Damper device

Abstract

To provide a damper device capable of attaining suitable torsion characteristics in a positive side and a negative side in accordance with a specification of a vehicle.SOLUTION: This device includes an input side plate 30, a hub flange 40, and an elastic connection part 50. The elastic connection part 50 has a first torsion characteristic T1, a second torsion characteristic T2, and a third torsion characteristic T3. The first torsion characteristic T1 has first rigidity in a first operational area in which a torsional angle range in a positive side is wider than in a negative side. The second torsion characteristic T2 has second rigidity higher than the first rigidity in a second operational area exceeding the positive side in the first operational area. The third torsion characteristic T3 has third rigidity higher than the first rigidity and lower than the second rigidity in a third operational area exceeding the negative side in the first operational area.SELECTED DRAWING: Figure 5

Description

Technical Field

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

Background Art

[0002] For example, in a hybrid vehicle equipped with an engine and an electric motor, in order to prevent excessive torque from being transmitted from the output side to the engine side when the engine is started, a damper device having a torque limiter function as shown in Patent Document 1 is used.

[0003] The damper device of Patent Document 1 has a damper portion having a pair of plates and a plurality of torsion springs, and a torque limiter is provided on the outer peripheral side of this damper portion. The torque limiter and the damper portion are connected by a rivet. And the plate of the torque limiter is fixed to the flywheel by bolts.

[0004] Here, the torque transmitted between the damper portion and the flywheel is limited by the torque limiter, and it is prevented that excessive torque is transmitted between them.

Prior Art Documents

Patent Documents

[0005]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0006] The damper device in a hybrid vehicle operates mainly in the positive torsional angle region (hereinafter, may be simply referred to as "positive side") in terms of torsional characteristics during engine operation such as during driving, and mainly operates in the negative torsional angle region (hereinafter, may be simply referred to as "negative side") when the engine is started. Therefore, the required torsional characteristics may be different between the positive side and the negative side.

[0007] For example, on the positive side, low stiffness and wide torsional characteristics are required in the region of small torsional angles. Also, to accommodate situations such as when a large torque is input from the tire side, high stiffness torsional characteristics are required in the region of large torsional angles. On the other hand, on the negative side, in order to efficiently absorb vibrations during engine startup, it is necessary to minimize the difference between the stiffness of the first-stage torsional characteristics and the stiffness of the subsequent second-stage torsional characteristics. Therefore, in the region of large torsional angles on the negative side, torsional characteristics with lower stiffness are required than the stiffness in the region of large torsional angles on the positive side.

[0008] The object of the present invention is to obtain appropriate torsional characteristics on the positive and negative sides in a damper device according to the specifications of the vehicle. [Means for solving the problem]

[0009] (1) The damper device according to the present invention comprises a first rotating body, a second rotating body, and an elastic connecting part. The second rotating body is rotatable relative to the first rotating body. The elastic connecting part elastically connects the first rotating body and the second rotating body in the rotational direction. The elastic connecting part also has a first torsional characteristic, a second torsional characteristic, and a third torsional characteristic. The first torsional characteristic has a first rigidity in a first operating region of torsional angle spanning both the positive and negative sides, and the torsional angle range of the first operating region differs between the positive and negative sides. The second torsional characteristic has a second rigidity that is higher than the first rigidity in a second operating region of torsional angle, and the second operating region is an operating region that extends beyond the positive side of the first operating region. The third torsional characteristic is that in the third operating region of the torsional angle, it has a third stiffness that is higher than the first stiffness and different from the second stiffness, and the third operating region is an operating region that exceeds the negative side of the first operating region.

[0010] In this device, the positive and negative sides of the first operating region, which has a first torsional characteristic, are different. For example, widening the positive operating region improves vibration absorption performance during engine operation, depending on the specifications. Beyond the first operating region, both the positive and negative sides have a second and third torsional characteristic with higher rigidity than the first torsional characteristic. Furthermore, the rigidity of the second torsional characteristic and the rigidity of the third torsional characteristic are different. For this reason, for example, increasing the rigidity of the second torsional characteristic on the positive side allows for more effective absorption of torque from the tires. Also, making the rigidity of the third torsional characteristic on the negative side close to the rigidity of the first torsional characteristic improves vibration absorption performance during engine startup in hybrid vehicles.

[0011] (2) Preferably, the first operating region is wider on the positive side than on the negative side. In this case, the vibration absorption performance during engine operation is improved.

[0012] (3) Preferably, the second stiffness of the second torsional characteristic of the elastic connecting portion is higher than the third stiffness of the third torsional characteristic. In this case, torque from the tires can be sufficiently absorbed. Moreover, when this damper is installed in a hybrid vehicle, vibrations during engine startup can be effectively absorbed.

[0013] (4) Preferably, the elastic coupling has a first elastic part and a second elastic part that are arranged side by side in the circumferential direction and operate in parallel. The first elastic part has a fourth torsional characteristic and a fifth torsional characteristic. The second elastic part has a sixth torsional characteristic and a seventh torsional characteristic.

[0014] The fourth torsional characteristic has a fourth stiffness in the fourth operating region of the torsional angle, spanning both the positive and negative sides. The fourth operating region differs between the positive and negative sides. The fifth torsional characteristic has a fifth stiffness that is higher than the fourth stiffness in the fifth operating region of the torsional angle. The fifth operating region is the operating region beyond the positive side of the fourth operating region and the operating region beyond the negative side of the fourth operating region. The sixth torsional characteristic has a sixth stiffness in the sixth operating region of the torsional angle, spanning both the positive and negative sides, and is offset from the fourth torsional characteristic in the torsional angle direction and the input torque direction. The seventh torsional characteristic has a seventh stiffness that is higher than the sixth stiffness and different from the fifth stiffness in the seventh operating region of the torsional angle, and the seventh operating region is the operating region beyond the positive side of the sixth operating region and the operating region beyond the negative side of the sixth operating region.

[0015] (5) Preferably, the first rotating body has a first support portion and a second support portion. The second rotating body has a first housing portion and a second housing portion. The first housing portion is provided offset from the first support portion toward the first rotation direction. The second housing portion is provided offset from the second support portion toward the second rotation direction. The elastic connecting portion has a first elastic member and a second elastic member. The first elastic member is pre-compressed and positioned in the first support portion and the first housing portion, and elastically connects the first rotating body and the second rotating body in the rotation direction. The second elastic member is pre-compressed and positioned in the second support portion and the second housing portion, and elastically connects the first rotating body and the second rotating body in the rotation direction.

[0016] (6) Preferably, the offset angle between the first support portion and the first housing portion is the same as the offset angle between the second support portion and the second housing portion. Also, the first elastic member and the second elastic member have the same rigidity.

[0017] (7) Preferably, the first elastic member has a first coil spring and a first elastic body. The first elastic body is disposed inside the first coil spring and has a shorter length than the first coil spring. Also, the second elastic member has a second coil spring and a second elastic body. The second elastic body is disposed inside the second coil spring, has a shorter length than the second coil spring, and has a different length from the first elastic body.

[0018] (8) Preferably, the first elastic body and the second elastic body are resin members.

Advantages of the Invention

[0019] In the present invention as described above, appropriate torsional characteristics can be obtained according to the vehicle specifications in both the positive and negative operating regions of the damper device.

Brief Description of the Drawings

[0020] [Figure 1] Cross-sectional view of a damper device according to an embodiment of the present invention. [Figure 2] Front view of the damper device of FIG. 1. [Figure 3] View showing the positional relationship between the input side plate and the hub flange. [Figure 4A] View showing the neutral state. [Figure 4B] View showing the state where the compression of the first resin member starts. [Figure 4C] View showing the state where the compression of the second resin member starts. [Figure 5] View showing the torsional characteristics of the damper unit. [Figure 6] Schematic diagram for explaining the operation of the first window portion. [Figure 7] Schematic diagram for explaining the operation of the second window portion. [Figure 8] View showing the torsional characteristics of the damper unit in another embodiment.

Mode for Carrying Out the Invention

[0021] [Overall Configuration] Figure 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. Figure 2 is a front view of the damper device 1, with some of its constituent components removed. In Figure 1, an engine (not shown) is located on the left side of the damper device 1, and a drive unit (not shown) including an electric motor and a transmission is located on the right side.

[0022] In the following explanation, 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 a circle centered on the rotation axis O. Note that the circumferential direction does not need to perfectly coincide with the circumferential direction of a circle centered on the rotation axis O. Similarly, the radial direction does not need to perfectly coincide with the diametrical direction of a circle centered on the rotation axis O.

[0023] This damper device 1 is installed between the flywheel (not shown) and the input shaft of the drive unit, and is a device for limiting the torque transmitted between the engine and the drive unit, as well as damping rotational fluctuations. The damper device 1 includes a torque limiter unit 10 and a damper unit 20.

[0024] [Torque limiter unit 10] The torque limiter unit 10 is located on the outer circumference of 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.

[0025] [Damper Unit 20] The damper unit 20 includes an input-side plate 30 (an example of a first rotating body), a hub flange 40 (an example of a second rotating body), an elastic connecting part 50, and a hiss generation mechanism 60.

[0026] <Input side plate 30> The input-side plate 30 has a first plate 31 and a second plate 32. The first plate 31 and the second plate 32 are formed in a disc shape with a hole in the center and are spaced apart from each other in the axial direction. The first plate 31 has four stopper portions 31a and four fixing portions 31b on its outer circumference. The first plate 31 and the second plate 32 also have one pair of first support portions 301 and one pair of second support portions 302, respectively. In the first plate 31 and the second plate 32, the first support portions 301 and the second support portions 302 are formed in the same position. The first plate 31 has a hole 31c for rivets 17, and the second plate 32 has an assembly hole 32a at a position corresponding to the hole 31c. The inner circumference of the friction disc 13 of the torque limiter unit 10 is fixed to the first plate 31 by rivets 17 passing through this assembly hole 32a.

[0027] The stopper portion 31a is formed by bending the outer circumference of the first plate 31 toward the second plate 32 and extends in the axial direction. The fixing portion 31b is formed by bending the tip of the stopper portion 31a radially outward. This fixing portion 31b is fixed to the outer circumference end of the second plate 32 by a plurality of rivets 33. Therefore, the first plate 31 and the second plate 32 are unable to rotate relative to each other and are unable to move relative to each other in the axial direction.

[0028] As shown in Figure 2 and Figure 3, which shows the first plate 31, a pair of first support parts 301 are arranged opposite each other with the rotation axis O in between. A pair of second support parts 302 are also arranged opposite each other with the rotation axis O in between, at a 90° distance from the first support parts. Each support part 301, 302 has the same shape and has a hole that penetrates in the axial direction, and a cut-out edge portion on the inner and outer periphery of this hole.

[0029] <Hub flange 40> As shown in Figures 1 and 2, the hub flange 40 comprises a hub 41 and a flange 42. The hub flange 40 is rotatable relative to the input plate 30 within a predetermined angular range. The hub 41 is formed in a cylindrical shape, with a spline hole 41a formed in its center. The hub 41 also penetrates the holes in the centers of the first plate 31 and the second plate 32. The flange 42 is formed in a disc shape, extending radially outward from the outer circumferential surface of the hub 41. The flange 42 is positioned axially between the first plate 31 and the second plate 32.

[0030] The flange 42 has four stopper projections 42b, a pair of first housing portions 401 and a pair of second housing portions 402, and four notches 403.

[0031] The four stopper protrusions 42b are formed to protrude radially outward from the outer circumferential surface of the flange 42. The positions where each stopper protrusion 42b is formed are radially outward from the circumferential center of each housing portion 401, 402. When the input-side plate 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 preventing relative rotation between the input-side plate 30 and the hub flange 40.

[0032] As shown in Figure 2 and Figure 3, which shows the hub flange 40 in detail, a pair of first housing portions 401 are arranged opposite each other with the rotation axis O in between. A pair of second housing portions 402 are also arranged opposite each other with the rotation axis O in between, between the circumferential directions of the first housing portions 401. Each housing portion 401, 402 is the same shape, and is a substantially rectangular hole with an arc-shaped outer circumference.

[0033] The four notches 403 are formed radially inward from the outer surface of the flange 42 at a predetermined depth between adjacent housing portions 401 and 402 in the circumferential direction. The positions where each notch 403 is formed correspond to the positions of the rivets 17 that connect 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 by the rivets 17 using the mounting holes 32a of the second plate 32 and the notches 403 of the flange 42.

[0034] <Arrangement of support and housing sections> Figure 3 shows the positional relationship of the hub flange 40 with respect to the input plate 30 (in this case, the first plate 31) in the neutral state. In Figure 3, line C1 is a line passing through the centers of the pair of first support parts 301 and the axis of rotation O. Line C2 is a line passing through the centers of the pair of second support parts 302 and the axis of rotation O. In the assembled state, the input plate 30 and the hub flange 40 are assembled so that they overlap each other, maintaining the positional relationship shown in Figure 3. Here, "neutral state" refers to a state where the relative rotation angle between the input plate 30 and the hub flange 40 is 0° (a torsional angle of 0°, meaning neither is twisted).

[0035] A pair of first housing sections 401 are positioned to correspond to a pair of first support sections 301. Similarly, a pair of second housing sections 402 are positioned to correspond to a pair of second support sections 302. More specifically, the pair of first housing sections 401 are positioned such that they partially overlap the first support sections 301 in an axial view and are offset by an angle θ0 in the first rotation direction (hereinafter simply referred to as the "R1 side"). That is, the first housing sections 401 are positioned offset by an angle θ0 in the R1 side with respect to the line C1. Similarly, the second housing sections 402 are positioned such that they partially overlap the second support sections 302 in an axial view and are offset by an angle θ0 in the second rotation direction (hereinafter simply referred to as the "R2 side"). That is, the second housing sections 402 are positioned offset by an angle θ0 in the R2 side with respect to the line C2.

[0036] <Spring seat 34> A pair of spring seats 34 are attached to the first support section 301 and the first housing section 401 (hereinafter, these may be collectively referred to as the "first window section w1") and the second support section 302 and the second housing section 402 (hereinafter, these may be collectively referred to as the "second window section w2"), facing each other (see Figure 2).

[0037] Here, spring seats 34 are placed in each window section w1, w2, and when the entirety of the first support section 301 of the input-side plate 30 and the entirety of the first housing section 401 of the hub flange 40 overlap in an axial view (i.e., the offset angle is "0"), the distance between opposing spring seats 34 (more precisely, the contact surfaces that abut the end faces of the coil springs on the opposing spring seats 34) is set to L. Similarly, when the entirety of the second support section 302 and the entirety of the second housing section 402 overlap in an axial view, the distance between opposing spring seats 34 is set to L.

[0038] <Elastic connecting part 50> The elastic connecting portion 50 has a first elastic portion 501 and a second elastic portion 502 arranged side by side in the circumferential direction. The first elastic portion 501 and the second elastic portion 502 operate in parallel. The first elastic portion 501 has two coil springs 51 and two first resin members 521 (an example of a first elastic body). The second elastic portion 502 has two coil springs 51 and two second resin members 522 (an example of a second elastic body).

[0039] Each coil spring 51 has the same stiffness k0 and comprises an outer spring and an inner spring positioned inside the outer spring. The four coil springs 51 are housed in the respective housings 401, 402 of the flange 42 and are supported radially and axially by the respective support portions 301, 302 of the input side plate 30. These coil springs 51 operate in parallel. Furthermore, the free length Sf of all four coil springs 51 is the same. The free length Sf of these coil springs 51 is the same as the distance L between opposing spring seats 34 mounted in the respective window portions w1, w2 (more precisely, between the contact surfaces where the end faces of the coil springs 51 of the spring seats 34 abut) when the offset angle is "0".

[0040] As shown in Figure 4A, the first resin member 521 is positioned inside the coil spring 51 in the first window portion w1. The second resin member 522 is positioned inside the coil spring 51 in the second window portion w2. The first resin member 521 is cylindrical in shape, with a length of d1 and a rigidity of k1. The second resin member 522 is roughly cylindrical in shape, having large diameter portions at both ends and a small diameter portion in the center, with a length of d2 and a rigidity of k2. Here, the relationship between the length and rigidity of the coil spring 51 and the two resin members 521 and 522 is: d1 <d2<Sf k1 > k2 > k0 It is set to this.

[0041] <Containment state of coil spring 51> Here, the state in which the coil springs 51 in each window section w1 and w2 are housed in the neutral position will be described in detail below.

[0042] As described above, in the neutral position, one pair of first housing sections 401 are offset by an angle θ0 toward R1 relative to the corresponding first support section 301. On the other hand, one pair of second housing sections 402 are offset by an angle θ0 toward R2 relative to the second support section 302. The coil spring 51 is fitted in a compressed state into the opening (a hole that penetrates in the axial direction) in the portion where each support section 301, 302 and the corresponding housing sections 401, 402 overlap in the axial direction.

[0043] [Twisting characteristics] Figure 5 is a torsional characteristic diagram (hysteresis torque is omitted), where the horizontal axis represents the torsional angle and the vertical axis represents the torque. In Figure 5, the dashed line represents the torsional characteristics of the first window section w1, the dashed line represents the torsional characteristics of the second window section w2, and the solid line represents the torsional characteristics of the damper unit 20, which is a combination of the torsional characteristics of the first window section w1 and the torsional characteristics of the second window section w2.

[0044] As is clear from the torsional characteristics shown by the solid line in Figure 5, the damper unit 20 of this embodiment has a first torsional characteristic T1 with low rigidity, a second torsional characteristic T2 with high rigidity on the positive side, and a third torsional characteristic T3 with high rigidity on the negative side. The first torsional characteristic T1 has a first rigidity KL in the first operating region of the torsional angle spanning both the positive and negative sides. The first operating region is wider on the positive side Ap than on the negative side An. The second torsional characteristic T2 has a second rigidity KHp that is more rigid than the first rigidity KL in the second operating region beyond the positive side of the first operating region. The third torsional characteristic T3 has a third rigidity KHn that is more rigid than the first rigidity KL and less rigid than the second rigidity KHp in the third operating region beyond the negative side of the first operating region. The relationship between the operating region and rigidity is shown below.

[0045] Ap>An KL <KHn<KHp

[0046] [Operation] The operation of each window section w1 and w2 will be explained in detail, but the hysteresis torque will be omitted. Figure 6 is a schematic diagram illustrating the operation of the first window section w1, and Figure 7 is a schematic diagram illustrating the operation of the second window section w2.

[0047] <First Window Section w1> Figures 4A and 6(a) show the neutral state in which the input plate 30 and the hub flange 40 are not rotating relative to each other. From this neutral state, Figures 4B and 6(b) show the state in which the hub flange 40 twists toward R1 relative to the input plate 30, and compression of the first resin member 521 begins. Conversely, Figure 6(c) shows the state in which the hub flange 40 twists toward R2 relative to the input plate 30 from the neutral state, and compression of the first resin member 521 begins. In the following description, the twist angle of the hub flange 40 relative to the input plate 30 may be simply referred to as the "twist angle".

[0048] First, in the neutral position, the first support portion 301 and the first housing portion 401 are offset from each other in the first window portion w1, so the distance between the opposing spring seats 34 in each window portion w1, w2 is shorter than the free length Sf of the coil spring 51. Therefore, in this neutral position, a torsional torque +t is generated by the compressed coil spring 51, as shown by the dashed line in Figure 5.

[0049] Furthermore, from a torsional angle of 0° on the R1 side to a torsional angle θ1 at which compression of the first resin member 521 begins, the coil spring 51 is always compressed. Therefore, in the range of torsional angles from 0 to θ1, a relatively low-stiffness torsional characteristic T4 (an example of a fourth torsional characteristic) is obtained due to the stiffness k4 (an example of a fourth stiffness) of the two coil springs 51.

[0050] Next, when both end faces of the first resin member 521 come into contact with the contact surfaces of the opposing spring seat 34 (see Figure 6(b)), a high-rigidity torsional characteristic T5 (an example of a fifth torsional characteristic) is obtained from this torsional angle θ1 onward due to the rigidity k1 (an example of a fifth rigidity) of the first resin member 521.

[0051] On the other hand, if the hub flange 40 is twisted relative to the input plate 30 by an offset angle θ0 from the neutral position toward R2, the distance between the pair of spring seats 34 supporting the coil spring 51 becomes L, which is the same as the free length Sf of the coil spring 51. Therefore, as shown by the dashed line in Figure 5, when the twist angle between the input plate 30 and the hub flange 40 is -θ0, the torsional torque becomes "0".

[0052] Furthermore, when the hub flange 40 twists to the R2 side beyond the offset angle θ0, the distance between the pair of spring seats 34 supporting the coil spring 51 becomes narrower than the free length Sf of the coil spring 51 again. Therefore, when the twist angle exceeds -θ0 on the negative side, the coil spring 51 is compressed from its free length Sf, and torsional characteristics similar to those on the positive side are obtained with two coil springs 51.

[0053] Then, as shown in Figure 6(c), when the torsion angle becomes -θ2, both end faces of the first resin member 521 come into contact with the contact surfaces of the opposing spring seat 34, and thereafter, as described above, a high-rigidity torsional characteristic (an example of the fifth torsional characteristic) is obtained due to the rigidity k1 (an example of the fifth rigidity) of the first resin member 521.

[0054] <Second window section w2> Figures 4A and 7(a) show the neutral state in which the input plate 30 and the hub flange 40 are not rotating relative to each other. From this neutral state, Figure 7(b) shows the state in which the hub flange 40 twists toward R1 relative to the input plate 30, and compression of the second resin member 522 begins. Conversely, Figures 4C and 7(c) show the state in which the hub flange 40 twists toward R2 relative to the input plate 30 from the neutral state, and compression of the second resin member 522 begins.

[0055] Similar to the first window section w1, in the neutral state, the second support section 302 and the second housing section 402 are offset from each other in the second window section w2. Therefore, the distance between the opposing spring seats 34 in each window section w1 and w2 is shorter than the free length Sf of the coil spring 51. Consequently, in this neutral state, a torsional torque -t is generated by the compressed coil spring 51, as shown by the dashed line in Figure 5.

[0056] When torque is applied to the damper unit 20, and the hub flange 40 twists relative to the input plate 30 by an offset angle θ0 from the neutral position toward R1, the entirety of the first support portion 301 and the entirety of the first housing portion 401 overlap in an axial view, and the distance between the opposing spring seats 34 becomes L, which is the same as the free length Sf of the coil spring 51. Therefore, in this state, as shown by the dashed line in Figure 5, the torsional torque becomes "0".

[0057] Furthermore, when the hub flange 40 twists toward R1 beyond the offset angle θ0, the distance between the pair of spring seats 34 supporting the coil spring 51 becomes narrower than the free length Sf of the coil spring 51 again. Therefore, when the twist angle exceeds θ0, the coil spring 51 is compressed from its free length Sf, resulting in a low-stiffness (an example of a sixth stiffness) torsional characteristic T6 (an example of a sixth torsional characteristic) due to the stiffness k4 of the two coil springs 51.

[0058] Next, as shown in Figure 7(b), when the torsion angle becomes θ3 and both end faces of the second resin member 522 come into contact with the contact surfaces of the opposing spring seat 34, a high-rigidity torsion characteristic T7 (an example of the seventh torsion characteristic) is obtained from this torsion angle θ3 onward due to the rigidity k2 (an example of the seventh rigidity) of the second resin member 522.

[0059] On the other hand, when the hub flange 40 twists from the neutral position towards the R2 side, the coil spring 51 is always compressed. Therefore, between the negative side twist angle of 0° and the twist angle -θ4 at which compression of the second resin member 522 begins, a relatively low-stiff torsional characteristic is obtained due to the stiffness k4 of the two coil springs 51, similar to the positive side.

[0060] Next, as shown in Figures 4C and 7(c), when both end faces of the second resin member 522 come into contact with the contact surfaces of the opposing spring seat 34, beyond this torsional angle θ4, a high-rigidity torsional characteristic T7 (an example of the seventh torsional characteristic) is obtained due to the rigidity k2 (an example of the seventh rigidity) of the second resin member 522, as shown by the dashed line in Figure 7.

[0061] <Synthesized torsional properties> As described above, the damper unit as a whole obtains a combined torsional characteristic (solid line in Figure 5) that is the sum of the torsional characteristics of the first window section w1 (dashed line in Figure 5) and the torsional characteristics of the second window section w2 (dotted line in Figure 5). In other words, in the neutral state, the torsional torque is "0", a first torsional characteristic T1 with a relatively low first stiffness KL is obtained in the first operating region (-θ4 to +θ1), a second torsional characteristic T2 with a second high stiffness KHp is obtained in the second operating region (positive region beyond +θ1), and a third torsional characteristic T3 with a third high stiffness KHn is obtained in the third operating region (negative region beyond -θ4).

[0062] Here, if we assume that the total lengths of the first resin member 521 and the second resin member 522 are the same, then the absolute values ​​of +θ1 and -θ4 in Figure 5 will be the same. Therefore, in the combined torsional characteristics, the positive operating region and the negative operating region of the low-torsion characteristics will be the same.

[0063] However, in this embodiment, since the total lengths of the first resin member 521 and the second resin member 522 are different, the angular range (0 to +θ1) and the angular range (0 to -θ4) are different, as shown in Figure 5. Therefore, in the combined torsional characteristics, the positive operating region and the negative operating region of the low-torsion characteristics in the first operating region are different. Specifically, in the first operating region, the positive operating region is wider than the negative operating region.

[0064] [Other embodiments] The present invention is not limited to the embodiments described above, and various modifications or alterations are possible without departing from the scope of the present invention.

[0065] (a) By appropriately setting the lengths of the first resin member and the second resin member, the amount of offset in the torsional angle direction between the torsional characteristics of the first window portion w1 and the torsional characteristics of the second window portion w2 can be changed.

[0066] For example, as shown in Figure 8, on the positive side of the torsional characteristics, the positive side high-rigidity section can be made multi-stage by overlapping a portion of the high-rigidity section of the torsional characteristics of the first window section w1 (see dashed line) and the torsional characteristics of the second window section w2 (see dashed line).

[0067] (b) In the above embodiment, each elastic part is made of a coil spring and a resin member, but a coil spring with high rigidity may be used instead of the resin member.

[0068] (c) The number of housings, support parts, coil springs, and resin members is an example and is not limited to the above embodiment. [Explanation of symbols]

[0069] 1. Damper device 30 Input side plate (first rotating body) 301,302 1st support part, 2nd support part 40 Hub flange (second rotating body) 401, 402 First containment section, Second containment section 50 Elastic connecting part 501, 502 First elastic section, second elastic section 51. Coil spring (first elastic member, second elastic member) 521, 522 First resin member, second resin member

Claims

1. A first rotating body; a second rotating body that is rotatable relative to the first rotating body; an elastic coupling portion that elastically couples the first rotating body and the second rotating body in a rotational direction; Equipped with The elastic connecting portion is a first torsional characteristic having a first stiffness in a first operating range of torsional angles across positive and negative sides, the first operating range being different between the positive and negative sides; a second torsional characteristic having a second stiffness higher than the first stiffness in a second operating range of a torsional angle, the second operating range being an operating range beyond the positive side of the first operating range; a third torsional characteristic having a third stiffness that is higher than the first stiffness and different from the second stiffness in a third operating range of a torsional angle, the third operating range being an operating range beyond the negative side of the first operating range; having Damper device.

2. The damper device according to claim 1 , wherein the first operating region is wider on the positive side than on the negative side.

3. 3. The damper device according to claim 1, wherein the second stiffness of the second torsional characteristic of the elastic connecting portion is higher than the third stiffness of the third torsional characteristic.

4. The elastic connecting portion has a first elastic portion and a second elastic portion that are arranged side by side in the circumferential direction and operate in parallel, The first elastic portion is a fourth torsional characteristic having a fourth stiffness in a fourth operating range of torsional angles across the positive and negative sides, the fourth operating range being different between the positive and negative sides; a fifth torsional characteristic having a fifth stiffness higher than the fourth stiffness in a fifth operating range of a torsional angle, the fifth operating range being an operating range that exceeds the positive side of the fourth operating range and an operating range that exceeds the negative side of the fourth operating range; and The second elastic portion is a sixth torsional characteristic having a sixth stiffness in a sixth operating range of torsional angles across positive and negative sides, the sixth torsional characteristic being offset in the torsional angle direction and the input torque direction relative to the fourth torsional characteristic; a seventh torsional characteristic having a seventh stiffness that is higher than the sixth stiffness and different from the fifth stiffness in a seventh operating range of a torsional angle, the seventh operating range being an operating range that exceeds the positive side of the sixth operating range and an operating range that exceeds the negative side of the sixth operating range; having The damper device according to any one of claims 1 to 3.

5. the first rotating body has a first support portion and a second support portion, the second rotating body has a first housing portion provided offset in a first rotation direction relative to the first support portion, and a second housing portion provided offset in a second rotation direction relative to the second support portion, The elastic connecting portion is a first elastic member that is pre-compressed and disposed in the first support portion and the first accommodation portion, and that elastically connects the first rotating body and the second rotating body in a rotational direction; a second elastic member that is pre-compressed and disposed in the second support portion and the second accommodation portion, and that elastically connects the first rotating body and the second rotating body in a rotational direction; having The damper device according to claim 1 .

6. an offset angle between the first support portion and the first housing portion and an offset angle between the second support portion and the second housing portion are the same; The first elastic member and the second elastic member have the same rigidity. The damper device according to claim 5 .

7. the first elastic member includes a first coil spring and a first elastic body disposed inside the first coil spring and having a length shorter than that of the first coil spring; The second elastic member includes a second coil spring and a second elastic body that is disposed inside the second coil spring and has a length shorter than that of the second coil spring and different from that of the first elastic body. The damper device according to claim 5 or 6.

8. The damper device according to claim 7 , wherein the first elastic body and the second elastic body are made of resin.

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