31b). With such a configuration, the grease is prevented from flowing out of the housing portion 20a. Further, as described above, since the radially outward end of the housing portion 20a is closed, the grease is radially outward in the housing portion 20a by centrifugal force while the damper 10 is rotating. Stay in a biased state.

Further, in the housing portion 20a, the outer periphery of the outer coil spring 50 in the radially outward direction (
A sliding member 25 is provided along the outer circumference of the coil. The sliding member 25 has an arc-shaped cross section with a constant width and extends along the circumferential direction. The material of the sliding member 25 is, for example, a synthetic resin having a relatively low coefficient of friction.

  The drive plate 20 has a hub 23 radially inwardly adjacent to the front plate 21. The shape of the hub 23 is cylindrical around the rotation center Ax. The hub 23 and the front plate 21 are integrated by an unshown connector such as a screw, for example. The hub 23 is provided rotatably around the rotation center Ax.

  Further, the drive plate 20 has a ring gear 26 adjacent to the front plate 21 radially outward. The shape of the ring gear 26 is annular. The ring gear 26 meshes with a gear of a starter motor (not shown).

  As shown in FIG. 1, the driven plate 30 has a center plate 31 and an end plate 32 extending axially rearward and radially outward from the radially inner end of the center plate 31. ing.

  The shape of the center plate 31 is a plate shape intersecting the rotation center Ax, and is a ring shape centered on the rotation center Ax. The center plate 31 receives the hub 23 along the front wall 21 a of the front plate 21 from the inner edge which is radially outward adjacent to the hub 23 or radially outward from the hub 23 through the narrowed portion 20 b. 20a and extend to the outer edge between the front wall 21a and the rear wall 22a.

  As shown in FIG. 2, the center plate 31 is provided with an arc-shaped opening 31 a at a position spaced radially inward from the housing 20 a housing the outer coil spring 50. The opening 31 a penetrates the center plate 31 in the axial direction, and extends in a circular arc shape with a constant width in the radial direction and a circumferential direction. The inner coil springs 61 and 62, the sheet 71, and the intermediate sheet 72 are accommodated in the opening 31a. As shown in FIGS. 1 and 2, the outer coil spring 50 is disposed radially outward from the inner coil springs 61 and 62. The inner coil springs 61 and 62 and the outer coil spring 50 are arranged in the radial direction. The circumferential length of the opening 31 a is shorter than the circumferential length of the housing 20 a of the outer coil spring 50. Moreover, the circumferential center position of the opening 31a and the circumferential center position of the accommodation portion 20a are aligned in the radial direction. The sheet 71 and the intermediate sheet 72 are an example of an interposed part. The inner coil springs 61 and 62 may also be referred to as elastic members.

  As shown in FIG. 1, the inner peripheral edge of the center plate 31 and the inner peripheral edge of the end plate 32 are integrated by a plurality of connectors 33 (only two are shown in FIG. 1). The plurality of connectors 33 are arranged at predetermined intervals in the circumferential direction.

  The end plate 32 has an inner wall 32a and an end wall 32b. The shape of the inner wall 32a is a stepped cylindrical shape in which a cylindrical small diameter portion and a cylindrical large diameter portion adjacent to the rear in the axial direction of the small diameter portion are connected. The end wall 32 b is in the form of a plate having a tolerance with respect to the rotation center Ax, and is in the shape of a ring centered on the rotation center Ax. The end wall 32b extends radially outward from the axially rearward end of the inner wall 32a. The inner wall 32 a is spaced radially inward of the rear plate 22, and the end wall 32 b is spaced axially outward of the rear plate 22.

  The driven plate 30 is supported by the hub 23 rotatably around the rotation center Ax around the hub 23 via the radial bearing 20 c. The radial bearing 20c may also be referred to as a support member.

  The intermediate plate 40 is fixed to an intermediate sheet 72 interposed between the inner coil springs 61 and 62 shown in FIGS. As shown in FIG. 1, the intermediate plate 40 has a connecting member 41 and a weight member 42.

  The connection member 41 has a first extending portion 41a and a second extending portion 41b. The first extending portion 41 a extends in the axial direction at a position radially inward of the rear wall 22 a of the rear plate 22, that is, between the rear wall 22 a and the inner wall 32 a. Further, the first extending portion 41 a penetrates the intermediate sheet 72 and is thereby connected to the intermediate sheet 72. The second extending portion 41 b extends radially outward from the axial rear end of the first extending portion 41 a. The connecting member 41 is a bent rod-like or band-plate-like member in which the first extending portion 41a and the second extending portion 41b are integrally connected in an L shape. The first extending portion 41a (the connecting member 41 and the intermediate plate 40) may move integrally with the intermediate sheet 72 in the circumferential direction, and may not be combined with the intermediate sheet 72. It does not have to penetrate.

  The weight member 42 is connected to the second extending portion 41 b of the connection member 41 by a connector 43 such as, for example, a rivet. The shape of the weight member 42 is a plate shape extending in the radial direction and the circumferential direction as shown in FIG. 1, and although not shown, it has a fan-like shape along the circumferential direction with a constant width in the radial direction in the axial view. It is.

  The weight member 42 is located between the rear wall 22 a of the rear plate 22 (drive plate 20) and the end wall 32 b of the driven plate 30. A leaf spring 44 extending radially in contact with the front of the second extending portion 41 b is attached to the connection member 41 by a connector 43. The coupler 43 is shared by the coupling of the leaf spring 44 to the intermediate plate 40 and the coupling of the connecting member 41 and the weight member 42. The plate spring 44 is interposed between the rear plate 22 and the weight member 42 (intermediate plate 40) and applies an elastic force to the rear plate 22 in the axial direction forward, and an elastic repulsive force in the weight member 42 axially backward. (Elasticity) is given. The contact point of the leaf spring 44 with the rear wall 22 a slides with the rear wall 22 a according to the twist between the drive plate 20 and the intermediate plate 40. The plate spring 44 may be fixed to the drive plate 20. In this case, the contact point of the plate spring 44 with the intermediate plate 40 slides with the intermediate plate 40. Further, the plate spring 44 may be stopped in the rotational direction such as being caught in the circumferential direction with one of the intermediate plate 40 and the drive plate 20, and may not be coupled with the one. The leaf spring 44 may also be referred to as an elastic member, a sliding member, or an elastic sliding member.

  Further, a slide bush 20d is interposed between the weight member 42 and the end wall 32b of the end plate 32 (driven plate 30). The slide bush 20d contacts a corner as a radially inward and axially rearward end of the weight member 42, and a corner (a recess (recess) provided at a boundary between the inner wall 32a of the end plate 32 and the end wall 32b. I am in contact with Specifically, the slide bush 20d has a cylindrical portion 20d1 and a flange 20d2. The cylindrical portion 20d1 contacts the radially inward of the weight member 42 and contacts the radially outward of the inner wall 32a of the end plate 32, in other words, is radially interposed between the weight 42 and the inner wall 32a. . The flange 20d2 protrudes radially outward from the axial rear end of the cylindrical portion 20d1. Further, the flange 20d2 is in contact with the axial direction rear of the weight member 42 and in contact with the axial direction front of the end wall 32b of the end plate 32, in other words, axially sandwiched between the weight member 42 and the end wall 32b There is. The weight member 42 is slidably supported in the circumferential direction on the end plate 32 via the slide bush 20 d. Further, the weight member 42 is positioned in the axial direction and the radial direction by the slide bush 20d. The material of the slide bush 20d is a synthetic resin with relatively high abrasion resistance. The slide bush 20d may also be referred to as a slide member, a slide support member, a bearing, or a positioning member.

  The slide bush 20d may be provided on the opposite side of the plate spring 44 with respect to the weight member 42 in the axial direction. Thus, the drive plate 20 rotatably supports the weight member 42 via the slide bush 20 d, and the plate spring 44 is interposed between the weight member 42 and the driven plate 30 so that the weight member 42 and the driven plate 30 are pivoted. Elastic forces may be applied to separate the directions. In this case, the plate spring 44 is fixed to one of the weight member 42 and the driven plate 30 and slides on the other. The plate spring 44 may be hooked to one of the weight member 42 and the driven plate 30 in the circumferential direction, and may not be coupled to the one. That is, the weight member 42 (intermediate plate 40) can slide in the circumferential direction via the slide bush 20d on any one of the end plate 32 (driven plate 30) and the rear plate 22 (drive plate 20). Can be axially and radially supported. Thereby, it can suppress that the weight member 42 vibrates to an axial direction or radial direction. The sliding support member of the weight member 42 is not limited to the slide bush 20d, and the axial sliding support member and the radial sliding support member may be separately provided.

  As shown in FIG. 2, the inner coil springs 61 and 62 which extend helically along the circumferential direction (tangential direction) and are elastically compressible in the circumferential direction are arranged in series along the circumferential direction of the opening 31a. It is done. Between the upper edge 31 d (one edge in the circumferential direction) and the inner coil spring 61 in FIG. 2 of the opening 31 a, and the lower edge 31 d (the other edge in the circumferential direction) in FIG. 2 of the opening 31 a and the inner coil spring A seat 71 intervenes between the sheet 62 and the sheet 62. The specifications such as the shape and size of the two sheets 71 are the same.

  The seat 71 has an end 71a, a protrusion 71b, and a guide 71c. The end 71a is in contact with the edge 31d of the opening 31a. The protrusion 71 b protrudes in the circumferential direction from the radial center of the end 71 a. The protrusion 71 b projects into the coil of the inner coil spring 61 or the inner coil spring 62. The guide portion 71c protrudes in the circumferential direction from the radially outer end portion of the end portion 71a, and extends along the outer peripheral edge 31a1 of the opening 31a. The guide portion 71 c extends in the circumferential direction so as to cover the outer periphery (the outer periphery of the coil) of the inner coil spring 61 or the inner coil spring 62 radially outward. The guide 71 c is guided along the outer peripheral edge 31 a 1 of the opening 31 a so that the seat 71 can swing in the circumferential direction along the opening 31 a. The sheet 71 may also be referred to as a retainer, a positioning member, or a guide member. Further, the sheet 71 suppresses the inner coil springs 61 and 62 from coming into contact with the edge of the opening 31 a and other peripheral members. Therefore, the sheet 71 can also be referred to as a protective member or a buffer member.

  The intermediate sheet 72 has a base portion 72a, two protrusions 72b, and two guide portions 72c. The base portion 72 a is interposed between the inner coil spring 61 and the inner coil spring 62 in the circumferential direction. The protrusion 72 b protrudes in the circumferential direction from the radial center portion of the base portion 72 a. One of the two projections 72 b projects into the coil of the inner coil spring 61 and the other of the two projections 72 b projects into the coil of the inner coil spring 62. The guide portion 72c protrudes in the circumferential direction from the radial outward end of the base portion 72a, and extends along the outer peripheral edge 31a1 of the opening 31a. One of the two guide portions 72c extends in the circumferential direction so as to cover the outer periphery (the outer periphery of the coil) of the inner coil spring 61 radially outward. The other one of the two guide portions 72c extends in the circumferential direction so as to cover the outer periphery (the outer periphery of the coil) of the inner coil spring 62 radially outward. By the guide portion 72c being guided along the outer peripheral edge 31a1 of the opening 31a, the intermediate sheet 72 can swing in the circumferential direction along the opening 31a. The intermediate sheet 72 may also be referred to as a retainer, a positioning member, or a guide member. In addition, the intermediate sheet 72 suppresses the inner coil springs 61 and 62 from coming into contact with the edge of the opening 31 a and other peripheral members. Therefore, the sheet 71 can also be referred to as a protective member or a buffer member.

  Further, a through hole 72d is provided at the central portion of the base portion 72a of the intermediate sheet 72, and the first extending portion 41a of the connection member 41 penetrates the through hole 72d in the axial direction.

  When twisting of a predetermined angle or more occurs between the drive plate 20 and the driven plate 30, the end 71a of one of the two sheets 71 in the opening 31a is one of the opening 31a and one of the circumferential directions. The force is received from the inner pressing portion 31c (see the lower side of FIG. 1 and FIG. 2) of the center plate 31 adjacent to the other in the circumferential direction. Further, in this case, the end 71a of the other sheet 71 of the two sheets 71 is the inner side of the drive plate 20 spaced apart in the other circumferential direction with respect to the opening 31a in the set state (initial state) without torsion. A force is received from one of the pressing portions 21e and 22d (see the lower side in FIG. 1) in one circumferential direction. Thus, the two inner coil springs 61 and 62 arranged in series in the circumferential direction are compressed in the circumferential direction. Each of the two sheets 71 is configured to be pressed in the circumferential direction by the inner pressing portion 31 c of the center plate 31 and the inner pressing portions 21 e and 22 d of the drive plate 20.

  Specifically, for example, in the arrangement shown in FIG. 2, when the drive plate 20 is rotated in a counterclockwise direction with respect to the driven plate 30 by a predetermined angle or more, the end of the opening 31a in the counterclockwise direction The sheet 71 (the sheet on the lower side in FIG. 2) in contact with the edge 31d (the lower edge in FIG. 2) positioned in the portion receives the force in the clockwise direction from the inner pressing portion 31c of the driven plate 30, The sheet 71 (upper sheet in FIG. 2) in contact with the edge 31d (upper edge in FIG. 2) positioned at the end of the clockwise direction of the portion 31a is opposed to the inner pressing parts 21e and 22d of the drive plate 20. Receives clockwise force.

  On the other hand, for example, in the arrangement shown in FIG. 2, in the twisted state in which the drive plate 20 is rotated clockwise by a predetermined angle or more with respect to the driven plate 30, the counterclockwise end of the opening 31a is The sheet 71 (the lower sheet in FIG. 2) in contact with the positioned edge 31d (the lower edge in FIG. 2) receives a force in the clockwise direction from the inner pressing portions 21e and 22d of the drive plate 20 and opens. The sheet 71 (upper sheet in FIG. 2) in contact with the edge 31d (upper edge in FIG. 2) positioned at the end of the clockwise direction of the portion 31a is counterclockwise from the inner pressing portion 31c of the driven plate 30. Receive the force of the direction.

  As described above, when twisting of a predetermined angle or more occurs between the drive plate 20 and the driven plate 30, the two inner coil springs 61 and 62 arranged in series are both compressed and have a circumferential length. (Coil length) becomes short. Along with this, the intermediate sheet 72 moves in the circumferential direction, and the connection member 41 connected with the intermediate sheet 72 and consequently the intermediate plate 40 moves in the circumferential direction.

  Further, as shown in FIG. 2, the outer coil spring 50 which extends helically along the circumferential direction and is elastically compressible in the circumferential direction extends along the circumferential direction of the housing portion 20 a. In place of the outer coil spring 50, a plurality of in-series coil springs and an intervening member interposed between the adjacent coil springs may be provided.

  When twisting occurs between the drive plate 20 and the driven plate 30, one end of the outer coil spring 50 in the circumferential direction is the outer pressing portion 31b of the center plate 31 adjacent to the housing portion 20a and one of the circumferential directions (FIG. 1). Receiving force from the lower side and the other in the circumferential direction from FIG. 2). Also, in this case, the other end of the outer coil spring 50 in the circumferential direction is the end 71 a of the other sheet 71 of the two sheets 71, the outer side of the drive plate 20 adjacent to the housing 20 a and the other in the circumferential direction. A force is received from one of the pressing portions 21d and 22c (see the lower side in FIG. 1) in one of the circumferential directions. Thereby, the outer coil spring 50 extending along the circumferential direction is compressed in the circumferential direction. Both ends of the outer coil spring 50 are configured to be circumferentially pressed by the outer pressing portion 31 b of the center plate 31 and the outer pressing portions 21 d and 22 c of the drive plate 20.

  Specifically, for example, in the arrangement shown in FIG. 2, when the drive plate 20 is twisted in the counterclockwise direction with respect to the driven plate 30, the drive plate 20 is positioned at the end of the accommodation portion 20 a in the counterclockwise direction. The end 50a of the outer coil spring 50 (the lower end in FIG. 2) receives a force in the clockwise direction from the outer pressing portion 31b of the driven plate 30, and the end of the accommodating portion 20a in the clockwise direction The end 50a (upper end in FIG. 2) of the positioned outer coil spring 50 receives a counterclockwise force from the outer pressing portions 21d and 22c of the drive plate 20.

  On the other hand, for example, in the arrangement shown in FIG. 2, in the twisting state in which the drive plate 20 is rotated clockwise by a predetermined angle or more with respect to the driven plate 30, the end of the accommodation portion 20a in the counterclockwise direction The end 50a (lower end in FIG. 2) of the positioned outer coil spring 50 receives a force in the clockwise direction from the outer pressing portions 21d and 22c of the drive plate 20, and the clockwise direction of the accommodation portion 20a. The end 50 a (upper end in FIG. 2) of the outer coil spring 50 positioned at the end receives a counterclockwise force from the outer pressing portion 31 b of the driven plate 30.

  Thus, when twisting occurs between the drive plate 20 and the driven plate 30, the outer coil spring 50 is compressed and the circumferential length (coil length) is shortened.

  FIG. 5 is a schematic view showing the schematic configuration of the damper 10 expanded in the circumferential direction, showing a set state without twisting, and FIG. 6 shows the rotational speed and torque fluctuation of the damper 10 in the state of FIG. FIG. 7 is a back view showing the internal configuration of the damper 10 in a state where the drive plate 20 has been rotated counterclockwise with respect to the driven plate 30 by a predetermined angle δ (see FIG. FIG. 6 is a view showing the damper 10 in a state where it is twisted by a predetermined angle δ from the set state. The solid line graph in FIG. 6 shows the characteristic shown by the solid line in FIG. 4, that is, the characteristic after elastic compression of the inner coil springs 61 and 62 is started.

  As shown in FIGS. 3, 5 and 7, the inner coil springs 61 and 62 are compressed from a state in which the drive plate 20 and the driven plate 30 are twisted by a predetermined angle δ. As shown in FIG. 7, the predetermined angle δ is, for example, an edge 21 f of the inner pressing portion 21 e of the drive plate 20 in the set state, that is, a pressing portion of the sheet 71 and an inner pressing portion 31 c of the driven plate 30 in the set state. It is an angle difference with the edge 31d. With the drive plate 20 rotated counterclockwise by the predetermined angle δ relative to the driven plate 30, the inner pressing portion 21e can press the upper sheet 71 of FIG. 7 in the counterclockwise direction. That is, in this embodiment, the first range (δ or more) of the twist angle in which the inner coil springs 61 and 62 are elastically compressed and the state in which the outer coil spring 50 is elastically compressed. And the second range (0 or more) of the twist angle that is the difference.

  As shown in FIG. 5, when there is a gap of a predetermined angle δ (angular difference), the inner coil spring 61, the inner coil spring 62, and the middle plate 40 are separated from the drive plate 20, It is supported by the driven plate 30. This state corresponds to a state in which the driven plate 30 is provided with a dynamic damper including the inner coil spring 61, the inner coil spring 62, and the intermediate plate 40. The correlation between the rotational speed and the torque fluctuation in this case is as shown by a broken line in FIG. 6, and the rotational speed N12 at the antiresonance point starts elastic compression of the inner coil spring 61 and the inner coil spring 62. It becomes lower than the rotational speed N1 of the antiresonance point in the state after being made. The broken line in FIG. 6 is a state in which the twist angle is small, and the solid line in FIG. 6 is a state in which the twist angle is large. That is, according to the configuration of the present embodiment, the rotation speed N1 (N12) of the antiresonance point becomes higher as the twist angle becomes larger. Therefore, according to the present embodiment, when the engine is configured or controlled so that the rotational speed is higher as the output torque is larger, the rotational speed N1 (N12) at the antiresonance point is higher as the torsion angle is larger. Become. Therefore, according to the present embodiment, the damper 10 can more effectively suppress the torque fluctuation in a wider range of the rotational speed of the engine.

  It can be understood from FIG. 4 that the torque fluctuation of the damper 10 can be suppressed when the rotation speed of the damper 10 is close to the rotation speed N2 of the anti-resonance point of the damper 10. Therefore, if the damper 10 in which the rotational speed N1 at the antiresonance point increases as the rotational speed of the engine increases is obtained, the damper 10 can more effectively suppress the torque fluctuation in a wider range of the rotational speed of the engine. It will be.

  Here, for example, in an engine or the like for a hybrid vehicle, the engine may be configured or controlled such that the rotational speed is higher as the output torque is larger. In such a case, as damper 10 increases in output torque of the engine, that is, as transmission torque in damper 10 increases, in other words, the twist angle between drive plate 20 and driven plate 30 (hereinafter simply referred to as the twist angle). If the rotation speed N1 of the antiresonance point can be increased as the rotation speed of the antiresonance point increases, the rotation speed N2 of the antiresonance point of the damper 10 increases as the rotation speed of the engine increases.

  Moreover, in this type of damper, generally, the rate of change of torsion torque (elastic torque) per unit angle of torsion angle (hereinafter simply referred to as the rate of change of torsion torque per unit angle or the rate of change of torsion torque) Note that the rotation speed N1 of the antiresonance point is higher as the value of.

  So, in this embodiment, although mentioned later in detail, damper 10 is constituted so that change rate of torsion torque may become large, so that a twist angle of drive plate 20 and driven plate 30 is large. Therefore, according to the present embodiment, when the engine is configured or controlled such that the rotational speed is higher as the output torque is larger, the larger the output torque of the engine is, that is, the larger the torsion angle of the damper 10 is. The rate of change per unit angle of the torsional torque of the damper 10 is increased, whereby the rotational speed N1 at the antiresonance point is increased. Therefore, according to the present embodiment, the damper 10 can suppress the torque fluctuation in a wider range of the rotational speed of the engine.

  8 and 9 are axial rear views of part of the damper 10 according to this embodiment, and FIG. 8 is a set of the drive plate 20 and the driven plate 30 not twisted, that is, having a twist angle of 0. FIG. 9 is a rear view in a state in which the drive plate 20 and the driven plate 30 are twisted (a predetermined angle δ is twisted from the set state). A seat 71 interposed between the center plate 31 and the inner coil spring 62 is shown in FIGS.

  In the set state of FIG. 8, of the end 71 a of the seat 71 in contact with the center plate 31, the inner end 71 ai positioned radially inward is in contact with the center plate 31. The radially outer end 71ao is not in contact with the center plate 31, and a gap g1 is provided between the radially outer end 71ao and the center plate 31.

  The damper 10 is configured such that the gap g1 becomes smaller and disappears as it twists from the set state. That is, in the twisted state of FIG. 9, the inner end 71 ai and the outer end 71 ao of the sheet 71 are both in contact with the center plate 31.

  In the state where there is the gap g1 in the state of FIG. 8, the inner coil spring 62 mainly contracts in the radially inner portion. On the other hand, when there is no gap g1 in the state of FIG. 9, the entire inner coil spring 62 contracts. Therefore, the rate of change per unit angle of the torsional torque is larger in the state of FIG. 9 than in the state of FIG. Here, the angular differences α0 and α1 shown in FIGS. 8 and 9 are the compression reaction force of the inner coil spring 62 at the action points Pp0 and Pp1 from the sheet 71 to the driven plate 30 of the compression reaction force of the inner coil spring 62. It is an angle difference between the action direction Ds and the tangential direction Dt. The tangential direction Dt is a direction orthogonal to the radial direction and the axial direction. In such a configuration, the component of the compression reaction force of the inner coil spring 62 in the tangential direction Dt decreases as the angle differences α0 and α1 increase, and the torsion torque based on the compression reaction force decreases. Become. Here, as is apparent from FIGS. 8 and 9, in the present embodiment, the angle difference α0 in the set state of FIG. 8 is larger than the angle difference α1 in the twisted state of FIG. Therefore, according to such a configuration, the torsional torque and the rate of change per unit angle of the torsional torque in the state of FIG. 9, that is, in the state where the torsion angle is larger than the state of FIG. Torsional torque in the state where the twist angle is smaller than the state 9 and the change rate is larger. In addition, as the torsion angle from the set state increases, the action points Pp0 and Pp1 of the compression reaction force of the inner coil spring 62 move radially outward, so the torsion angle from the set state increases with this point as well. , Twist torque and the rate of change per unit angle of the twist torque. Although not shown, the other sheet 71 and the intermediate sheet 72 are also twisted from the set state, so that the gap g1 on the radially outer side is reduced and eliminated, so that the same effect can be obtained. Further, even when the twisting direction from the set state is opposite to that in FIGS. 8 and 9, the inner coil springs 61 and 62 are compressed, so that the same effect can be obtained. In addition, the gap g1 may be provided in at least one sheet 71 in the set state, and may not be provided in all the sheets 71. Also, by providing a similar sheet (not shown) at the end of the outer coil spring 50, the same function and effect can be obtained for the outer coil spring 50 as well.

  Thus, in the present embodiment, the damper 10 is configured such that the change rate per unit angle of the torsional torque due to the compression of the inner coil springs 61 and 62 becomes larger as the torsion angle is larger. According to the present embodiment, when the engine is configured or controlled such that the rotational speed increases as the output torque increases, the larger the output torque of the engine, that is, the drive plate 20 and the driven plate 30 of the damper 10 As the torsion angle of the damper 10 becomes larger, the rate of change per unit angle of the torsion torque of the damper 10 becomes larger, whereby the rotational speed N1 of the antiresonance point becomes higher. Therefore, according to the present embodiment, the damper 10 can suppress the torque fluctuation in a wider range of the rotational speed of the engine.

  Further, in the present embodiment, the sheet 71 (intervening part) and the sheet between the inner coil springs 61 and 62 or the outer coil spring 50 among the three rotating elements of the drive plate 20, the driven plate 30, and the intermediate plate 40. In the set state (initial state) where there is no twist, the rotary element 71 contacts with the rotary element in a state where the gap g1 is opened radially outward, and the gap g1 becomes smaller as the twist angle from the set state increases. It is configured as follows. According to the present embodiment, the damper 10 having a configuration in which the rate of change per unit angle of the torsional torque increases as the torsion angle increases can be obtained as a relatively simple configuration. The first elastic element or the second elastic element may be an elastic element other than a coil spring, such as an elastomer, a plate spring, or the like.

  FIG. 10 is a graph showing the rate of change per unit angle of the torsional torque in the torsion state of the damper 10 in the present embodiment. Although FIG. 10 shows the characteristic in the case where drive plate 20 is twisted in one direction with respect to driven plate 30, the same characteristic, however, the direction or the sign is obtained also in the case where it is twisted in the opposite direction. It shows the opposite characteristic. As shown in FIG. 10, in the first transmission path, the elastic compression of the inner coil springs 61 and 62 is started (the first range) from the twist angle θ2 (the predetermined angle δ,) 0). Furthermore, in the first transmission path, for example, by providing the configuration shown in FIGS. 8 and 9, the rate of change K12 per unit angle of twisting torque when the twisting angle is θ3 or more has a twisting angle smaller than θ3. It can be configured to be larger than the rate of change K11 per unit angle of the torsional torque in the case.

  In the second transmission path, when the drive plate 20 and the driven plate 30 are twisted, elastic compression of the outer coil spring 50 is started from the set state. Also in the second transmission path, for example, by providing the configuration shown in FIGS. 8 and 9, in the second transmission path, the rate of change K22 per unit angle of torsion torque when the twist angle is θ1 or more is It can be configured to be larger than the rate of change K21 per unit angle of the twisting torque when the twisting angle is smaller than θ1.

  Furthermore, in the damper 10, the torsion angles θ2 and θ3 are made larger than the torsion angle θ1. Therefore, as shown in FIG. 10, in the damper 10 (assembly), the torsion angle is greater than or equal to θ1 and less than θ2 than the rate of change K21 per unit angle of torsion torque between 0 and less than θ1. The rate of change in torsional torque per unit angle of twist angle θ2 or more but less than θ3 is greater than the rate of change K22 per unit angle of torsional torque with a large rate of change K22 per unit angle of torque and a twist angle less than θ1. The rate of change K12 + K22 per unit angle of torsion torque between θ3 and θ4 is larger than the rate of change K11 + K22 per unit angle between torsion torques θ2 and θ3 where K11 + K22 is large. According to the present embodiment, it is possible to obtain the damper 10 (assembly) in which the rate of change in torsional torque per unit angle increases as the twist angle increases. The twist angle θ4 is the upper limit of the twist angle.

  As described above, in the present embodiment, in the damper 10, the outer coil spring 50 is elastically compressed when the torsion angle (size, absolute value) thereof is 0 or more and less than θ2 (= δ), and the inner coil Inner springs 61 and 62 (first elastic element) and outer coil springs 50 (second elasticity) when springs 61 and 62 are not elastically compressed (first state) and the twist angle is θ2 or more The element has a state (second state) in which it is elastically compressed. Thereby, for example, in a state (first state) in which the twist angle is relatively small, such as a state in which the twist angle is, for example, close to 0, the rate of change per unit angle of the twist torque can be set lower.

  Therefore, according to the present embodiment, when vibration occurs in the circumferential direction, it is possible to further reduce the torque acting between two members having a gap (backlash) in the circumferential direction. Therefore, the resonance point of the damper 10 can be moved to a lower rotational speed. Thereby, torque vibration can be suppressed in a wider range of rotational speed, and sound and vibration can be further reduced. The same effect can be obtained even if the damper 10 has a configuration in which the inner coil springs 61 and 62 are elastically compressed and the outer coil spring 50 is not elastically compressed in the first state.

  Further, according to the present embodiment, since the inner coil springs 61 and 62 (first elastic element) and the outer coil spring 50 (second elastic element) are arranged in the radial direction, the first elastic element and the second elastic element are arranged. The axial size of the damper 10 can be made smaller as compared with the configuration in which the elements are arranged in the axial direction.

  Moreover, in the present embodiment, the damper 10 has a torsion angle (size, absolute value) of 0 or more and less than θ2, and the outer coil spring 50 (second elastic element) is elastically compressed, and the inner coil In a state where the spring 61 and the inner coil spring 62 (first elastic element) are not elastically compressed (first state), the characteristic is such that it has a dynamic damper including the inner coil spring 61, the inner coil spring 62, and the middle plate 40. Indicates In this case, the rotation speed N12 at the antiresonance point in the state where the twist angle is less than θ2 can be lower than the rotation speed N1 at the antiresonance point in the state where the twist angle is θ2 or more. Therefore, according to the present embodiment, the damper 10 can more effectively suppress the torque fluctuation in a wider range of the rotational speed of the engine.

  Further, in the present embodiment, although not shown, the rate of change per unit angle of the torsion torque in the inner coil springs 61 and 62 (first elastic element) is a unit of the torsion torque in the outer coil spring 50 (second elastic element). It can be smaller than the rate of change per angle. In this case, the lighter weight member 42 (intermediate mass element) can obtain the effect of suppressing the torque fluctuation at the rotational speeds N1 and N12 at the antiresonance point, which contributes to the downsizing and weight reduction of the damper 10.

  Further, in the present embodiment, the weight member 42 (intermediate mass element) is disposed between the drive plate 20 (first rotation element) and the driven plate 30 (second rotation element) in the axial direction of the rotation center Ax. Ru. According to such a configuration, for example, the size in the radial direction at a portion including the weight member 42 of the damper 10 can be further reduced.

  As mentioned above, although the embodiment of the present invention was illustrated, the above-mentioned embodiment is an example, and limiting the scope of the invention is not intended. The embodiment can be implemented in various other forms, and various omissions, substitutions, 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 replaced and implemented. Further, specifications (structure, type, direction, shape, size, length, width, height, number, arrangement, position, etc.) of each configuration and shape can be appropriately changed and implemented.

  For example, it is also possible to implement drive plate 20 of the said embodiment as a driven plate, and to implement driven plate 30 as a drive plate. Also, as an embodiment in which the rate of change in torsional torque per unit angle increases with an increase in the twist angle, for example, the first elastic element or the second elastic element included in the damper may be, for example, a coil of unequal pitch. It may be a coil spring, such as a spring, in which the gap is clogged at a required compression amount. In another embodiment, the first elastic element or the second elastic element has, for example, a plurality of elastic members arranged in parallel, and the compression angle range of the plurality of elastic members is different, that is, a twist that starts to be compressed The corners may be configured to be different.

  DESCRIPTION OF SYMBOLS 10 ... Damper, 20 ... Drive plate (1st rotation element) 30, 30 ... Driven plate (2nd rotation element) 40 ... Intermediate plate (intermediate mass element) 42 ... Weight member (intermediate mass element) 61, 62 ... Inner coil spring (first elastic element), 50: outer coil spring (second elastic element), Ax: center of rotation, g1: gap.

Claims (4)

A first rotating element rotatable around the rotation center,
A second rotating element rotatable about the rotation center;
A first elastic element interposed between the first rotation element and the second rotation element and elastically extended and contracted in the circumferential direction of the rotation center;
The first elastic element is arranged in the radial direction of the rotation center, and is elastically extended and contracted in the circumferential direction, being interposed between the first rotating element and the second rotating element in parallel with the first elastic element. A second elastic element,
An intermediate mass element provided at an intermediate position in the circumferential direction of the first elastic element;
Equipped with
A first state in which one of the first elastic element and the second elastic element is elastically compressed and the other is not elastically compressed due to the twisting of the first rotating element and the second rotating element; And a second state in which both the first elastic element and the second elastic element are elastically compressed by a larger twist angle between the first rotating element and the second rotating element than in the first state. damper.   The damper according to claim 1, wherein in the first state, the first elastic element is not elastically compressed and the second elastic element is elastically compressed.   The rate of change per unit angle of the twist angle between the first elastic element and the second elastic element of the torsion torque between the first rotary element and the second rotary element due to the expansion and contraction of the first elastic element is the above The damper according to claim 1, wherein the torsion torque due to the expansion and contraction of the second elastic element is smaller than a rate of change per unit angle of the torsion angle.   The damper according to any one of claims 1 to 3, wherein the intermediate mass element is disposed between the first rotation element and the second rotation element in the axial direction of the rotation center.

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