JP7013958B2 - Damper device - Google Patents

Description

An embodiment of the present invention relates to a damper device that attenuates rotational fluctuations between rotating members.

Conventionally, as a spring assembly installed in a damper mechanism such as a clutch disc used for a clutch, the input side rotating member and the output side rotating member are arranged so as to be elastically connected in the rotational direction, and the input side is arranged when the clutch is connected. And a spring assembly is known in which the output side rotating member is compressed by relative rotation.

The spring assembly includes a first coil spring, a second coil spring arranged on the inner peripheral side thereof, and a pair of spring seats arranged so as to face both end faces of the first coil spring. The spring seat has a support portion that supports the end portion of the first coil spring, and is provided on the support portion so that it can be engaged with the inner circumference of the first coil spring and can be in contact with one end surface and the other end surface of the second coil spring. It has a columnar protrusion and a columnar positioning member fixed to the protrusion and fitted to the inner circumference of the second coil spring.

According to this configuration, the trajectory in which the first coil spring is operated by the protrusion and the trajectory in which the second coil spring is operated by the positioning member are stably maintained, so that the inner circumference of the first coil spring and the second coil spring are maintained. It becomes difficult for the coil spring to come into contact with the outer periphery, and possible wear can be reduced.

Japanese Unexamined Patent Publication No. 2005-24506

However, in the configuration of the prior art, since the columnar protrusion is provided on the inner peripheral side of the first coil spring with respect to the spring seat, the inner diameter of the first coil spring is equal to or larger than the outer diameter of the protrusion. Is restricted to. Therefore, the diameter of the first coil spring is limited from the inside, and for example, a desired coil wire diameter may not be obtained.

Further, in order to provide a columnar positioning member that fits with the inner circumference of the second coil spring on the inner circumference side of the spring seat, the diameter dimension of the second coil spring is limited as in the above-mentioned relationship. Will be done. Further, since the protrusion is provided on the end face of the second coil spring, the axial length of the second coil spring is limited. For example, the axial length of the second coil spring must be shorter than that of the first coil spring by the length of the protrusion.

Therefore, the first and second coil springs are limited in the degree of freedom in design such as the coil wire diameter dimension and the axial length, and can generate an urging force according to the amount of deflection generated by compression when the clutch is connected. However, there is a risk that the desired torsional characteristics of the damper device cannot be obtained.

Therefore, the present invention has been made in view of such circumstances, and one of the purposes thereof is to provide a damper device capable of obtaining a degree of freedom in designing a coil spring.

In order to solve the above-mentioned problems, the damper device according to one aspect of the present invention has a first rotating member that can rotate around the rotation axis and a first rotating member that is arranged to face the first rotating member and can rotate around the rotation axis. A first coil spring that elastically connects the first and second rotating members in the circumferential direction of the first and second rotating members and attenuates rotational fluctuations between the first and second rotating members. , A second coil spring arranged on the inner peripheral side of the first coil spring and one of both end faces of the first coil spring while being arranged on both end faces of the first and second coil springs to sandwich both end faces. A convex portion that projects radially outward from the radial outer portion of the support surface that supports the end face and restricts the radial outward movement of the first coil spring in the first and second rotating members, and a circumferential portion that supports the support surface. It is formed in a recess and is located on the inner peripheral side of the first coil spring, is smaller than the inner diameter of the first coil spring, opens larger than the outer diameter of the second coil spring, and moves outward in the radial direction of the second coil spring. It is configured to include a recess for regulating the above and a pair of seat members having.

As a result, since the convex portion of the seat member is arranged on the outer peripheral side of the first coil spring, the inner diameter dimension of the first and second coil springs is not limited. Further, since the recess formed by being recessed from the support surface supporting one end surface of the first coil spring supports one end surface of the second coil spring, the axial length of the second coil spring is shortened. It is not limited to the direction, and it is possible to set it longer with respect to the first coil spring. Therefore, the degree of freedom in designing the coil springs (first and second coil springs) can be obtained.

Preferably, the convex portion includes a first regulating surface formed by bending in an arc shape along the winding direction of the first coil spring with a radius of curvature larger than the outer diameter of the first coil spring, and the concave portion includes the second coil. It is preferable to include an inner peripheral surface formed in a circular shape along the winding direction of the second coil spring with a radius of curvature larger than the outer diameter of the spring.

As a result, since the radius of curvature of the first regulating surface and the inner peripheral surface are larger than the outer diameters of the first and second coil springs, respectively, the first and second coil springs can stably hold their respective outer circumferences. Therefore, since the operating trajectories of the first and second coil springs are stably maintained, the inner circumference of the first coil spring and the outer circumference of the second coil spring are less likely to come into contact with each other, and the wear that may occur is reduced. Can be done.

Further, preferably, the convex portion includes a first regulating surface extending parallel to the central axis of the first coil spring, and the concave portion includes an inner peripheral surface extending parallel to the central axis of the second coil spring. Is good.

As a result, the first regulation surface and the inner peripheral surface extend along the outer periphery of the first and second coil springs in the central axis direction of the first and second coil springs, respectively, so that they are stable with the outer periphery. Since the first and second coil springs are in contact with each other, the outer circumferences of the first and second coil springs can be stably held. Therefore, since the operating trajectories of the first and second coil springs are stably maintained, the inner circumference of the first coil spring and the outer circumference of the second coil spring are less likely to come into contact with each other, and the wear that may occur is reduced. Can be done.

Further, it is preferable that the convex portion includes a second regulating surface formed so as to be separated from the coil center of the first coil spring as it approaches the tip of the convex portion.

As a result, the second regulating surface can stably hold the first coil spring that has moved outward in the radial direction. Therefore, the first coil spring can stably maintain the operating trajectory.

Further, it is preferable that the convex portion and the concave portion are separated from each other by a larger diameter than the coil wire diameter of the first coil spring.

As a result, when the outer peripheral surface of the radial outer side of the first coil spring and the first regulating surface of the convex portion come into contact with each other, and the outer peripheral surface of the radial outer side of the second coil spring and the inner peripheral surface of the concave portion come into contact with each other. The inner circumference of the radial inner side of the first coil spring and the outer circumference of the radial inner side of the second coil spring are less likely to come into contact with each other, and possible wear can be reduced.

According to the damper device according to one aspect of the present invention, the degree of freedom in designing the coil spring can be obtained.

FIG. 1 is a plan view showing a configuration of a damper device according to an embodiment of the present invention. FIG. 2 is a sectional view taken along line II-II of the damper device shown in FIG. FIG. 3 is an enlarged schematic view of a seat member portion of the damper device shown in FIG. 1. FIG. 3 is a schematic view illustrating a state in which the seat member of FIG. 3 restricts the movement of the first and second coil springs to the outside in the radial direction. It is a schematic diagram explaining the state which restricts the movement of the 1st and 2nd coil springs outward in the radial direction by the seat member which concerns on another Embodiment. FIG. 3 is an enlarged schematic view of a seat member portion according to another embodiment of the damper device shown in FIG. 1.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings. At that time, unless otherwise specified, the radial direction, the circumferential direction, and the axial direction refer to the radial direction, the circumferential direction, and the axial direction of the rotation axis Ax shown in FIGS. 1 and 2, respectively.

FIG. 1 is a plan view showing the configuration of a damper device according to an embodiment of the present invention, and FIG. 2 is a sectional view taken along line II-II of the damper device shown in FIG. The damper device 1 is used, for example, as a clutch disc of a friction clutch disposed between an automobile engine and a transmission. In this case, the facings 26A and 26B of the disc member 20 are appropriately sandwiched between the flywheel (not shown) connected to the drive shaft (not shown) and the pressure plate (not shown), and the hub member 10 outputs. Spline fitted to the transmission input shaft (not shown) as a shaft. Further, the rotation shaft Ax, which is the rotation center of the damper device 1, substantially coincides with the drive shaft and the transmission input shaft.

As shown in FIGS. 1 and 2, the damper device 1 includes the above-mentioned hub member 10, a disk member 20, an elastic member assembly 30 that elastically connects the two in the circumferential direction, and a hysteresis generating member 40. Be prepared. Here, the hub member 10 is an example of the first rotating member, and the disc member 20 is an example of the second rotating member.

As shown in FIG. 2, the hub member 10 has an inner hub 11 having a tubular portion 11a and a flange portion 11b, and a ring-shaped outer hub 12 coaxially arranged on the outer peripheral side of the inner hub 11. The tubular portion 11a is formed in a cylindrical shape coaxial with the rotation shaft Ax so as to surround the transmission input shaft, is coupled to the transmission input shaft by spline fitting, and rotates integrally. The flange portion 11b is formed in a ring shape and a plate shape orthogonal to the rotation axis Ax, extending radially outward from a substantially central portion in the axial direction of the tubular portion 11a. Further, the outer hub 12 is arranged so as to be relatively rotatable on the inner hub 11.

The disc member 20 has side plates 21 and 22 arranged coaxially and relatively on both sides of the inner hub 11 and the outer hub 12 in the axial direction. The side plates 21 and 22 are formed in a ring shape and a plate shape orthogonal to the rotation axis Ax, which are arranged radially outside the tubular portion 11a of the inner hub 11. The side plates 21 and 22 are connected by a pin 23 on the radial outer side of the outer hub 12 at a constant distance from each other, and further, a ring-shaped cushioning is provided at the outer diameter end of the side plate 21 by a pin 23. The plate 24 is fixed.

The cushioning plate 24 is a ring-shaped member that generates an elastic force with respect to axial pressing on the facings 26A and 26B. One surface of the cushioning plate 24 in the axial direction (the left surface of FIG. 2) has a facing 26A by the rivet 25A, and the other surface (the right surface of FIG. 2) has a facing 26B by the rivet 25B. It will be fixed. Here, the facings 26A and 26B are friction materials, and for example, those containing rubber, resin, fibers (short fibers, long fibers), particles for adjusting the friction coefficient μ, and the like may be used.

The elastic member assembly 30 includes a first coil spring 31 that elastically connects the outer hub 12 and the side plates 21 and 22 in the circumferential direction, and a second coil spring 32 that is accommodated and arranged in parallel on the inner peripheral side thereof. , A pair of seat members 33A, 33B arranged on both end faces of the first and second coil springs 31, 32. For example, the seat members 33A and 33B are formed of resin in order to reduce the wear of the first and second coil springs 31 and 32, and the first and second coil springs 31 and 32 generate a large restoring force at the time of bending. A metal spring is adopted to make it.

Further, here, the first and second coil springs 31 and 32 both adopt an equal winding pitch, but for example, the winding pitch on the center side is denser than the winding pitch near the winding end. It may be 1 coil spring 31. Further, the first and second coil springs 31 and 32 may have their winding directions opposite to each other. As a result, it may be difficult for the first coil spring 31 to bite the winding of the second coil spring 32 between the windings.

Further, the first and second coil springs 31, 32 and the seat members 33A and 33B have accommodation windows provided in several places, for example, four places at equal intervals in the circumferential direction in the outer hub 12 and the side plates 21 and 22, respectively. It is arranged and accommodated inside the 12a and the accommodation windows 22a and 22b. Taking the set as an example, it will be described below.

The accommodation window 12a is formed in the shape of a notch on the outer side in the radial direction, which is arranged on the outer peripheral portion of the outer hub 12. The accommodation windows 22a and 22b are window holes that penetrate the side plates 21 and 22 in the axial direction, respectively, and are punched and formed by, for example, pressing. The accommodating windows 22a and 22b are formed in a half-bag shape, and accommodate the sheet members 33A and 33B in a manner of covering a part thereof. Further, the peripheral end faces of the accommodation windows 22a and 22b are in contact with the seat members 33A and 33B so as to be in contact with each other.

As shown in FIG. 1, each of the seat members 33A and 33B has a concave shape formed in a portion facing the circumferential end surface of the accommodation window 12a, and a convex portion 12a1 (convex portion 12a1) formed on the circumferential end surface of the accommodation window 12a. FIG. 1) is fitted to the outer hub 12 from both sides in the circumferential direction. Therefore, the first and second coil springs 31 and 32 are sandwiched between the side plates 21 and 22 and the outer hub 12 via the seat members 33A and 33B.

When the side plates 21 and 22 rotate, the first and second coil springs 31 and 32 are bent via the seat members 33A and 33B, and the restoring force causes the outer hub 12 to rotate. On the contrary, when the outer hub 12 rotates, the first and second coil springs 31 and 32 are bent, and the restoring force causes the side plates 21 and 22 to rotate.

Here, as shown in FIG. 1, a part of the seat members 33A and 33B is located radially outside the outer peripheral surface 12b of the outer hub 12. As a result, the first and second coil springs 31 and 32 can be arranged in the accommodation window 12a, the accommodation window 22a, and 22b as radially outward as possible, and the diameter can be increased. It can be possible.

FIG. 3 is an enlarged schematic view of a seat member portion of the damper device shown in FIG. The support surfaces 33a are formed in a planar shape so that the seat members 33A and 33B shown in FIG. 3 are supported by abutting on one end surface of both end surfaces of the first coil spring 31, respectively. For example, the support surface 33a may be formed to be larger than the outer diameter De1 of the first coil spring 31, so that the contact area with the first coil spring 31 can be made large, the contact surface pressure can be lowered, and the strength can be easily secured. ..

Further, a convex portion 33b and a concave portion 33c are formed on the support surface 33a. The convex portion 33b is formed so as to project in the circumferential direction from the radial outer portion 33a1 of the support surface 33a. Further, the radial inner portion of the convex portion 33b is in contact with the outer peripheral portion of the first coil spring 31 on the radial outer side to restrict the movement of the first coil spring 31 to the radial outer side. , The second regulation surface 33b2 is formed, and the guide surface 33b4 along the accommodating windows 22a and 22b is formed on the radial outer portion of the convex portion 33b.

As shown in FIG. 2, the first regulating surface 33b1 is formed to be curved in an arc shape along the winding direction of the first coil spring 31 with a radius of curvature larger than the outer diameter De1 of the first coil spring 31. In other words, the first regulating surface 33b1 has a cross-sectional shape obtained by cutting the convex portion 33b on a plane orthogonal to the central axis Ac1 of the first coil spring 31, and the shape of the side that comes into contact with the outer circumference of the first coil spring 31 is the first. 1 The coil spring 31 is formed so as to have an arc shape along the outer diameter De1 and having a radius of curvature larger than the outer diameter De1.

Further, the first regulation surface 33b1 is formed parallel to the central axis Ac1 of the first coil spring 31 from the support surface 33a to a predetermined length H1. The predetermined length H1 is adjusted according to the wire diameter, the number of turns, etc. of the first coil spring 31, and is set to a length at which the first regulation surface 33b1 abuts on the outer periphery of the end portion of the first coil spring 31. .. For example, the length may be set to correspond to 1.5 turns of the first coil spring 31.

The second regulating surface 33b2 is formed on the radial inside of the convex portion 33b formed so as to extend in the circumferential direction beyond the predetermined length H1, and exceeds the predetermined length H1 to the tip of the convex portion 33b. As it approaches, it is formed so as to be separated from the coil center C1 of the first coil spring 31, in other words, the distance D from the coil center C1 is gradually increased. For example, when viewed from the axial direction, it is formed on an arcuate surface having a radius R centered on the rotation axis Ax.

Here, the radius R is determined based on, for example, the amount of movement of the first coil spring 31 to the outside in the radial direction when the damper device 1 rotates and centrifugal force is generated, and the second regulation surface 33b2 is determined. , Set along the outer circumference of the first coil spring 31 at that time. This radius R may be determined by an experiment or the like. As a result, the second regulating surface 33b2 can more stably hold the outer periphery of the portion of the first coil spring 31 that has moved outward in the radial direction, away from the end portion, even when centrifugal force is generated.

The guide surface 33b4 is formed in a substantially arc shape when viewed from the axial direction. For example, in a state where the relative rotation angle between the outer hub 12 and the side plates 21 and 22 is zero (FIG. 1), the shape may be formed along the radial inner shape of the accommodation windows 22a and 22b, and the outer hub 12 and the side plate may be formed. The sliding resistance between the seat members 33A and 33B and the accommodation windows 22a and 22b when the 21 and 22 start relative rotation can be reduced. Alternatively, when the relative rotation angle between the outer hub 12 and the side plates 21 and 22 reaches the maximum angle θ1, the shape may be formed along the radial inner shape of the accommodation windows 22a and 22b, and the seat members 33A and 33B may be formed. It can be stably held by the accommodation windows 22a and 22b.

The recess 33c is formed by being recessed in the circumferential direction on the support surface 33a. The recess 33c is located on the inner peripheral side of the first coil spring 31, is smaller than the inner diameter Di1 of the first coil spring 31, and opens larger than the outer diameter De2 of the second coil spring 32. Therefore, the end portion of the second coil spring 32 is housed in the recess 33c, and the second coil spring 32 is sandwiched between the bottom surfaces 33c1 of the recesses 33c of the seat members 33A and 33B arranged on both end faces thereof.

Further, the recess 33c is formed with an inner peripheral surface 33c2 formed in a circular shape along the winding direction of the second coil spring 32 with a radius of curvature larger than the outer diameter De2 of the second coil spring 32. The inner peripheral surface 33c2 may be coaxial with the first regulation surface 33b1. Here, the diameters of the first regulation surface 33b1 and the inner peripheral surface 33c2 are the outer diameters De1 and De2 of the first and second coil springs 31 and 32, respectively, and the relative rotation between the outer hub 12 and the side plates 21 and 22, respectively. When the angle reaches the maximum angle θ1, the first and second coil springs 31 and 32 bend in the circumferential direction, respectively, so that the new outer diameters De1 and De2 swelling toward the outer peripheral side are equal to or larger than the new outer diameters De1 and De2. It is good to say.

As a result, even when the outer hub 12 and the side plates 21 and 22 rotate relative to each other, the first regulating surface 33b1 and the inner peripheral surface 33c2 have a radius of curvature from the outer periphery of the first and second coil springs 31 and 32, respectively. Due to its large size, the first and second coil springs 31 and 32 can stably hold their respective outer circumferences. Therefore, since the operating trajectories of the first and second coil springs 31 and 32 are stably maintained, the inner circumference of the first coil spring 31 and the outer circumference of the second coil spring 32 are less likely to come into contact with each other, which may occur. Wear can be reduced.

Further, since the second coil spring 32 is not restricted by the inner peripheral surface 33c2 of the recess 33c even when it swells to the outer peripheral side, the outer peripheral surface of the second coil spring 32 and the inner peripheral surface 33c2 are scooped and slid. Wear due to motion can be reduced.

Further, the recess 33c has a predetermined depth H2 from the support surface 33a. The predetermined depth H2 is adjusted according to the wire diameter, the number of turns, etc. of the second coil spring 32, and is set to a length at which the inner peripheral surface 33c2 abuts on the outer periphery of the end portion of the second coil spring 32, for example. , The length corresponding to 1.5 turns of the second coil spring 32 is preferable.

Further, as shown in FIG. 4 (a schematic view illustrating a state in which the seat member of FIG. 3 restricts the movement of the first and second coil springs to the outside in the radial direction), the convex portion 33b and the concave portion 33c are formed. The first coil spring 31 is arranged at a distance larger than the coil wire diameter dc1. The amount of separation thereof is defined as the amount obtained by adding a predetermined amount L to the coil wire diameter dc1 of the first coil spring 31, for example, the predetermined amount L is larger than zero and the inner diameter Di1 of the first coil spring 31 to the second coil. It is preferable to set it smaller than the value obtained by subtracting the outer diameter De2 of the spring 32.

As a result, the outer peripheral surface of the first coil spring 31 on the radial outer side and the first regulating surface 33b1 of the convex portion 33b come into contact with each other, and the outer peripheral surface on the radial outer side of the second coil spring 32 and the inner peripheral surface 33c2 of the concave portion 33c come into contact with each other. At the time of abutting, the inner circumference of the radial inner side of the first coil spring 31 and the outer circumference of the radial inner side of the second coil spring 32 are less likely to come into contact with each other, and possible wear can be reduced.

Further, as shown in FIG. 5 (a schematic view illustrating a state in which the seat member according to another embodiment restricts the movement of the first and second coil springs to the outside in the radial direction), for example, a predetermined amount. It is preferable to set L to be larger than zero and smaller than the value obtained by subtracting the diameter B of the inner peripheral surface 33c2 from the inner diameter Di1 of the first coil spring 31. As a result, the outer outer circumference of the first coil spring 31 and the first regulation surface 33b1 of the convex portion 33b come into contact with each other, and the outer outer circumference of the second coil spring 32 and the inner peripheral surface 33c2 of the recess 33c come into contact with each other. At the time of contact, the inner circumference of the radial inner side of the first coil spring 31 and the outer circumference of the radial inner side of the second coil spring 32 are less likely to come into contact with each other, and the end portion of the first coil spring 31 is recessed 33c. In particular, the first coil spring 31 can be stably supported by the support surface 33a because it is less likely to fall into the concave portion 33c on the inner side in the radial direction.

Further, the amount of movement of the first coil spring 31 in the radial direction when the damper device 1 is rotated and centrifugal force is generated is defined as the amount of movement s (FIG. 4), and the amount of movement s is added to the predetermined amount L. Let the amount be a new predetermined amount L. The amount of movement s is determined experimentally, for example. Then, the amount at which the convex portion 33b and the concave portion 33c are separated from each other may be an amount obtained by adding a new predetermined amount L to the coil wire diameter dc1 of the first coil spring 31. As a result, even when the damper device 1 rotates, it becomes difficult for the inner circumference of the radial inner side of the first coil spring 31 to come into contact with the outer circumference of the radial inner side of the second coil spring 32, and the wear that may occur is reduced. obtain.

In this embodiment, the convex portion 33b (first regulating surface 33b1 and second regulating surface 33b2) that restricts the movement of the first coil spring 31 to the outside in the radial direction is provided, but in addition, as shown in FIG. A third regulation surface 33b3 that restricts the movement of the first coil spring 31 inward in the radial direction may be provided. FIG. 6 is an enlarged schematic view of a seat member portion according to another embodiment of the damper device shown in FIG. For example, a second convex portion 33d protruding in the circumferential direction from the radial inner portion 33a2 of the support surface 33a is provided, a third regulation surface 33b3 is formed on the radial outer side of the second convex portion 33d, and a first coil spring is provided. It is preferable to bring the outer peripheral surface of the radial inner side of 31 into contact with the third regulation surface 33b3.

As a result, when the damper device 1 is stopped rotating or rotating at a low speed, the first coil spring 31 that tends to move inward in the radial direction due to gravity or the like is restricted from moving by the third regulating surface 33b3, so that the trajectory operates. Is maintained stably. Further, the second coil spring 32 is restricted from moving inward in the radial direction by the radial inner surface of the inner peripheral surface 33c2 of the recess 33c, so that the operating track is stably maintained. Therefore, it becomes difficult for the inner circumference of the first coil spring 31 to come into contact with the outer circumference of the second coil spring 32 in the radial direction, and the wear that may occur can be reduced.

By the way, the situation where there is concern about wear / sliding due to contact between the inner and outer circumferences of the first and second coil springs 31 and 32 is a situation where the first and second coil springs 31 and 32 come into contact with each other while expanding and contracting, that is, a damper. When the device 1 is rotating, a torque fluctuation is input, and a relative rotation occurs between the outer hub 12 and the side plates 21 and 22. In that situation, it is assumed that the first and second coil springs 31 and 32 are moving outward in the radial direction due to the generated centrifugal force. Therefore, the convex portion 33b (first regulation surface 33b1, the second regulation surface 33b2) and the recess 33c (inner peripheral surface 33c2) that restrict the movement of the first and second coil springs 31 and 32 to the outside in the radial direction are provided. Is more effective than providing the second convex portion 33d (third regulation surface 33b3).

Further, as shown in FIG. 3, the seat members 33A and 33B may be provided with stopper portions 33e protruding toward the seat members 33A and 33B facing each other in the accommodation window 12a and the accommodation windows 22a and 22b, respectively.

The stopper portion 33e is located on the inner peripheral side of the second coil spring 32, for example, and has a substantially truncated cone shape that is formed so as to project in the circumferential direction from the bottom surface 33c1 of the concave portion 33c and taper toward the end portion. .. The outer peripheral surface of the stopper portion 33e has a gap between the outer peripheral surface and the inner circumference of the second coil spring 32 that has moved inward or outward in the radial direction.

The stopper portion 33e has a flat portion 33e1 at the tip thereof. The flat portions 33e1 of the seat members 33A and 33B are configured to be parallel to each other and abut against each other when the relative rotation angle between the outer hub 12 and the side plates 21 and 22 reaches the maximum angle θ1. The position where the flat portions 33e1 come into contact with each other is the stopper position, and further relative rotation is not allowed.

Further, although not shown in the figure, the stopper portion 33e may be formed by extending the convex portion 33b in the circumferential direction as another example. As a result, the volume of the seat members 33A and 33B is smaller than that of forming a substantially truncated cone shape on the inner peripheral side of the second coil spring 32, and the mass corresponding to the volume and the rotational inertia caused by the volume can be reduced. It may be easy to secure the strength of the portion of the damper device 1 that holds the elastic member assembly 30.

Next, as shown in FIG. 1, the damper device 1 includes a subcoil spring 34 that elastically connects the inner hub 11 and the outer hub 12 in the circumferential direction, and a pair arranged on both end faces of the subcoil spring 34. It has the sub-seat members 35A and 35B of the above.

The subcoil spring 34 is arranged in the space formed by the notches 11c and 12c provided in the inner hub 11 and the outer hub 12, respectively. The notch 11c is provided on the outer peripheral portion of the flange portion 11b of the inner hub 11, and the notch 12c is provided on the inner peripheral portion of the outer hub 12, and they are arranged so as to face each other in the radial direction.

Further, the sub-coil spring 34 is supported on both end surfaces by the sub-seat members 35A and 35B, and the sub-seat members 35A and 35B are sandwiched in the circumferential direction by notches 11c and 12c, respectively, in half in the radial direction. Therefore, when the outer hub 12 rotates relative to the inner hub 11, the subcoil spring 34 bends, and the restoring force causes the inner hub 11 to rotate.

The inner hub 11 is formed with a protrusion 11d protruding outward in the radial direction, and the outer hub 12 is formed with a protrusion 12d protruding radially inward. The outer hub 12 rotates relative to the inner hub 11 and the relative rotation angle is set. When the predetermined angle θ2 is reached, the protrusion 11d and the protrusion 12d come into contact with each other and the relative rotation is restricted.

The combined spring constant K1 of the first and second coil springs 31 and 32 may be set to be several times larger than the spring constant K2 of the sub coil spring 34. When the torque from the engine is input to the side plate 21 by the frictional engagement of the facings 26A and 26B, the synthetic spring constant K1 is sufficiently larger than the spring constant K2, so that the first and second coil springs 31 and 32 immediately repel. The side plates 21 and 22 and the outer hub 12 rotate integrally without shrinking. Due to this integral rotation, the outer hub 12 rotates relative to the inner hub 11, the subcoil spring 34 is elasticized, and the torque is transmitted to the transmission input shaft via the inner hub 11.

Relative rotation progresses between the outer hub 12 and the inner hub 11, and when the relative rotation angle reaches a predetermined angle θ2, the protrusions 11d and 12d come into contact with each other, and the outer hub 12 and the inner hub 11 rotate integrally. .. Further, the first and second coil springs 31 and 32 begin to contract, and the side plates 21 and 22 and the outer hub 12 start relative rotation. When a larger torque is input, the relative rotation angle reaches the maximum angle θ1, the side plates 21, 22 and the outer hub 12 and the inner hub 11 rotate integrally, and the torque is directly transmitted to the transmission input shaft. ..

According to this two-stage relative rotation mechanism, in the damper mechanism 1 of the present embodiment, small torque fluctuations caused by engine combustion or the like are absorbed by a subcoil spring 34 having a small spring constant K2, and the vehicle shifts and accelerators. Large torque fluctuations due to on, off, etc. are absorbed by the first and second coil springs 31 and 32 of the large combined spring constant K1. Therefore, the damper mechanism 1 can effectively absorb the torque fluctuation of the engine.

Next, as shown in FIG. 2, the hysteresis generating member 40 includes an inner hub 11, a first inner thrust member 41 disposed between the outer hub 12 and the side plate 21, and a first outer thrust member 42. The inner hub 11, the second inner thrust member 43, the second outer thrust member 44, and the inner urging the second inner thrust member 43 arranged between the outer hub 12 and the side plate 22 toward the inner hub 11 side. It has a countersunk spring 45 and an outer countersunk spring 46 that urges the second outer thrust member 44 toward the outer hub 12. The first inner thrust member 41, the first outer thrust member 42, the second inner thrust member 43, and the second outer thrust member 44 are, for example, members made of resin.

The first inner thrust member 41 rotates integrally by fitting the side plate 21, the detent protrusions 41a (FIG. 1) and the detent groove 21a (FIG. 1) provided to each other. Further, one end surface of the first inner thrust member 41 contacts the flange portion 11b of the inner hub 11, and the other end surface contacts the side plate 21. The second inner thrust member 43 is arranged so as to face the first inner thrust member 41 with the inner hub 11 interposed therebetween. The inner disc spring 45 is arranged between the second inner thrust member 43 and the side plate 22.

Further, since the side plate 21 and the side plate 22 are connected by a pin 23 at the outer diameter end, the inner hub 11 and the first and second inner thrust members 41 and 43 are connected by the urging force of the inner disc spring 45. A constant pressing force is generated between the and. From the relationship between the friction coefficient determined by the mutual relationship between the flange portion 11b of the inner hub 11 and the contact surfaces of the first and second inner thrust members 41 and 43 and the pressing force, the inner hub 11 and the side plates 21 and 22 The maximum static friction torque TSin and the dynamic friction torque TDin in the rotation direction during relative rotation are determined.

Here, when a small torque fluctuation caused by engine combustion or the like is transmitted to the inner hub 11, if the absolute value of the torque fluctuation is smaller than the maximum static friction torque TSin, the first and second inner thrust members No slip in the rotational direction occurs between the 41 and 43 and the inner hub 11, and the torque fluctuation is directly transmitted to the transmission input shaft. In this case, the torque fluctuation is sufficiently small that almost no vibration or noise is generated inside the vehicle.

When the absolute value of the transmitted torque fluctuation is larger than the maximum static friction torque TSin, slippage occurs and the subcoil spring 34 contracts, so that the torque fluctuation between the side plates 21 and 22 and the inner hub 11 is increased. , The torque fluctuation absorbed by the damper mechanism 1 and transmitted to the transmission input shaft can be suppressed.

Further, the first outer thrust member 42 rotates integrally by fitting the side plate 21, the detent portion 42a (FIG. 1) provided with each other, and the detent hole 21b (FIG. 1). Further, one end surface of the first outer thrust member 42 comes into contact with the outer hub 12, and the other end surface comes into contact with the side plate 21. The second outer thrust member 44 is arranged so as to face the first outer thrust member 42 with the outer hub 12 interposed therebetween. The outer disc spring 46 is arranged between the second outer thrust member 44 and the side plate 22.

Further, since the side plate 21 and the side plate 22 are connected by a pin 23 at the outer diameter end, the outer hub 12 and the first and second outer thrust members 42 and 44 are connected by the urging force of the outer disc spring 46. A constant pressing force is generated between the and. When the outer hub 12 and the side plates 21 and 22 rotate relative to each other, the friction coefficient determined by the mutual relationship between the contact surfaces of the outer hub 12 and the first and second outer thrust members 42 and 44 and the pressing force are related to each other. The maximum static friction torque TSout and the dynamic friction torque TDout in the rotational direction of are determined.

Here, when a large torque fluctuation caused by acceleration by fully opening the accelerator pedal or deceleration by fully closing is transmitted to the inner hub 11, the inner hub 11 and the outer hub 12 rotate relative to each other, and the protrusions 11d and 12d Are in contact with each other, and the inner hub 11 and the outer hub 12 start to rotate integrally. At that time, when the absolute value of the torque fluctuation is smaller than the maximum static friction torque TSout, no slip in the rotational direction occurs between the first and second outer thrust members 42 and 44 and the outer hub 12, and the torque is torqued. The fluctuation is directly transmitted to the transmission input shaft.

When the absolute value of the transmitted torque fluctuation is larger than the maximum static friction torque TSout, slippage occurs and the first and second coil springs 31 and 32 are elasticized, so that the side plates 21 and 22 and the outer hub are used. The torque fluctuation with the 12 is absorbed by the damper mechanism 1, and the torque fluctuation transmitted to the transmission input shaft can be suppressed.

Further, on the contact surfaces of the first and second inner thrust members 41 and 43 with the inner hub 11, the taper 41b formed in the axial direction so as not to come into contact with the inner hub 11 with respect to the outer peripheral portions thereof. It is good to form 43a. As a result, the first and second inner thrust members 41 and 43 come into contact with the inner hub 11 at the outer peripheral portions thereof, and even if there is a wavy swell or protrusion due to manufacturing variation, the influence thereof is reduced. It can be deformed and come into constant contact with the inner hub 11 at each outer peripheral portion.

On the contact surfaces of the first and second outer thrust members 42 and 44 with the outer hub 12, tapers 42b and 44a formed in the axial direction so as not to come into contact with the outer hub 12 with respect to the outer peripheral portions thereof. Good to form. As a result, the first and second outer thrust members 42 and 44 come into contact with the outer hub 12 at their respective outer peripheral portions, and even if there is a wavy swell or protrusion due to manufacturing variation, the influence thereof is reduced. It can be deformed and make constant contact with the outer hub 12 at each outer peripheral portion.

Due to such tapers 41b, 43a, 42b, 44a, the thrust members 41, 42, 43, 44 uniformly contact the inner hub 11 and the outer hub 12 at the time of initial assembly, and a friction torque is generated, so that stable hysteresis is generated. It can exhibit its characteristics. The tapers 41b, 43a, 42b, and 44a may have the same shape or non-same shape, and the taper angles and the like may be appropriately set according to the desired hysteresis characteristics.

As described above, in the present embodiment, for example, a convex portion 33b protruding in the circumferential direction from the radial outer portion 33a1 of the support surface 33a and a first coil spring formed by being recessed in the support surface 33a in the circumferential direction. It is provided with a pair of seat members 33A and 33B located on the inner peripheral side of 31 and having a recess 33c which is smaller than the inner diameter Di1 of the first coil spring 31 and opens larger than the outer diameter De2 of the second coil spring 32.

As a result, for example, since the convex portions 33b of the seat members 33A and 33B are arranged on the outer peripheral side of the first coil spring 31, the inner diameter dimensions of the first and second coil springs 31 and 32 are not limited. Further, since the recess 33c formed by being recessed from the support surface 33a supporting one end surface of the first coil spring 31 supports one end surface of the second coil spring 32, the axial direction of the second coil spring 32 The length is not limited to the shorter one, and it can be set longer with respect to the first coil spring 31. Therefore, the degree of freedom in designing the coil springs (first and second coil springs 31, 32) can be obtained.

Further, in the present embodiment, for example, the convex portion 33b is formed by being curved in an arc shape along the winding direction of the first coil spring 31 with a radius of curvature larger than the outer diameter De1 of the first coil spring 31. The recess 33c includes a regulating surface 33b1 and includes an inner peripheral surface 33c2 formed in a circular shape along the winding direction of the second coil spring 32 with a radius of curvature larger than the outer diameter De2 of the second coil spring 32. As a result, for example, the first regulation surface 33b1 and the inner peripheral surface 33c2 have a radius of curvature larger than the outer diameters of the first and second coil springs 31 and 32, respectively, so that the first and second coil springs 31 and 32 have larger radii of curvature, respectively. The outer circumference of the spring can be stably held. Therefore, since the operating trajectories of the first and second coil springs 31 and 32 are stably maintained, the inner circumference of the first coil spring 31 and the outer circumference of the second coil spring 32 are less likely to come into contact with each other, which may occur. Wear can be reduced.

Further, in the present embodiment, for example, the convex portion 33b includes the first regulating surface 33b1 extending in parallel with the central axis Ac1 of the first coil spring 31, and the concave portion 33c is formed on the central axis Ac2 of the second coil spring 32. It is preferable to include the inner peripheral surface 33c2 extending in parallel. As a result, for example, the first regulation surface 33b1 and the inner peripheral surface 33c2 are located on the outer periphery of the first and second coil springs 31 and 32 in the directions of the central axes Ac1 and Ac2 of the first and second coil springs 31 and 32, respectively. By extending along the line, the first and second coil springs 31 and 32 can stably hold their respective outer circumferences because they are in stable contact with the outer circumference. Therefore, since the operating trajectories of the first and second coil springs 31 and 32 are stably maintained, the inner circumference of the first coil spring 31 and the outer circumference of the second coil spring 32 are less likely to come into contact with each other, which may occur. Wear can be reduced.

Further, in the present embodiment, for example, the convex portion 33b includes a second regulation surface 33b2 formed so as to be separated from the coil center C1 of the first coil spring 31 as it approaches the tip of the convex portion 33b. Therefore, for example, the second regulating surface 33b2 can stably hold the first coil spring 31 that has moved outward in the radial direction. Therefore, the first coil spring 31 can stably maintain the operating trajectory.

Further, in the present embodiment, for example, the convex portion 33b and the concave portion 33c are separated from each other by a larger distance than the coil wire diameter dc1 of the first coil spring 31. As a result, for example, the outer outer peripheral surface of the first coil spring 31 and the first regulating surface 33b1 of the convex portion 33b come into contact with each other, and the outer outer peripheral surface of the second coil spring 32 and the inner peripheral surface 33c2 of the concave portion 33c come into contact with each other. When they come into contact with each other, the inner circumference of the radial inner side of the first coil spring 31 and the outer circumference of the radial inner side of the second coil spring 32 are less likely to come into contact with each other, and possible wear can be reduced.

Moreover, the above-described embodiment is presented as an example, and is not intended to limit the scope of the invention. The above-described embodiment can be implemented in various other embodiments, and various omissions, substitutions, and changes can be made without departing from the gist of the invention. The above-described embodiments and modifications thereof are included in the scope and gist of the invention, and are also included in the scope of the invention described in the claims and the equivalent scope thereof.

1 Damper device 10 Hub member (first rotating member)
20 Disc member (second rotating member)
30 Elastic member assembly 31 1st coil spring 32 2nd coil spring 33A Seat member 33B Seat member 33a Support surface 33a1 Radial outer part 33a2 Radial inner part 33b Convex part 33b1 1st regulation surface 33b2 2nd regulation surface 33c Recess 33c2 Inner peripheral surface 40 Hysteresis generating member Ax Rotating shaft Ac1 Central axis of first coil spring 31 Ac2 Central axis of second coil spring 32 Di1 Inner diameter of first coil spring 31 Di2 Inner diameter of second coil spring 32 De1 First coil spring 31 Outer diameter De2 Outer diameter of the second coil spring 32 dc1 Coil wire diameter of the first coil spring 31 C1 Coil center of the first coil spring 31

Claims (5)

The first rotating member that can rotate around the axis of rotation,
A second rotating member that is arranged to face the first rotating member and can rotate around the rotation axis.
A first coil spring that elastically connects the first and second rotating members in the circumferential direction of the first and second rotating members and attenuates rotational fluctuations between the first and second rotating members.
A second coil spring arranged on the inner peripheral side of the first coil spring, and
The first and second coil springs are arranged on both end faces, respectively, to sandwich the both end faces, and from the radial outer portion of the support surface supporting one end face of the both end faces of the first coil spring to the circumferential direction. The first coil spring is formed by protruding in the circumferential direction and forming a convex portion that restricts the movement of the first coil spring outward in the radial direction in the first and second rotating members, and a concave portion in the support surface in the circumferential direction. A recess located on the inner peripheral side of the coil spring, which is smaller than the inner diameter of the first coil spring and larger than the outer diameter of the second coil spring, and restricts the movement of the second coil spring outward in the radial direction. A damper device comprising a pair of seat members with and. The convex portion includes a first regulating surface formed by being curved in an arc shape along the winding direction of the first coil spring with a radius of curvature larger than the outer diameter of the first coil spring.
The recess includes an inner peripheral surface formed in a circle along the winding direction of the second coil spring with a radius of curvature larger than the outer diameter of the second coil spring.
The damper device according to claim 1. The convex portion includes a first regulatory plane extending parallel to the central axis of the first coil spring.
The recess comprises an inner peripheral surface extending parallel to the central axis of the second coil spring.
The damper device according to claim 1. The convex portion includes a second regulating surface formed so as to move away from the coil center of the first coil spring as it approaches the tip of the convex portion.
The damper device according to any one of claims 1 to 3. The convex portion and the concave portion are separated from each other by a larger distance than the coil wire diameter of the first coil spring.
The damper device according to any one of claims 1 to 4.

Images