Damper Device

Abstract

To suppress a decrease attenuation performance.SOLUTION: A damper device includes an input rotor 30, an output rotor 40, an elastic connection part 50, and a hysteresis torque generation mechanism 60. The hysteresis torque generation mechanism 60 generates hysteresis torque with at least one of the input rotor 30 and the output rotor 40. The damper device 1 is configured so as to be in a neutral state, a first torsional state, and a second torsional state. The hysteresis torque generation mechanism 60 is configured so as not to generate hysteresis torque when the damper device 1 is in a first torsional state. The hysteresis torque generation mechanism 60 is also configured so as not to generate hysteresis torque in a first area having a torsional angle of less than a first angle when the damper device is in the second torsional state.SELECTED DRAWING: Figure 1

Description

[Technical Field]

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

[0002] The damper device is configured to absorb and attenuate torque fluctuations from the engine using coil springs. Specifically, the damper device has an input rotor, an output rotor, and a plurality of coil springs that elastically connect them. In addition, a damper device that generates hysteresis torque using a friction material has also been proposed to further absorb and attenuate torque fluctuations.

[0003] For example, the damper device disclosed in Patent Document 1 includes a first plate, a second plate, an elastic member that elastically connects them, and first and second friction materials. When torque from the engine is transmitted and the damper device twists, the first friction material generates a relatively small hysteresis torque. On the other hand, when the damper device twists in the opposite direction during engine start-up, the second friction material generates a relatively large hysteresis torque. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Patent Application Laid-Open No. 2014-214819 Summary of the Invention [Problem to be solved by the invention]

[0005] In the damper device configured as described above, there is a problem in that the damping performance of a hybrid vehicle decreases when the vehicle is on standby with the engine running.

[0006] An object of the present invention is to suppress the deterioration of damping performance. [Means for solving the problem]

[0007] A damper device according to one aspect of the present invention is disposed between an engine and a drive unit. The damper device includes an input rotor, an output rotor, an elastic coupling, and a hysteresis torque generating mechanism. The input rotor is rotatably disposed. The output rotor is rotatably disposed relative to the input rotor. The elastic coupling elastically couples the input rotor and the output rotor. The hysteresis torque generating mechanism is configured to generate hysteresis torque between at least one of the input rotor and the output rotor. The damper device is configured to be in a neutral state, a first torsional state, and a second torsional state. The neutral state is a state of the damper device when no torque is transmitted from the engine and the drive unit. The first torsional state is a state of the damper device when torque is transmitted from the engine. The second torsional state is a state of the damper device when torque is transmitted from the drive unit. The hysteresis torque generating mechanism is configured not to generate hysteresis torque when the damper device is in the first torsional state. Furthermore, the hysteresis torque generating mechanism is configured so as not to generate hysteresis torque in a first region where the torsion angle is less than the first angle when the damper device is in the second torsion state.

[0008] As described above, the hysteresis torque generating mechanism does not generate hysteresis torque in the first torsional state, nor does it generate hysteresis torque when the torsional angle is in the first region less than the first angle in the second torsional state. This configuration prevents a sudden change in hysteresis torque when switching between the first torsional state and the second torsional state, thereby preventing a decrease in damping performance when the engine is in standby mode. Note that hysteresis torque refers to torque generated by friction material sliding against other components. For example, minute torques such as those generated by a coil spring sliding against other components are not included in the hysteresis torque of the present invention.

[0009] Preferably, the hysteresis torque generation mechanism is configured to generate a first hysteresis torque in a second region where the torsion angle is equal to or greater than the first angle and less than a second angle when the damper device is in the second torsional state.

[0010] Preferably, the hysteresis torque generating mechanism is configured to generate a second hysteresis torque larger than the first hysteresis torque in a third region where the torsion angle is equal to or greater than the second angle and less than a third angle when the damper device is in the second torsional state.

[0011] Preferably, the hysteresis torque generating mechanism is configured to generate a third hysteresis torque larger than the second hysteresis torque in a fourth region where the torsion angle is equal to or greater than the third angle and equal to or less than the maximum angle when the damper device is in the second torsional state.

[0012] Preferably, the hysteresis torque generating mechanism is configured to generate a second hysteresis torque greater than the first hysteresis torque in the third region when the damper device is in the second torsional state, and not to generate a hysteresis torque within a predetermined small torsional angle range. [Effects of the Invention]

[0013] According to the present invention, it is possible to suppress the deterioration of damping performance. [Brief explanation of the drawings]

[0014] [Figure 1] FIG. [Figure 2] FIG. [Figure 3A] FIG. 4 is a schematic diagram showing the relationship between an input rotor and a hub flange. [Figure 3B] Schematic diagram showing the input rotating body twisted at an angle θ1 toward the R1 side relative to the hub flange. [Figure 3C] Schematic diagram showing the input rotating body twisted toward the R1 side by an angle θ3 relative to the hub flange. [Figure 3D]Schematic diagram showing the input rotating body twisted at an angle θ1 toward the R2 side relative to the hub flange. [Figure 4] An enlarged view of the hysteresis torque generation mechanism. [Figure 5] FIG. 10 is an enlarged front view showing the relationship between the restriction protrusion and the elongated hole. [Figure 6] Enlarged partial view of Figure 2. [Figure 7] Graph showing torsional characteristics. [Figure 8] FIG. [Figure 9] An explanatory diagram showing the state when twisted 2° to the R1 side from the neutral state. [Figure 10] An explanatory diagram showing the state when twisted 4° to the R1 side from the neutral state. [Figure 11] An explanatory diagram showing the state when twisted 2° to the R2 side from the neutral state. [Figure 12] An explanatory diagram showing the state when twisted 4° to the R2 side from the neutral state. [Figure 13] An explanatory diagram showing the state when twisted 3° to the R2 side from the neutral state. [Figure 14] An explanatory diagram showing the state when twisted 2° to the R2 side from the neutral state. [Figure 15] An explanatory diagram showing the state when twisted 1° to the R2 side from the neutral state. [Figure 16] FIG. [Figure 17] An explanatory diagram showing the state when twisted 2° to the R2 side from the neutral state. [Figure 18] An explanatory diagram showing the state when twisted 4° to the R2 side from the neutral state. [Figure 19] An explanatory diagram showing the state when twisted 7° to the R2 side from the neutral state. [Figure 20] An explanatory diagram showing the state when twisted 5° to the R2 side from the neutral state. [Figure 21] An explanatory diagram showing the state when twisted 3° to the R2 side from the neutral state. DETAILED DESCRIPTION OF THE INVENTION

[0015] [Overall configuration] Fig. 1 is a cross-sectional view of a damper device 1 with a torque limiter (hereinafter simply referred to as "damper device") according to one embodiment of the present invention. Fig. 2 is a front view of the damper device 1, with some of its constituent members removed. In Fig. 1, an engine (not shown) is disposed on the left side of the damper device 1, and a drive unit (not shown) including an electric motor, a transmission, etc. is disposed on the right side.

[0016] In the following description, the axial direction refers to the direction in which the rotation axis O of the damper device 1 extends. The circumferential direction refers to the circumferential direction of a circle centered on the rotation axis O, and the radial direction refers to the radial direction of the circle centered on the rotation axis O. The circumferential direction does not have to perfectly coincide with the circumferential direction of the circle centered on the rotation axis O. The radial direction does not have to perfectly coincide with the diameter direction of the circle centered on the rotation axis O. The torsion angle refers to the angle at which the input rotor 30 is twisted relative to the hub flange 40.

[0017] As shown in FIG. 1, the damper device 1 is configured to transmit torque between a flywheel (not shown) and an input shaft (not shown) of a drive unit. The damper device 1 is disposed between an engine and the drive unit. The damper device 1 is a device for limiting the torque transmitted between the engine and the drive unit and for damping rotational fluctuations. The damper device 1 includes a torque limiter unit 10 and a damper unit 20. The damper device 1 rotates in a first rotational direction when transmitting torque from the engine to the drive unit.

[0018] [Torque limiter unit 10] The torque limiter unit 10 is disposed radially outward from the damper unit 20. The torque limiter unit 10 limits the torque transmitted between the flywheel and the damper unit 20. The torque limiter unit 10 includes a cover plate 11, a support plate 12, a friction disc 13, a pressure plate 14, and a cone spring 15.

[0019] The cover plate 11 and the support plate 12 are arranged at a predetermined distance in the axial direction. The outer periphery of the cover plate 11 and the outer periphery of the support plate 12 are fixed to the flywheel by a plurality of bolts 16.

[0020] The friction disc 13, the pressure plate 14 and the cone spring 15 are arranged axially between the cover plate 11 and the support plate 12.

[0021] The friction disc 13 has a core plate and a pair of friction members fixed to both sides of the core plate. The inner periphery of the friction disc 13 is fixed to the damper unit 20 by a plurality of rivets 17. The pressure plate 14 and the cone spring 15 are disposed between the friction disc 13 and the support plate 12.

[0022] The pressure plate 14 is formed in an annular shape. The pressure plate 14 is disposed on the support plate 12 side with respect to the friction disc 13. The pressure plate 14 has a plurality of claws 14a on its outer periphery. The claws 14a engage with a plurality of engagement holes 12a formed in the support plate 12.

[0023] The cone spring 15 is disposed between the pressure plate 14 and the support plate 12. The cone spring 15 presses the friction disc 13 against the cover plate 11 via the pressure plate 14.

[0024] [Damper unit 20] The damper unit 20 has an input rotor 30, a hub flange 40 (an example of an output rotor), an elastic connecting portion 50, and a hysteresis torque generating mechanism 60.

[0025] <Input rotor 30> 1 and 2, the input rotor 30 is rotatably arranged. The input rotor 30 has a first plate 31 and a second plate 32. The first plate 31 and the second plate 32 are formed in a circular plate shape with a hole in the center. The first plate 31 and the second plate 32 are arranged with a gap between them in the axial direction.

[0026] Each of the first plate 31 and the second plate 32 has a pair of first support portions 301 and a pair of second support portions 302. The first support portions 301 of the first plate 31 are formed in the same position as the first support portions 301 of the second plate 32. The second support portions 302 of the first plate 31 are formed in the same position as the second support portions 302 of the second plate 32. The second plate 32 has assembly holes 32a at positions corresponding to the rivets 17.

[0027] The first plate 31 has a plurality of stopper portions 31a and a plurality of fixing portions 31b. The stopper portions 31a and the fixing portions 31b are arranged on the outer periphery of the first plate 31.

[0028] The stopper portion 31a extends in the axial direction toward the second plate 32. The stopper portion 31a is formed by bending the outer periphery of the first plate 31 toward the second plate 32 side.

[0029] The fixed portion 31b is formed by bending the tip of the stopper portion 31a radially outward. The fixed portion 31b is fixed to the outer peripheral end of the second plate 32 with a plurality of rivets 33. Therefore, the first plate 31 and the second plate 32 cannot rotate relative to each other and cannot move axially relative to each other.

[0030] The pair of first support portions 301 of the first plate 31 are arranged at an interval of 180 degrees from each other around the rotation axis O. Furthermore, each second support portion 302 of the first plate 31 is arranged at an interval of 90 degrees from each other. The first support portion 301 and the second support portion 302 of the second plate 32 are also arranged in similar positions. Each support portion 301, 302 has a hole penetrating in the axial direction and raised edges on the inner and outer peripheral edges of the hole.

[0031] 3A to 3D, each support portion 301, 302 has an R1 support surface 301a, 302a at its end on the first rotation direction side (hereinafter simply referred to as the "R1 side") and an R2 support surface 301b, 302b at its end on the second rotation direction side (hereinafter simply referred to as the "R2 side"). The width of the hole in each support portion 301, 302 (the distance between the R1 support surface and the R2 support surface) is L.

[0032] 3A to 3D, the first support portion 301 and the second support portion 302 are indicated by solid lines, and the first housing portion 401 and the second housing portion 402 of the hub flange 40, which will be described later, are indicated by dashed lines. Also, FIG. 3 is a schematic view, and differs from the actual specific shape shown in FIG.

[0033] <Hub flange 40> As shown in Figures 1 and 2, the hub flange 40 has a hub 41 and a flange 42. The hub 41 and the flange 42 are integrally formed as a single member. The hub flange 40 is rotatable relative to the input rotor 30 within a predetermined angular range. The hub 41 is formed in a cylindrical shape, and has a spline hole 41a formed in the center. The hub 41 also passes through holes in the centers of the first plate 31 and the second plate 32.

[0034] The flange 42 is disk-shaped and extends radially outward from the outer circumferential surface of the hub 41. The flange 42 is disposed between the first plate 31 and the second plate 32 in the axial direction.

[0035] The flange 42 has a plurality of stopper projections 42 b, a pair of first accommodating portions 401 , a pair of second accommodating portions 402 , and a plurality of notches 403 .

[0036] The stopper protrusions 42b are formed to protrude radially outward from the outer peripheral surface of the flange 42. Each stopper protrusion 42b is formed radially outward from the circumferential center of each accommodation portion 401, 402. When the input rotor 30 and the hub flange 40 rotate relative to each other, the stopper protrusions 42b come into contact with the stopper portion 31a of the first plate 31, thereby prohibiting the input rotor 30 and the hub flange 40 from rotating relative to each other.

[0037] As shown in Fig. 3A, the pair of first accommodating portions 401 are disposed at positions corresponding to the pair of first support portions 301. Furthermore, the pair of second accommodating portions 402 are disposed at positions corresponding to the pair of second support portions 302. More specifically, in a neutral state (torsion angle 0°) where the relative rotation angle between the input rotor 30 and the hub flange 40 is 0° and they are not twisted, as shown in Fig. 3A, the pair of first accommodating portions 401 are disposed so as to partially overlap with the first support portions 301 when viewed in the axial direction and are offset by an angle θ1 (for example, a torsion angle of 2°) toward the R1 side. Furthermore, the second accommodating portion 402 is disposed so as to partially overlap with the second support portions 302 when viewed in the axial direction and is offset by the same angle θ1 toward the R2 side.

[0038] Each of the housing portions 401, 402 is a substantially rectangular hole with an arc-shaped outer periphery when viewed in the axial direction. Each of the housing portions 401, 402 has an R1 housing surface 401a, 402a at the R1 end and an R2 housing surface 401b, 402b at the R2 end. The width of the hole of each of the housing portions 401, 402 (the distance between the R1 housing surface 401a, 402a and the R2 housing surface 401b, 402b) is set to L, which is the same as the width of the hole of each of the support portions 301, 302.

[0039] 2, the notch 403 is disposed between the first accommodating portion 401 and the second accommodating portion 402 that are adjacent to each other in the circumferential direction. The notch 403 is formed to a predetermined depth from the outer peripheral surface of the flange 42 toward the inside in the radial direction. The position where each notch 403 is formed corresponds to the position of the rivet 17 that connects the friction disc 13 of the torque limiter unit 10 to the first plate 31. Therefore, the torque limiter unit 10 and the damper unit 20, which are assembled in separate processes, can be fixed together with the rivet 17 by using the assembly hole 32a of the second plate 32 and the notch 403 of the flange 42.

[0040] <Elastic connecting portion 50> 1 and 2, the elastic connecting portion 50 elastically connects the input rotor 30 and the hub flange 40. The elastic connecting portion 50 has a plurality of coil springs 51 and a plurality of resin members 52. Note that the elastic connecting portion 50 does not necessarily have to have a plurality of resin members 52.

[0041] Each coil spring 51 has an outer spring and an inner spring. The coil springs 51 are housed in the housing portions 401, 402 of the flange 42. The coil springs 51 are supported in the radial and axial directions by the support portions 301, 302 of the input rotor 30. These coil springs 51 operate in parallel.

[0042] The coil springs 51 have the same free length. The free length of the coil springs 51 is the same as the width L of each of the support portions 301, 302 and each of the accommodating portions 401, 402. The coil springs 51 have the same rigidity. The resin members 52 have the same rigidity.

[0043] <Stored state of the coil spring 51> Hereinafter, the arrangement of the support portions 301, 302 and the housing portions 401, 402 in the neutral state, and the housing state of each coil spring 51 will be described in detail. In the following description, the first support portion 301 and the first housing portion 401 may be referred to as the "first window set w1," and the second support portion 302 and the second housing portion 402 may be referred to as the "second window set w2."

[0044] 3A, in the neutral state, each first housing portion 401 is offset by angle θ1 toward the R1 side relative to the corresponding first support portion 301. Meanwhile, each second housing portion 402 is offset by angle θ1 toward the R2 side relative to the corresponding second support portion 302. Coil springs 51 are mounted in a compressed state in openings (holes penetrating in the axial direction) in the axially overlapping portions of each support portion 301, 302 and each corresponding housing portion 401, 402.

[0045] 3A, in the neutral state, in each first window set w1, the R1-side end face of the coil spring 51 abuts against the R1 support surface 301a, and the R2-side end face abuts against the R2 housing surface 401b. That is, in the neutral state, in each first window set w1, the R1-side end face of the coil spring 51 contacts the input rotor 30 but does not contact the hub flange 40. Also, in the neutral state, in each first window set w1, the R2-side end face of the coil spring 51 contacts the hub flange 40 but does not contact the input rotor 30.

[0046] In each second window set w2, the R1-side end face of the coil spring 51 abuts against the R1 housing surface 402a, and the R2-side end face abuts against the R2 support surface 302b. That is, in the neutral state, in each second window set w2, the R1-side end face of the coil spring 51 contacts the hub flange 40 but does not contact the input rotor 30. Also, in the neutral state, in each second window set w2, the R2-side end face of the coil spring 51 contacts the input rotor 30 but does not contact the hub flange 40.

[0047] <Hysteresis torque generation mechanism 60> 1 and 4, the hysteresis torque generating mechanism 60 has a first bushing 61, a second bushing 62, a cone spring 63, and a friction plate 64. The hysteresis torque generating mechanism 60 generates hysteresis torque between the input rotor 30 and the hysteresis torque generating mechanism 60.

[0048] The hysteresis torque generating mechanism 60 generates hysteresis torque by rotating relative to the input rotor 30. Specifically, as will be described below, the hysteresis torque generating mechanism 60 generates hysteresis torque by rotating the first bushing 61 and the friction plate 64 relative to the input rotor 30. Note that FIG. 4 is an enlarged partial view of FIG. 1.

[0049] The first bushing 61 is disposed between the first plate 31 and the flange 42 in the axial direction. The second bushing 62, the cone spring 63, and the friction plate 64 are disposed between the second plate 32 and the flange 42 in the axial direction. Note that the friction plate 64 is disposed between the flange 42 and the second bushing 62, and the cone spring 63 is disposed between the second plate 32 and the second bushing 62 in the axial direction.

[0050] The first bushing 61 is rotatable relative to the first plate 31. The first bushing 61 is also rotatable relative to the flange 42. A friction member 611 is fixed to the surface of the first bushing 61 facing the first plate 31. Therefore, when the first bushing 61 rotates relative to the first plate 31, hysteresis torque is generated.

[0051] The first bushing 61 and the friction plate 64 rotate integrally with each other. More specifically, as shown in Fig. 4, the first bushing 61 has a plurality of restricting protrusions 61a and a plurality of engaging protrusions 61b. The engaging protrusions 61b engage with engaging holes 64a formed in the friction plate 64. Therefore, the first bushing 61 and the friction plate 64 cannot rotate relative to each other and rotate integrally.

[0052] The restricting protrusion 61a is formed to protrude in the axial direction on the side surface of the first bushing 61 on the flange 42 side. As shown in a further enlarged view in FIG. 5 (a partial front view), the restricting protrusion 61a passes through a circumferentially long hole 42c formed in the flange 42.

[0053] In the neutral state, a gap is formed between the restricting protrusion 61a and the circumferential end face of the elongated hole 42c on both the R1 side and the R2 side. The gap on the R2 side corresponds to the torsional angle θ1. In other words, the gap on the R2 side is the same as the offset amount between each of the accommodating portions 401, 402 and each of the support portions 301, 302. The gap on the R1 side corresponds to the torsional angle θ2. The torsional angle θ2 is sufficiently larger than the torsional angle θ1. Therefore, when the damper device 1 is in use, the restricting protrusion 61a will not abut against the end face of the elongated hole 42c even if it is twisted toward the R1 side. The position of the first bushing 61 and the friction plate 64 in the neutral state is referred to as the "neutral position."

[0054] As shown in Fig. 4, the second bush 62 is rotatable relative to the friction plate 64. A friction member 621 is fixed to the surface of the second bush 62 facing the friction plate 64. Therefore, when the second bush 62 rotates relative to the friction plate 64, hysteresis torque is generated. The cone spring 63 is disposed in a compressed state between the second bush 62 and the second plate 32 in the axial direction. That is, the cone spring 63 biases the second bush 62 toward the friction plate 64.

[0055] The second bushing 62 rotates integrally with the second plate 32. More specifically, a plurality of engagement protrusions 62a (see FIG. 2) protruding in the axial direction are formed on the surface of the second bushing 62 facing the second plate 32. The engagement protrusions 62a engage with the engagement holes 32b of the second plate 32. Therefore, the second bushing 62 and the second plate 32 rotate integrally.

[0056] With the above configuration, the first bushing 61 and the friction plate 64 are rotatable relative to the hub flange 40 by an angle θ2 toward the R1 side and by an angle θ1 toward the R2 side. Therefore, within the above torsion angle range, there is basically no frictional contact between the first bushing 61 and the first plate 31, and no hysteresis torque is generated between them. Similarly, within the above torsion angle range, the friction plate 64 rotates in synchronization with the first plate 31, so there is no frictional contact between the second bushing 62 and the friction plate 64, and no hysteresis torque is generated between them.

[0057] On the other hand, in a range exceeding the above torsion angle, the first bushing 61 and the friction plate 64 are prohibited from rotating relative to the flange 42. Therefore, frictional contact occurs between the first bushing 61 and the first plate 31, and between the second bushing 62 and the friction plate 64, and hysteresis torque is generated between them.

[0058] Here, as shown in Fig. 2 and Fig. 6, which is an enlarged partial view of Fig. 2, the friction plate 64 has a rectangular shape when viewed from the front. The friction plate 64 also has a pair of protrusions 641. The protrusions 641 protrude radially outward from the outer circumferential surface of the friction plate 64. The protrusions 641 are disposed on opposite sides of the rotation axis O.

[0059] The protrusions 641 are located between the first window set w1 and the second window set w2 in the circumferential direction. The R1-side contact surface 641a of each protrusion 641 abuts against the R2-side end surface of the coil spring 51 arranged compressed in the second window set w2. The R2-side contact surface 641b of each protrusion 641 abuts against the R1-side end surface of the coil spring 51 arranged compressed in the first window set w1.

[0060] As described above, the protrusions 641 of the friction plate 64 are pressed in opposite directions by the pair of compressed coil springs 51. Therefore, the friction plate 64 and the first bushing 61, which rotates in synchronization with the friction plate 64, are always positioned in the neutral position in the neutral state.

[0061] [Torsion characteristics: No hysteresis torque] To facilitate the explanation of operation, we will first explain the torsional characteristics of the four coil springs 51 when there is no hysteresis torque. In Figure 7, the dashed line represents the torsional characteristics of the coil springs 51 of the first window set w1, the two-dot chain line represents the torsional characteristics of the coil springs 51 of the second window set w2, and the solid line represents the torsional characteristics w0 that are a combination of these torsional characteristics.

[0062] The damper device 1 is configured to be in a neutral state, a first torsional state, and a second torsional state. FIG. 3A is a schematic diagram of the damper device 1 in the neutral state, FIGS. 3B and 3C are views of the damper device 1 in the first torsional state, and FIG. 3D is views of the damper device 1 in the second torsional state. The neutral state refers to the state of the damper device 1 when no torque is transmitted to the damper device 1 from either the engine or the drive unit. The first torsional state refers to the state of the damper device 1 when torque is transmitted from the engine to the damper device 1, causing the input rotor 30 to twist toward the R1 side relative to the hub flange 40. The second torsional state refers to the state of the damper device 1 when torque is transmitted from the drive unit to the damper device 1, causing the input rotor 30 to twist toward the R2 side relative to the hub flange 40.

[0063] <First window set w1> As shown in Fig. 3A, in a neutral state where the input rotor 30 and the hub flange 40 are not rotating relative to each other, the coil spring 51 of the first window set w1 is compressed and disposed between the R1 support surface 301a and the R2 housing surface 401b. A gap G0 between the R1 support surface 301a and the R2 housing surface 401b is narrower than the width L (equal to the free length of the coil spring) of each support portion 301, 302 and each housing portion 401, 402. Therefore, as shown by the chain line in Fig. 7, a torsional torque -t is generated by the compressed coil spring 51 in the first window set w1.

[0064] 3B, when torque is input from the engine to the damper device 1, the damper device 1 enters a first torsional state. That is, the hub flange 40 twists from the neutral state toward the R2 side (the positive side in the torsional characteristics) by an angle θ1 relative to the input rotor 30. In this state, the offset amount between the first support portion 301 and the first accommodating portion 401 becomes "0."

[0065] Here, in the first window set w1, the distance G1 between the R1 support surface 301a, against which the R1-side end face of the coil spring 51 abuts, and the R2 housing surface 401b, against which the R2-side end face of the coil spring 51 abuts, is wider than the distance G0. This distance G1 is the same as the free length of the coil spring. In other words, when the torsion angle between the input rotor 30 and the hub flange 40 is +θ1, in the first window set w1, the coil spring 51 has its free length, and as shown in FIG. 7, the torsional torque is "0."

[0066] Furthermore, when the hub flange 40 twists relative to the input rotor 30 beyond angle θ1, as shown in FIG. 3C (FIG. 3C shows the case where the torsion angle is θ3 (>θ1)), the R1-side end face of the coil spring 51 of the first window set w1 abuts against the R1 housing surface 401a, and the R2-side end face abuts against the R2 support surface 301b. Here, the gap G2 between the R1 housing surface 401a and the R2 support surface 301b is narrower than the free length of the coil spring 51. In other words, when the torsion angle between the input rotor 30 and the hub flange 40 exceeds θ1, the coil spring 51 is compressed from its free length, and the torsional torque gradually increases, as shown in FIG.

[0067] On the other hand, as shown in Fig. 3D, when the damper device 1 is in the second torsional state, that is, when the hub flange 40 is twisted from the neutral state toward the R1 side (negative side in terms of torsional characteristics) relative to the input rotor 30, the coil spring 51 of the first window set w1 is constantly compressed between the R1 support surface 301a and the R2 receiving surface 401b. That is, in the first window set w1, as shown in Fig. 7, in the negative torsional region, the torsional torque increases toward the negative side as the torsion angle increases.

[0068] <Second window set w2> As shown in Fig. 3A, in the neutral state, the coil spring 51 of the second window set w2 is compressed and disposed between the R1 housing surface 402a and the R2 support surface 302b. The gap G0 between the R1 housing surface 402a and the R2 support surface 302b is narrower than the width L (equal to the free length of the coil spring) of each support portion 301, 302 and each housing portion 401, 402. Therefore, as shown by the two-dot chain line in Fig. 7, in the neutral state, a torsional torque +t is generated by the compressed coil spring 51 in the second window set w2.

[0069] 3B and 3C, when the damper device 1 is in the first torsion state, the coil spring 51 of the second window set w2 is constantly compressed between the R1 receiving surface 402a and the R2 support surface 302b. That is, in the second window set w2, as shown in FIG. 7, in the positive torsion region, the torsional torque increases in the positive direction as the torsion angle increases.

[0070] On the other hand, as shown in FIG. 3D, when the damper device 1 enters the second torsional state, that is, when the hub flange 40 is twisted by an angle θ1 from the neutral state toward the R1 side (negative side) with respect to the input rotor 30, Second support portion 302 and second accommodation portion 402 The offset amount will be "0".

[0071] Here, in the second window set w2, a gap G3 between the R1 housing surface 402a, with which the R1-side end face of the coil spring 51 abuts, and the R2 support surface 302b, with which the R2-side end face of the coil spring 51 abuts, is wider than the gap G0. This gap G3 is the same as the free length of the coil spring 51. In other words, when the torsion angle between the input rotating body 30 and the hub flange 40 is −θ1, in the second window set w2, the coil spring 51 has its free length, and as shown in FIG. 7, the torsional torque is “0.”

[0072] Furthermore, when the hub flange 40 is twisted toward the R1 side relative to the input rotor 30 beyond the angle θ1, the R1-side end face of the coil spring 51 of the second window set w2 abuts against the R1 support surface 302a, and the R2-side end face abuts against the R2 housing surface 402b. As the torsion angle increases further, the coil spring 51 is compressed from its free length, and as shown in FIG. 7, the torsional torque gradually increases toward the negative side.

[0073] <Composite torsional characteristics> For the damper unit as a whole, the characteristic w1 indicated by the dashed line and the characteristic w2 indicated by the two-dot chain line in Fig. 7 are combined to form the torsional characteristic w0 indicated by the solid line. That is, in the neutral state, the torsional torque is "0", and as the torsional angle increases to the positive and negative sides, the torsional torque also increases to the positive and negative sides.

[0074] [Operation: With hysteresis torque] Next, the torsional characteristics taking hysteresis torque into consideration will be explained using the schematic diagrams from FIG. 8 onwards. In the schematic diagrams, the first bushing 61 and the friction plate 64 will be explained as the "friction member FP". In the following explanation, the angle θ1 will be explained as "2°", but this angle is just an example. In the following explanation, the torsional angle means the torsional angle of the input rotor 30 relative to the hub flange 40. The torsional angle will be expressed as an absolute value.

[0075] <Neutral state> 8 shows the neutral state. In this neutral state, the coil springs 51 of each window set w1, w2 are compressed. As described above, the abutment surfaces 641a, 641b, which are the end faces of the protrusions 641 of the friction plate 64, abut against the end faces of the corresponding coil springs 51. Therefore, the friction plate 64 is positioned in the neutral position. Therefore, a gap of θ2 (e.g., 20°) is secured on the R1 side and a gap of θ1 (e.g., 2°) is secured on the R2 side between the restricting projections 61a of the first bushing 61 and the end faces of the elongated holes 42c of the flange 42.

[0076] First, the torsional characteristics when the damper device 1 is in the first torsional state (hereinafter also referred to as "positive torsional characteristics") will be described.

[0077] <Neutral state → Twist angle 2°> FIG. 9 shows a state in which the input rotor 30 is twisted 2° toward the R1 side relative to the hub flange 40 from the neutral state.

[0078] 8 to 9, i.e., while the friction member FP is twisted by a torsion angle of 2° from the neutral state, the coil spring 51 of the first window set w1 expands from its compressed state to its free length, while the coil spring 51 of the second window set w2 is further compressed from its compressed state. Furthermore, because the friction member FP and the input rotor 30 rotate synchronously toward the R1 side, no hysteresis torque is generated between the friction member FP and the input rotor 30. Specifically, no hysteresis torque is generated between the first bushing 61 of the friction member FP and the first plate 31. Similarly, no hysteresis torque is generated between the second bushing 62 and the friction plate 64.

[0079] <Twist angle 2°→4°> FIG. 10 shows a state in which the input rotor 30 is twisted 4° to the R1 side relative to the hub flange 40.

[0080] 9 to 10, i.e., while the torsion angle is changing from 2° to 4°, the coil spring 51 of the first window set w1 is compressed from its free length to a compressed state, and the coil spring 51 of the second window set w2 is further compressed from its compressed state. Furthermore, because the friction member FP and the input rotor 30 rotate synchronously toward the R1 side, no hysteresis torque is generated between the friction member FP and the input rotor 30.

[0081] <Torsion angle 4° → Neutral state> When returning from a torsion angle of 4° to the neutral state, the state changes in the reverse order to the above, i.e., from the state in Figure 10 to the state in Figure 9, and finally back to the neutral state in Figure 8.

[0082] As described above, the hysteresis torque generating mechanism 60 is configured not to generate hysteresis torque while the damper device 1 is in the first torsion state.

[0083] Next, the torsional characteristics when the damper device 1 is in the second torsional state (hereinafter also referred to as "negative torsional characteristics") will be described.

[0084] <Neutral state → Twist angle 2°> 11 shows a state in which, as the torsion angle increases, the input rotor 30 is twisted 2° toward the R2 side relative to the hub flange 40. In this state, the restricting projection 61a of the first bushing 61 abuts against the end face of the elongated hole 42c of the flange 42 on the R2 side.

[0085] 8 to 11, i.e., while the rotor is twisted 2° toward the R2 side from the neutral state, the coil spring 51 of the second window set w2 expands from its compressed state to its free length, while the coil spring 51 of the first window set w1 is further compressed from its compressed state. Furthermore, the friction member FP rotates toward the R2 side in synchronization with the input rotor 30. Therefore, no hysteresis torque is generated between the friction member FP and the input rotor 30. Specifically, no hysteresis torque is generated between the first bushing 61 of the friction member FP and the first plate 31, and no hysteresis torque is generated between the second bushing 62 of the friction member FP and the friction plate 64.

[0086] <Twist angle 2°→4°> FIG. 12 shows a state in which the input rotor 30 is twisted 4° toward the R2 side relative to the hub flange 40 as the twist angle increases.

[0087] As the state changes from Figure 11 to Figure 12, i.e., as the torsion angle changes from 2° to 4°, the coil spring 51 of the first window set w1 becomes further compressed, and the coil spring 51 of the second window set w2 is compressed from its free length to a compressed state.

[0088] Furthermore, the input rotor 30 rotates toward the R2 side. Meanwhile, the friction member FP is prohibited from rotating toward the R2 side because the restricting projection 61a abuts against the end surface of the elongated hole 42c of the flange 42. As a result, the friction member FP rotates relative to the input rotor 30, and hysteresis torque is generated between them. More specifically, the first bushing 61 rotates relative to the first plate 31, and hysteresis torque is generated between them. Furthermore, the second bushing 62 rotates relative to the friction plate 64, and hysteresis torque is generated.

[0089] <Twist angle 4°→3°> FIG. 13 shows the input rotor 30 twisted 3° toward the R2 side relative to the hub flange 40 during the process of returning to the neutral state. While the state changes from FIG. 12 to FIG. 13 , i.e., while the torsion angle returns from 4° to 3°, the input rotor 30 rotates toward the R1 side, while the friction member FP does not rotate. Specifically, the abutment surface 641a of the friction member FP abuts against the end face of the coil spring 51 of the second window set w2, while the abutment surface 641b does not abut against the end face of the coil spring 51 of the first window set w1. In other words, the friction member FP is biased only toward the R2 side by the coil spring 51 of the second window set w2. Therefore, the friction member FP does not rotate toward the R1 side. Therefore, the input rotor 30 rotates relative to the friction member FP, generating hysteresis torque from a torsion angle of 4° to 3°.

[0090] <Twist angle 3°→2°> Figure 14 shows a state in which the input rotor 30 is twisted 2° toward R2 relative to the hub flange 40 during the process of returning to the neutral state. While the state changes from Figure 13 to Figure 14, that is, while the torsion angle returns from 3° to 2°, the input rotor 30 and the friction member FP rotate synchronously. In other words, the input rotor 30 and the friction member FP do not rotate relative to each other.

[0091] More specifically, in the process of returning to the neutral state, the torsion angle becomes 3° (as an example), and the torque due to the coil springs 51 of the second window set w2 decreases, so that the torque due to the coil springs 51 of the second window set w2 and the hysteresis torque generated between the input rotor 30 and the friction member FP are balanced. As a result, the coil springs 51 of the second window set w2 do not extend any further due to the hysteresis torque. In other words, the coil springs 51 of the second window set w2 do not operate until the torsion angle changes from 3° to 2°. Therefore, the torsional rigidity of the entire damper device 1 becomes the rigidity of the coil springs 51 of the first window set w1 alone (specifically, half the composite rigidity).

[0092] Furthermore, while the torsion angle returns from 3° to 2°, the friction member FP and the input rotor 30 rotate in synchronization with each other toward the R1 side, and no hysteresis torque is generated between them.

[0093] <Twist angle 2° to 1°> 15 shows a state in which the input rotor 30 is twisted 1° toward the R2 side relative to the hub flange 40 during the process of returning to the neutral state. While the state changes from FIG. 14 to FIG. 15, that is, while the torsion angle returns from 2° to 1°, the input rotor 30 rotates relative to the friction member FP.

[0094] More specifically, when the torsion angle reaches 2°, the end face on the R1 side of the coil spring 51 of the second window set w2 abuts against the end face of the hub flange 40. Therefore, when the torsion angle is between 2° and 1°, the friction member FP is subjected to repulsion from the coil spring 51 of the second window set w2 and is unable to rotate together with the input rotor 30. As a result, the input rotor 30 rotates relative to the friction member FP, and a hysteresis torque corresponding to the force (torque) with which the coil spring 51 of the second window set w2 is compressed is generated.

[0095] Furthermore, the coil spring 51 of the second window set w2 does not operate until the torsion angle changes from 2° to 1°. Therefore, the torsional rigidity of the entire damper device 1 is the rigidity of the coil spring 51 of the first window set w1 alone (specifically, half the rigidity of the composite characteristic).

[0096] <Torsion angle 1° to neutral state> 15, when the torsion angle reaches 1°, the end face on the R2 side of the coil spring 51 of the second window set w2 abuts against the end face of the input rotor 30. Therefore, while the state changes from FIG. 15 to FIG. 8, that is, while returning from a torsion angle of 1° to the neutral state, the input rotor 30 rotates in synchronization with the friction member FP, and no hysteresis torque is generated.

[0097] Furthermore, while the torsion angle returns from 1° to the neutral state, the coil springs 51 of the first window set w1 and the second window set w2 operate, and the stiffness becomes the combined stiffness of the coil springs 51 of both window sets w1 and w2. At this point, the friction member FP is positioned in the neutral position.

[0098] As described above, the hysteresis torque generating mechanism 60 is configured not to generate hysteresis torque in the first region (0° to 1°) where the torsion angle is less than the first angle when the damper device 1 is in the second torsion state. Specifically, the hysteresis torque generating mechanism 60 does not generate hysteresis torque in both the process in which the torsion angle changes from 0° to 1° and the process in which the torsion angle changes from 1° back to 0°.

[0099] Furthermore, the hysteresis torque generating mechanism 60 generates a first hysteresis torque in a second region (1° to 2°) where the torsion angle is equal to or greater than the first angle and less than the second angle. Specifically, the hysteresis torque generating mechanism 60 does not generate hysteresis torque when the torsion angle changes from 1° to 2°, but generates hysteresis torque when the torsion angle changes from 2° back to 1°.

[0100] Furthermore, the hysteresis torque generating mechanism 60 generates a second hysteresis torque in a third region (2° to 3°) that is equal to or greater than the second angle and less than the third angle. Specifically, the hysteresis torque generating mechanism 60 generates hysteresis torque when the torsion angle changes from 2° to 3°, but does not generate hysteresis torque when the torsion angle changes from 3° back to 2°. The second hysteresis torque is greater than the first hysteresis torque.

[0101] Furthermore, the hysteresis torque generating mechanism 60 generates a third hysteresis torque in a fourth region where the torsion angle is equal to or greater than the third angle and equal to or less than the maximum angle (3° to MAX). Specifically, the hysteresis torque generating mechanism 60 generates hysteresis torque both in the process where the torsion angle moves from 3° toward MAX and in the process where the torsion angle returns from MAX to 3°. The third hysteresis torque is greater than the second hysteresis torque.

[0102] [Other embodiments] The present invention is not limited to the above-described embodiments, and various modifications and alterations are possible without departing from the scope of the present invention.

[0103] (a) In the above embodiment, the torsion angle θ1 of the gap between the restricting protrusion 61a and the end face on the R2 side of the elongated hole 42c in the circumferential direction was the same as the offset amount θ1 between the first support portion 301 on the R2 side and the first accommodating portion 401, but the configuration of the damper device 1 is not limited to this. For example, the torsion angle of the gap between the restricting protrusion 61a and the end face on the R2 side of the elongated hole 42c in the circumferential direction can be made larger than the offset amount θ1.

[0104] For example, the twist angle of the gap between the restricting protrusion 61a on the R2 side and the circumferential end face of the elongated hole 42c can be set to 2·θ1.

[0105] The torsional characteristics in this case will be described below using a schematic diagram. Note that the torsional characteristics when the damper device 1 is in the first torsional state are the same as those in the above embodiment, so the torsional characteristics when the damper device 1 is in the second torsional state will be described.

[0106] 16 shows the neutral state. In this neutral state, the arrangement is the same as the above embodiment except for the gap between the restricting protrusion 61a on the R2 side and the end face of the elongated hole 42c. The gap 2·θ1 between the restricting protrusion 61a on the R2 side and the end face of the elongated hole 42c is set to, for example, 4°.

[0107] <Neutral state → Twist angle 2°> FIG. 17 shows a state in which the input rotor 30 is twisted by 2° to the R2 side relative to the hub flange 40 as the twist angle increases.

[0108] 16 to 17, i.e., while twisting 2° from the neutral state to the R2 side, the coil spring 51 of the first window set w1 is further compressed from its compressed state, and the coil spring 51 of the second window set w2 is expanded from its compressed state to its free length.

[0109] Furthermore, the friction member FP rotates in synchronization with the input rotor 30. Therefore, no hysteresis torque is generated between the friction member FP and the input rotor 30. In particular, no hysteresis torque is generated between the first bushing 61 of the friction member FP and the first plate 31, and no hysteresis torque is generated between the second bushing 62 of the friction member FP and the friction plate 64.

[0110] <Twist angle 2°→4°> FIG. 18 shows a state in which the input rotor 30 is twisted by 4° to the R2 side relative to the hub flange 40 as the twist angle increases.

[0111] 17 to 18, i.e., while the torsion angle changes from 2° to 4°, the coil spring 51 of the first window set w1 is further compressed from its compressed state, and the coil spring 51 of the second window set w2 is compressed from its free length to its compressed state.

[0112] The friction member FP continues to rotate in synchronization with the input rotor 30, and therefore no hysteresis torque is generated between the friction member FP and the input rotor 30.

[0113] The contact surface 641a of the friction member FP moves away from the end face of the coil spring 51 of the second window set w2, and when the torsion angle is 4°, the gap between the contact surface 641a and the end face of the coil spring 51 of the second window set w2 becomes 2°. <Twist angle 4°→7°> FIG. 19 shows a state in which the input rotor 30 is twisted by 7° to the R2 side relative to the hub flange 40 as the twist angle increases.

[0114] While the state changes from FIG. 18 to FIG. 19, that is, while the torsion angle changes from 4° to 7°, the coil springs 51 of the first and second window sets w1, w2 continue to be compressed.

[0115] Furthermore, the input rotor 30 rotates toward the R2 side. Meanwhile, the friction member FP is prohibited from rotating toward the R2 side because the restricting projection 61a abuts against the end surface of the elongated hole 42c of the flange 42. As a result, the friction member FP rotates relative to the input rotor 30, and hysteresis torque is generated between them. More specifically, the first bushing 61 rotates relative to the first plate 31, and hysteresis torque is generated between them. Furthermore, the second bushing 62 rotates relative to the friction plate 64, and hysteresis torque is generated.

[0116] Furthermore, when the torsion angle is 4° or more, the gap between the contact surface 641a and the end face of the coil spring 51 of the second window set w2 is always maintained at 2°. This gap of 2° is the angle obtained by subtracting the torsion angle corresponding to the offset amount (2°) from the gap (4°) between the restricting protrusion 61a and the R2 side of the hole 42c. Therefore, in the high torsion angle range where the torsion angle is 4° or more, the friction member FP is Input rotor 30 That is, no hysteresis torque is generated within an angle range where the relative torsion angle is 2° (an example of a small torsion angle range).

[0117] Therefore, in a high torsion angle region where the torsion angle is 4° or more (absolute angle), a relatively large hysteresis torque can be obtained, and at a torsion angle where the absolute torsion angle is 4° or more, Input rotor 30 No hysteresis torque occurs within the small torsion angle range of 2°, where the relative torsion angle between the hub flange 40 and the hub flange 40 is 2°. Therefore, in the running region where the torsion characteristics are in the high torsion angle region, small torque fluctuations can be effectively damped.

[0118] <Twist angle 7°→5°> Figure 20 shows the state in which the input rotor 30 is twisted 5° toward R2 relative to the hub flange 40 during the process of returning to the neutral state. While the state changes from Figure 19 to Figure 20, that is, while the torsion angle returns from 7° to 5°, the input rotor 30 rotates toward R1 in synchronization with the friction member FP. Therefore, no hysteresis torque is generated from the torsion angle of 7° to 5°.

[0119] <Torsion angle 5°→3°> FIG. 21 shows the input rotor 30 twisted 3° toward the R2 side relative to the hub flange 40 during the process of returning to the neutral state. While the state changes from FIG. 20 to FIG. 21 , i.e., while the torsion angle returns from 5° to 3°, the input rotor 30 rotates toward the R1 side, while the friction member FP does not rotate. Specifically, the abutment surface 641a of the friction member FP abuts against the end face of the coil spring 51 of the second window set w2, while the abutment surface 641b does not abut against the end face of the coil spring 51 of the first window set w1. In other words, the friction member FP is biased only toward the R2 side by the coil spring 51 of the second window set w2. Therefore, the friction member FP does not rotate toward the R1 side. Therefore, the input rotor 30 rotates relative to the friction member FP, generating hysteresis torque from the torsion angle of 5° to 3°.

[0120] <Torsion angle 3° → Neutral state> The torsional characteristics from a torsion angle of 3° to returning to the neutral state are the same as those in the above embodiment, and therefore a detailed description thereof will be omitted.

[0121] As described above, the hysteresis torque generating mechanism 60 is configured not to generate hysteresis torque in the first region (0° to 1°) where the torsion angle is equal to or greater than 0° and less than the first angle when the damper device 1 is in the second torsion state. Specifically, the hysteresis torque generating mechanism 60 does not generate hysteresis torque in both the process in which the torsion angle changes from 0° to 1° and the process in which the torsion angle changes from 1° back to 0°.

[0122] Furthermore, the hysteresis torque generating mechanism 60 generates a first hysteresis torque in a second region (1° to 4°) where the torsion angle is equal to or greater than the first angle and less than the second angle. Specifically, the hysteresis torque generating mechanism 60 does not generate hysteresis torque when the torsion angle changes from 1° to 4°, but generates hysteresis torque when the torsion angle changes from 4° back to 3° and from 2° back to 1°.

[0123] Furthermore, the hysteresis torque generating mechanism 60 generates a second hysteresis torque in a third region (4° to 5°) that is equal to or greater than the second angle and less than the third angle. Specifically, the hysteresis torque generating mechanism 60 generates hysteresis torque both in the process in which the torsion angle changes from 4° to 5° and in the process in which the torsion angle changes from 5° back to 4°. The second hysteresis torque is greater than the first hysteresis torque.

[0124] Furthermore, the hysteresis torque generating mechanism 60 generates a third hysteresis torque in a fourth region where the torsion angle is equal to or greater than the third angle and equal to or less than the maximum angle (5° to 7°). Specifically, the hysteresis torque generating mechanism 60 generates hysteresis torque when the torsion angle changes from 5° to 7°, but does not generate hysteresis torque when the torsion angle changes from 7° to 5°. The third hysteresis torque is smaller than the second hysteresis torque.

[0125] (b) The specific values ​​of the width of each of the support portions 301, 302 and each of the accommodating portions 401, 402, the length of the coil spring 51, and the torsion angle are merely examples and are not limited to these values.

[0126] (c) In the above embodiment, all the coil springs have the same stiffness, but coil springs of different stiffness may also be used.

[0127] (d) The numbers of the housing portions, support portions, and coil springs are merely examples and are not limited to those in the above-described embodiment.

[0128] (e) In the above embodiment, the hysteresis torque generating mechanism 60 includes the first bush 61, the second bush 62, the cone spring 63, and the friction plate 64. However, the configuration of the hysteresis torque generating mechanism 60 is not limited to this. For example, the hysteresis torque generating mechanism 60 does not have to include the second bush 62 and the cone spring 63.

[0129] Furthermore, the hysteresis torque generating mechanism 60 does not necessarily have to have the friction plate 64. In this case, it is sufficient that the first bush 61 has the pair of protrusions 641 of the friction plate 64. [Explanation of symbols]

[0130] 1 Damper device 30 Input rotor 40 Hub flange 50 Elastic connection part 60 Hysteresis Torque Generation Mechanism

Claims

1. A damper device disposed between an engine and a drive unit, an input rotor that is rotatably disposed; an output rotor arranged to be rotatable relative to the input rotor; an elastic coupling portion that elastically couples the input rotor and the output rotor; a hysteresis torque generating mechanism configured to generate a hysteresis torque between at least one of the input rotor and the output rotor; Equipped with the damper device is configured to be in a neutral state when no torque is transmitted from the engine and the drive unit, to be in a first torsional state when torque is transmitted from the engine, and to be in a second torsional state when torque is transmitted from the drive unit; the hysteresis torque generating mechanism is configured not to generate hysteresis torque when the damper device is in the first torsional state, and is configured not to generate hysteresis torque in a first region where the torsional angle is less than a first angle when the damper device is in the second torsional state. Damper device.

2. the hysteresis torque generating mechanism is configured to generate a first hysteresis torque in a second region where the torsion angle is equal to or greater than the first angle and less than the second angle when the damper device is in the second torsional state. The damper device according to claim 1 .

3. the hysteresis torque generating mechanism is configured to generate, when the damper device is in the second torsional state, a second hysteresis torque larger than the first hysteresis torque in a third region where the torsional angle is equal to or larger than the second angle and smaller than a third angle. The damper device according to claim 2 .

4. the hysteresis torque generating mechanism is configured to generate a third hysteresis torque larger than the second hysteresis torque in a fourth region where the torsion angle is equal to or larger than the third angle and equal to or smaller than the maximum angle when the damper device is in the second torsional state. The damper device according to claim 3 .

5. The hysteresis torque generating mechanism is configured to generate a second hysteresis torque greater than the first hysteresis torque in the third region when the damper device is in the second torsional state, and not to generate a hysteresis torque in response to minute vibrations occurring within a predetermined small torsional angle range. The damper device according to claim 3 or 4.

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