JP2016114193A - Damper device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a damper device having a new configuration capable of attaining entirely a larger difference between the first sliding torque and the second sliding torque, for example.SOLUTION: A damper device 100 in accordance with one preferred embodiment is provided with first sliding members 6, 7 for generating first sliding torques T11, T12 both when a second rotating member 2 rotates in the first direction [F direction] in respect to a first rotating member 1 under the first state, for example, and when the second rotating member 2 rotates in the second direction [opposite direction of F direction] opposite to the first direction in respect to the first rotating member 1; and second sliding members 8, 9 for generating larger second sliding torques T21, T22 than the first sliding torques T11, T12 both when the second rotating member 2 rotates in the second direction in respect to the first rotating member 1 under the second state and when the second rotating member 2 rotates in the first direction in respect to the first rotating member 1.SELECTED DRAWING: Figure 4

Description

  Embodiments described herein relate generally to a damper device.

  Conventionally, the elastic member that is elastically deformed by the relative rotation of the first rotating member and the second rotating member, and the second rotating member is in a first angle with respect to the first rotating member. A first sliding member that generates a first sliding torque when rotating in one direction, and a second rotating member that is at a first angle relative to the first rotating member; There is known a damper device including a second sliding member that generates a second sliding torque larger than the first sliding torque when rotating in a direction.

JP 2014-214819 A

  In this type of damper device, for example, it is preferable if a new configuration capable of further increasing the difference between the first sliding torque and the second sliding torque as a whole is obtained.

  The damper device according to the embodiment includes, for example, a first rotating member that can rotate around the rotation center, a second rotating member that can rotate around the rotation center, the first rotating member, and the second rotation. An elastic member that is elastically deformed by relative rotation with the member, and a first twisted in a first direction from a state where the second rotating member is at a first angle with respect to the first rotating member. The second rotating member rotates in the first direction with respect to the first rotating member, and the second rotating member is in the first direction with respect to the first rotating member. A first sliding member for generating a first sliding torque in both cases of rotating in a second direction opposite to the direction, and the second rotating member relative to the first rotating member. In the second state twisted in the second direction from the state at the first angle, the second Both when the rotating member rotates in the second direction with respect to the first rotating member and when the second rotating member rotates in the first direction with respect to the first rotating member And a second sliding member for generating a second sliding torque larger than the first sliding torque. Therefore, for example, the torque relaxation performance can be varied depending on the twist direction of the second rotating member relative to the first rotating member. In addition, for example, compared to the conventional configuration in which the second sliding member generates the second sliding torque only in one direction in which the second rotating member rotates in the second direction with respect to the first rotating member in the second state. As a whole, the difference between the first sliding torque and the second sliding torque can be further increased.

  Further, the damper device includes, for example, a third rotating member that can rotate around the rotation center, and the first sliding member is provided between the second rotating member and the third rotating member. And the second sliding member is provided between the first rotating member and the third rotating member, and in the first state, the first rotating member The first rotating member and the second rotating member are rotated by the relative rotation between the second rotating member and the third rotating member. Are rubbed against each other to generate the first sliding torque, and in the second state, the second rotating member and the third rotating member rotate integrally, The relative rotation between the rotating member and the third rotating member causes the second sliding member and the third rotating member to rotate. The second sliding torque is generated by the third rotating member rub against each other. Thus, for example, a damper device that can increase the difference between the first sliding torque and the second sliding torque as a whole can be realized by the configuration using the third rotating member.

  In the damper device, for example, when the third rotating member rotates in the second direction with respect to the first rotating member in the second state, A first receiving portion pushed in the second direction by the second rotating member; and the second rotating member in the first direction with respect to the first rotating member in the second state. A second receiving portion that is pushed in the first direction by the elastic member together with the second rotating member when rotating. Thus, for example, when rotating in the second direction, the second rotating member and the first receiving portion are hooked together in the circumferential direction, and when rotating in the first direction, the elastic member and the second receiving portion are engaged. With the configuration in which the portion and the second rotating member are hooked in the circumferential direction, a damper device that can obtain the second sliding torque in both the second direction and the first direction can be realized.

  In the damper device, for example, the fourth rotating member connected to the engine side and rotatable around the rotation center, and sandwiched between the first rotating member and the fourth rotating member. A friction member, and when the difference in torque between the first rotation member and the fourth rotation member is equal to or greater than a predetermined value, the friction member is the first rotation member and the first rotation member. And a limiter configured to slide with at least one of the four rotating members so that the first rotating member and the fourth rotating member rotate relatively around the rotation center. Therefore, since the limiter unit can be provided in the fourth rotating member connected to the input side, for example, each rotating member is compared with the case where the limiter unit is provided in the second rotating member connected to the output side. The shape, that is, the power transmission path may be further simplified, or the damper device may be configured to be smaller in the axial direction.

FIG. 1 is an exemplary front view of a damper device according to an embodiment. 2 is a cross-sectional view taken along the line II-II in FIG. FIG. 3 is an enlarged view of a part of FIG. FIG. 4 is an exemplary characteristic diagram showing a relationship between a torsion angle and a torque difference between the input side and the output side of the damper device according to the embodiment. FIG. 5 is a front view of a part of the damper device in the O state shown in FIG. 6 is a front view of a part of the damper device in the state A shown in FIG. FIG. 7 is a front view of a part of the damper device in the B state shown in FIG. FIG. 8 is a front view of a part of the damper device in the C state shown in FIG. FIG. 9 is a front view of a part of the damper device in the D state shown in FIG. FIG. 10 is a front view of a part of the damper device in the E state shown in FIG. FIG. 11 is a front view of a part of the damper device in the F state shown in FIG. 12 is a front view of a part of the damper device in the G state shown in FIG. FIG. 13 is a front view of a part of the damper device in the H state shown in FIG. FIG. 14 is a front view of a part of the damper device in the I state shown in FIG. FIG. 15 is a front view of a part of the damper device in the J state shown in FIG.

  Hereinafter, exemplary embodiments of the present invention are disclosed. The configuration of the embodiment shown below and the operations, results, and effects brought about by the configuration are merely examples. The present invention can be realized by configurations other than those disclosed in the following embodiments. Further, according to the present invention, it is possible to obtain at least one of various effects obtained by the configuration.

  As shown in FIG. 2, the damper device 100 is positioned, for example, between an output shaft S1 of the engine on the input side and an input shaft S2 of the transmission on the output side. The damper device 100 can reduce fluctuations such as torque and rotation as driving force between the input side and the output side. The damper device 100 can also be referred to as a torque fluctuation absorber. The damper device 100 is not limited to be provided between the engine and the transmission, but can be provided between the other two rotating elements, for example, between the engine and the motor generator. It can be provided in a vehicle or a machine having a rotating element. In the following description, the axial direction indicates the axial direction of the input shaft S2, the radial direction indicates the radial direction of the input shaft S2, and the circumferential direction indicates the circumferential direction of the input shaft S2. In the present embodiment, the rotation center Ax of the damper device 100 substantially coincides with the rotation centers of the input shaft S2 and the output shaft S1. In the drawing, one side in the axial direction is indicated by an arrow X, the outer side in the radial direction is indicated by an arrow R, and one side in the circumferential direction is indicated by an arrow F. In the present embodiment, the F direction is an example of a first direction. In the following description, for the sake of convenience, the line of sight from the right side of FIG. 2 is a front view, and the line of sight from the left side of FIG.

  The damper device 100 rotates around the rotation center Ax. As shown in FIGS. 1 and 2, the damper device 100 is configured as a flat disk that is thin in the axial direction as a whole.

  The damper device 100 includes a damper unit 101 and a limiter unit 102. The damper part 101 is located on the radially inner side of the damper device 100, and the limiter part 102 is located on the radially outer side than the damper part 101. Moreover, the damper part 101 is comprised by the flat disk shape thin in the axial direction, and the limiter part 102 is comprised by the annular | circular shape.

  As shown in FIG. 2, the damper portion 101 includes a first rotating member 1, a second rotating member 2, a third rotating member 3, a first rotating member 1 and a second rotating member 2. And an elastic member 51 positioned between the two. The damper portion 101 relieves torque fluctuation by the elastic member 51 elastically expanding and contracting with relative rotation around the rotation center Ax between the first rotating member 1 and the second rotating member 2. Further, as shown in the upper side of FIG. 2, the limiter unit 102 is provided between the first rotating member 1, the fourth rotating member 4, and the first rotating member 1 and the fourth rotating member 4. And positioned friction members 55 and 56. The limiter unit 102 has the friction members 55 and 56 as the first rotating member 1 and the fourth rotating member in accordance with the relative rotation of the first rotating member 1 and the fourth rotating member 4 around the rotation center Ax. By sliding with at least one of the four members, transmission of excessive torque is blocked between the first rotating member 1 and the fourth rotating member 4.

  As shown in FIG. 2, the first rotating member 1, the second rotating member 2, the third rotating member 3, and the fourth rotating member 4 each cross the rotation center Ax in the radial direction. It has an annular shape and a plate shape. The first rotating member 1, the second rotating member 2, the third rotating member 3, and the fourth rotating member 4 are each provided so as to be rotatable around the rotation center Ax. In the present embodiment, for example, the fourth rotating member 4 is connected to the output shaft S1 of the engine on the input side via the flywheel FW, and the first rotating member 1 includes the second rotating member 2. To the input shaft S2 of the transmission on the output side.

  The first rotating member 1 constitutes a part of the damper part 101 and the limiter part 102. As shown in FIG. 2, the first rotating member 1 includes a plurality of side plates 11 and 12 and a lining plate 13. In the present embodiment, for example, the two side plates 11 and 12 are positioned on the radially inner side of the first rotating member 1, and the lining plate 13 is positioned on the radially outer side of the side plates 11 and 12. ing.

  The side plate 11 is located on one side (X direction) of the side plate 12 in the axial direction, that is, on the left side in FIG. The side plates 11 and 12 are each configured in an annular shape spreading in the radial direction. The side plates 11 and 12 are at least partially positioned at an axial distance from each other. The side plates 11 and 12 are coupled to each other by a coupler C1 such as a rivet shown on the upper side of the elastic member 51 in FIG. 2, and rotate integrally around the rotation center Ax. As shown in FIG. 1, the side plates 11 and 12 are provided with a plurality of openings 11 a and 12 a that are spaced apart from each other in the circumferential direction. As shown in FIG. 2, the opening 11a and the opening 12a are configured as through holes that overlap each other in the axial direction, for example. In the opening 11a and the opening 12a, an elastic member 51 is disposed between one circumferential edge and the other circumferential edge.

  As shown in the upper side and the lower side of FIG. 2, the lining plate 13 is configured in an annular shape spreading in the radial direction. A radially outer portion of the lining plate 13 is sandwiched between the friction member 55 and the friction member 56. Further, the radially inner portion of the lining plate 13 is coupled together with the side plates 11 and 12 by a coupler C1. Therefore, the lining plate 13 rotates integrally with the side plates 11 and 12. The first rotating member 1, that is, the side plates 11 and 12 and the lining plate 13 can be made of, for example, a metal material. Moreover, the lining plate 13 can be comprised with the metal material different from the side plates 11 and 12, such as stainless steel, for example.

  The second rotating member 2 constitutes a part of the damper portion 101. The second rotating member 2 has a hub member 21. As shown in FIG. 2, the hub member 21 has a cylindrical portion 21a and an overhang portion 21b. The overhang portion 21b can also be referred to as a wall portion. The cylindrical portion 21a is a radially inner portion of the hub member 21, and is configured in a cylindrical shape. As shown in FIG. 3, the cylindrical portion 21 a is located inside the side plates 11 and 12 in the radial direction and is provided so as to surround the input shaft S <b> 2 of the transmission. The cylindrical portion 21a is coupled to the input shaft S2 by, for example, press-fitting or spline coupling, and rotates integrally with the input shaft S2.

  As shown in FIG. 2, the overhanging portion 21b protrudes outward in the radial direction from a substantially central portion in the axial direction of the cylindrical portion 21a. The overhanging portion 21 b is configured in a plate shape spreading in the radial direction, and is positioned between the side plate 11 and the side plate 12. Further, as shown in FIG. 5, the overhanging portion 21 b is provided with a plurality of openings 22 at intervals in the circumferential direction. The opening 22 is configured as, for example, a notch that opens toward the outside in the radial direction of the overhang 21b. Moreover, the opening part 22 has penetrated the overhang | projection part 21b along the axial direction. The opening 22 includes openings 22a and 22b. The opening 22a is located outside the opening 22 in the radial direction, and the opening 22b is located inside the opening 22a in the radial direction. As shown in FIG. 2, the opening 22a and the openings 11a and 12a of the side plates 11 and 12 overlap each other in the axial direction. In the opening 22a, an elastic member 51 is disposed between the edge on one side and the edge on the other side in the circumferential direction. Moreover, the opening part 22b is comprised as an elongate hole which the coupler C3 shown by FIG.

  The hub member 21 is provided to be relatively rotatable around the side plates 11 and 12 and the rotation center Ax. However, the relative rotation between the hub member 21 and the side plates 11 and 12 is limited to a predetermined angle range by, for example, contact of stoppers (not shown). The hub member 21, that is, the second rotating member 2, can be made of, for example, a metal material.

  The elastic member 51 shown in FIGS. 1 and 2 is a coil spring made of, for example, a metal material and extending substantially along the circumferential direction. The elastic member 51 functions as a compression spring that elastically expands and contracts substantially along the circumferential direction. As shown in FIG. 1, in the present embodiment, support members 52 that support the end portions 51 a of the elastic member 51 are provided on both sides of the elastic member 51 in the circumferential direction. The support member 52 is a retainer, for example. The support member 52, for example, supports the elastic member 51 more stably, elastically deforms the elastic member 51 more stably, or directly connects the elastic member 51 with the side plates 11, 12 and the hub member 21. It can have a function of suppressing contact. The support member 52 can be made of, for example, a synthetic resin material.

  As shown in FIG. 1, the elastic member 51 and the support member 52 are accommodated in the openings 11 a and 12 a and the opening 22 a that overlap each other in the axial direction, and are connected to the side plates 11 and 12 and the hub member 21. ing. With such a configuration, when the edge on one side in the circumferential direction of the openings 11a and 12a and the edge on the other side in the circumferential direction of the opening 22a rotate relatively to each other, the edges are elastic. The member 51 is elastically contracted. Conversely, in a state where the openings 11a and 12a and the opening 22a are elastically shrunk, one edge in the circumferential direction of the openings 11a and 12a and the other edge in the circumferential direction of the opening 22a When they are relatively rotated in the direction away from each other, the elastic member 51 is elastically extended. That is, the elastic member 51 is sandwiched between the first rotating member 1 and the second rotating member 2, and elastically expands and contracts along the substantially circumferential direction with relative rotation around the rotation center Ax. . The elastic member 51 stores torque as a compression force by being elastically contracted, and releases the compression force as a torque by being elastically extended. Thus, the elastic member 51 is positioned between the first rotating member 1 and the second rotating member 2, and substantially extends in the circumferential direction between the first rotating member 1 and the second rotating member 2. It is sandwiched and elastically expands and contracts substantially along the circumferential direction. The damper part 101 can relieve torque fluctuations by the expansion and contraction of the elastic member 51.

  The fourth rotating member 4 constitutes a part of the limiter unit 102. As shown in the upper side and the lower side of FIG. 2, the fourth rotating member 4 includes a support plate 41, a cover plate 42, and a pressure plate 43. The support plate 41 is positioned on one side of the fourth rotating member 4 in the axial direction, that is, on the left side in FIG. 2, the cover plate 42 is positioned on the other side of the support plate 41 in the axial direction, and the pressure plate 43 is The support plate 41 and the cover plate 42 are positioned. In the present embodiment, the limiter unit 102 includes the cover plate 42, the friction member 56, the lining plate 13, the friction member 55, the pressure plate 43, the elastic member 53, and the other side in the axial direction from the other side in the axial direction. A support plate 41 is provided. The cover plate 42, the friction member 56, the lining plate 13, the friction member 55, the pressure plate 43, the elastic member 53, and the support plate 41 overlap with each other in close contact with each other in the axial direction. The fourth rotating member 2 and the elastic member 53 sandwich the friction member 56, the lining plate 13, and the friction member 55 from the outside in the radial direction and press them elastically by sandwiching them in the axial direction.

  The support plate 41 is configured in an annular shape spreading in the radial direction. A radially outer portion of the support plate 41 is located on the other side in the axial direction of the flywheel FW. An opening 41a through which a coupler C2 such as a bolt or a screw is passed is provided in the radially outer portion. Further, the radially inner portion of the support plate 41 is positioned on one side of the elastic member 53 in the axial direction.

  The cover plate 42 is configured in an annular shape spreading in the radial direction. The radially outer portion of the cover plate 42 is located on the other side of the support plate 41 in the axial direction. Moreover, the opening part 42a which overlapped with the opening part 41a and the axial direction is provided in the part outside this radial direction. In the present embodiment, the support plate 41 and the cover plate 42 are coupled to the flywheel FW by the coupling tool C2 through which the openings 41a and 42a are passed. The support plate 41 and the cover plate 42 are coupled to the engine output shaft S1 via the flywheel FW, and rotate integrally with the output shaft S1. The flywheel FW can also be referred to as a mass body or an inertial body. Further, the radially inner portion of the cover plate 42 is located on the other side of the friction member 56 in the axial direction.

  The pressure plate 43 is formed in an annular shape spreading in the radial direction. As shown in the lower side of FIG. 2, the pressure plate 43 has a protrusion 43 a that protrudes from the outer end in the radial direction to the other side in the axial direction, that is, the right side in FIG. 2. The protrusion 43 a is inserted into an opening 42 b provided in the cover plate 42. The protrusion 43a and the edge of the opening 42b of the cover plate 42 are hooked to each other in the circumferential direction. Therefore, the pressure plate 43 rotates integrally with the cover plate 42 and the support plate 41 around the rotation center Ax. The fourth rotating member 4, that is, the support plate 41, the cover plate 42, and the pressure plate 43 can be made of, for example, a metal material.

  In the present embodiment, for example, the friction member 55 is positioned between the pressure plate 43 and the lining plate 13, and the friction member 56 is positioned between the cover plate 42 and the lining plate 13. The friction members 55 and 56 are each configured in an annular and plate shape spreading in the radial direction. The friction member 55 and the pressure plate 43, and the friction member 56 and the cover plate 42 may be provided with hooking portions that are hooked to each other in the circumferential direction. Therefore, the friction members 55 and 56 rotate integrally with the pressure plate 43 and the cover plate 42 around the rotation center Ax. The friction members 55 and 56 can be made of, for example, a synthetic resin material containing glass fiber material or synthetic rubber.

  The elastic member 53 is positioned between the support plate 41 and the pressure plate 43, and gives the support plate 41 and the pressure plate 43 elastic forces in a direction away from each other in the axial direction. The elastic member 53 presses the pressure plate 43 against the cover plate 42 with the friction member 55, the lining plate 13, and the friction member 56 interposed therebetween. That is, a frictional force is generated between the friction members 55 and 56 and the lining plate 13 by the load due to the elastic force of the elastic member 53. In the present embodiment, the fourth rotating member 4 and the first rotating member 1 do not slip until the torque difference exceeds the maximum static friction force as the friction force. The elastic member 53 can be constituted by, for example, an annular cone spring made of a metal material.

  In the limiter unit 102, when the value of the difference in torque between the damper unit 101 and the side of the limiter unit 102 opposite to the damper unit 101 is smaller than a threshold value within the set range, the elastic pressing force of the elastic member 53 causes The limiter unit 102 does not slip, and the damper device 100 including the damper unit 101 and the limiter unit 102 rotates integrally. In other words, in a state where the difference in torque between the damper portion 101 and the side of the limiter portion 102 opposite to the damper portion 101 is larger than the threshold value, the friction force generated by the elastic pressing force of the elastic member 53 in the limiter portion 102. Sliding beyond the range occurs. The limiter unit 102 thus functions as a torque limiter, and excessive torque transmission exceeding the set value is suppressed.

  Here, in the present embodiment, the limiter unit 102 is provided between the first rotating member 1 and the fourth rotating member 4 connected to the input side. Therefore, according to the present embodiment, for example, the limiter unit 102 can suppress transmission of excessive torque between the damper unit 101 and the input side. Further, since the limiter unit 102 can be provided on the fourth rotating member 4 connected to the input side, for example, compared to the case where the limiter unit 102 is provided on the second rotating member 2 connected to the output side. The shape of each rotating member, that is, the power transmission path may be further simplified, or the damper device 100 may be configured to be smaller in the axial direction.

  The third rotating member 3 constitutes a part of the damper portion 101. As shown in FIG. 3, the third rotating member 3 has a plurality of control plates 31 and 32. In the present embodiment, for example, two control plates 31 and 32 are provided in parallel to each other with an interval in the axial direction. The control plates 31 and 32 are each configured in an annular shape spreading in the radial direction. The control plate 31 is located between the side plate 11 and the overhanging portion 21b, and the control plate 32 is located between the side plate 12 and the overhanging portion 21b. The control plates 31 and 32 are coupled to each other by a coupler C3 such as a rivet that penetrates the opening 22b in the axial direction, and rotate integrally around the rotation center Ax. As shown in FIG. 5, in the present embodiment, four couplers C <b> 3 are accommodated in the openings 22 b at intervals from each other, corresponding to the four openings 22 b arranged in the circumferential direction. Further, the control plates 31 and 32 have projecting portions 31a and 32a projecting radially outward from the respective outer peripheral portions. As shown in FIG. 5, in the present embodiment, the protruding portions 31 a and 32 a are located on one side (F direction side) of the elastic member 51 in the circumferential direction. In the present embodiment, the control plates 31 and 32 are each provided with two protrusions 31a and 32a spaced apart from each other in the circumferential direction. The third rotating member 3, that is, the control plates 31 and 32 can be made of, for example, a metal material.

  Also, as shown in FIG. 3, first sliding members 6 and 7 are provided between the control plates 31 and 32 and the overhanging portion 21b, respectively. The first sliding members 6 and 7 are each configured in an annular and plate shape spreading in the radial direction. The first sliding member 6 is in contact with the control plate 31 and the overhanging portion 21b, and the first sliding member 7 is in contact with the overhanging portion 21b. Further, the radially inner portion of the first sliding member 7 is formed in a cylindrical shape protruding to the control plate 32 side, and is in contact with the outer surface of the cylindrical portion 21 a and the inner peripheral portion of the control plate 32. . The first sliding member 7 and the control plate 32, and the first sliding member 6 and the control plate 31 may be provided with hook portions that are hooked to each other in the circumferential direction. Therefore, the first sliding members 6 and 7 rotate integrally around the control plates 31 and 32 and the rotation center Ax. In the present embodiment, when the hub member 21 and the control plates 31 and 32 rotate relatively, the first sliding torque T11 is caused by rubbing the hub member 21 and the first sliding members 6 and 7 with each other. , T12 (see FIG. 4) occurs. The first sliding torques T11 and T12 can suppress, for example, relatively small vibrations and noises that occur during normal running after the engine is started. The first sliding members 6 and 7 can be made of, for example, a synthetic resin material.

  Further, as shown in FIG. 3, an elastic member 57 is provided between the control plate 32 and the first sliding member 7. The elastic member 57 overlaps the sliding surfaces of the first sliding members 6 and 7 in the axial direction. The elastic member 57 gives the control plate 32 and the first sliding member 7 an elastic force in a direction away from each other in the axial direction. That is, the elastic member 57 presses the first sliding member 7 against the overhanging portion 21 b and presses the first sliding member 6 against the overhanging portion 21 b via the control plate 32 and the control plate 31. Thus, the elastic member 57 can give sliding resistance to the first sliding members 6 and 7. The elastic member 57 is, for example, an annular cone spring made of a metal material.

  Also, as shown in FIG. 3, second sliding members 8 and 9 are provided between the side plates 11 and 12 and the control plates 31 and 32, respectively. The second sliding members 8 and 9 are each configured in an annular and plate shape that expands in the radial direction. The second sliding member 8 is in contact with the side plate 11 and the control plate 31, and the second sliding member 9 is in contact with the control plate 32. Further, the radially inner portion of the second sliding member 8 is formed in a cylindrical shape projecting toward the side plate 11, and is in contact with the outer surface of the cylindrical portion 21 a and the inner peripheral portion of the side plate 11. . Further, the radially inner portion of the second sliding member 9 is formed in a cylindrical shape projecting toward the side plate 12 and is in contact with the outer surface of the cylindrical portion 21 a and the inner peripheral portion of the side plate 12. . Further, as shown below the rotation center Ax in FIG. 2, the second sliding members 8, 9 have protrusions 8 a, 9 a that protrude in the axial direction from the respective outer ends in the radial direction. Have. The protrusion 8 a is inserted into the opening 11 b of the side plate 11, and the protrusion 9 a is inserted into the opening 12 b of the side plate 12. The protrusions 8a and 9a and the edges of the openings 11b and 12b are hooked to each other in the circumferential direction. Therefore, the second sliding members 8 and 9 rotate integrally around the side plates 11 and 12 and the rotation center Ax. In the present embodiment, when the side plates 11 and 12 and the control plates 31 and 32 rotate relatively, the control plates 31 and 32 and the second sliding members 8 and 9 rub against each other to cause the second Sliding torques T21 and T22 (see FIG. 4) are generated. Here, in the present embodiment, for example, the second sliding torque is determined depending on the material of the first sliding members 6 and 7 and the second sliding members 8 and 9, the surface roughness, the contact area, and the like. T21 and T22 are configured to be larger than the first sliding torques T11 and T12. In the present embodiment, the second sliding torques T21 and T22 can suppress, for example, relatively large vibrations and noises generated when the engine is started. The second sliding members 8 and 9 can be made of, for example, a synthetic resin material.

  Further, as shown in FIG. 3, an elastic member 58 is provided between the side plate 12 and the second sliding member 9. The elastic member 58 overlaps the sliding surfaces of the second sliding members 8 and 9 in the axial direction. The elastic member 58 gives the side plate 12 and the second sliding member 9 an elastic force in a direction away from each other in the axial direction. That is, the elastic member 58 presses the second sliding member 9 against the control plate 32, and consequently presses the control plate 31 against the second sliding member 8 via the control plate 32. As described above, the elastic member 58 can give a sliding resistance to the second sliding members 8 and 9. The elastic member 58 is, for example, an annular cone spring made of a metal material.

  As shown in FIGS. 1 and 5, in the present embodiment, for example, the elastic member 51 includes a first elastic member 51 </ b> A and a second elastic member 51 </ b> B. In FIG. 5 and subsequent figures, for convenience, only the center line of the first elastic member 51A and the second elastic member 51B is shown. As shown in FIG. 5, in this embodiment, for example, the first elastic member 51 </ b> A and the second elastic member 52 </ b> B are arranged in the circumferential direction in four sets of openings 11 a, 12 a, and 22 a arranged in the circumferential direction. They are housed alternately. Here, in the present embodiment, the free length of the second elastic member 51B is longer than the free length of the first elastic member 51A. In the present embodiment, the lengths of the four openings 22a in the circumferential direction are also different from each other, corresponding to the free lengths of the first elastic member 51A and the second elastic member 51B. That is, the circumferential length of the two openings 22a in which the first elastic member 51A is disposed is configured to be shorter than the circumferential length of the two openings 22a in which the second elastic member 51B is disposed. ing. On the other hand, the circumferential lengths of the openings 11a and 12a are all the same. Specifically, the circumferential lengths of the openings 11a and 12a correspond to the free length of the second elastic member 51B, respectively.

  Next, with reference to FIGS. 4 to 15, the relative rotational states of the first rotating member 1, the second rotating member 2, and the third rotating member 3 and the accompanying change in the sliding torque will be described. Is done. FIG. 4 shows an example of the relationship between the twist angle and the torque difference between the input side and the output side. The twist angle may also be referred to as an angle difference. The horizontal axis of the characteristic diagram shown in FIG. 4 is the twist angle, and the vertical axis is the torque difference. The horizontal axis of FIG. 4 is the rotation angle of the second rotating member 2 with respect to the first rotating member 1. In FIG. 4, the rotation angle of the 1st direction (F direction of FIG. 1) of the 2nd rotation member 2 with respect to the 1st rotation member 1 is so large that it goes to the right side of a horizontal axis. The vertical axis in FIG. 4 is the relative torque difference of the second rotating member 2 with respect to the first rotating member 1. In FIG. 4, the torque difference in the first direction increases toward the upper side of the vertical axis.

  FIG. 5 shows the state O of FIG. 4 in which no torque difference is generated between the first rotating member 1 and the second rotating member 2. In the O state, the free-length second elastic member 51B is in contact with the edges on both sides in the circumferential direction of the openings 11a, 12a, and 22a via the support member 52. On the other hand, the first elastic member 51A having a free length is in contact with the edges on both sides in the circumferential direction of the opening 22a via the support member 52, but is in contact with the edges on both sides in the circumferential direction of the openings 11a and 12a. Not done. In the O state, the coupler C3 is positioned close to the end face on one side (F direction side) in the circumferential direction of the opening 22b. Further, in the O state, the protrusions 31a and 32a enter the openings 11a and 12a with the axial line of sight shown in FIG. 5, and the support member 52 and one side in the circumferential direction of the first elastic member 51A. In contact.

  FIG. 6 shows a state in which the second rotating member 2 is rotated by a predetermined angle in the F direction with respect to the first rotating member 1 from the state O in FIG. The state in FIG. 6 corresponds to the state A in FIG. Between the O state in FIG. 5 and the A state in FIG. 6, the second elastic member 51B has one side in the circumferential direction of the openings 11a and 12a, in other words, the edge on the F direction side and the circumference of the opening 22a. It shrinks elastically with the edge on the other side of the direction. On the other hand, since the first elastic member 51A is shorter in the circumferential direction than the second elastic member 51B, the first elastic member 51A and the second rotating member 2 together with the second rotating member 2 maintain the free length. Rotate in the direction. Further, between the state O in FIG. 5 and the state A in FIG. 6, the protruding portions 31 a and 32 a are pushed by the first elastic member 51 </ b> A to the one side in the circumferential direction via the support member 52. As a result, the second rotating member 2 and the third rotating member 3 are integrally rotated in the circumferential direction with respect to the first rotating member 1, and the control plates 31, 32 and the second sliding members 8, 9 are rotated. And the second sliding torque T22 above the center line in FIG. 4 is generated. In the present embodiment, the protruding portions 31a and 32a are an example of a second receiving portion.

  FIG. 7 shows a state in which the second rotating member 2 is rotated by a predetermined angle in the F direction with respect to the first rotating member 1 from the state A in FIG. 6. 7 corresponds to the state B in FIG. In the state A of FIG. 6, the first elastic member 51A contacts the edge on one side in the circumferential direction of the openings 11a and 12a via the support member 52, and the protrusions 31a and 32a are shown in FIG. It deviates to the one side of the circumferential direction of opening part 11a, 12a with the eyes | visual_axis of an axial direction. The first elastic member 51A having a free length is sandwiched between the edge on one side in the circumferential direction of the openings 11a and 12a and the edge on the other side in the circumferential direction of the opening 22a. Moreover, in the A state of FIG. 6, the state which the coupler C3 adjoined to the end surface of the one side of the circumferential direction of the opening part 22b is maintained. Thereby, when the 2nd rotation member 2 rotates further to the one side of the circumferential direction from the A state of FIG. 6, the 2nd rotation member 2 and the 3rd rotation member 3 do not rotate integrally. The second rotating member 2 rotates in the circumferential direction with respect to the first rotating member 1 and the third rotating member 3. Between the state A of FIG. 6 and the state B of FIG. 7, the second rotating member 2 rotates in the circumferential direction with respect to the first rotating member 1 and the third rotating member 3, and the hub member 21 and the first rotating member 3 When the first sliding members 6 and 7 rub against each other, a first sliding torque T11 above the center line in FIG. 4 is generated. In addition, between the A state of FIG. 6 and the B state of FIG. 7, the 1st elastic member 51A and the 2nd elastic member 51B are the edge part and opening part of the one side of the circumferential direction of opening part 11a, 12a. It contracts elastically between the edge part of the other circumferential side of 22a.

  FIG. 8 shows a state in which the second rotating member 2 is rotated by a predetermined angle in the F direction with respect to the first rotating member 1 from the state B in FIG. 7. The state in FIG. 8 corresponds to the state C in FIG. Between the B state in FIG. 7 and the C state in FIG. 8, the first sliding torque T <b> 11 is generated as in the state between the A state in FIG. 6 and the B state in FIG. 7. In the state C in FIG. 8, rotation of the second rotating member 2 to one side in the circumferential direction with respect to the first rotating member 1 is restricted by contact of stoppers (not shown).

  FIG. 9 shows a state in which the second rotating member 2 is rotated by a predetermined angle in the direction opposite to the F direction with respect to the first rotating member 1 from the state C in FIG. The state in FIG. 9 corresponds to the D state in FIG. Between the C state of FIG. 8 and the D state of FIG. 9, the first elastic member 51A and the second elastic member 51B are connected to the edges on one side in the circumferential direction of the openings 11a and 12a and the openings 22a. Elastically stretches between the other edge in the circumferential direction. Further, the second rotating member 2 rotates in the circumferential direction with respect to the first rotating member 1 and the third rotating member 3, and the hub member 21 and the first sliding members 6 and 7 rub against each other. As a result, a first sliding torque T12 below the center line in FIG. 4 is generated. The second rotating member 2 rotates to the other side in the circumferential direction with respect to the first rotating member 1 and the third rotating member 3, so that the coupler C3 is on one side in the circumferential direction of the opening 22b. It returns to the state close to the end face. In the present embodiment, the A state and the D state described above are examples of a state in which the second rotating member 2 is at a first angle with respect to the first rotating member 1.

  FIG. 10 shows a state in which the second rotating member 2 is rotated by a predetermined angle in the direction opposite to the F direction with respect to the first rotating member 1 from the state D in FIG. 9. The state in FIG. 10 corresponds to the E state in FIG. In the D state of FIG. 9, the first elastic member 51A returns to the free length. Therefore, between the D state of FIG. 9 and the E state of FIG. 10, the second elastic member 51B has one edge in the circumferential direction of the openings 11a and 12a and the other side in the circumferential direction of the opening 22a. The first elastic member 51 </ b> A rotates in the circumferential direction with respect to the first rotating member 1 together with the second rotating member 2 while maintaining a free length. Moreover, between the D state of FIG. 9 and the E state of FIG. 10, the 1st sliding torque T12 arises similarly to between the C state of FIG. 8, and the D state of FIG.

  FIG. 11 shows a state in which the second rotating member 2 is rotated by a predetermined angle in the direction opposite to the F direction with respect to the first rotating member 1 from the E state of FIG. Note that the state of FIG. 11 corresponds to the F state of FIG. In the E state of FIG. 10, the coupler C3 and the end surface on one side in the circumferential direction of the opening 22b are in contact with each other. Accordingly, when the second rotating member 2 further rotates from the E state in FIG. 10 to the other side in the circumferential direction, the coupler C3 is pushed to the other side in the circumferential direction, whereby the second rotating member 2 is pressed. And the third rotating member 3 rotate together. Between the E state in FIG. 10 and the F state in FIG. 11, the second rotating member 2 and the third rotating member 3 integrally rotate in the circumferential direction with respect to the first rotating member 1, and the control plate As a result of rubbing 31 and 32 and the second sliding members 8 and 9, a second sliding torque T <b> 21 below the center line in FIG. 4 is generated. In the present embodiment, the coupler C3 is an example of a first receiving unit. In addition, between the E state of FIG. 10, and the F state of FIG. 11, the 2nd elastic member 51B is the edge part of the circumferential direction of opening part 11a, 12a, and the other side of the circumferential direction of opening part 22a. The first elastic member 51 </ b> A rotates in the circumferential direction with respect to the first rotating member 1 together with the second rotating member 2 while maintaining a free length.

  FIG. 12 shows a state in which the second rotating member 2 is rotated by a predetermined angle in the direction opposite to the F direction with respect to the first rotating member 1 from the F state of FIG. 11. The state in FIG. 12 corresponds to the G state in FIG. In the F state of FIG. 11, the second elastic member 51B returns to the free length. Therefore, between the F state in FIG. 11 and the G state in FIG. 12, the second elastic member 51B has the other edge in the circumferential direction of the openings 11a and 12a and the one side in the circumferential direction of the opening 22a. It elastically shrinks between the edges of the. On the other hand, since the first elastic member 51A is shorter in the circumferential direction than the second elastic member 51B, the first elastic member 51A and the second rotating member 2 together with the second rotating member 2 maintain the free length. Rotate in the direction. In addition, between the F state of FIG. 11 and the G state of FIG. 12, the 2nd sliding torque T21 arises similarly to between the E state of FIG. 10, and the F state of FIG.

  FIG. 13 shows a state in which the second rotating member 2 is rotated by a predetermined angle in the direction opposite to the F direction with respect to the first rotating member 1 from the G state of FIG. The state in FIG. 13 corresponds to the H state in FIG. In the G state of FIG. 12, the first elastic member 51A having a free length is sandwiched between the edge on the other side in the circumferential direction of the openings 11a and 12a and the edge on the one side in the circumferential direction of the opening 22a. It is. Therefore, between the G state in FIG. 12 and the H state in FIG. 13, the first elastic member 51 </ b> A and the second elastic member 51 </ b> B have the edge and the opening on the other side in the circumferential direction of the openings 11 a and 12 a. It contracts elastically between the edges on one side in the circumferential direction of 22a. Between the G state in FIG. 12 and the H state in FIG. 13, the second sliding torque T <b> 21 is generated as in the F state in FIG. 11 and the G state in FIG. 12. In the H state of FIG. 13, the rotation of the second rotating member 2 to the other side in the circumferential direction with respect to the first rotating member 1 is limited by contact of stoppers (not shown). Further, between the E state in FIG. 10 and the H state in FIG. 13, the second rotating member 2 and the third rotating member 3 rotate integrally with the first rotating member 1 in the circumferential direction. Thus, the protrusions 31a and 32a enter the openings 11a and 12a with the line of sight in the axial direction shown in FIGS.

  FIG. 14 shows a state in which the second rotating member 2 is rotated by a predetermined angle in the F direction with respect to the first rotating member 1 from the H state in FIG. 13. The state in FIG. 14 corresponds to the I state in FIG. Between the H state in FIG. 13 and the I state in FIG. 14, the first elastic member 51 </ b> A and the second elastic member 51 </ b> B are connected to the edges on the other side in the circumferential direction of the openings 11 a and 12 a and the openings 22 a. It stretches elastically between the edges on one side in the circumferential direction. Further, in the present embodiment, in the H state of FIG. 13, a slight gap is formed between the first elastic member 51A and the projecting portions 31a and 32a. Therefore, when the second rotating member 2 rotates from the H state in FIG. 13 to one side in the circumferential direction, the second rotating member 2 and the third rotating member 3 do not rotate integrally, The second rotating member 2 rotates in the circumferential direction with respect to the first rotating member 1 and the third rotating member 3. Between the H state in FIG. 13 and the I state in FIG. 14, the second rotating member 2 rotates in the circumferential direction with respect to the first rotating member 1 and the third rotating member 3, and the hub member 21 and the first rotating member 3 When the first sliding members 6 and 7 rub against each other, a first sliding torque T11 above the center line in FIG. 4 is generated.

  FIG. 15 shows a state in which the second rotating member 2 is rotated by a predetermined angle in the F direction with respect to the first rotating member 1 from the state I in FIG. 14. The state in FIG. 15 corresponds to the J state in FIG. In the I state of FIG. 14, the first elastic member 51 </ b> A and the protruding portions 31 a and 32 a are in contact with each other through the support member 52. Thereby, when the 2nd rotation member 2 rotates further to the one side of the circumferential direction from the I state of FIG. 14, protrusion part 31a, 32a is pushed to the one side of the circumferential direction, and 2nd rotation The member 2 and the third rotating member 3 rotate integrally. Between the I state in FIG. 14 and the J state in FIG. 15, the second rotating member 2 and the third rotating member 3 integrally rotate in the circumferential direction with respect to the first rotating member 1, and the control plate As a result of rubbing 31 and 32 and the second sliding members 8 and 9, a second sliding torque T <b> 22 above the center line in FIG. 4 is generated. In addition, between the I state in FIG. 14 and the J state in FIG. 15, the first elastic member 51A and the second elastic member 51B have the edge and the opening on the other side in the circumferential direction of the openings 11a and 12a. It extends elastically between the edge part of the circumferential direction of 22a. The first elastic member 51A returns to the free length, that is, the neutral state in the J state of FIG. 15, and the second elastic member 51B returns to the free length in the O state of FIG.

  As described above, in the present embodiment, for example, the damper device 100 is configured such that the second rotating member 2 is in the first angle with respect to the first rotating member 1 (state A in FIG. 4). When the second rotating member 2 rotates in the first direction (F direction) with respect to the first rotating member 1 in the first state twisted in the direction (F direction), and the second rotation In both cases where the member 2 rotates in the second direction opposite to the first direction with respect to the first rotating member 1 (the direction opposite to the F direction), the first sliding torques T11 and T12 are applied. The first sliding members 6 and 7 to be generated and the second rotating member 2 are at a first angle with respect to the first rotating member 1 (D state in FIG. 4) to the second direction (F The second rotating member 2 is in the second direction (opposite to the F direction) with respect to the first rotating member 1 in the second state twisted in the direction opposite to the direction). In the case of rolling, and in the case where the second rotating member 2 rotates in the first direction (F direction) with respect to the first rotating member 1, the second rotating member 2 is larger than the first sliding torque T11, T12. Second sliding members 8 and 9 for generating second sliding torques T21 and T22. Therefore, according to the present embodiment, for example, the torque relaxation performance can be varied depending on the twist direction of the second rotating member 2 relative to the first rotating member 1. In addition, for example, compared to the conventional configuration in which the second sliding member generates the second sliding torque only in one direction in which the second rotating member rotates in the second direction with respect to the first rotating member in the second state. As a whole, the difference between the first sliding torques T11 and T12 and the second sliding torques T21 and T22 can be further increased.

  In the present embodiment, for example, in the first state, the first rotating member 1 and the third rotating member 3 rotate integrally, and the second rotating member 2 and the third rotating member 3 The first sliding members 6, 7 and the second rotating member 2 are rubbed against each other by the relative rotation of the first and second sliding torques T11, T12 are generated. The rotating member 2 and the third rotating member 3 of the first rotating integrally rotate, and the second rotating members 8 and 9 and the third rotating member 3 are rotated by relative rotation between the first rotating member 1 and the third rotating member 3. Second sliding torques T21 and T22 are generated by rubbing the three rotating members 3 against each other. Therefore, according to the present embodiment, for example, by using the third rotating member 3, the difference between the first sliding torque T11, T12 and the second sliding torque T21, T22 as a whole is further increased. A possible damper device 100 can be realized.

  In the present embodiment, for example, the third rotating member 3 has the second rotating member 2 in the second direction (the direction opposite to the F direction) with respect to the first rotating member 1 in the second state. A coupler C3 (first receiving portion) pushed in the second direction by the second rotating member 2 when rotating, and a second rotating member relative to the first rotating member 1 in the second state When the 2 rotates in the first direction (F direction), the protruding portions 31a and 32a (second receiving portions) pushed in the first direction together with the second rotating member 2 by the first elastic member 51A Have. Therefore, according to this embodiment, when rotating in the second direction, the second rotating member 2 and the coupler C3 are hooked together in the circumferential direction, and when rotating in the first direction, the first Due to the configuration in which the elastic member 51A, the protrusions 31a, 32a and the second rotating member 2 are hooked together in the circumferential direction, the second sliding torque T21, both when rotating in the second direction and the first direction, The damper device 100 that can obtain T22 can be realized.

  Further, in the present embodiment, for example, the damper device 100 is connected to the engine side, and can be rotated around the rotation center Ax, the fourth rotation member 4, the first rotation member 1, and the fourth rotation member 4. The friction members 55 and 56 are sandwiched between the friction members 55 and 56 when the torque difference value between the first rotating member 1 and the fourth rotating member 4 exceeds a predetermined value. 56 slides with at least one of the first rotating member 1 and the fourth rotating member 4 so that the first rotating member 1 and the fourth rotating member 4 rotate relatively around the rotation center Ax. And a limiter unit 102 configured. Therefore, according to the present embodiment, for example, the limiter unit 102 can be provided in the fourth rotating member 4 connected to the input side, and thus, for example, the second rotation in which the limiter unit 102 is connected to the output side. Compared with the case where the member 2 is provided, the shape of each rotating member, that is, the power transmission path may be further simplified, or the damper device 100 may be configured to be smaller in the axial direction.

  Moreover, in this embodiment, when protrusion part 31a, 32a (2nd receiving part) rotates in a 1st direction (F direction) with respect to the 1st rotation member 1 in a 2nd state, for example. The first elastic member 51A is pushed by the support member 52 in the first direction (F direction). Therefore, according to the present embodiment, for example, the first elastic member 51A and the protruding portions 31a and 32a are compared with the case where the protruding portions 31a and 32a (second receiving portions) are pushed by the first elastic member 51A. Wear of the (second receiving part) is easily suppressed.

  In the present embodiment, the protrusions 31a, 32a (second receiving part) and the support member 52 of the first elastic member 51A are provided without being integrated, but the protrusions 31a, 32a (second And the support member 52 may be integrated. For example, a recess opened toward the first elastic member 51A side is provided on the other circumferential side of the support member 52 (opposite to the F direction), and the protrusions 31a and 32a (second receiving portions) are provided in the recess. ) May be accommodated. Movement of one side (F direction side) of the protrusions 31a, 32a (second receiving part) in the circumferential direction is restricted by the bottom surface of the recess, and movement to the other side in the circumferential direction is restricted by the first elastic member 51A. sell. Thereby, since the support member 52 and protrusion part 31a, 32a (2nd receiving part) are integrated in the circumferential direction, the coupling tool C3 may be unnecessary. Further, the support member 52 may be provided with a recessed portion opened on one side in the axial direction, and the protruding portions 31a and 32a (second receiving portions) may be accommodated in the recessed portion. Moreover, in this embodiment, although the protrusion parts 31a and 32a (2nd receiving part) were provided in both the control plates 31 and 32, the structure provided in either one may be sufficient.

  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 above embodiment can be implemented in various other forms, and various omissions, replacements, combinations, and changes can be made without departing from the spirit of the invention. The above embodiments are included in the scope and gist of the invention, and are included in the invention described in the claims and the equivalents thereof. The present invention can be realized by configurations other than those disclosed in the above embodiments, and various effects (including derivative effects) obtained by the basic configuration (technical features) can be obtained. is there. In addition, the specifications of each component (structure, type, direction, shape, size, length, width, thickness, height, number, arrangement, position, material, etc.) should be changed as appropriate. Can do.

  DESCRIPTION OF SYMBOLS 1 ... 1st rotation member, 2 ... 2nd rotation member, 3 ... 3rd rotation member, 4 ... 4th rotation member, 6, 7 ... 1st sliding member, 8, 9 ... 2nd Sliding member, 31a, 32a ... projecting part (second receiving part), 51 ... elastic member, 55, 56 ... friction member, 100 ... damper device, 102 ... limiter part, Ax ... center of rotation, C3 ... coupler ( First receiving part), F ... circumferential direction (first direction), T11, T12 ... first sliding torque, T21, T22 ... second sliding torque.

Claims (4)

A first rotating member rotatable around a center of rotation;
A second rotating member rotatable around the rotation center;
An elastic member that is elastically deformed by relative rotation between the first rotating member and the second rotating member;
In the first state in which the second rotating member is twisted in the first direction from the state at the first angle with respect to the first rotating member, the second rotating member is in the first rotation. When rotating in the first direction with respect to the member, and when the second rotating member rotates in the second direction opposite to the first direction with respect to the first rotating member A first sliding member for generating a first sliding torque on both sides;
In the second state where the second rotating member is twisted in the second direction from the state at the first angle with respect to the first rotating member, the second rotating member is the first rotating member. Both when rotating in the second direction relative to the rotating member, and when the second rotating member rotates in the first direction relative to the first rotating member. A second sliding member that generates a second sliding torque greater than the sliding torque;
A damper device comprising: A third rotating member rotatable around the rotation center;
The first sliding member is provided between the second rotating member and the third rotating member, and the second sliding member includes the first rotating member and the first rotating member. Provided between the three rotating members,
In the first state, the first rotating member and the third rotating member rotate integrally, and the second rotating member and the third rotating member rotate relative to each other to rotate the first rotating member and the third rotating member. The first sliding torque is generated by rubbing one sliding member and the second rotating member against each other,
In the second state, the second rotating member and the third rotating member rotate integrally, and the first rotating member and the third rotating member rotate relative to each other to rotate the first rotating member. The damper device according to claim 1, wherein the second sliding torque is generated by rubbing the second sliding member and the third rotating member against each other. The third rotating member is
When the second rotating member rotates in the second direction with respect to the first rotating member in the second state, the first rotating member is pushed in the second direction by the second rotating member. The receiving part of
When the second rotating member rotates in the first direction relative to the first rotating member in the second state, the elastic member causes the second rotating member to move in the first direction. A second receiving part to be pressed;
The damper device according to claim 2, comprising: A fourth rotating member connected to the engine side and rotatable about the rotation center;
A friction member sandwiched between the first rotating member and the fourth rotating member; and a value of a difference in torque between the first rotating member and the fourth rotating member is predetermined. When the value exceeds the value, the friction member slides with at least one of the first rotating member and the fourth rotating member, and the first rotating member and the fourth rotating member rotate the rotation. A limiter configured to rotate relative to the center;
The damper device according to any one of claims 1 to 3, further comprising:

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