Damper Device

Abstract

To provide a novel damper device capable of generating friction resistance between a first rotation element and a second rotation element and a support member regardless of rotation speed when the damper device is rotated, and capable of suppressing increase in the friction resistance when the damper device is rotated at relatively high rotation speed.SOLUTION: A damper device includes a first rotation element, a second rotation element, an elastic element, and a pair of support members. A sliding surface of the support member slides on a third support surface of the second rotation element. A first support surface of the first rotation element restricts rotation of the support member with respect to the first support surface. A second support surface of the second rotation element restricts rotation of the support member with respect to the second support surface. There is a gap between the first support surface and a first facing surface when the first rotation element and the support member are relatively rotated, and there is a gap between the second support surface and a second facing surface when the second rotation element and the support member are relatively rotated.SELECTED DRAWING: Figure 8

Description

[Technical Field]

[0001] The present invention relates to a damper device. [Background technology]

[0002] A damper device has been known that includes a first rotating element, a second rotating element, an elastic element interposed between the first and second rotating elements, and a pair of support members provided on both sides of the elastic element and interposed between the first and second rotating elements and the elastic elements (Patent Document 1). The damper device is installed in, for example, a vehicle. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Publication No. 2017-172692 Summary of the Invention [Problem to be solved by the invention]

[0004] In this type of damper device, when the first rotating element and the second rotating element rotate relative to each other, the support member moves while rotating radially outward due to centrifugal force, but this movement is restricted by contact with the first rotating element or the second rotating element. At this time, frictional resistance occurs between the first rotating element or the second rotating element and the support member due to sliding. It is desirable for this frictional resistance to be small when the engine is rotating at high speed, i.e., when the entire damper device is rotating at high speed. However, at low speeds, such as when the engine is starting, i.e., when the entire damper device is rotating at low speeds, it is desirable for there to be some frictional resistance between the first rotating element or the second rotating element and the support member in order to reduce the impact of vibrations during engine start-up, etc.

[0005] Therefore, one of the objectives of the present invention is to provide a novel damper device that can generate frictional resistance between the first and second rotating elements and the support member regardless of the rotation speed when the damper device is rotating, and that can prevent the frictional resistance from increasing when the damper device is rotating at a relatively high speed. [Means for solving the problem]

[0006] The damper device of the present invention includes a first rotating element rotatably provided around a rotation center, a second rotating element rotatably provided around the rotation center, an elastic element interposed between the first rotating element and the second rotating element and elastically expanding and contracting in a circumferential direction of the rotation center, and a pair of support members provided on both sides of the elastic element in the circumferential direction, interposed between the first rotating element and the second rotating element and the elastic element, and supporting the elastic element, wherein the first rotating element is provided for each of the support members, is located radially outward of the rotation center relative to the support members, and is positioned forward. In a first state in which the first rotating element and the second rotating element are not rotating relative to each other, the first rotating element has a first support surface extending around a first point located on the radially outer side of the rotation center on a first line passing through a middle between the pair of support members and the rotation center, as viewed in an axial direction of the rotation center, and the second rotating element has a second support surface provided for each of the support members and located on the radially outer side of the support members, and in the first state, when viewed in the axial direction, the second rotating element has a second support surface provided for each of the support members and located on the radially outer side of the rotation center on the first line and a third support surface located radially inward relative to the first support surface and the second support surface, and the support member has a first opposing surface that faces the first support surface in the first state and extends around a third point located radially outward relative to the rotation center on the first line when viewed from the axial direction, a second opposing surface that faces the second support surface in the first state and extends around a fourth point located radially outward relative to the rotation center on the first line when viewed from the axial direction, and a third opposing surface that comes into contact with the third support surface in the first state and connects the first rotating element and the second rotating element to each other. and a sliding surface that slides on the third support surface as the support member rotates relative to the element, wherein the first support surface contacts the first opposing surface to limit the rotation of the support member relative to the first support surface, and the second support surface contacts the second opposing surface to limit the rotation of the support member relative to the second support surface, and when the first rotating element and the support member rotate relative to each other, there is a gap between the first support surface and the first opposing surface, and when the second rotating element and the support member rotate relative to each other, there is a gap between the second support surface and the second opposing surface.

[0007] According to this configuration, for example, the sliding surface of the support member slides on the third support surface in accordance with the relative rotation of the first rotating element and the second rotating element, so that frictional resistance due to the sliding can be generated regardless of the rotation speed of the damper device. Therefore, the influence of vibrations, such as those occurring during engine start-up, can be suppressed when the damper device is operating at a relatively low rotation speed. Furthermore, according to the configuration, when the first rotating element and the support member are rotating relative to each other, there is a gap between the first support surface and the first opposing surface, and when the second rotating element and the support member are rotating relative to each other, there is a gap between the second support surface and the second opposing surface. Therefore, even when the rotation speed of the damper device is relatively high, the frictional resistance can be suppressed from increasing compared to a configuration without the gap.

[0008] In the damper device, the first support surface is an arc-shaped curved surface centered on the first point when viewed from the axial direction, and the first opposing surface is an arc-shaped curved surface centered on the third point when viewed from the axial direction, and the curvature of the first support surface and the curvature of the first opposing surface are the same.

[0009] According to this configuration, the attitude of the support member supported by the first rotating element can be stabilized in a state where the first support surface and the first opposing surface are in contact with each other.

[0010] In the damper device, for example, the third point is located more inward in the radial direction than the first point.

[0011] According to this configuration, for example, a gap can be generated between the first support surface and the first opposing surface when the first rotating element and the second rotating element are not rotating relative to each other.

[0012] In the damper device, the second support surface is an arc-shaped curved surface centered on the second point when viewed from the axial direction, and the second opposing surface is an arc-shaped curved surface centered on the fourth point when viewed from the axial direction, and the curvature of the second support surface and the curvature of the second opposing surface are the same.

[0013] According to this configuration, the posture of the support member supported by the second rotating element can be stabilized in a state in which the second support surface and the second opposing surface are in contact with each other.

[0014] In the damper device, for example, the fourth point is located more inward in the radial direction than the second point.

[0015] According to this configuration, for example, a gap can be generated between the second support surface and the second opposing surface when the first rotating element and the second rotating element are not rotating relative to each other.

[0016] In the damper device, for example, in the first state, there is a gap between the first support surface and the first opposing surface, and there is also a gap between the second support surface and the second opposing surface.

[0017] According to this configuration, when the damper device starts to rotate, the sliding surface of the support member is pressed against the third support surface by centrifugal force, so that the sliding surface and the third support surface can be prevented from separating from each other.

[0018] In the damper device, for example, the third support surface and the sliding surface are arc-shaped curved surfaces centered on the center of rotation when viewed from the axial direction.

[0019] With this configuration, it is possible to make the sliding between the third support surface and the sliding surface smooth.

[0020] The third support surface and the sliding surface slide within an angular range of relative rotation between the first rotating element and the second rotating element.

[0021] With this configuration, the range in which frictional resistance occurs due to sliding between the third support surface and the sliding surface can be easily adjusted at the time of design.

[0022] In the damper device, for example, the first rotating element has a first connecting surface that connects the two first support surfaces corresponding to one of the elastic elements and is arc-shaped with the rotation center as viewed from the axial direction.

[0023] According to this configuration, for example, the radial size of the first rotating element can be made smaller than in a configuration in which the two first support surfaces are directly connected without the first connecting surface therebetween.

[0024] In the damper device, for example, the second rotating element has a second connecting surface that connects two of the second support surfaces corresponding to one of the elastic elements and is arc-shaped with the center of rotation as viewed from the axial direction.

[0025] According to this configuration, for example, the radial size of the second rotating element can be made smaller than in a configuration in which two second support surfaces are directly connected without an intervening second connecting surface.

[0026] In the damper device, for example, the second rotation element has an open space between the two second support surfaces corresponding to one of the elastic elements.

[0027] With this configuration, the weight of the second rotating element can be reduced.

[0028] In the damper device, for example, the support member is provided with a groove recessed radially inward from the first opposing surface, and the second opposing surface is provided in the groove.

[0029] With this configuration, the weight of the support member can be reduced compared to a configuration in which no groove is provided, for example. [Brief explanation of the drawings]

[0030] [Figure 1] FIG. 1 is an exemplary front view showing a damper device according to an embodiment as viewed from the axial direction. [Figure 2] FIG. 2 is an exploded perspective view illustrating an example of the damper device according to the embodiment. [Figure 3] FIG. 3 is a cross-sectional view taken along line III-III in FIG. [Figure 4]FIG. 4 is a perspective view illustrating an example of a driven plate according to the embodiment. [Figure 5] FIG. 5 is a perspective view illustrating an example of a pair of sheets according to the embodiment. [Figure 6] FIG. 6 is a cross-sectional view exemplarily showing a part of a cross section taken along line VI-VI in FIG. [Figure 7] FIG. 7 is an explanatory diagram for explaining the shapes of the support portion and the seat of the drive plate according to the embodiment. [Figure 8] FIG. 8 is a cross-sectional view exemplarily showing a part of a cross section taken along line VIII-VIII in FIG. [Figure 9] FIG. 9 is an explanatory diagram for explaining the shapes of the support portion and the seat of the driven plate according to the embodiment. [Figure 10] FIG. 10 is a cross-sectional view exemplarily showing the support portion of the drive plate and the seat when the damper device of the embodiment is in operation, and is a view showing the case where the rotation speed of the damper device is relatively low. [Figure 11] FIG. 11 is a cross-sectional view exemplarily showing the support portion of the driven plate and the seat when the damper device of the embodiment is in operation, and is a view showing the case where the rotation speed of the damper device is relatively low. [Figure 12] FIG. 12 is a cross-sectional view exemplarily showing the support portion of the drive plate and the seat when the damper device of the embodiment is in operation, and is a view showing the case where the rotation speed of the damper device is relatively high. [Figure 13] FIG. 13 is a cross-sectional view exemplarily showing the support portion of the driven plate and the seat when the damper device of the embodiment is in operation, and is a view showing the case where the rotation speed of the damper device is relatively high. [Figure 14] FIG. 14 is a diagram showing an example of the relationship between the torsional torque and the torsional angle of the damper device according to the embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0031] Exemplary embodiments of the present invention are disclosed below. The configurations of the embodiments described below, as well as the actions and results (effects) brought about by the configurations, are merely examples. The present invention can also be realized by configurations other than those disclosed in the following embodiments. Furthermore, according to the present invention, it is possible to obtain at least one of the various effects (including derivative effects) obtained by the configurations.

[0032] In the following description, for convenience, the side closer to the engine (not shown) is referred to as the front, and the side farther from the engine is referred to as the rear. The terms "front" and "rear" in the following description do not necessarily correspond to the front and rear when mounted on a vehicle.

[0033] In the following description, the axial direction of the rotation center Ax1 will be simply referred to as the “axial direction,” the radial direction of the rotation center Ax1 will be simply referred to as the “radial direction,” and the circumferential direction of the rotation center Ax1 will be simply referred to as the “circumferential direction.” The rotation center Ax1 will also be referred to as the central axis.

[0034] FIG. 1 is an exemplary front view showing a damper device 1 according to an embodiment as viewed from the axial direction.

[0035] 1 can be provided, for example, between the engine and motor and a propeller shaft in a hybrid vehicle equipped with an engine and a motor. Note that the damper device 1 is not limited to the above, and can also be provided between other two rotating elements (for example, between an engine and a transmission), and can be provided in various vehicles (for example, vehicles other than hybrid vehicles) and machines having rotating elements.

[0036] Fig. 2 is an exploded perspective view illustrating an example of the damper device 1 according to the embodiment. Fig. 3 is a cross-sectional view taken along line III-III in Fig. 1.

[0037] As shown in Figures 1 to 3, the damper device 1 includes a damper section 2 and a limiter section 3. The damper section 2 can absorb (temporarily store) fluctuations in driving force (torque, rotation). The limiter section 3 can block the transmission of excessive driving force to the damper section 2.

[0038] The damper section 2 includes a drive plate 10 and a driven plate 20. The drive plate 10 and the driven plate 20 are provided so as to be rotatable independently about a rotation center Ax1. In other words, the drive plate 10 and the driven plate 20 are rotatable relative to each other. The drive plate 10 and the driven plate 20 are made of a metal material such as an iron-based material. The drive plate 10 is an example of a first rotating element, and the driven plate 20 is an example of a second rotating element. The drive plate 10 may also be referred to as an outer plate or an input member, and the driven plate 20 may also be referred to as an inner plate or an output member.

[0039] The drive plate 10 has a central portion 10a, multiple drive arms 10b, and a peripheral portion 10c. The central portion 10a is located radially inward of the drive plate 10 and has an annular shape centered on the rotation center Ax1. The peripheral portion 10c is located radially outward of the central portion 10a and has an annular shape centered on the rotation center Ax1. The drive arms 10b protrude radially outward from the central portion 10a and bridge between the central portion 10a and the peripheral portion 10c. In this embodiment, the multiple drive arms 10b are spaced apart in the circumferential direction.

[0040] The drive plate 10 is also provided with a plurality of window portions 15. The plurality of window portions 15 are provided at intervals in the circumferential direction. The drive plate 10 also has support portions 16 that surround the window portions 15. In other words, the support portions 16 form the window portions 15.

[0041] The drive plate 10 is made up of multiple members. Specifically, as shown in FIGS. 2 and 3 , the drive plate 10 has a front plate 11, a rear plate 12, and a lining plate 13. The lining plate 13 is located between the front plate 11 and the rear plate 12. The front plate 11, the rear plate 12, and the lining plate 13 are joined together by connecting members 14. The connecting members 14 are, for example, rivets, but may also be other fasteners such as bolts and nuts, or may be shafts, etc. The front plate 11, the rear plate 12, and the lining plate 13 may also be joined by welding, adhesive, etc., without using the connecting members 14.

[0042] The front plate 11 is located between the engine and the rear plate 12. In other words, the rear plate 12 is located on the opposite side of the engine from the front plate 11. The front plate 11 and the rear plate 12 are shaped like plates that intersect (are perpendicular to) the center of rotation Ax1 (axial direction).

[0043] 4 is a perspective view illustrating an example of the driven plate 20 of the embodiment. As shown in FIGS. 2 to 4, the driven plate 20 has a hub 20a, a flange 20b, a plurality of driven arms 20c, and a peripheral edge portion 20d.

[0044] The hub 20a has a cylindrical shape with the rotation center Ax1 at its center, and is located radially inside the driven plate 20.

[0045] The flange 20b protrudes radially outward from the hub 20a. The flange 20b is located between the front plate 11 and the rear plate 12 of the drive plate 10. The flange 20b has a plate shape that intersects (is perpendicular to) the center of rotation Ax1 (axial direction).

[0046] The peripheral edge portion 20d is located radially outward of the flange 20b, and has an annular shape centered on the rotation center Ax1.

[0047] The driven arms 20c protrude radially outward from the flange 20b and bridge between the flange 20b and the peripheral edge 20d. In this embodiment, the driven arms 20c are spaced apart in the circumferential direction. The drive arm 10b and the driven arms 20c overlap in the axial direction.

[0048] The driven plate 20 is also provided with a plurality of window portions 21. The plurality of window portions 21 are provided at intervals in the circumferential direction. The driven plate 20 also has support portions 22 that surround the window portions 21. In other words, the support portions 22 form the window portions 21.

[0049] A cylindrical first friction element 61 and a cylindrical second friction element 62 are provided on both axial sides of the flange 20b of the driven plate 20. The first friction element 61 and the second friction element 62 both provide frictional resistance (sliding resistance) between the drive plate 10 and the driven plate 20 when they rotate relative to each other. In this embodiment, the first friction element 61 is provided rotatably together with the rear plate 12 and slidably on the driven plate 20. The first friction element 61 is coupled to the rear plate 12, for example, by fitting a mating portion of the first friction element 61 with a mating portion of the rear plate 12. The mating portions of the first friction element 61 and the rear plate 12 are, for example, a claw on one side and a recess on the other side. The second friction element 62 is provided rotatably together with the front plate 11 and slidably on the driven plate 20. The second friction element 62 is coupled to the front plate 11, for example, by fitting a fitting portion of the second friction element 62 with a fitting portion of the front plate 11. The fitting portion of the second friction element 62 and the fitting portion of the front plate 11 may, for example, be a claw on one side and a recess on the other side.

[0050] The first friction element 61 and the second friction element 62 are made of, for example, a synthetic resin material.

[0051] In addition, a disc spring 71 is interposed between the first friction element 61 and the driven plate 20.

[0052] As shown in FIG. 1 , the damper section 2 includes a plurality of coil springs 41. The coil springs 41 are placed in the windows 15, 21 and are interposed between the drive arm 10b and the driven arm 20c. Each of the coil springs 41 extends substantially along the circumferential direction (tangential direction). The coil springs 41 are an example of an elastic element. The elastic element is not limited to a coil spring, and may be another elastic element such as an elastomer. The coil springs 41 expand and contract in accordance with the relative rotation, i.e., twisting, of the drive plate 10 and the driven plate 20.

[0053] FIG. 5 is a perspective view illustrating a pair of seats 43 according to an embodiment. As shown in FIGS. 2 and 5, a pair of seats 43A and 43B are provided on both circumferential sides of the coil spring 41. The pair of seats 43A and 43B are symmetrical with respect to a predetermined plane perpendicular to the axial direction. The seats 43 are collectively referred to as seats 43A and 43B. The seats 43 are interposed between the support portion 16 (drive arm 10b) of the drive plate 10 and the support portion 22 of the driven plate 20) and the coil spring 41, and support the coil spring 41. The seats 43 may also be referred to as a retainer. The seats 43 are an example of a support member.

[0054] Next, the support portion 16 of the drive plate 10, the support portion 22 of the driven plate 20, and the seat 43 will be described. Fig. 6 is a cross-sectional view showing an example of a portion of a cross section taken along line VI-VI in Fig. 3. Fig. 7 is an explanatory view showing the shapes of the support portion 16 of the drive plate 10 and the seat 43 of the embodiment. Fig. 8 is a cross-sectional view showing an example of a portion of a cross section taken along line VIII-VIII in Fig. 3. Fig. 9 is an explanatory view showing the shapes of the support portion 22 of the driven plate 20 and the seat 43 of the embodiment.

[0055] As shown in FIG. 6, the support portion 16 of the drive plate 10 has a first support surface 16a, a surface 16b, and a first connecting surface 16c. The first support surface 16a is provided for each seat 43 and is located radially outward of the center of rotation Ax1 relative to the seat 43. As shown in FIG. 7, the first support surface 16a extends around a first center point C11 in a first state in which the drive plate 10 and the driven plate 20 are not rotating relative to each other. In the first state, the first center point C11 passes through the center of rotation Ax1 and the middle of the pair of seats 43 when viewed from the axial direction of the center of rotation Ax1. The first support surface 16a is an arc-shaped curved surface with a radius R11 centered on the first center point C11 when viewed from the axial direction. The surface 16b extends radially inward from the first support surface 16a. The first center point C11 is an example of a first point.

[0056] 6, the first connection surface 16c connects two first support surfaces 16a corresponding to one coil spring 41. The first connection surface 16c has an arc shape centered on the rotation center Ax1 when viewed from the axial direction.

[0057] As shown in FIG. 8, the support portion 22 of the driven plate 20 has a second support surface 22a, a third support surface 22d, and a second connection surface 22e.

[0058] The second support surface 22a is provided for each seat 43 and is located radially outward from the seat 43. As shown in FIG. 9, in the first state, the second support surface 22a extends around a second center point C21 (second point) when viewed from the axial direction. In the first state, the second center point C21 is located radially outward from the center of rotation Ax1 on the first line L1. The second support surface 22a is an arc-shaped curved surface with a radius R21 centered on the second center point C21 when viewed from the axial direction.

[0059] As shown in Fig. 8, the third support surface 22d is provided for each seat 43 and is located radially inward of the first support surface 16a and the second support surface 22a. As shown in Fig. 9, the third support surface 22d is an arc-shaped curved surface with a radius R23 centered on the rotation center Ax1 when viewed in the axial direction.

[0060] As shown in Fig. 8, the second connection surface 22e connects two second support surfaces 22a corresponding to one coil spring 41. As shown in Fig. 9, the second connection surface 22e is an arc-shaped curved surface with a radius R25 centered on the rotation center Ax1 when viewed from the axial direction.

[0061] The support portion 22 also has a protruding portion 22c that includes a third support surface 22d. The protruding portion 22c has a shape that protrudes toward the seat 43 in the circumferential direction.

[0062] As shown in FIGS. 5, 6, and 8, the seat 43 has a base portion 43a and a protruding portion 43b that protrudes from the base portion 43a into the coil spring 41.

[0063] The base portion 43a has a first opposing surface 43c1, a second opposing surface 43c2, and a sliding surface 43f2.

[0064] As shown in FIG. 6, the first opposing surface 43c1 faces the first support surface 16a in the first state. As shown in FIG. 7, the first opposing surface 43c1 extends around a third center point C12 (third point) when viewed in the axial direction. The third center point C12 is located on the first line L1 radially outward from the rotation center Ax1. The third center point C12 is located radially inward from the first center point C11. That is, there is a difference L1a between the distance L11 between the rotation center Ax1 and the first center point C11 and the distance L12 between the rotation center Ax1 and the third center point C12. The first opposing surface 43c1 is an arc-shaped curved surface with a radius R12 centered on the third center point C12 when viewed in the axial direction. The curvature of the first opposing surface 43c1 is the same as the curvature of the first support surface 16a.

[0065] As shown in FIG. 8, the second opposing surface 43c2 faces the second support surface 22a in the first state. As shown in FIG. 9, the second opposing surface 43c2 extends around a fourth center point C22 (fourth point) when viewed in the axial direction. The fourth center point C22 is located on the first line L1 radially outward from the rotation center Ax1. The fourth center point C22 is located radially inward from the second center point C21. That is, there is a difference L2a between the distance L21 between the rotation center Ax1 and the second center point C21 and the distance L22 between the rotation center Ax1 and the fourth center point C22. The second opposing surface 43c2 is an arc-shaped curved surface with a radius R22 centered on the fourth center point C22 when viewed in the axial direction. The curvature of the second opposing surface 43c2 is the same as the curvature of the second support surface 22a.

[0066] The sliding surface 43f2 comes into contact with the third support surface 22d in the first state. The sliding surface 43f2 slides on the third support surface 22d as the drive plate 10 and the driven plate 20 rotate relative to each other.

[0067] 5, the seat 43 is provided with a groove 43g recessed radially inward from the first opposing surface 43c1. The second opposing surface 43c2 is provided in the groove 43g. The seat 43 is also provided with surfaces 43d1 and 43d2 and recessed surfaces 43e1 and 43e2 in addition to the above.

[0068] Next, the operation of the damper device 1 will be described.

[0069] As shown in Figures 7 and 9, in the first state in which the drive plate 10 and the driven plate 20 are not rotating relative to each other, i.e., in an untwisted state, there is a gap D1 (Figure 7) between the first support surface 16a and the first opposing surface 43c1, and there is a gap D2 (Figure 9) between the second support surface 22a and the second opposing surface 43c2.

[0070] Fig. 10 is a cross-sectional view showing an example of the support portion 16 of the drive plate 10 and the seat 43 when the damper device 1 of the embodiment is operating, when the rotation speed of the damper device 1 is relatively low. Fig. 11 is a cross-sectional view showing an example of the support portion 22 of the driven plate 20 and the seat 43 when the damper device 1 of the embodiment is operating, when the rotation speed of the damper device 1 is relatively low.

[0071] 10 and 11 show a state in which the coil spring 41 is compressed when the drive plate 10 and the driven plate 20 rotate relative to each other, i.e., twist, when the rotation speed of the damper device 1 is relatively low. In this case, for example, one sheet 43B is pressed against the drive plate 10 (FIG. 10) and rotates integrally with the drive plate 10, and the other sheet 43A is pressed against the driven plate 20 (FIG. 11) and rotates integrally with the driven plate 20.

[0072] At this time, the seat 43B and the driven plate 20 rotate relative to each other so that the protruding portion 22c of the driven plate 20 enters the recessed surface 43e2 of the seat 43B while the sliding surface 43f2 of the seat 43B slides against the third support surface 22d of the driven plate 20 (FIG. 11). At this time, the second opposing surface 43c2 of the seat 43B is spaced from the second support surface 22a of the driven plate 20 (FIG. 11). That is, a gap D2 is formed between the second opposing surface 43c2 of the seat 43B and the second support surface 22a of the driven plate 20. This gap D2 changes depending on the angle of relative rotation between the drive plate 10 and the driven plate 20. Also, a gap D1 is formed between the first opposing surface 43c1 of the seat 43B and the first support surface 16a of the drive plate 10. At this time, the centrifugal force is relatively small, so even if there is a gap D1, the sheet 43B does not rotate (tilt) relative to the first support surface 16a.

[0073] At this time, the sliding surface 43f2 of the other sheet 43A does not slide against the third support surface 22d of the driven plate 20 (FIG. 11). At this time, the first opposing surface 43c1 of the other sheet 43A is separated from the first support surface 16a of the drive plate 10 (FIG. 10). That is, a gap D1 is present between the first opposing surface 43c1 of the other sheet 43A and the first support surface 16a of the drive plate 10. This gap D1 changes depending on the angle of relative rotation between the drive plate 10 and the driven plate 20. At this time, a gap D2 is present between the second opposing surface 43c2 of the other sheet 43A and the second support surface 22a of the driven plate 20. Because the centrifugal force is relatively small at this time, the sheet 43A does not rotate (tilt) relative to the second support surface 22a even though there is a gap D2.

[0074] Fig. 12 is a cross-sectional view showing an example of the support portion 16 of the drive plate 10 and the seat 43 when the damper device 1 of the embodiment is operating, when the rotation speed of the damper device 1 is relatively high. Fig. 13 is a cross-sectional view showing an example of the support portion 22 of the driven plate 20 and the seat 43 when the damper device 1 of the embodiment is operating, when the rotation speed of the damper device 1 is relatively high.

[0075] 12 and 13 show a state in which the coil spring 41 is compressed when the drive plate 10 and the driven plate 20 rotate relative to each other, i.e., twist, when the rotation speed of the damper device 1 is relatively high. In this case, for example, one sheet 43B is pressed against the drive plate 10 (FIG. 12) and rotates integrally with the drive plate 10, and the other sheet 43A is pressed against the driven plate 20 (FIG. 13) and rotates integrally with the driven plate 20.

[0076] At this time, the seat 43B and the driven plate 20 rotate relative to each other so that the protruding portion 22c of the driven plate 20 enters the depth of the concave surface 43e2 of the seat 43B while the sliding surface 43f2 of the one seat 43B slides against the third support surface 22d of the driven plate 20 (FIG. 13). At this time, the second opposing surface 43c2 of the one seat 43B is spaced apart from the second support surface 22a of the driven plate 20 (FIG. 13). That is, as in the example of FIG. 11, there is a gap D2 between the second opposing surface 43c2 of the one seat 43B and the second support surface 22a of the driven plate 20, and this gap D2 changes depending on the angle of relative rotation between the drive plate 10 and the driven plate 20. At this time, centrifugal force causes one of the seats 43B to move radially outward, but the first opposing surface 43c1 of the seat 43B comes into contact with the first support surface 16a of the drive plate 10, restricting the movement of the seat 43B radially outward (FIG. 12). That is, the rotation (tilt) of the seat 43B relative to the first support surface 16a is restricted.

[0077] At this time, the sliding surface 43f2 of the other seat 43A does not slide against the third support surface 22d of the driven plate 20 (FIG. 13). At this time, the first opposing surface 43c1 of the other seat 43A is separated from the first support surface 16a of the drive plate 10 (FIG. 12). That is, as in the example of FIG. 10, a gap D1 is formed between the first opposing surface 43c1 of the other seat 43A and the first support surface 16a of the drive plate 10, and this gap D1 changes depending on the angle of relative rotation between the drive plate 10 and the driven plate 20. At this time, the other seat 43A moves radially outward due to centrifugal force, but the second opposing surface 43c2 of the other seat 43A comes into contact with the second support surface 22a of the driven plate 20, restricting the radially outward movement (FIG. 13). That is, the rotation (tilt) of the seat 43A relative to the second support surface 22a is restricted.

[0078] As described above, in this embodiment, the first support surface 16a contacts the first opposing surface 43c1, thereby restricting rotation of the seat 43 relative to the first support surface 16a. The second support surface 22a contacts the second opposing surface 43c2, thereby restricting rotation of the seat 43 relative to the second support surface 22a. When the drive plate 10 and the seat 43 (seat 43A or 43B) are rotating relative to each other, a gap D1 is formed between the first support surface 16a and the first opposing surface 43c1. When the driven plate 20 and the seat 43 (seat 43A or 43B) are rotating relative to each other, a gap D2 is formed between the second support surface 22a and the second opposing surface 43c2.

[0079] FIG. 14 is a diagram showing an example of the relationship between torsional torque and torsional angle in the damper device 1 of the embodiment. With the above-described configuration, in this embodiment, as shown in FIG. 14, torsional torque indicated by line L51 is generated during operation of the damper device 1. Line L52 indicates the torsional torque when the sliding surface 43f2 of the seat 43 and the third support surface 22d of the driven plate 20 do not slide against each other. As can be seen from FIG. 14, the third support surface 22d and the sliding surface 43f2 slide against each other within the angle range M1 of the relative rotation between the drive plate 10 and the driven plate 20, and this sliding increases the torsional torque. Note that "in" in FIG. 14 indicates the case where the protruding portion 22c of the driven plate 20 enters the concave surface 43e2 of the seat 43, and "out" in FIG. 14 indicates the case where the protruding portion 22c of the driven plate 20 leaves the concave surface 43e2 of the seat 43.

[0080] As described above, in this embodiment, the damper device 1 includes the drive plate 10 (first rotating element), the driven plate 20 (second rotating element), the coil spring 41 (elastic element), and a pair of seats 43 (support members). The drive plate 10 is rotatable about the rotation center Ax1. The driven plate 20 is rotatable about the rotation center Ax1. The coil spring 41 is interposed between the drive plate 10 and the driven plate 20 and elastically expands and contracts in the circumferential direction of the rotation center Ax1. The pair of seats 43 are provided on both sides of the coil spring 41 in the circumferential direction and are interposed between the drive plate 10 and the driven plate 20 and the coil spring 41 to support the coil spring 41. The drive plate 10 has a first support surface 16a. The first support surface 16a is provided for each seat 43 and is located radially outward of the rotation center Ax1 relative to the seats 43. The first support surface 16a extends around a first center point C11 (first point) in a first state in which the drive plate 10 and the driven plate 20 are not rotating relative to each other. In the first state, the first center point C11 passes through the center of rotation Ax1 and the center of rotation between the pair of seats 43 when viewed in the axial direction of the rotation center Ax1. The driven plate 20 has a second support surface 22a and a third support surface 22d. The second support surface 22a is provided for each seat 43 and is located radially outward from the seats 43. In the first state, the second support surface 22a extends around a second center point C21 (second point) when viewed in the axial direction. In the first state, the second center point C21 is located radially outward from the rotation center Ax1 on the first line L1. The third support surface 22d is provided for each seat 43 and is located radially inward from the first support surface 16a and the second support surface 22a. The seat 43 (support member) has a first opposing surface 43c1, a second opposing surface 43c2, and a sliding surface 43f2. The first opposing surface 43c1 faces the first support surface 16a in the first state. The first opposing surface 43c1 extends around a third center point C12 (third point) when viewed in the axial direction. The third center point C12 is located on the first line L1 radially outward from the rotation center Ax1. The second opposing surface 43c2 faces the second support surface 22a in the first state. The second opposing surface 43c2 extends around a fourth center point C22 (fourth point) when viewed in the axial direction.The fourth center point C22 is located on the first line L1 radially outward from the rotation center Ax1. The sliding surface 43f2 contacts the third support surface 22d in the first state and slides on the third support surface 22d in response to the relative rotation of the drive plate 10 and the driven plate 20. The first support surface 16a contacts the first opposing surface 43c1, thereby limiting the rotation of the seat 43 relative to the first support surface 16a. The second support surface 22a contacts the second opposing surface 43c2, thereby limiting the rotation of the seat 43 relative to the second support surface 22a. When the drive plate 10 and the seat 43 (seat 43A or 43B) are rotating relative to each other, a gap D1 is formed between the first support surface 16a and the first opposing surface 43c1. When the driven plate 20 and the seat 43 (seat 43A or 43B) are rotating relative to each other, a gap D2 is formed between the second support surface 22a and the second opposing surface 43c2.

[0081] According to this configuration, for example, the sliding surface 43f2 of the seat 43 slides on the third support surface 22d as the drive plate 10 and the driven plate 20 rotate relative to each other. This allows frictional resistance to be generated by the sliding, regardless of the rotation speed of the damper device 1. Therefore, for example, the influence of vibrations occurring at engine start or other times when the damper device 1 is rotating at a relatively low speed can be suppressed. Furthermore, according to the above configuration, when the drive plate 10 and the seat 43 are rotating relative to each other, a gap D1 is formed between the first support surface 16a and the first opposing surface 43c1. When the driven plate 20 and the seat 43 are rotating relative to each other, a gap D2 is formed between the second support surface 22a and the second opposing surface 43c2. Therefore, even when the rotation speed of the damper device 1 is relatively high, the frictional resistance can be suppressed from increasing compared to a configuration without the gaps D1 and D2.

[0082] Furthermore, the first support surface 16a is an arc-shaped curved surface centered on the first center point C11 when viewed from the axial direction. The first opposing surface 43c1 is an arc-shaped curved surface centered on the third center point C12 when viewed from the axial direction. The curvature of the first support surface 16a and the curvature of the first opposing surface 43c1 are the same.

[0083] According to this configuration, the position of the seat 43 supported by the drive plate 10 can be stabilized in a state where the first support surface 16a and the first opposing surface 43c1 are in contact with each other.

[0084] Furthermore, the third center point C12 is located radially inward of the first center point C11.

[0085] According to this configuration, for example, a gap D1 can be generated between the first support surface 16a and the first opposing surface 43c1 when the drive plate 10 and the driven plate 20 are not rotating relative to each other.

[0086] The second support surface 22a is an arc-shaped curved surface centered on the second center point C21 when viewed from the axial direction. The second opposing surface 43c2 is an arc-shaped curved surface centered on the fourth center point C22 when viewed from the axial direction. The curvature of the second support surface 22a and the curvature of the second opposing surface 43c2 are the same.

[0087] According to this configuration, the posture of the seat 43 supported by the driven plate 20 can be stabilized in a state where the second support surface 22a and the second opposing surface 43c2 are in contact with each other.

[0088] The fourth center point C22 is located radially inward of the second center point C21.

[0089] According to this configuration, for example, a gap D2 can be generated between the second support surface 22a and the second opposing surface 43c2 when the drive plate 10 and the driven plate 20 are not rotating relative to each other.

[0090] In the first state, there is a gap D1 between the first support surface 16a and the first opposing surface 43c1, and there is a gap D2 between the second support surface 22a and the second opposing surface 43c2.

[0091] According to this configuration, when the damper device 1 starts to rotate, the sliding surface 43f2 of the seat 43 is pressed against the third support surface 22d by centrifugal force, so that the sliding surface 43f2 and the third support surface 22d can be prevented from separating from each other.

[0092] Additionally, the third support surface 22d and the sliding surface 43f2 are arc-shaped curved surfaces centered on the rotation center Ax1 when viewed from the axial direction.

[0093] With this configuration, the third support surface 22d and the sliding surface 43f2 can slide smoothly against each other.

[0094] The third support surface 22d and the sliding surface 43f2 slide on each other within an angular range M1 (FIG. 14) of relative rotation between the drive plate 10 and the driven plate 20.

[0095] With this configuration, the range in which frictional resistance occurs due to sliding between the third support surface 22d and the sliding surface 43f2 can be easily adjusted at the time of design.

[0096] The drive plate 10 also has a first connection surface 16c. The first connection surface 16c connects two first support surfaces 16a corresponding to one coil spring 41. When viewed in the axial direction, the first connection surface 16c has an arc shape centered on the rotation center Ax1.

[0097] According to this configuration, the radial size of the drive plate 10 can be made smaller than, for example, a configuration in which the two first support surfaces 16a are directly connected without the first connecting surface 16c therebetween.

[0098] The driven plate 20 also has a second connection surface 22e. The second connection surface 22e connects two second support surfaces 22a corresponding to one coil spring 41. The second connection surface 22e has an arc shape centered on the rotation center Ax1 when viewed from the axial direction.

[0099] According to this configuration, the radial size of the driven plate 20 can be made smaller than, for example, a configuration in which the two second support surfaces 22a are directly connected without the second connecting surface 22e therebetween.

[0100] Further, a groove 43g recessed radially inward from the first opposing surface 43c1 is provided in the sheet 43. The second opposing surface 43c2 is provided in the groove 43g.

[0101] According to this configuration, the weight of the sheet 43 can be reduced compared to a configuration in which the grooves 43g are not provided, for example.

[0102] In the above embodiment, for example, an example in which the two second support surfaces 22a are connected via the second connection surface 22e has been described, but the present invention is not limited to this. For example, the driven plate 20 may have an open space between the two second support surfaces 22a corresponding to one coil spring 41. That is, a hole may be provided between the line L2 and the line L3 in FIG. 8. With this configuration, the weight of the driven plate 20 can be reduced.

[0103] Although the embodiments of the present invention have been described above, they are merely examples and are not intended to limit the scope of the invention. The embodiments can be implemented in various other forms, and various omissions, substitutions, combinations, and modifications can be made without departing from the spirit of the invention. Furthermore, the configurations and shapes of each example can be partially interchanged. Furthermore, the specifications of each configuration and shape (structure, type, direction, shape, size, length, width, height, number, arrangement, position, etc.) can be appropriately changed and implemented. [Explanation of symbols]

[0104] 1...Damper device 10...Drive plate (first rotating element) 16a...first support surface 16c...First connecting surface 20...Driven plate (second rotating element) 22a…Second support surface 22d…Third support surface 22e...Second connecting surface 41... Coil spring (elastic element) 43...Sheet (support member) 43c1...First facing surface 43c2…Second opposing surface 43f2…Sliding surface Ax1...Center of rotation C11...1st center point (1st point) C12...Third center point (third point) C21…Second center point (second point) C22…4th center point (4th point) D1, D2...gap L1…First line

Claims

1. a first rotating element provided rotatably around a rotation center; a second rotating element provided rotatably around the rotation center; an elastic element interposed between the first rotating element and the second rotating element and elastically expanding and contracting in a circumferential direction of the rotation center; a pair of support members provided on both sides of the elastic element in the circumferential direction, interposed between the first rotating element and the elastic element, and between the second rotating element and the elastic element, and supporting the elastic element; Equipped with The first rotating element is a first support surface provided for each of the support members, positioned radially outward from the rotation center with respect to the support members, and extending around a first point positioned radially outward from the rotation center on a first line passing through a midpoint between the pair of support members and the rotation center when viewed in the axial direction of the rotation center in a first state in which the first rotation element and the second rotation element are not rotating relative to each other; The second rotating element is a second support surface provided for each of the support members, positioned radially outward relative to the support members, and extending around a second point positioned radially outward relative to the rotation center on the first line when viewed from the axial direction in the first state; a third support surface provided for each of the support members and positioned radially inward relative to the first support surface and the second support surface; and The support member is a first opposing surface that faces the first support surface in the first state and extends around a third point that is located on the first line and radially outward with respect to the rotation center when viewed in the axial direction; a second opposing surface that faces the second support surface in the first state and extends around a fourth point that is located on the first line and radially outward with respect to the rotation center when viewed in the axial direction; a sliding surface that contacts the third support surface in the first state and slides on the third support surface in accordance with relative rotation between the first rotating element and the second rotating element; and the first support surface contacts the first opposing surface to limit rotation of the support member relative to the first support surface; the second support surface contacts the second opposing surface to limit rotation of the support member relative to the second support surface; When the first rotating element and the support member rotate relative to each other, there is a gap between the first support surface and the first opposing surface, and when the second rotating element and the support member rotate relative to each other, there is a gap between the second support surface and the second opposing surface. Damper device.

2. the first support surface is an arc-shaped curved surface centered at the first point when viewed from the axial direction, the first opposing surface is an arc-shaped curved surface having the third point as a center when viewed from the axial direction, The curvature of the first support surface and the curvature of the first opposing surface are the same. The damper device according to claim 1 .

3. The damper device according to claim 1 , wherein the third point is located radially inward of the first point.

4. the second support surface is an arc-shaped curved surface having the second point as a center when viewed from the axial direction, the second opposing surface is an arc-shaped curved surface having the fourth point as a center when viewed from the axial direction, The curvature of the second support surface and the curvature of the second opposing surface are the same. The damper device according to any one of claims 1 to 3.

5. 5. The damper device according to claim 1, wherein the fourth point is located radially inward of the second point.

6. In the first state, there is a gap between the first support surface and the first opposing surface, and there is a gap between the second support surface and the second opposing surface. The damper device according to any one of claims 1 to 5.

7. 7. The damper device according to claim 1, wherein the third support surface and the sliding surface are arc-shaped curved surfaces centered on the center of rotation when viewed from the axial direction.

8. The third support surface and the sliding surface slide within an angle range of relative rotation between the first rotation element and the second rotation element. The damper device according to any one of claims 1 to 7.

9. The first rotation element has a first connection surface that connects the two first support surfaces corresponding to one of the elastic elements and is arc-shaped with the rotation center as the center when viewed from the axial direction. The damper device according to any one of claims 1 to 8.

10. The second rotation element has a second connection surface that connects the two second support surfaces corresponding to one of the elastic elements and is arc-shaped with the rotation center as the center when viewed from the axial direction. The damper device according to any one of claims 1 to 9.

11. The second rotation element has an open space between the two second support surfaces corresponding to one of the elastic elements. The damper device according to any one of claims 1 to 9.

12. The support member is provided with a groove recessed radially inward from the first opposing surface, The second opposing surface is provided in the groove, The damper device according to any one of claims 1 to 11.

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