JP7768006B2 - Damper - Google Patents

Description

The present invention relates to a damper.

Conventionally, a damper has been known that includes a first rotating element, a second rotating element, a friction element interposed between the first and second rotating elements that rotates integrally with the second rotating element and slides against the first rotating element, and a pressing element that generates an elastic force that presses the first rotating element and the friction element against each other (Patent Document 1). In such dampers, grease may be applied to the connecting portion provided on the second rotating element that is connected to a connecting object, for example, by a spline connection.

JP 2012-67877 A

In this type of damper, if the grease applied to the connecting part is scattered by centrifugal force and adheres to the friction surface of the friction element that slides against the first rotating element, there is a risk that the friction force between the first rotating element and the friction element will decrease.

Therefore, one of the objectives of the present invention is to provide a new damper that, for example, when grease is applied to the connecting portion, is more likely to prevent the grease from adhering to the friction surface of the friction element.

The damper of the present invention comprises: a first rotating element rotatable about a rotation center, having two friction wall portions formed in an annular shape around the rotation center and aligned in the axial direction of the rotation center; a second rotating element rotatable about the rotation center, having a connecting portion positioned radially inward of the rotation center relative to the two friction wall portions and formed in a cylindrical shape around the rotation center; and a support wall portion extending from the connecting portion between the two friction wall portions and formed in an annular shape 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 an elastic element provided on both sides of the support wall portions in the axial direction and rotatable about the rotation center integrally with the second rotating element. The friction element comprises two friction elements supported by a support wall portion, each having an inner circumferential surface extending from a radially inner position of the friction wall portion toward the support wall portion, a friction surface located radially outward from the inner circumferential surface and between the friction wall portion and the support wall portion, and capable of sliding against the friction wall portion, and an opposing surface located on the support wall portion side of the friction surface, extending radially outward from the inner circumferential surface and opposing the support wall portion; and a pressing element interposed between the friction element and the support wall portion, generating an elastic force that presses the friction wall portion and the friction surface against each other, and the inner circumferential surface of at least one of the two friction elements has an inclined surface that slopes radially outward as it approaches the support wall portion.

With this configuration, for example, the inner circumferential surface of at least one of the two friction elements is provided with an inclined surface that slopes radially outward as it approaches the support wall portion. Therefore, when grease is applied to the connecting portion, even if the grease is scattered radially outward due to centrifugal force, the grease is likely to hit the inclined surface. The grease that hits the inclined surface moves along the inclined surface toward the opposing surface, passing between the opposing surface and the support wall portion and moving radially outward. This helps to prevent grease from adhering to the friction surfaces of the friction elements.

In the damper, for example, the radially outer end of the opposing surface of the friction element on which the inclined surface is provided is located radially outward of the friction surface.

This configuration helps prevent grease moving from the radially outer edge of the opposing surface to the radially outer side from adhering to the friction surface.

In the damper, for example, the opposing surface of the friction element on which the inclined surface is provided has a groove extending in the radial direction.

With this configuration, grease that flows from the inclined surface to the opposing surface can be guided radially outward by the groove.

In the damper, for example, the groove is provided at a position offset in the circumferential direction relative to the elastic element.

This configuration helps prevent grease that flows radially outward from the groove from adhering to the elastic element and to the friction surface of the friction element.

In the damper, for example, the inclined surface is aligned in the radial direction with the axial end of the connecting portion, and the end of the inclined surface opposite the support wall portion is located in the axial direction from the support wall portion toward the end of the inclined surface, further than the end of the connecting portion.

With this configuration, if grease applied to the connecting portion is scattered radially outward due to centrifugal force, the grease is more likely to come into contact with the inclined surface. This further reduces the likelihood of grease adhering to the friction surfaces of the friction elements.

FIG. 1 is an exemplary front view of a damper according to an embodiment, as viewed from the axial direction. FIG. 2 is an exemplary exploded perspective view of the damper according to the embodiment. FIG. 3 is a cross-sectional view taken along line III-III in FIG. FIG. 4 is a cross-sectional view taken along line IV-IV in FIG. FIG. 5 is an enlarged view of part V in FIG. 6 is a cross-sectional view of a portion of the VI-VI cross section of FIG. 1, which corresponds to FIG. 5 in the radial direction. FIG. 7 is an exemplary view of the first friction element of the damper according to the embodiment as viewed from the axial direction. FIG. 8 is an exemplary perspective view of a first friction element of the damper according to the embodiment. FIG. 9 is an exemplary view of the second friction element of the damper according to the embodiment as viewed from the axial direction. FIG. 10 is an exemplary perspective view of a second friction element of the damper 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, hereinafter, the axial direction of the center of rotation Ax will be simply referred to as the axial direction, the radial direction of the center of rotation Ax will be simply referred to as the radial direction, and the circumferential direction of the center of rotation Ax will be simply referred to as the circumferential direction. The center of rotation Ax will also be referred to as the central axis.

Figure 1 is an exemplary front view of the damper 1 of the embodiment as viewed from the axial direction. Figure 2 is an exemplary exploded perspective view of the damper 1 of the embodiment. Figure 3 is a cross-sectional view taken along III-III in Figure 1. Figure 4 is a cross-sectional view taken along IV-IV in Figure 1.

As shown in Figures 1 to 4, the damper 1 includes a drive plate 10, a driven plate 20, and an intermediate plate 30. The drive plate 10, the driven plate 20, and the intermediate plate 30 are each independently rotatable around the center of rotation Ax. In other words, the drive plate 10, the driven plate 20, and the intermediate plate 30 are rotatable relative to one another. The drive plate 10, the driven plate 20, and the intermediate plate 30 are made of a metal material such as an iron-based material. The drive plate 10 is an example of a first rotating element, the driven plate 20 is an example of a second rotating element, and the intermediate plate 30 is an example of a third 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.

As shown in FIG. 1, the drive plate 10 has a central wall portion 10a, multiple drive arms 10b, and a peripheral edge portion 10c. The central wall portion 10a is located radially inward of the drive plate 10 and has an annular shape centered on the center of rotation Ax. The drive arms 10b protrude radially outward from the central wall portion 10a and bridge between the central wall portion 10a and the peripheral edge portion 10c. In this embodiment, the multiple drive arms 10b are spaced apart circumferentially. The central wall portion 10a is an example of a friction wall portion.

The drive plate 10 is composed of multiple components. Specifically, as shown in Figures 3 and 4, the drive plate 10 has a front plate 11 and a rear plate 12. Each of the front plate 11 and the rear plate 12 has a central wall portion 10a, multiple drive arms 10b, and a peripheral portion 10c. In other words, there are two central walls 10a. The front plate 11 and the rear plate 12 are joined together by connecting members 14 (Figure 4). 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 and the rear plate 12 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 Ax (axial direction).

The driven plate 20 has a hub 21, a flange 22, and multiple driven arms 23. The hub 21 is an example of a connecting portion. The flange 22 is an example of a support wall portion.

The hub 21 is cylindrical, centered on the rotation center Ax. It is located radially inside the driven plate 20. A female spline portion 21a is provided on the inner surface of the hub 21. The female spline portion 21a is provided between both axial ends 21b, 21c of the hub 21. End 21b is the end in the other direction D2, and end 21c is the end in one direction. A shaft or other connecting object is connected to the hub 21. Specifically, a male spline portion of the connecting object is spline-connected to the female spline portion 21a. Grease is applied to the hub. Specifically, grease (lubricant) is applied to the inner surface of the hub 21, i.e., between the female spline portion 21a and the male spline portion of the connecting object.

The flange 22 protrudes radially outward from the hub 21. The flange 22 is located between the front plate 11 and rear plate 12 of the drive plate 10. The flange 22 is shaped like a plate that intersects (is perpendicular to) the center of rotation Ax (axial direction).

The multiple driven arms 23 protrude radially outward from the flange 22. The multiple driven arms 23 are spaced apart in the circumferential direction. The drive arm 10b and the driven arms 23 overlap in the axial direction.

The intermediate plate 30 has a central portion 30a and multiple intermediate arms 30b. The central portion 30a is located radially inward of the intermediate plate 30 and has an annular shape centered on the rotation center Ax. The intermediate arms 30b protrude radially outward from the central portion 30a. In this embodiment, the multiple intermediate arms 30b are spaced apart in the circumferential direction.

Furthermore, the intermediate plate 30 is composed of multiple members. Specifically, the intermediate plate 30 has a first intermediate plate 31 and a second intermediate plate 32. The first intermediate plate 31 and the second intermediate plate 32 are joined together by a connecting member 33 (Figure 4). The connecting member 33 is, for example, a rivet, but may also be other fasteners such as a bolt and nut, or a shaft, etc.

The first intermediate plate 31 is located between the front plate 11 of the drive plate 10 and the hub 21 of the driven plate 20. The second intermediate plate 32 is located between the rear plate 12 of the drive plate 10 and the hub 21 of the driven plate 20. The first intermediate plate 31 and the second intermediate plate 32 are shaped like plates that intersect (are perpendicular to) the center of rotation Ax.

A cylindrical first friction element 61 and a cylindrical second friction element 62 are provided on both axial sides of the flange 22 of the driven plate 20. The first friction element 61 and the second friction element 62 both provide 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 to be rotatable integrally with the driven plate 20 and to be slidable relative to the rear plate 12. The first friction element 61 is coupled to the driven plate 20, for example, by fitting a recess provided on one side of the first friction element 61 and the flange 22 of the driven plate 20 with a protrusion provided on the other side of the first friction element 61 and the flange 22 of the driven plate 20. In other words, the first friction element 61 is supported by the flange 22. The second friction element 62 is provided to be rotatable integrally with the driven plate 20 and to be slidable relative to the front plate 11. The second friction element 62 is coupled to the driven plate 20, for example, by fitting a recess provided on one of the second friction element 62 and the flange 22 of the driven plate 20 into a protrusion provided on the other of the second friction element 62 and the flange 22 of the driven plate 20. In other words, the second friction element 62 is supported by the flange 22.

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

A disc spring 71 is interposed between the first friction element 61 and the driven plate 20. The disc spring 71 is an example of a pressing element. The disc spring 71 is also referred to as an elastic element.

As shown in FIG. 1, the damper 1 includes a plurality of first coil springs 41 and a plurality of second coil springs 42. The first coil springs 41 and second coil springs 42 are interposed between the drive arm 10b and the intermediate arm 30b, and between the driven arm 23 and the intermediate arm 30b.

The first coil spring 41 and the second coil spring 42 each extend substantially along the circumferential direction (tangential direction). The first coil spring 41 is positioned adjacent to the drive arm 10b and the driven arm 23 in the clockwise direction in FIG. 1, and adjacent to the intermediate arm 30b in the counterclockwise direction in FIG. 1. The second coil spring 42 is positioned adjacent to the drive arm 10b and the driven arm 23 in the counterclockwise direction in FIG. 1, and adjacent to the intermediate arm 30b in the clockwise direction in FIG. 1. The first coil spring 41 and the second coil spring 42 are arranged alternately in the circumferential direction. The first coil spring 41 and the second coil spring 42 are an example of an elastic element interposed between the drive plate 10 and the driven plate 20. The elastic element is not limited to a coil spring and may be another elastic element, such as an elastomer.

1, during acceleration, the relative torsion between the drive plate 10 and the driven plate 20 causes the drive arm 10b and the intermediate arm 30b to elastically compress the first coil spring 41, and the intermediate arm 30b and the driven arm 23 to elastically compress the second coil spring 42. On the other hand, during deceleration, the relative torsion between the drive plate 10 and the driven plate 20 causes the drive arm 10b and the intermediate arm 30b to elastically compress the second coil spring 42, and the intermediate arm 30b and the driven arm 23 to elastically compress the first coil spring 41. The torsional state during acceleration is a state in which the drive plate 10 is twisted in the forward direction relative to the driven plate 20 from its neutral position (untwisted position, position where the torsion angle is 0). In this specification, this state is referred to as the forward torsional state of the damper 1. On the other hand, the torsional state during deceleration is a state in which the drive plate 10 is twisted in the reverse direction (opposite the normal rotation direction) relative to the driven plate 20 from its neutral position; in this specification, this state is referred to as the reverse torsional state of the damper 1.

In addition, sheet members 43 are interposed between both ends of the first coil spring 41 and the second coil spring 42 in the longitudinal direction (winding axis direction, circumferential direction of the damper 1) and the drive arm 10b, driven arm 23, and intermediate arm 30b. The sheet members 43 may also be referred to as retainers.

Next, we will explain the positioning structure for the drive plate 10, driven plate 20, and intermediate plate 30.

Figure 5 is an enlarged view of part V in Figure 3. Figure 6 is a cross-sectional view of part of the VI-VI section in Figure 1, corresponding to Figure 5 in the radial direction.

As shown in Figures 5 and 6, the drive plate 10 has friction surfaces 10fa and 10fb. Friction surface 10fa is provided on the rear plate 12 and faces in one direction D1 in the axial direction of the rotation center Ax. Friction surface 10fa is formed in an annular shape around the rotation center Ax. Friction surface 10fb is provided on the front plate 11 and is located on the one direction D1 side of friction surface 10fa. Friction surface 10fb faces in the other direction D2, opposite the one axial direction D1. Friction surface 10fb is formed in an annular shape around the rotation center Ax. Friction surfaces 10fa and 10fb face each other in the axial direction. That is, friction surfaces 10fa and 10fb are aligned in the axial direction. The flange 22 of the driven plate 20 is located between friction surfaces 10fa and 10fb.

The driven plate 20 also has surfaces 20fa and 20fb. Surfaces 20fa and 20fb are provided on the flange 22. Surface 20fa faces in the other direction D2, and surface 20fb faces in the one direction D1.

The intermediate plate 30 has opposing surfaces 30fa and 30fb. Opposing surface 30fa is located axially between the flange 22 and friction surface 10fa and faces in one direction D1. Opposing surface 30fb is located axially between the flange 22 and friction surface 10fb and faces in the other direction D2.

Figure 7 is an exemplary view of the first friction element 61 of the damper 1 of the embodiment, viewed from the axial direction. Figure 8 is an exemplary perspective view of the first friction element 61 of the damper 1 of the embodiment.

As shown in Figures 5 to 8, the first friction element 61 has a base portion 61a, a support portion 61b, and a standing wall portion 61c. At least a portion of the base portion 61a is located between the central wall portion 10a of the rear plate 12 of the drive plate 10 and the flange 22 of the driven plate 20. The support portion 61b is located radially inward of the central wall portion 10a of the rear plate 12. The standing wall portion 61c extends radially outward from the base portion 61a.

The first friction element 61 also has an inner circumferential surface 61ff. The inner circumferential surface 61ff is provided across the base portion 61a and the support portion 61b.

The first friction element 61 also has a friction surface 61fa and a contact surface 61fb. Friction surface 61fa and contact surface 61fb are located radially outward from inner circumferential surface 61ff. Friction surface 61fa is located on the one side of friction surface 10fa of the drive plate 10 in direction D1 and faces the other side of direction D2. Friction surface 61fa is in contact with friction surface 10fa. Friction surface 61fa can slide against friction surface 10fa. Contact surface 61fb is located on the one side of opposing surface 30fa of the intermediate plate 30 in direction D1 and faces the other side of direction D2. Contact surface 61fb can come into contact with opposing surface 30fa. Contact surface 61fb can slide against opposing surface 30fa.

The first friction element 61 also has opposing surface 61fc and surfaces 61fd and 61e. Opposing surface 61fc faces in direction D1 and faces surface 20fa of the flange 22 of the intermediate plate 30 at a distance. Surface 61fd faces radially outward and is in contact with the inner periphery of the rear plate 12 of the drive plate 10. This allows the drive plate 10 to position the first friction element 61 radially. Surface 61fe faces radially outward and supports the inner periphery of the second intermediate plate 32 of the intermediate plate 30, radially positioning the second intermediate plate 32 and therefore the intermediate plate 30.

Furthermore, the opposing surface 61fc has a recess 61fm. The recess 61fm is recessed from the opposing surface 61fc in a direction away from the flange 22, i.e., in the other direction D2. The opposing surface 61fc is included in the opposing surface 61fc.

Figure 9 is an exemplary view of the second friction element 62 of the damper 1 of the embodiment, viewed from the axial direction. Figure 10 is an exemplary perspective view of the second friction element 62 of the damper 1 of the embodiment.

As shown in Figures 5, 6, 9, and 10, the second friction element 62 has a base portion 62a, a support portion 62b, and a standing wall portion 62c. At least a portion of the base portion 62a is located between the central wall portion 10a of the front plate 11 of the drive plate 10 and the flange 22 of the driven plate 20. The support portion 62b is located radially inward of the central wall portion 10a of the front plate 11. The standing wall portion 62c extends radially outward from the base portion 62a.

The second friction element 62 also has an inner circumferential surface 62ff. The inner circumferential surface 62ff is provided across the base portion 61a and the support portion 62b.

The second friction element 62 also has a friction surface 62fa and a contact surface 62fb. The friction surface 62fa and the contact surface 62fb are located radially outward from the inner circumferential surface 62ff. The friction surface 62fa is located on the other direction D2 side of the friction surface 10fb of the drive plate 10 and faces in one direction D1. The friction surface 62fa is in contact with the friction surface 10fb. The friction surface 62fa can slide against the friction surface 10fb. The contact surface 62fb is located on the other direction D2 side of the opposing surface 30fb of the intermediate plate 30 and faces in one direction D1. The contact surface 62fb can come into contact with the opposing surface 30fb. The contact surface 62fb can slide against the opposing surface 30fb.

The second friction element 62 also has opposing surface 62fc and surfaces 62fd and 62e. Opposing surface 62fc faces the other direction D2 and faces surface 20fb of the flange 22 of the intermediate plate 30. Opposing surface 62fc is in contact with surface 20fb. Surface 62fd faces radially outward and is in contact with the inner periphery of the front plate 11 of the drive plate 10. This allows the drive plate 10 to position the second friction element 62 radially. Surface 62fe faces radially outward and supports the inner periphery of the first intermediate plate 31 of the intermediate plate 30, radially positioning the first intermediate plate 31 and therefore the intermediate plate 30.

Next, the inner circumferential surfaces 61ff, 62ff and the opposing surfaces 61fc, 62fc will be described in detail. As shown in Figures 5 and 6, the inner circumferential surfaces 61ff, 62ff include surfaces 61fg, 62g and inclined surfaces 61fh, 62fh.

Surfaces 61fg and 62fg are located radially inward of the central wall portions 10a of the rear plate 12 and front plate 11. Surfaces 61fg and 62fg are formed in an annular shape parallel to the axial direction.

The inclined surfaces 61fh, 62fh are inclined in the axial direction so as to extend radially outward toward the flange 22. The inclined surfaces 61fh, 62fh are formed in an annular shape. Note that the inclined surfaces 61fh, 62fh may be provided partially on the inner circumferential surfaces 61ff, 62ff.

Furthermore, the inclined surfaces 61fh, 62fh are aligned radially with the axial ends 21b, 21c of the hub 21. The ends 61fi, 62fi of the inclined surfaces 61fh, 62fh opposite the flange 2 are located further axially (in one direction D1 or the other direction D2) from the flange 22 toward the ends 61fi, 62fi of the inclined surfaces 61fh, 62fh than the ends 21b, 21c of the hub 21. In other words, the ends 21b, 21c of the hub 21 are aligned radially with the intermediate portions of the inclined surfaces 61fh, 62fh between the ends 61fi, 62fi and the ends 61fj, 62fj.

Furthermore, the radially outer ends 61fk, 62fk of the opposing surfaces 61fc, 62fc are located radially outward from the friction surfaces 61fa, 62fa. In other words, the radially outer ends of the standing wall portions 61c, 62c are located radially outward from the friction surfaces 61fa, 62fa.

Furthermore, grooves 61fp, 62fp extending radially are provided on the opposing surfaces 61fc, 62fc. Grooves 61fp, 62fp are provided at positions offset in the circumferential direction relative to the first coil spring 41 and the second coil spring 42. In other words, grooves 61fp, 62fp are provided at positions that are not aligned radially with the first coil spring 41 and the second coil spring 42.

The disc spring 71 is interposed between the first friction element 61 and the flange 22. The disc spring 71 is annular about the center of rotation Ax. The disc spring 71 has a conical shape whose diameter gradually increases in the other direction D2. The disc spring 71 has a first end 71a and a second end 71b. The first end 71a is the inner end (edge) and is in contact with the surface 20fa of the flange 22 of the driven plate 20. The second end 71b is the outer end (edge) and is inserted into the recess 61fm of the first friction element 61. That is, at least a portion of the disc spring 71 is accommodated in the recess 61fm. The recess 61fm is also referred to as the accommodation portion. The second end 71b is in contact with the surface 61fn that forms the recess 61fm in the first friction element 61. The second end 71b is aligned axially with the friction surfaces 10fa, 10fb, 61fa, and 62fa. In other words, the second end 71b overlaps the friction surface 10fa in the axial direction via the first friction element 61, and overlaps the friction surface 10fb in the axial direction via the second friction element 62. The radial position of the second end 71b is within the radial position range E1 of the overlapping portion between the friction surfaces 10fa and 61fa, and within the radial position range E2 of the overlapping portion between the friction surfaces 10fb and 62fa. The disc spring 71 is an example of a third elastic element. The disc spring 71 may be made of an iron-based metallic material, such as spring steel.

The disc spring 71 uses its elastic force to press the friction surfaces 10fa and 61fa against each other, and also press the friction surfaces 10fb and 62fa against each other. That is, the disc spring 71 generates an elastic force that presses the friction surfaces 10fa and 61fa against each other, and also presses the friction surfaces 10fb and 62fa against each other. This generates a frictional force between the friction surfaces 10fa and 61fa, and a frictional force between the friction surfaces 10fb and 62fa.

In the above configuration, the disc spring 71 presses the friction surface 10fa of the drive plate 10 against the friction surface 61fa of the first friction element 61, and presses the friction surface 10fb of the drive plate 10 against the friction surface 62fa of the second friction element 62, causing contact between the friction surface 10fa and the friction surface 61fa, and between the friction surface 10fb and the friction surface 62fa. This allows the drive plate 10 and the driven plate 20 to be positioned relative to each other in the axial direction. Furthermore, the axial contact between the opposing surface 30fa of the intermediate plate 30 and the contact surface 61fb of the first friction element 61, and the axial contact between the opposing surface 30fb of the intermediate plate 30 and the contact surface 62fb of the second friction element 62, also allows the driven plate 20 and the intermediate plate 30 to be positioned relative to each other in the axial direction.

At this time, as the first friction element 61 and the second friction element 62 slide against the drive plate 10 and wear, at least a portion of each of the first friction element 61 and the second friction element 62 thins in the axial direction. Because the disc spring 71 is interposed between the first friction element 61 and the flange 22 of the intermediate plate 30, at least a portion of each of the first friction element 61 and the second friction element 62 thins in the axial direction so as to separate from each other in the axial direction. Specifically, the first friction element 61 thins in the axial direction at a portion between the friction surface 61fa and the opposing surface 61fc, and the second friction element 62 thins in the axial direction at a portion between the friction surface 62fa and the opposing surface 62fc. This prevents the gap between the contact surface 61fb of the first friction element 61 and the contact surface 62fb of the second friction element 62 from narrowing. In other words, the first friction element 61 and the second friction element 62 wear so that the rattle between the second intermediate plate 32 of the intermediate plate 30 and the first friction element 61, and the rattle between the first intermediate plate 31 of the intermediate plate 30 and the second friction element 62, are reduced.

Furthermore, with the above configuration, grease applied to the hub 21 may be scattered radially outward due to centrifugal force. When this happens, the grease hits the inclined surfaces 61fh, 62fh. The grease that hits the inclined surfaces 61fh, 62fh moves along the inclined surfaces 61fh, 62fh toward the opposing surfaces 61fc, 62fc, passing between the opposing surfaces 61fc, 62fc and the flange 22 and moving radially outward. The grease that passes between the opposing surfaces 61fc, 62fc and the flange 22 flows out radially outward through the opening between the front plate 11 and the rear plate 12.

As described above, in this embodiment, the damper 1 includes a drive plate 10 (first rotating element), a driven plate 20 (second rotating element), a first coil spring 41 and a second coil spring 42 (elastic elements), a first friction element 61 and a second friction element 62 (two friction elements), and a disc spring 71 (pressing element). The drive plate 10 is rotatable around a rotation center Ax. The drive plate 10 has two central wall portions 10a (friction wall portions) formed in an annular shape around the rotation center Ax and aligned in the axial direction of the rotation center Ax. The driven plate 20 is rotatable around the rotation center Ax. The driven plate 20 has a hub 21 (connecting portion) and a flange 22 (support wall portion). The hub 21 is located radially inward of the rotation center Ax relative to the two central wall portions 10a and is cylindrically formed around the rotation center Ax. The flange 22 extends from the hub 21 between the two central wall portions 10a and is formed in an annular shape around the center of rotation Ax. The first coil spring 41 and the second coil spring 42 are interposed between the drive plate 10 and the driven plate 20 and elastically expand and contract in the circumferential direction of the center of rotation Ax. The first friction element 61 and the second friction element 62 are provided on both axial sides of the flange 22 and are supported by the flange 22 so as to be rotatable integrally with the driven plate 20 around the center of rotation Ax. The first friction element 61 and the second friction element 62 each have inner circumferential surfaces 61ff, 62ff, friction surfaces 61fa, 62fa, and opposing surfaces 61fc, 62fc. The inner circumferential surfaces 61ff, 62ff extend from radially inner positions of the central wall portion 10a toward the flange 22. The friction surfaces 61fa, 62fa are located radially outward from the inner circumferential surfaces 61ff, 62ff and between the central wall portion 10a and the flange 22, allowing them to slide against the central wall portion 10a. The opposing surfaces 61fc, 62fc are located on the flange 22 side of the friction surfaces 61fa, 62fa, extending radially outward from the inner circumferential surfaces 61ff, 62ff and facing the flange 22. The disc springs 71 (pressing elements) are interposed between the first friction element 61 and the second friction element 62 and the flange 22, generating an elastic force that presses the central wall portion 10a and the friction surfaces 61fa, 62fa against each other. The inner circumferential surfaces 61ff, 62ff of at least one of the first friction element 61 and the second friction element 62 (for example, both) are provided with inclined surfaces 61fh, 62fh that slope radially outward toward the flange 22.

With this configuration, for example, at least one of the first friction element 61 and the second friction element 62 (for example, both) has the inclined surfaces 61fh and 62fh. Therefore, even if grease is applied to the hub 21 and the grease scatters radially outward due to centrifugal force, the grease easily strikes the inclined surfaces 61fh and 62fh. The grease that strikes the inclined surfaces 61fh and 62fh moves along the inclined surfaces 61fh and 62fh toward the opposing surfaces 61fc and 62fc, passing between the opposing surfaces 61fc and 62fc and the flange 22, moving radially outward. This effectively prevents grease from adhering to the friction surfaces 61fa and 62fa of the first friction element 61 and the second friction element 62 and the friction surfaces fa and 10fb of the drive plate 10. This effectively prevents a decrease in the frictional force between the drive plate 10 and the first friction element 61 and the second friction element 62. That is, the friction force between the drive plate 10 and the first and second friction elements 61 and 62 is stabilized. This suppresses the occurrence of resonance in the damper 1, making it easier to ensure the performance of the damper 1. Furthermore, with the above configuration, it is not necessary to provide grooves or the like in the hub 21 to prevent grease from adhering to the friction surfaces 61fa, 62fa of the first and second friction elements 61 and 62 and the friction surfaces fa, 10fb of the drive plate 10. This prevents the shape of the hub 21 from becoming too complicated, and also prevents an increase in the manufacturing costs of the hub 21.

Furthermore, the radially outer ends 61fk, 62fk of the opposing surfaces 61fc, 62fc of the first friction element 61 and the second friction element 62, on which the inclined surfaces 61fh, 62fh are provided, are located radially outward of the friction surfaces 61fa, 62fa.

This configuration helps prevent grease that moves radially outward from the radially outer ends 61fk, 62fk of the opposing surfaces 61fc, 62fc from adhering to the friction surfaces 61fa, 62fa.

In addition, grooves 61fp and 62fp extending in the radial direction are provided on the opposing surfaces 61fc and 62fc of the first and second friction elements 61 and 62, on which the inclined surfaces 61fh and 62fh are provided.

With this configuration, grease that has flowed from the inclined surfaces 61fh, 62fh to the opposing surfaces 61fc, 62fc can be guided (discharged) radially outward by the grooves 61fp, 62fp.

In addition, grooves 61fp, 62fp are provided at positions offset circumferentially relative to the first coil spring 41 and the second coil spring 42.

This configuration helps prevent grease flowing radially outward from grooves 61fp, 62fp from adhering to the first coil spring 41 and second coil spring 42, and more effectively prevents grease from adhering to the friction surfaces 61fa, 62fa.

Furthermore, the inclined surfaces 61fh, 62fh are aligned radially with the axial ends 21b, 21c of the hub 21, and the ends 61fi, 62fi of the inclined surfaces 61fh, 62fh opposite the flange 2 are located further in the axial direction (one direction D1 or the other direction D2) from the flange 22 toward the ends 61fi, 62fi of the inclined surfaces 61fh, 62fh than the ends 21b, 21c of the hub 21.

With this configuration, if grease applied to the hub 21 is scattered radially outward due to centrifugal force, the grease is more likely to come into contact with the inclined surfaces 61fh, 62fh. This further reduces the likelihood of grease adhering to the friction surfaces 61fa, 62fa of the first friction element 61 and the second friction element 62.

In the above embodiment, an example was shown in which the disc spring 71 was interposed between the first friction element 61 and the second friction element 62 and the flange 22, but this is not limited to this. For example, the disc spring 71 may be interposed between the first friction element 61 and the second friction element 62 and the flange 22.

In addition, in the above embodiment, an example in which the recess 61fm is provided is shown, but this is not limited to this. For example, the recess 61fm may not be provided.

In addition, in the above embodiment, an example in which an intermediate plate 30 is provided is shown, but this is not limiting. For example, the intermediate plate 30 may not be provided.

In addition, in the above embodiment, an example was shown in which the inclined surfaces 61fh, 62fh were provided on both the first friction element 61 and the second friction element 62, but this is not limited to this. For example, the inclined surfaces 61fh, 62fh may be provided on only one of the first friction element 61 and the second friction element 62.

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 10... Drive plate (first rotating element)
10a...Central wall part (friction wall part)
20...Driven plate (second rotating element)
21...Hub (connecting part)
21b, 21c... ends 22... flange (support wall portion)
41...First coil spring (elastic element)
42...Second coil spring (pressing element)
61...First friction element (friction element)
61fa...Friction surface 61fc...Opposing surface 61ff...Inner peripheral surface 61fh...Slanted surface 61fk...End 61fp...Groove 62...Second friction element (friction element)
62fa... friction surface 62fc... opposing surface 62ff... inner peripheral surface 62fh... inclined surface 62fk... end 62fp... groove 71... disc spring (pressing element)
Ax...center of rotation

Claims (5)

a first rotating element that is rotatable around a rotation center and has two friction wall portions that are annularly formed around the rotation center and aligned in an axial direction of the rotation center;
a second rotating element provided rotatably around the rotation center, the second rotating element including: a connecting portion located radially inside the rotation center relative to the two friction wall portions and formed in a cylindrical shape around the rotation center; and a support wall portion extending from the connecting portion between the two friction wall portions and formed in an annular shape 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;
two friction elements provided on both sides of the support wall portion in the axial direction, supported by the support wall portion so as to be rotatable around the rotation center integrally with the second rotating element, each having an inner circumferential surface extending from a radially inner position of the friction wall portion toward the support wall portion, a friction surface located radially outward from the inner circumferential surface and between the friction wall portion and the support wall portion, and capable of sliding against the friction wall portion, and an opposing surface located on the support wall portion side with respect to the friction surface, extending radially outward from the inner circumferential surface and opposing the support wall portion;
a pressing element that is interposed between the friction element and the support wall portion and generates an elastic force that presses the friction wall portion and the friction surface against each other;
Equipped with
The inner circumferential surface of at least one of the two friction elements is provided with an inclined surface that extends radially outward toward the support wall portion.
Damper. The radially outer end of the opposing surface of the friction element on which the inclined surface is provided is located radially outer than the friction surface.
The damper according to claim 1 . The opposing surface of the friction element on which the inclined surface is provided is provided with a groove extending in the radial direction.
The damper according to claim 1 or 2. The groove is provided at a position offset in the circumferential direction relative to the elastic element.
The damper according to claim 3 . the inclined surface is aligned in the radial direction with the axial end of the coupling portion;
an end of the inclined surface opposite to the support wall portion is located further in the axial direction from the support wall portion toward the end of the inclined surface than the end of the connecting portion;
A damper according to any one of claims 1 to 4.