Damper Device

Abstract

To provide a serialized damper device for which a hiss generation mechanism to be used for a parallelly operating damper device can be utilized, as it is.SOLUTION: A damper device 1 includes an input side plate 3, a hub flange 4, two spring sets 41, 42, an intermediate member 30, and a hiss generation mechanism 6, the intermediate member 30 being arranged between the input side plate 3 and the hub flange 4 in the axial direction, the hiss generation mechanism 6 being arranged between the input side plate 3 and the hub flange 4, the intermediate member 30 having an annular part 34 and an intermediate support part 35, the annular part 34 being provided radially outward of the spring sets 41, 42, the intermediate support part 35 being formed protruding radially inward from the annular part 34 and arranged between springs 411, 412 adjacent to each other in at least two circumferential directions for allowing the operation of the adjacent springs 411, 412 in series.SELECTED DRAWING: Figure 5

Description

[Technical field]

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

[0002] A damper device is provided in a power transmission path of a vehicle to damp vibrations caused by torque fluctuations from a drive source. The damper device generally includes an input rotor and an output rotor that are rotatable relative to each other within a predetermined angular range, a plurality of springs that elastically connect these rotors in the rotational direction, and a hysteresis generating mechanism. The hysteresis generating mechanism generates a hysteresis torque when the input rotor and the output rotor rotate relative to each other, and the hysteresis torque damps vibrations caused by the input torque fluctuations.

[0003] In addition, in this type of damper device, in order to further attenuate vibration, it is preferable to increase the relative rotation angle (maximum torsional angle) between the input rotor and the output rotor, i.e., to widen the angle. For this reason, a damper device such as that shown in Patent Document 1 has been provided. In the device of Patent Document 1, an intermediate plate is disposed axially between the input rotor and the output rotor. This intermediate plate operates at least two of the multiple springs in series (hereinafter simply referred to as "series") to achieve a wide angle. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] JP 2018-96534 A Summary of the Invention [Problem to be solved by the invention]

[0005] In a damper device in which multiple springs operate in parallel, an intermediate plate as shown in Patent Document 1 is not required. Therefore, the hysteresis generating mechanism is provided between the flange of the output rotor and each of the pair of plates constituting the input rotor in the axial direction. Since this type of hysteresis generating mechanism is widely used in general-purpose damper devices, it is preferable to make it usable in a serial damper device as well.

[0006] However, in a serially connected damper device, an intermediate plate is provided axially between the plate constituting the input rotor and the flange of the output rotor, so the hysteresis generating mechanism of a damper device in which multiple springs operate in parallel cannot be utilized as is.

[0007] An object of the present invention is to make it possible to utilize, in serially connected damper devices, a hysteresis generating mechanism that is used in damper devices operating in parallel. [Means for solving the problem]

[0008] (1) A damper device according to the present invention includes a first rotating body, a second rotating body, a plurality of elastic members, an intermediate member, and a hysteresis generating mechanism. The second rotating body is rotatable relative to the first rotating body. The plurality of elastic members are arranged in a line in the circumferential direction and elastically connect the first rotating body and the second rotating body in the rotational direction. The intermediate member is arranged between the first rotating body and the second rotating body in the axial direction and is rotatable relative to the first rotating body and the second rotating body. The hysteresis generating mechanism is arranged between the first rotating body and the second rotating body in the axial direction and generates a hysteresis torque when the first rotating body and the second rotating body rotate relative to each other.

[0009] The intermediate member has an annular portion and a support portion. The annular portion is provided radially outward from the elastic members. The support portion is formed to protrude radially inward from the annular portion and is disposed between at least two circumferentially adjacent elastic members to operate the adjacent elastic members in series.

[0010] In this damper device, for example, when torque is input to the first rotor, the torque is transmitted to the second rotor via the multiple elastic members. When torque fluctuation is input to the first rotor, the torque fluctuation is suppressed by the operation of the multiple elastic members and the hysteresis generating mechanism, and vibration is damped. In particular, since at least two elastic members are operated in series by the intermediate member, the torsion angle is made wider, and vibration caused by torque fluctuation can be further damped.

[0011] Here, the intermediate member has an annular portion on the outer periphery of the device, which is radially outward of the multiple elastic members, and supports the adjacent elastic members with support portions that protrude radially inward from this annular portion. Therefore, there is no need to provide a portion that constitutes the intermediate member on the inner periphery of the device, and a member that constitutes the hysteresis generating mechanism can be disposed axially between the first and second rotors. In other words, in serially connected damper devices, the hysteresis generating mechanism used in damper devices operating in parallel can be used as is.

[0012] (2) Preferably, the hysteresis generating mechanism has a friction member disposed axially between the first rotor and the second rotor, the friction member having a first axial side surface in contact with the first rotor and a second axial side surface in contact with the second rotor.

[0013] Here, the friction member constituting the hysteresis generating mechanism can be disposed between the first rotor and the second rotor, meaning that the hysteresis generating mechanism used in the damper device operating in parallel can be used as is.

[0014] (3) Preferably, the first rotor has a first input plate and a second input plate, which are disk-shaped and fixed to each other and disposed opposite to each other in the axial direction. In this case, the second rotor has a flange disposed axially between the first input plate and the second input plate. The intermediate member has a first intermediate plate and a second intermediate plate. The first intermediate plate is disposed axially between the first input plate and the flange. The second intermediate plate is disposed axially between the second input plate and the flange, and is fixed to the first intermediate plate so as to be immovable in the axial and rotational directions.

[0015] When the intermediate member supports the elastic member, it is necessary to support the center of the elastic member in the axial direction. If the intermediate member is made of a single plate, the plate must overlap with the second rotating body in the axial direction in order to support the center of the elastic member in the axial direction. For this reason, if the intermediate member is made of a single plate, the intermediate member cannot support the center of the elastic member in the axial direction.

[0016] Therefore, in this damper device, the intermediate member is composed of a first intermediate plate and a second intermediate plate, and these intermediate plates are arranged to sandwich the flange of the second rotating body. In this case, the flange, the first intermediate plate, and the second intermediate plate can uniformly press and compress the elastic member.

[0017] (4) Preferably, the first intermediate plate has a first annular portion constituting the annular portion and a first support portion constituting the support portion. The first annular portion is disposed radially outward from the multiple elastic members. The first support portion is formed to protrude radially inward from the first annular portion. The second intermediate plate has a second annular portion constituting the annular portion and a second support portion constituting the support portion. The second annular portion is disposed radially outward from the multiple elastic members. The second support portion is formed to protrude radially inward from the second annular portion.

[0018] In this case, the damper device further includes a first spacer and a second spacer. The first spacer is disposed axially between the first annular portion of the first intermediate plate and the outer periphery of the flange. The second spacer is disposed axially between the second annular portion of the second intermediate plate and the outer periphery of the flange.

[0019] Here, in order to achieve miniaturization of the device in the axial direction, it is necessary to minimize the gap between axially adjacent members. On the other hand, in order to suppress the generation of unintended hysteresis torque, it is necessary to avoid frictional contact between members in parts other than the hysteresis generating mechanism. In order to avoid such frictional contact while minimizing the gap between members, it is necessary to control the machining accuracy and assembly accuracy of the members with high precision.

[0020] Therefore, in this damper device, a first spacer and a second spacer are provided between the flange and the first intermediate plate and between the flange and the second intermediate plate, respectively. By forming these spacers from a thin material with a small coefficient of friction, it is possible to suppress unintended hysteresis torque and achieve axial size reduction without increasing the machining accuracy and assembly accuracy of the members.

[0021] (5) Preferably, the friction member has a first friction plate and a second friction plate. The first friction plate is disposed between the first input plate and the flange. The second friction plate is disposed between the second input plate and the flange.

[0022] (6) Preferably, the first rotating body has a plurality of arc-shaped holding portions, and the second rotating body has a plurality of accommodating portions. The holding portions hold a plurality of elastic members. The accommodating portions are provided corresponding to the plurality of holding portions and accommodate the plurality of elastic members. At least two of the plurality of elastic members accommodated and held in the plurality of accommodating portions and the holding portions are operated in series by the intermediate member.

[0023] (7) Preferably, the first rotating body has a plurality of notches and a plurality of stopper portions. The notches are radially outward of the circumferential end region of the holding portion, and have a predetermined length in the circumferential direction. The stopper portions are provided at positions corresponding to the notches in the circumferential direction, and have a predetermined length in the circumferential direction. The second rotating body has a protrusion. The protrusion protrudes radially outward from the outer peripheral surface of the flange, and is formed at a position overlapping with the stopper portions in the axial direction. The protrusion regulates the relative rotation angle between the first rotating body and the second rotating body by abutting against the circumferential end faces of the stopper portions.

[0024] Here, a stopper mechanism that regulates the relative rotation angle (torsion angle) between the first and second rotors is configured by the stopper portion of the first rotor and the protrusion of the second rotor. Here, the holding portion of the first rotor generally has a wider radial width at the circumferential center than at both ends. Therefore, in the first rotor, the radial width is narrower on the radial outside of the circumferential center of the holding portion. If a notch and a stopper portion for the stopper mechanism are formed in this portion, the rotation strength of the first rotor is reduced.

[0025] Therefore, in this damper device, the notches and the stopper portions are formed in the circumferential end regions of the holding portion, which makes it possible to suppress a decrease in the rotational strength of the first rotor caused by the holding portion and the notches (stopper portions). Effect of the Invention

[0026] In the present invention as described above, in serially connected damper devices, the hysteresis generating mechanism used in damper devices operating in parallel can be utilized as is. [Brief description of the drawings]

[0027] [Figure 1] 1 is a cross-sectional view of a damper device according to an embodiment of the present invention; [Diagram 2] FIG. [Diagram 3] FIG. 4 is an external perspective view of a first input plate. [Figure 4]FIG. [Diagram 5] FIG. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0028] [Overall configuration] Fig. 1 is a cross-sectional view of a damper device 1 according to an embodiment of the present invention, taken along line II in Fig. 2. Fig. 2 is a front view of the damper device 1, with some of its constituent members removed. In Fig. 1, a drive source is disposed on the left side of the damper device 1, and a transmission and other devices are disposed on the right side.

[0029] In the following description, the axial direction is the direction in which the rotation axis O of the damper device 1 extends. The circumferential direction is the circumferential direction of a circle centered on the rotation axis O, and the radial direction is the radial direction of the circle centered on the rotation axis O. The circumferential direction does not have to completely coincide with the circumferential direction of the circle centered on the rotation axis O. The radial direction does not have to completely coincide with the diameter direction of the circle centered on the rotation axis O.

[0030] The damper device 1 is a device for damping rotational fluctuations input from a drive source. The damper device 1 has a drive plate 2, an input side plate (an example of a first rotating body) 3, a hub flange 4 (an example of a second rotating body), an elastic connecting portion 5, and a hysteresis generating mechanism 6.

[0031] <Input side plate 3> The input side plate 3 has a first input plate 11 and a second input plate 12. The first input plate 11 and the second input plate 12 are substantially annular disc members. The first input plate 11 and the second input plate 12 are arranged with a predetermined gap in the axial direction. The first input plate 11 and the second input plate 12 have the same basic configuration and are formed symmetrically in the axial direction. The first input plate 11 will be described in detail below.

[0032] As shown in Figs. 1 to 3, the first input plate 11 has a disk portion 11a, a cylindrical portion 11b, and an outer peripheral extension portion 11c. Fig. 3 is an external perspective view of the first input plate 11. The disk portion 11a has a circular opening 11d in the center. The cylindrical portion 11b extends in the axial direction from the outer peripheral end of the disk portion 11a toward the second input plate 12. The outer peripheral extension portion 11c extends radially outward from the axial tip of the cylindrical portion 11b.

[0033] Two arc-shaped windows 11e (an example of a holding portion) are formed in the radial middle of the disk portion 11a. The windows 11e are formed to face each other in the radial direction. The central portion of the window 11e in the circumferential direction has a wider radial width than both ends. In other words, the distance between the outer circumferential surface of the window 11e and the outer circumferential surface of the plate 11 is smaller in the central portion of the window 11e than in both ends.

[0034] 2 and 3, four notches 11f are formed radially outward from both ends of the window portion 11e in the outer periphery of the disk portion 11a and in the cylindrical portion 11b. Each of the notches 11f has a predetermined length in the circumferential direction.

[0035] Four fixing portions 11g (one example of a stopper portion) are formed on a part of the outer peripheral extension portion 11c. The fixing portions 11g are arranged at positions corresponding to the notches 11f in the circumferential direction. More specifically, the fixing portions 11g are formed simultaneously with the notches 11f when the notches 11f are punched out by press molding. The end faces in the circumferential direction of the fixing portions 11g serve as stopper surfaces 11s.

[0036] As described above, the second input plate 12 has a configuration basically similar to that of the first input plate 11, and includes the disk portion 12a, the cylindrical portion 12b, the outer peripheral extension portion 12c, the opening 12d, the window portion 12e, the notch 12f, the fixing portion 12g, and the stopper surface 12s. The first input plate 11 and the second input plate 12 are connected to each other so as to be rotatable together with the drive plate 2 by a plurality of rivets (not shown) that penetrate the fixing portions 11g and 12g.

[0037] As shown in FIG. 3, the first input plate 11 has four engagement holes 11h formed radially inward of the window portion 11e, and an inner peripheral end face , radially inward The second input plate 12 has four notches 11i formed therein, which open toward the inner periphery of the plate 11. The second input plate 12 also has four engagement holes 12h formed at its inner periphery.

[0038] <Hub flange 4> As shown in Figures 1, 2, and 4, the hub flange 4 has a hub 21 and a flange 22. Note that Figure 4 is an exploded perspective view of the hub flange 4. The hub flange 4 is rotatable within a predetermined angular range relative to the first input plate 11 and the second input plate 12 (hereinafter, these two plates 11, 12 may also be referred to as "input side plates 3").

[0039] -Hub 21- The hub 21 has a cylindrical portion 24 and a disk portion 25. A spline hole 24a is formed on the inner peripheral surface of the cylindrical portion 24. The cylindrical portion 24 also penetrates through openings 11d, 12d at the center of the first input plate 11 and the second input plate 12. The disk portion 25 is formed to protrude radially outward from the axial center of the cylindrical portion 24. The disk portion 25 is formed with a plurality of teeth 25a and two notches 25b. The two notches 25b are disposed opposite each other across the rotation axis O and open radially outward.

[0040] -Flange 22- The flange 22 is disposed radially outward of the disc portion 25 of the hub 21 at a position overlapping with the disc portion 25 in the axial direction. The flange 22 has a disc portion 26, a pair of protrusions 27, and a pair of output side accommodating portions 28.

[0041] The disk portion 26 is formed in an annular shape, and has a plurality of engagement portions 26a and two notches 26b formed on its inner circumferential surface. Teeth 25a of the hub 21 engage with the engagement portions 26a via a predetermined gap. The two notches 26b are formed facing each other across the rotation axis O. The two notches 26b are disposed to face the notches 25b of the hub 21, and open radially inward.

[0042] A spring 29 (see FIG. 1) is disposed in the space formed by the notches 25b, 26b of the hub 21 and the flange 22. The spring 29 elastically connects the hub 21 and the flange 22 in the circumferential direction. The stiffness of the spring 29 is set to be smaller than the stiffness of the elastic connecting portion 5.

[0043] More specifically, the hub 21 and the flange 22 are capable of relative rotation by an angle corresponding to the gap between the teeth 25a of the hub 21 and the engagement portion 26a of the flange 22, and the spring 29 operates within this range of rotation angles. When the hub 21 and the flange 22 are twisted by an angle corresponding to the aforementioned gap, the teeth 25a come into contact with the wall surface of the engagement portion 26a, and thereafter, relative rotation between the hub 21 and the flange 22 is prohibited, and the two members 21, 22 rotate together.

[0044] The pair of protrusions 27 are formed to protrude radially outward from the outer circumferential surface of the disc portion 26, and are disposed at positions facing each other across the rotation axis O. A stopper protrusion 27s protruding radially outward is formed on the outer circumferential surface of each protrusion 27. The stopper protrusion 27s is formed at a position overlapping with the fixing portions 11g, 12g of the input side plate 3 in the axial direction. Therefore, when the stopper protrusion 27s abuts against the stopper surfaces 11s, 12s, which are both end surfaces of the fixing portion 11g, the relative rotation of the hub flange 4 with respect to the input side plate 3 is prohibited. In other words, the stopper surfaces 11s, 12s and the stopper protrusion 27s form a stopper mechanism.

[0045] The pair of output side accommodating portions 28 are formed circumferentially between the pair of protrusions 27. The output side accommodating portion 28 has an end face support portion 28a and an outer periphery support portion 28b. The end face support portion 28a is the circumferential end face of the protrusion 27. The outer periphery support portion 28b is formed to extend a predetermined distance in each of both circumferential directions from the outer periphery end portion of the end face support portion 28a.

[0046] <Elastic connecting part 5> 1 and 5, the elastic connecting portion 5 has a first support plate 31 (an example of a first intermediate plate) and a second support plate 32 (an example of a second intermediate plate) that constitute the intermediate member 30, a first spring set 41, a second spring set 42, and a pair of spacers 45. The elastic connecting portion 5 elastically connects the input side plate 3 and the hub flange 4 in the rotational direction.

[0047] -Intermediate member 30 (support plates 31, 32)- The first support plate 31 is disposed axially between the first input plate 11 and the flange 22. The second support plate 32 is disposed axially between the second input plate 12 and the flange 22. The first support plate 31 and the second support plate 32 are fixed to each other in the axial and rotational directions. Both support plates 31, 32 are rotatable relative to the input side plate 3 and the hub flange 4.

[0048] Since the first support plate 31 and the second support plate 32 have the same configuration, they may be hereinafter referred to as "intermediate member 30" in the description.

[0049] The intermediate member 30 has an annular portion 34, two support portions 35, and two reinforcing protrusions 36. The annular portion 34 is continuous in the circumferential direction. The two support portions 35 are arranged opposite to each other across the rotation axis O, and are formed to protrude a predetermined distance radially inward from the annular portion 34. A fixing hole 35a is formed in the support portion 35, and the first support plate 31 and the second support plate 32 are fixed by a rivet that penetrates the hole 35a. The two protrusions 36 are arranged at an interval of 90 degrees from the two support portions 35. The protrusions 36 are formed to protrude radially inward from the annular portion 34 by approximately the same distance as the support portions 35, and suppress a decrease in the strength of each of the support plates 31 and 32.

[0050] A pair of intermediate accommodating portions 38 are formed by two spaces between the two protrusions 36 in the circumferential direction. The intermediate accommodating portions 38 are disposed at positions corresponding to the windows 11e, 12e of the input side plate 3 and the output side accommodating portion 28 of the flange 22. A first spring set 41 and a second spring set 42 (see FIG. 2) are accommodated in each of the pair of intermediate accommodating portions 38.

[0051] -Spring set 41, 42- The first spring set 41 and the second spring set 42 are respectively accommodated in the output side accommodation portion 28 of the flange 22 and the intermediate accommodation portion 38 of the first support plate 31 and the second support plate 32, and are held by the windows 11e and 12e of the input side plate 3. Each spring set 41 and 42 has an R1 spring 411 and 421 arranged on a first circumferential side (hereinafter, R1 side) and an R2 spring 412 and 422 arranged on a second circumferential side (hereinafter, R2 side).

[0052] In a neutral state where there is no torsional angle between the input side plate 3 and the hub flange 4, in each spring set 41, 42, the R1 side end faces of the R1 springs 411, 421 abut against the R1 side end faces of the windows 11e, 12e and the output side accommodating portion 28, and the R2 side end faces abut against the support portions 35 of the pair of support plates 31, 32. In addition, the R1 side end faces of the R2 springs 412, 422 abut against the support portions 35 of the pair of support plates 31, 32, and the R2 side end faces abut against the window portions 11e, 12e and the R2 side end faces of the output side accommodating portion 28.

[0053] Due to the above-described arrangement of the springs 411, 412, 421, 422 and both support plates 31, 32, when the input side plate 3 and the hub flange 4 are twisted, the R1 spring 411 and R2 spring 412 of the first spring set 41 operate in series, and the R1 spring 421 and R2 spring 422 of the second spring set 42 operate in series. On the other hand, the first spring set 41 and the second spring set 42 operate in parallel.

[0054] -Spacer 45- The pair of spacers 45 are disposed axially between the annular portions 34 of the first support plate 31 and the second support plate 32 and the outer periphery of the flange 22. The spacers 45 are annular with a predetermined width in the radial direction and are made of a resin member with a small friction coefficient. The spacers 45 are sandwiched between the outer periphery of each of the support plates 31, 32 and the flange 22 and are in contact with both components, but can rotate freely.

[0055] Providing this spacer 45 makes it possible to avoid unintended hysteresis torque caused by direct contact between each of the support plates 31, 32 and the flange 22. In addition, although the spacer 45 and each of the members 31, 32, 22 are in frictional contact, the spacer 45 is made of a resin with a small coefficient of friction, so that the hysteresis torque caused by this frictional contact can be kept small.

[0056] <Hiss Generation Mechanism 6> As shown in FIG. 1, the hysteresis generating mechanism 6 includes a first friction plate 51, a second friction plate 52, a first bush 61, a second bush 62, a support plate 63, an outer circumferential cone spring 64, and an inner circumferential cone spring 65.

[0057] The first friction plate 51 is disposed between the first input plate 11 and the flange 22 in the axial direction. An annular resin member is fixed to the first friction plate 51, and this resin member is in contact with the flange 22. A plurality of protrusions 51a protruding toward the first input plate 11 are formed on the outer circumferential end of the first friction plate, and these protrusions 51a engage with engagement holes 11h formed in the first input plate 11. Therefore, the first friction plate 51 rotates in synchronization with the first input plate 11.

[0058] The first bush 61 is annular, and is disposed on the inner circumferential side of the first friction plate 51, between the first input plate 11 and the disk portion 25 of the hub 21. A plurality of protrusions protruding radially outward are formed on the outer circumferential surface of the first bush 61, and these protrusions can abut against a part of the inner circumferential end portion of the first friction plate 51. This restricts the movement of the first bush 61 toward the second input plate 12. The first bush 61 and the first input plate 11 are partially engaged with each other. Therefore, the first bush 61 rotates in synchronization with the first input plate 11 and the first friction plate 51.

[0059] The second friction plate 52 is disposed between the second input plate 12 and the flange 22 in the axial direction. An annular resin member is fixed to the second friction plate 52, and this resin member is in contact with the flange 22. Four protrusions 52a that protrude toward the second input plate 12 are formed on the inner peripheral end of the second friction plate 52, and these protrusions 52a engage with engagement holes 12h formed in the second input plate 12. Therefore, the second friction plate 52 rotates in synchronization with the second input plate 12.

[0060] The second bush 62 is annular, and is disposed on the inner circumferential side of the second friction plate 52, between the second input plate 12 and the disk portion 25 of the hub 21. The outer circumferential surface of the second bush 62 is formed with a plurality of protrusions that protrude radially outward, and these protrusions engage with parts of the second friction plate 52. This causes the second bush 62 to rotate in synchronization with the second friction plate 52 and the second input plate 12.

[0061] The support plate 63 and the outer circumferential cone spring 64 are disposed axially between the second friction plate 52 and the second input plate 12. More specifically, the support plate 63 is disposed so as to contact the second friction plate 52, and the outer circumferential cone spring 64 is disposed between the support plate 63 and the second input plate 12. The support plate 63 is formed in an annular shape, and the outer circumferential cone spring 64 presses the second friction plate 52 against the flange 22 via the support plate 63.

[0062] The inner cone spring 65 is disposed axially between the second bush 62 and the second input plate 12. The inner cone spring 65 presses the second bush 62 against the disk portion 25 of the hub 21.

[0063] [Operation] When the input torque or torque fluctuation is small, only the spring 29 arranged between the hub 21 and the flange 22 operates. That is, the input side plate 3 and the flange 22 rotate integrally, and the flange 22 and the hub 21 rotate relatively to each other by an angle corresponding to the gap between the teeth 25a and the engagement portion 26a. Here, the first bush 61 and the second bush 62 come into frictional contact with the disk portion 25 of the hub 21, which generates a hysteresis torque.

[0064] When the torque fluctuation increases and the torsion angle between the flange 22 and the hub 21 increases, and the teeth 25a come into contact with the wall surface of the engagement portion 26a, the operation of the spring 29 stops, and the hub 21 and the flange 22 rotate together. Then, relative rotation occurs between the input side plate 3 and the hub flange 4, and the two springs 411, 412 of the first spring set 41 are operated in series by the intermediate member 30 (the first support plate 31 and the second support plate 32), and the two springs 421, 422 of the second spring set 42 are similarly operated in series by the intermediate member 30. In addition, the first spring set 41 and the second spring set 42 operate in parallel. In this state, the first friction plate 51 and the second friction plate 52 each rotate in synchronization with the input side plate 3, so that both friction plates 51, 52 and the flange 22 are in frictional contact. Therefore, a hysteresis torque is generated due to this frictional contact.

[0065] Furthermore, when the torsion angle between the input side plate 3 and the hub flange 4 becomes even larger, the stopper projections 27s formed on the outer peripheral surface of the flange 22 come into contact with the stopper surfaces 11s, 12s of the input side plate 3. This prohibits relative rotation between the input side plate 3 and the flange 22.

[0066] During the above operation, the first support plate 31 and the second support plate 32 rotate relative to the flange 22. However, since the spacer 45 is provided between the flange 22 and both the support plates 31, 32, the hysteresis torque therebetween can be reduced.

[0067] [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.

[0068] (a) The number of spring sets is not limited to that in the above embodiment, and the number of springs constituting each spring set is also not limited to that in the above embodiment.

[0069] (b) In the above embodiment, the hub flange 4 is divided into the hub 21 and the flange 22, but the present invention can also be applied to an integrated hub flange.

[0070] (c) In the above embodiment, a spacer is provided between each support plate and the flange, but it is possible to omit the spacer.

[0071] (d) The configuration of the hysteresis generating mechanism is not limited to that in the above embodiment, and various configurations of hysteresis generating mechanisms of general-purpose damper devices operating in parallel can be similarly applied. [Explanation of symbols]

[0072] 1 Damper device 3 Input plate (first rotor) 4 Hub flange (second rotating body) 6 Hiss generation mechanism 11 First input plate 11e Window (holding part) 11s Stopper surface 12 Second input plate 12e Window (holding part) 12s Stopper surface 27s Stopper protrusion 28 Output side housing section 30 Intermediate parts 31, 32 Support plate (intermediate member) 34 Circular section 35 Support part 41,42 Spring set 411, 412, 422, 421 Spring (elastic member) 45 Spacer 51,52 Friction plate

Claims

1. A first rotating body; A second rotating body that is rotatable relative to the first rotating body; a plurality of elastic members arranged in a circumferential direction and elastically connecting the first rotating body and the second rotating body in a rotational direction; an intermediate member disposed axially between the first rotor and the second rotor so as to be rotatable relative to the first rotor and the second rotor; a hysteresis generating mechanism that is disposed between the first rotor and the second rotor in an axial direction and generates a hysteresis torque when the first rotor and the second rotor rotate relative to each other; Equipped with The intermediate member has an annular portion and a support portion, The annular portion is provided radially outward of the plurality of elastic members, the support portion is formed to protrude radially inward from the annular portion, and is disposed between at least two circumferentially adjacent elastic members to operate the adjacent elastic members in series; the hysteresis generating mechanism has at least one friction plate and a bush disposed between the first rotor and the second rotor in an axial direction, the friction plate being disposed radially inward of the support portion, and the bush being disposed radially inward of the friction plate so as to rotate in synchronization with the friction plate; The friction plate and the bush have a first axial side surface that contacts the first rotating body and a second axial side surface that contacts the second rotating body, The first rotor has a first input plate and a second input plate, which are circular and fixed to each other and disposed opposite to each other in the axial direction. the second rotor has a flange disposed axially between the first input plate and the second input plate, The intermediate member is a first intermediate plate disposed axially between the first input plate and the flange; a second intermediate plate disposed between the second input plate and the flange in an axial direction, the second intermediate plate being fixed by a rivet passing through a fixing hole formed in the support portion so as to be immovable in an axial direction and a rotational direction relative to the first intermediate plate; having Damper device.

2. the first intermediate plate has a first annular portion constituting the annular portion and a first support portion constituting the support portion, the first annular portion is disposed radially outward of the plurality of elastic members, and the first support portion is formed to protrude radially inward from the first annular portion, the second intermediate plate has a second annular portion constituting the annular portion and a second support portion constituting the support portion, the second annular portion is disposed radially outward of the plurality of elastic members, and the second support portion is formed to protrude radially inward from the second annular portion, a first spacer disposed axially between a first annular portion of the first intermediate plate and an outer circumferential portion of the flange; a second spacer disposed axially between a second annular portion of the second intermediate plate and an outer circumferential portion of the flange; Further equipped with The damper device according to claim 1 .

3. The friction plate is disposed between the first input plate and the flange, and is also disposed between the second input plate and the flange. The damper device according to claim 1 or 2.

4. the first rotating body has a plurality of arc-shaped holding portions that hold a plurality of the elastic members, the second rotating body has a plurality of accommodation portions provided corresponding to the plurality of holding portions and accommodating the plurality of elastic members; At least two of the elastic members housed and held in the housing portions and the holding portion are actuated in series by the intermediate member. The damper device according to any one of claims 1 to 3.

5. The first rotating body has a plurality of notches and a plurality of stopper portions, the notches having a predetermined length in a circumferential direction radially outward of an end region in a circumferential direction of the holding portion, the stopper portions being provided at positions corresponding to the notches in the circumferential direction and having a predetermined length in the circumferential direction, The second rotating body has a protrusion formed on an outer circumferential surface thereof so as to protrude in a radial direction, the protrusion being formed at a position overlapping with the stopper portion in the axial direction, and contacting an end surface of the stopper portion in the circumferential direction, thereby regulating a relative rotation angle between the first rotating body and the second rotating body. The damper device according to claim 4.

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