JP7735892B2 - Damper Device - Google Patents

Description

The present invention relates to a damper device.

A conventional damper device is 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.

Japanese Patent Application Laid-Open No. 2017-172692

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

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 of the damper device, and that can prevent this frictional resistance from increasing when the damper device is rotating at relatively high speeds.

The damper device of the present invention comprises a first rotating element rotatably arranged around a rotation center, a second rotating element rotatably arranged around the rotation center, an elastic element interposed between the first rotating element and the second rotating element and elastically expanding and contracting in the circumferential direction of the rotation center, and a pair of support members provided on both sides of the elastic element in the circumferential direction and interposed between the first rotating element and the second rotating element and the elastic element to support the elastic element, wherein the first rotating element is provided for each support member, 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. The first support surface contacts the first opposing surface to limit rotation of the support member relative to the first support surface, and 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.

With this configuration, for example, the sliding surface of the support member slides on the third support surface as the first rotating element and the second rotating element rotate relative to each other. This allows frictional resistance to be generated by this sliding, regardless of the rotation speed of the damper device. This makes it possible to suppress the effects of vibrations, such as those that occur when the engine is started, when the damper device is rotating at relatively low speeds. Furthermore, with this 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, frictional resistance can be suppressed from increasing compared to a configuration without this gap.

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.

With this configuration, the posture of the support member supported by the first rotating element can be stabilized when the first support surface and the first opposing surface are in contact.

In the damper device, for example, the third point is located radially inward of the first point.

With this configuration, for example, a gap can be created 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.

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.

With this configuration, the posture of the support member supported by the second rotating element can be stabilized when the second support surface and the second opposing surface are in contact.

In the damper device, for example, the fourth point is located radially inward of the second point.

With this configuration, for example, a gap can be created 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.

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 a gap between the second support surface and the second opposing surface.

With this configuration, when the damper device starts to rotate, centrifugal force presses the sliding surface of the support member against the third support surface, preventing the sliding surface and the third support surface from separating.

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.

This configuration allows for smooth sliding between the third support surface and the sliding surface.

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

This configuration makes it easy to adjust the range of frictional resistance caused by sliding between the third support surface and the sliding surface during design.

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.

With this configuration, the radial size of the first rotating element can be reduced compared to, for example, a configuration in which two first support surfaces are directly connected without a first connecting surface.

In the damper device, for example, the second rotating element has a second connecting surface that connects the two 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.

With this configuration, the radial size of the second rotating element can be reduced compared to, for example, a configuration in which two second support surfaces are directly connected without a second connecting surface.

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

This configuration allows the second rotating element to be made lighter.

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

With this configuration, the support member can be made lighter than, for example, a configuration without grooves.

FIG. 1 is an exemplary front view showing a damper device according to an embodiment as viewed from the axial direction. FIG. 2 is an exploded perspective view illustrating an example of the damper device according to the embodiment. FIG. 3 is a cross-sectional view taken along line III-III in FIG. FIG. 4 is a perspective view illustrating an example of a driven plate according to the embodiment. FIG. 5 is a perspective view illustrating an example of a pair of sheets according to the embodiment. FIG. 6 is a cross-sectional view exemplarily showing a part of a cross section taken along line VI-VI in FIG. 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. FIG. 8 is a cross-sectional view exemplarily showing a part of a cross section taken along line VIII-VIII in FIG. FIG. 9 is an explanatory diagram for explaining the shapes of the support portion of the driven plate and the seat in the embodiment. FIG. 10 is a cross-sectional view showing an example of 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. 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. FIG. 12 is a cross-sectional view showing an example of 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. 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. 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.

The following describes exemplary embodiments of the present invention. The configurations of the embodiments described below, as well as the actions and results (effects) achieved by these configurations, are merely examples. The present invention can also be realized using 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) achieved by the configurations.

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

Furthermore, below, the axial direction of the rotation center Ax1 will be referred to simply as the axial direction, the radial direction of the rotation center Ax1 will be referred to simply as the radial direction, and the circumferential direction of the rotation center Ax1 will be referred to simply as the circumferential direction. The rotation center Ax1 will also be referred to as the central axis.

Figure 1 is an exemplary front view showing the damper device 1 of the embodiment as viewed from the axial direction.

The damper device 1 shown in FIG. 1 can be installed, for example, between the engine and motor and the propeller shaft in a hybrid vehicle equipped with an engine and motor. The damper device 1 is not limited to the above, and can also be installed between two other rotating elements (for example, between an engine and a transmission), and can be installed in various vehicles (for example, vehicles other than hybrid vehicles) and machines with rotating elements.

Figure 2 is an exemplary exploded perspective view of the damper device 1 according to the embodiment. Figure 3 is a cross-sectional view taken along line III-III in Figure 1.

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

The damper section 2 includes a drive plate 10 and a driven plate 20. The drive plate 10 and the driven plate 20 are each independently rotatable around the center of rotation 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 is also referred to as an outer plate or input member, and the driven plate 20 is also referred to as an inner plate or output member.

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 a circular ring shape centered on the rotation center Ax1. The peripheral portion 10c is located radially outward from the central portion 10a and has a circular ring 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 circumferentially.

The drive plate 10 also has a plurality of window portions 15. The window portions 15 are spaced apart 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.

The drive plate 10 is also made up of multiple members. Specifically, as shown in Figures 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, rear plate 12, and 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, rear plate 12, and lining plate 13 may also be joined by welding, adhesive, etc., without using the connecting members 14.

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 rear plate 12 are shaped like plates that intersect (are perpendicular to) the center of rotation Ax1 (axial direction).

Figure 4 is an exemplary perspective view of the driven plate 20 of this embodiment. As shown in Figures 2 to 4, the driven plate 20 has a hub 20a, a flange 20b, multiple driven arms 20c, and a peripheral portion 20d.

The hub 20a is cylindrical and centered on the rotation center Ax1. It is located radially inside the driven plate 20.

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

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

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

The driven plate 20 also has a plurality of window portions 21. The window portions 21 are spaced apart 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.

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. Both the first friction element 61 and the second friction element 62 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 rotatable integrally with the rear plate 12 and is slidable relative to the driven plate 20. The first friction element 61 is coupled to the rear plate 12, for example, by a mating portion of the first friction element 61 mating 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 rotatable integrally with the front plate 11 and is slidable relative to the driven plate 20. The second friction element 62 is coupled to the front plate 11, for example, by fitting a mating portion of the second friction element 62 with a mating portion of the front plate 11. For example, one of the mating portions of the second friction element 62 and the front plate 11 is a claw and the other is a recess.

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

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

As shown in FIG. 1, the damper section 2 also 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 coil spring 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 response to the relative rotation, or twisting, of the drive plate 10 and the driven plate 20.

Figure 5 is an exemplary perspective view of a pair of seats 43 in this embodiment. As shown in Figures 2 and 5, a pair of seats 43A, 43B are provided on both circumferential sides of the coil spring 41. The pair of seats 43A, 43B are symmetrical with respect to a predetermined plane perpendicular to the axial direction. The seats 43A, 43B are collectively referred to as seats 43. The seats 43 are interposed between the support portion 16 of the drive plate 10 (drive arm 10b) 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.

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. Figure 6 is a cross-sectional view showing an example of a portion of a cross section taken along line VI-VI in Figure 3. Figure 7 is an explanatory diagram illustrating the shapes of the support portion 16 of the drive plate 10 and the seat 43 in this embodiment. Figure 8 is a cross-sectional view showing an example of a portion of a cross section taken along line VIII-VIII in Figure 3. Figure 9 is an explanatory diagram illustrating the shapes of the support portion 22 of the driven plate 20 and the seat 43 in this embodiment.

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 connection 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 in the axial direction of the center of rotation Ax1. Furthermore, the first support surface 16a is an arc-shaped curved surface with a radius R11 centered on the first center point C11 when viewed in 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.

As shown in Figure 6, the first connection surface 16c connects two first support surfaces 16a corresponding to one coil spring 41. When viewed from the axial direction, the first connection surface 16c has an arc shape centered on the rotation center Ax1.

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.

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.

As shown in Figure 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 Figure 9, the third support surface 22d is an arc-shaped curved surface with a radius R23 centered on the rotation center Ax1 when viewed from the axial direction.

As shown in Figure 8, the second connection surface 22e connects two second support surfaces 22a corresponding to one coil spring 41. As shown in Figure 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.

The support portion 22 also has a protruding portion 22c that includes a third support surface 22d. The protruding portion 22c protrudes circumferentially toward the seat 43.

As shown in Figures 5, 6, and 8, the seat 43 has a base portion 43a and a protrusion 43b that protrudes from the base portion 43a into the coil spring 41.

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

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.

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.

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

As shown in FIG. 5, the seat 43 has 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 also has surfaces 43d1 and 43d2 and recessed surfaces 43e1 and 43e2 in addition to the above.

Next, we will explain the operation of the damper device 1.

As shown in Figures 7 and 9, in the first state in which the drive plate 10 and 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.

Figure 10 is an exemplary cross-sectional view showing 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. Figure 11 is an exemplary cross-sectional view showing 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.

Figures 10 and 11 show the state in which the coil spring 41 is compressed when the drive plate 10 and 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 (Figure 10) and rotates integrally with the drive plate 10, while the other sheet 43A is pressed against the driven plate 20 (Figure 11) and rotates integrally with the driven plate 20.

At this time, the sliding surface 43f2 of one seat 43B slides against the third support surface 22d of the driven plate 20, and the seat 43B and the driven plate 20 rotate relative to each other so that the protrusion 22c of the driven plate 20 enters the recessed surface 43e2 of the seat 43B (Figure 11). 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 (Figure 11). That is, a gap D2 exists between the second opposing surface 43c2 of the one 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. Furthermore, a gap D1 exists between the first opposing surface 43c1 of the one seat 43B and the first support surface 16a of the drive plate 10. In this case, because the centrifugal force is relatively small, the sheet 43B does not rotate (tilt) relative to the first support surface 16a even if there is a gap D1.

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 (Figure 11). At this time, the first opposing surface 43c1 of the other sheet 43A is spaced from the first support surface 16a of the drive plate 10 (Figure 10). That is, a gap D1 exists 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 exists between the second opposing surface 43c2 of the other sheet 43A and the second support surface 22a of the driven plate 20. At this time, because the centrifugal force is relatively small, the sheet 43A does not rotate (tilt) relative to the second support surface 22a even though there is a gap D2.

Figure 12 is an exemplary cross-sectional view showing 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. Figure 13 is an exemplary cross-sectional view showing 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.

Figures 12 and 13 show the state in which the coil spring 41 is compressed when the drive plate 10 and 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 (Figure 12) and rotates integrally with the drive plate 10, while the other sheet 43A is pressed against the driven plate 20 (Figure 13) and rotates integrally with the driven plate 20.

At this time, the sliding surface 43f2 of one seat 43B slides against the third support surface 22d of the driven plate 20, and the seat 43B and the driven plate 20 rotate relative to each other so that the protrusion 22c of the driven plate 20 enters the recessed surface 43e2 of the seat 43B (Figure 13). At this time, the second opposing surface 43c2 of one seat 43B is spaced apart from the second support surface 22a of the driven plate 20 (Figure 13). That is, as in the example of Figure 11, there is a gap D2 between the second opposing surface 43c2 of 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 radial outward movement (Figure 12). In other words, rotation (tilt) of the seat 43B relative to the first support surface 16a is restricted.

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. 13 ). At this time, the first opposing surface 43c1 of the other sheet 43A is spaced apart 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 exists between the first opposing surface 43c1 of the other sheet 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 sheet 43A moves radially outward due to centrifugal force, but the second opposing surface 43c2 of the other sheet 43A comes into contact with the second support surface 22a of the driven plate 20, limiting its radially outward movement ( FIG. 13 ). That is, the rotation (tilt) of the sheet 43A relative to the second support surface 22a is limited.

As described above, in this embodiment, 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. Furthermore, 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 seat 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 seat 43B) are rotating relative to each other, a gap D2 is formed between the second support surface 22a and the second opposing surface 43c2.

Figure 14 shows an example of the relationship between torsional torque and torsional angle for the damper device 1 of this embodiment. With the above-described configuration, in this embodiment, as shown in Figure 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. Figure 14 shows that the third support surface 22d and the sliding surface 43f2 slide within the angle range M1 of the relative rotation between the drive plate 10 and the driven plate 20, and that this sliding increases the torsional torque. Note that "in" in Figure 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 Figure 14 indicates the case where the protruding portion 22c of the driven plate 20 exits the concave surface 43e2 of the seat 43.

As described above, in this embodiment, the damper device 1 includes a drive plate 10 (first rotating element), a driven plate 20 (second rotating element), a coil spring 41 (elastic element), and a pair of seats 43 (support members). The drive plate 10 is rotatable around the center of rotation Ax1. The driven plate 20 is rotatable around the center of rotation 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 center of rotation 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 center of rotation 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 from the axial direction. The third center point C12 is located on the first line L1 radially outward from the center of rotation 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 from the axial direction. The fourth center point C22 is located on the first line L1 radially outward from the center of rotation Ax1. In the first state, the sliding surface 43f2 contacts the third support surface 22d 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 seat 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 seat 43B) are rotating relative to each other, a gap D2 is formed between the second support surface 22a and the second opposing surface 43c2.

With 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 driven plate 20 rotate relative to each other. This allows frictional resistance to be generated by this sliding, regardless of the rotation speed of the damper device 1. Therefore, for example, the effects of vibrations during engine start-up, etc., can be suppressed when the damper device 1 is rotating at a relatively low speed. Furthermore, with this configuration, when the drive plate 10 and seat 43 are rotating relative to each other, a gap D1 exists between the first support surface 16a and the first opposing surface 43c1. When the driven plate 20 and seat 43 are rotating relative to each other, a gap D2 exists 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, frictional resistance can be suppressed from increasing compared to a configuration without the above gaps D1 and D2.

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.

With this configuration, the position of the seat 43 supported by the drive plate 10 can be stabilized when the first support surface 16a and the first opposing surface 43c1 are in contact.

Furthermore, the third center point C12 is located radially inward from the first center point C11.

With this configuration, for example, a gap D1 can be created 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.

Furthermore, 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.

With this configuration, the position of the seat 43 supported by the driven plate 20 can be stabilized when the second support surface 22a and the second opposing surface 43c2 are in contact.

Furthermore, the fourth center point C22 is located radially inward from the second center point C21.

With this configuration, for example, a gap D2 can be created 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.

In addition, 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.

With this configuration, when the damper device 1 starts to rotate, centrifugal force presses the sliding surface 43f2 of the sheet 43 against the third support surface 22d, preventing the sliding surface 43f2 and the third support surface 22d from separating.

Furthermore, 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.

This configuration allows smooth sliding between the third support surface 22d and the sliding surface 43f2.

Furthermore, the third support surface 22d and the sliding surface 43f2 slide within the angular range M1 (Figure 14) of relative rotation between the drive plate 10 and the driven plate 20.

This configuration makes it easy to adjust the range of frictional resistance caused by sliding between the third support surface 22d and the sliding surface 43f2 during design.

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 from the axial direction, the first connection surface 16c has an arc shape centered on the rotation center Ax1.

With this configuration, the radial size of the drive plate 10 can be reduced compared to, for example, a configuration in which two first support surfaces 16a are directly connected without the first connecting surface 16c.

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

With this configuration, the radial size of the driven plate 20 can be reduced compared to, for example, a configuration in which two second support surfaces 22a are directly connected without the second connecting surface 22e.

The seat 43 also has a groove 43g recessed radially inward from the first opposing surface 43c1. The second opposing surface 43c2 is located in the groove 43g.

With this configuration, the sheet 43 can be made lighter than, for example, a configuration in which the grooves 43g are not provided.

In the above embodiment, for example, an example was shown in which two second support surfaces 22a were connected via the second connection surface 22e, but this 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. In other words, a hole may be provided between lines L2 and L3 in Figure 8. This configuration allows the weight of the driven plate 20 to be reduced.

The above describes exemplary embodiments of the present invention, but the above embodiments are merely examples and are not intended to limit the scope of the invention. The embodiments can be implemented in a variety of 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, placement, position, etc.) can be modified as appropriate.

1... damper device 10... drive plate (first rotating element)
16a...first support surface 16c...first connection surface 20...driven plate (second rotating element)
22a... Second support surface 22d... Third support surface 22e... Second connection surface 41... Coil spring (elastic element)
43...Sheet (support member)
43c1...First opposing surface 43c2...Second opposing surface 43f2...Sliding surface Ax1...Rotation center C11...First center point (first point)
C12...Third center point (third point)
C21...Second center point (second point)
C22...Fourth center point (fourth point)
D1, D2...Gap L1...First line

Claims (12)

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. 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 . The damper device according to claim 1 or 2, wherein the third point is located radially inward of the first point. 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. A damper device according to any one of claims 1 to 4, wherein the fourth point is located radially inward of the second point. 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. The damper device described in any one of claims 1 to 6, 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. 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. 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. 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. 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. 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.