Damping device

Abstract

The present application relates to a damping device, so that in series damping device, can use and parallel work damping device used hysteresis generating mechanism as it is. The damping device (1) has input side plate (3), hub flange (4), two spring groups (41, 42), intermediate part (30), hysteresis generating mechanism (6). Intermediate part (30) is arranged between the input side plate (3) and the hub flange (4) in the axial direction. Hysteresis generating mechanism (6) is arranged between the input side plate (3) and the hub flange (4). The intermediate part (30) has a ring portion (34) and a support portion (35). The ring portion (34) is arranged radially outside the spring groups (41, 42). The support portion (35) is formed by protruding radially inward from the ring portion (34) and is arranged between at least two adjacent springs (411, 412) in the circumferential direction, so that the adjacent springs (411, 412) work in series.

Description

Technical Field

[0001] This invention relates to vibration damping devices. Background Technology

[0002] A vibration damping device is installed along the power transmission path of the vehicle to attenuate vibrations caused by torque variations from the drive source. The damping device typically includes an input rotating body and an output rotating body, multiple springs, and a hysteresis generating mechanism. The input and output rotating bodies are capable of rotating relative to each other within a specified angular range, and the multiple springs elastically connect these rotating bodies along the direction of rotation. The hysteresis generating mechanism produces a hysteresis torque when the input and output rotating bodies rotate relative to each other. Due to this hysteresis torque, vibrations caused by variations in the input torque are attenuated.

[0003] Furthermore, in such vibration damping devices, to further attenuate vibrations, it is preferable to increase the angle (maximum torsional angle) at which the input rotating body and the output rotating body can rotate relative to each other, i.e., to make the angle larger. Therefore, for example, a vibration damping device as shown in Patent Document 1 is provided. In the device of Patent Document 1, an intermediate plate is disposed between the input rotating body and the output rotating body along their axial direction. Moreover, due to this intermediate plate, the large angle is achieved by having at least two of the multiple springs operate in series (hereinafter simply referred to as "series connection").

[0004] Existing technical documents

[0005] Patent documents

[0006] Patent Document 1: Japanese Patent Application Publication No. 2018-96534 Summary of the Invention

[0007] The technical problem that the invention aims to solve

[0008] In vibration damping devices where multiple springs operate in parallel, an intermediate plate as shown in Patent Document 1 is unnecessary. Therefore, the hysteresis generating mechanism is positioned axially between the flange of the output rotating body and each of the pair of plates constituting the input rotating body. Such a hysteresis generating mechanism is widely used in general vibration damping devices, and is therefore preferably configured to be usable even in series-connected vibration damping devices.

[0009] However, in a series-connected vibration damping device, an intermediate plate is provided between the plate constituting the input rotating body and the flange of the output rotating body in the axial direction, so the hysteresis generation mechanism of the vibration damping device that works in parallel with multiple springs cannot be used in the same way.

[0010] The technical problem of the present invention is that the hysteresis generating mechanism used in parallel vibration damping devices can be used in series vibration damping devices without any difference.

[0011] Solutions for solving technical problems

[0012] (1) The vibration damping device of the present invention comprises a first rotating body, a second rotating body, a plurality of elastic components, an intermediate component, and a hysteresis generating mechanism. The second rotating body is capable of rotating relative to the first rotating body. The plurality of elastic components are arranged in a circumferential direction, elastically connecting the first rotating body and the second rotating body in the rotation direction. The intermediate component is rotatably disposed between the first rotating body and the second rotating body in the axial direction. The hysteresis generating mechanism is disposed between the first rotating body and the second rotating body in the axial direction, generating a hysteresis torque when the first rotating body and the second rotating body rotate relative to each other.

[0013] Furthermore, the intermediate component has an annular portion and a support portion. The annular portion is disposed radially outward of the plurality of elastic components. The support portion is formed by protruding radially inward from the annular portion and is disposed between at least two adjacent elastic components in the circumferential direction, so that the adjacent elastic components operate in series.

[0014] In this vibration damping device, for example, when torque is input to the first rotating body, the torque is transmitted to the second rotating body via multiple elastic components. When torque variation is input to the first rotating body, the torque variation is suppressed and vibration is attenuated due to the operation of the multiple elastic components and the hysteresis generation mechanism. In particular, through the intermediate component, at least two elastic components operate in series, so the torsional angle is maximized, further attenuating the vibration caused by torque variation.

[0015] Here, the intermediate component has an annular portion on the outer periphery of the device, which serves as the radially outer side of multiple elastic components. Adjacent elastic components are supported by a support portion protruding radially inward from this annular portion. Therefore, it is unnecessary to provide a portion constituting the intermediate component on the inner periphery of the device, allowing the components constituting the hysteresis generating mechanism to be arranged axially between the first and second rotating bodies. That is, the hysteresis generating mechanism used in parallel-operating vibration damping devices can be utilized unchanged in a series-connected vibration damping device.

[0016] (2) Preferably, the hysteresis generating mechanism has a friction member disposed axially between the first rotating body and the second rotating body. A first axial side of the friction member contacts the first rotating body, and a second axial side contacts the second rotating body.

[0017] Here, the friction component constituting the hysteresis generating mechanism can be positioned between the first rotating body and the second rotating body. That is, the hysteresis generating mechanism used in the parallel-operating vibration damping device can be utilized as is.

[0018] (3) Preferably, the first rotating body has a first input plate and a second input plate that are axially opposed to each other and fixed in the shape of circular plates. In this case, the second rotating body has a flange disposed axially between the first input plate and the second input plate. Furthermore, the intermediate component 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 so that it cannot move relative to the first intermediate plate in the axial and rotational directions.

[0019] When supporting the elastic member via an intermediate component, it is necessary to support the axial central portion of the elastic member. However, in the case where the intermediate component is constructed from a single plate, it overlaps with the second rotating body axially in order to support the axial central portion of the elastic member via the single plate. Therefore, in the case where the intermediate component is constructed from a single plate, it is impossible to support the axial central portion of the elastic member via the intermediate component.

[0020] Therefore, in this vibration damping device, an intermediate component is formed by a first intermediate plate and a second intermediate plate, and these intermediate plates are configured as flanges that clamp the second rotating body. In this case, the elastic component can be compressed by pressing it equally through the flange, the first intermediate plate, and the second intermediate plate.

[0021] (4) Preferably, the first intermediate plate has a first annular portion constituting an annular portion and a first support portion constituting a support portion. The first annular portion is disposed radially outside the plurality of elastic members. The first support portion is formed by protruding radially inward from the first annular portion. Furthermore, the second intermediate plate has a second annular portion constituting an annular portion and a second support portion constituting a support portion. The second annular portion is disposed radially outside the plurality of elastic members. The second support portion is formed by protruding radially inward from the second annular portion.

[0022] In this case, the vibration damping 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.

[0023] Here, in order to achieve miniaturization of the axial device, it is necessary to minimize the gap between adjacent axial components. On the other hand, in order to suppress the occurrence of unintended hysteresis torque, it is necessary to avoid frictional contact between components other than the hysteresis generating mechanism. Thus, in order to minimize the gap between components and avoid their frictional contact, the working accuracy and assembly accuracy of the components need to be managed with high precision.

[0024] Therefore, in this vibration damping device, a first spacer and a second spacer are provided between each of the first and second intermediate plates and the flange. By making these spacers thinner and forming them with components with a low coefficient of friction, unintended hysteresis torque can be suppressed without improving the working accuracy and assembly accuracy of the components, thus achieving axial miniaturization.

[0025] (5) Preferably, the friction component has a first friction plate and a second friction plate. The first friction plate is disposed between the first input plate and the flange, and the second friction plate is disposed between the second input plate and the flange.

[0026] (6) Preferably, the first rotating body has a plurality of arc-shaped holding portions, and the second rotating body has a plurality of receiving portions. The holding portions hold a plurality of elastic members. The receiving portions are provided corresponding to the plurality of holding portions and accommodate the plurality of elastic members. Furthermore, at least two of the plurality of elastic members respectively accommodated and held in the plurality of receiving portions and holding portions operate in series through an intermediate member.

[0027] (7) Preferably, the first rotating body has multiple slits and multiple stops. The slits have a predetermined length in the circumferential direction on the radially outer side of the end region of the retaining portion. Furthermore, the stops are provided at positions corresponding to the slits 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 the stops in the axial direction. Moreover, the protrusion limits the relative rotation angle between the first rotating body and the second rotating body by abutting against the circumferential end face of the stops.

[0028] Here, a stopping mechanism is configured such that the relative rotation angle (torsion angle) between the first and second rotating bodies is limited by a stopping portion of the first rotating body and a protrusion of the second rotating body. Here, the radial width of the central portion of the holding portion of the first rotating body is generally wider than that of its two ends in the circumferential direction. Therefore, at the first rotating body, the radial width of the radially outer side of the central portion of the holding portion in the circumferential direction becomes narrower. If a cutout and a stopping portion for the stopping mechanism are formed in this portion, the rotational strength of the first rotating body decreases.

[0029] Therefore, in this vibration damping device, a cutout and a stop are formed radially outward in the end region of the retaining part in the circumferential direction. Thus, the decrease in the rotational strength of the first rotating body caused by the retaining part and the cutout (stop) can be suppressed.

[0030] Invention Effects

[0031] In the present invention described above, the hysteresis generating mechanism used in the parallel-operating vibration damping device can be utilized in the series-connected vibration damping device as is. Attached Figure Description

[0032] Figure 1 This is a cross-sectional view of a vibration damping device according to an embodiment of the present invention.

[0033] Figure 2 This is the front view of the vibration damping device.

[0034] Figure 3 This is a 3D view of the first input board.

[0035] Figure 4 This is an exploded 3D view of the wheel hub flange.

[0036] Figure 5 It is an exploded three-dimensional view of the flange, intermediate components, and spacers.

[0037] Explanation of reference numerals in the attached figures

[0038] 1: Vibration damping device; 3: Input side plate (first rotating body); 4: Hub flange (second rotating body); 6: Hysteresis generating mechanism; 11: First input plate; 11e: Window (holding part); 11s: Stop surface; 12: Second input plate; 12e: Window (holding part); 12s: Stop surface; 27s: Stop protrusion; 28: Output side receiving part; 30: Intermediate component; 31, 32: Support plate (intermediate component); 34: Annular part; 35: Support part; 41, 42: Spring assembly; 411, 412, 422, 421: Spring (elastic component); 45: Spacer; 51, 52: Friction plate. Detailed Implementation

[0039] [Overall Structure]

[0040] Figure 1 This is a cross-sectional view of a vibration damping device 1 according to an embodiment of the present invention. Figure 2 A section view along line II. Furthermore... Figure 2 This is the front view of the vibration damping device 1, showing the components that make up part of it after they have been removed. Figure 1 In the middle, a drive source is arranged on the left side of the vibration damping device 1, and a speed change device is arranged on the right side.

[0041] In the following description, axial direction refers to the direction in which the rotation axis O of the vibration damping device 1 extends. Furthermore, circumferential direction refers to the circumferential direction of the circle centered on the rotation axis O, and radial direction refers to the radial direction of the circle centered on the rotation axis O. Additionally, the circumferential direction does not need to be perfectly aligned with the circumferential direction of the circle centered on the rotation axis O. Furthermore, the radial direction does not need to be perfectly aligned with the diametrical direction of the circle centered on the rotation axis O.

[0042] The vibration damping device 1 is a device for attenuating rotational fluctuations input from a drive source. The vibration damping 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 connection part 5, and a hysteresis generation mechanism 6.

[0043] <Input Side Panel 3>

[0044] 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 essentially annular circular plate components. The first input plate 11 and the second input plate 12 are arranged at a predetermined interval in the axial direction. The first input plate 11 and the second input plate 12 have the same basic structure and are formed symmetrically in the axial direction. Hereinafter, the first input plate 11 will be described in detail.

[0045] like Figures 1-3 As shown, the first input plate 11 has a circular plate portion 11a, a cylindrical portion 11b, and an outer peripheral extension portion 11c. Furthermore, Figure 3 This is a perspective view of the first input plate 11. The circular plate portion 11a has a circular opening 11d at its center. The cylindrical portion 11b extends axially from the outer peripheral end of the circular plate portion 11a toward the second input plate 12. The outer peripheral extension portion 11c extends radially outward from the axial front end of the cylindrical portion 11b.

[0046] Furthermore, two arc-shaped windows 11e (an example of a retaining portion) are formed in the radial middle portion of the circular plate portion 11a. Each window 11e is formed opposite to the other in the radial direction. Moreover, the radial width of the central portion of the window 11e is larger than that of its two ends in the circumferential direction. In other words, the distance between the outer peripheral surface of the window 11e and the outer peripheral surface of the plate 11 is smaller in the central portion of the window 11e than at its two ends.

[0047] In addition, according to Figure 2 and Figure 3 It can be seen that four cuts 11f are formed radially outward at both ends of the window portion 11e at the outer periphery of the circular plate portion 11a and the cylindrical portion 11b. The cuts 11f have a predetermined length in the circumferential direction.

[0048] Four fixing portions 11g (an example of a stop portion) are formed on a portion of the outer peripheral extension 11c. The fixing portions 11g are arranged at positions corresponding to the cut 11f in the circumferential direction. More specifically, the fixing portions 11g are formed simultaneously with the cut 11f when the cut 11f is punched by pressure forming. Furthermore, the circumferential end face of the fixing portion 11g serves as a stop surface 11s.

[0049] As previously described, the second input plate 12 has a structure substantially the same as the first input plate 11, having a circular plate portion 12a, a cylindrical portion 12b, an outer peripheral extension portion 12c, an opening 12d, a window portion 12e, a cutout 12f, a fixing portion 12g, and a stop surface 12s. Furthermore, the first input plate 11 and the second input plate 12 are connected by a plurality of rivets (not shown) passing through the fixing portions 11g and 12g, enabling them to rotate integrally with the drive plate 2.

[0050] In addition, such as Figure 3 As shown, at the first input plate 11, four engaging holes 11h are formed on the radially inner side of the window portion 11e, and four cutouts 11i opening radially inward are formed on the inner peripheral end face. In addition, a plurality of four engaging holes 12h are formed at the inner peripheral end of the second input plate 12.

[0051] <Hub flange 4>

[0052] like Figure 1 , Figure 2 and Figure 4 As shown, the hub flange 4 has a hub 21 and a flange 22. Additionally, Figure 4 This is an exploded perspective view of the hub flange 4. The hub flange 4 can rotate relative to the first input plate 11 and the second input plate 12 (hereinafter, these two plates 11 and 12 may also be referred to as "input side plates 3") within a specified angle range.

[0053] -Wheel hub 21-

[0054] The hub 21 has a cylindrical portion 24 and a circular plate portion 25. A spline hole 24a is formed on the inner circumferential surface of the cylindrical portion 24. In addition, the cylindrical portion 24 has openings 11d and 12d that pass through the center portions of the first input plate 11 and the second input plate 12. The circular plate portion 25 is formed by protruding radially outward from the axial center portion of the cylindrical portion 24. A plurality of teeth 25a and two cuts 25b are formed in the circular plate portion 25. The two cuts 25b are arranged opposite each other across the rotation axis O and open radially outward.

[0055] -Flange 22-

[0056] The flange 22 is located radially outside the circular plate portion 25 of the hub 21, at a position where it overlaps with the circular plate portion 25 in the axial direction. The flange 22 has a circular plate portion 26, a pair of protrusions 27, and a pair of output-side receiving portions 28.

[0057] The circular plate portion 26 is formed in an annular shape, and has multiple engaging portions 26a and two slits 26b formed on its inner circumferential surface. The teeth 25a of the hub 21 engage with the engaging portions 26a at a predetermined gap. The two slits 26b are formed opposite to each other across the rotation axis O. The two slits 26b are configured to face the slits 25b of the hub 21 and open radially inward.

[0058] A spring 29 is disposed in the space formed by the cutouts 25b and 26b of the hub 21 and the flange 22 (see reference). Figure 1 The spring 29 elastically connects the hub 21 and the flange 22 in the circumferential direction. In addition, the stiffness of the spring 29 is set to be less than the stiffness of the elastic connection part 5.

[0059] More specifically, the hub 21 and flange 22 can rotate relative to each other at a rotation angle corresponding to the gap between the tooth 25a of the hub 21 and the engagement portion 26a of the flange 22, and the spring 29 operates within this rotation angle range. Furthermore, when the hub 21 and flange 22 are twisted at an angle corresponding to the aforementioned gap, the tooth 25a abuts against the wall of the engagement portion 26a, after which relative rotation between the hub 21 and flange 22 is prohibited, and the two components 21 and 22 rotate as a single unit.

[0060] A pair of protrusions 27 are formed by projecting radially outward from the outer peripheral surface of the circular plate portion 26 and are positioned opposite each other across the rotation axis O. On the outer peripheral surface of each protrusion 27, a stop protrusion 27s is formed that projects radially outward. This stop protrusion 27s is formed at a position where it overlaps axially with the fixing portions 11g and 12g of the input side plate 3. Therefore, if the stop protrusion 27s abuts against the stop surfaces 11s and 12s, which are the two end faces of the fixing portion 11g, the relative rotation of the hub flange 4 relative to the input side plate 3 is prohibited. That is, the stop surface 11s and 12s and the stop protrusion 27s constitute a stop mechanism.

[0061] A pair of output-side receiving portions 28 are formed between a pair of protrusions 27 in the circumferential direction. The output-side receiving portion 28 has an end face support portion 28a and an outer peripheral support portion 28b. The end face support portion 28a is the end face of the protrusion 27 in the circumferential direction. The outer peripheral support portion 28b is formed to extend from the outer peripheral end of the end face support portion 28a in each of the two circumferential directions by a predetermined distance.

[0062] <Elastic Connector 5>

[0063] like Figure 1 and Figure 5 As shown, the elastic connection part 5 includes 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) constituting the intermediate component 30, a first spring assembly 41, a second spring assembly 42, and a pair of spacers 45. The elastic connection part 5 elastically connects the input side plate 3 and the hub flange 4 in the rotational direction.

[0064] -Intermediate component 30 (support plates 31, 32)-

[0065] 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. Furthermore, the two support plates 31 and 32 are capable of rotating relative to the input side plate 3 and the hub flange 4.

[0066] The first support plate 31 and the second support plate 32 have the same structure, so they will be referred to as "intermediate component 30" in the following description.

[0067] The intermediate component 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 each other across the rotation axis O and are formed by protruding radially inward from the annular portion 34 by a predetermined distance. 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 passing through the hole 35a. The two protrusions 36 are arranged at a 90-degree interval from the two support portions 35. The protrusions 36 are formed by protruding radially inward from the annular portion 34 by approximately the same distance as the support portions 35, thereby suppressing the decrease in strength of each support plate 31, 32.

[0068] Furthermore, a pair of intermediate receiving portions 38 are formed through the two spaces between the two protrusions 36 in the circumferential direction. The intermediate receiving portions 38 are positioned corresponding to the window portions 11e and 12e of the input side plate 3 and the output side receiving portion 28 of the flange 22. Each of the pair of intermediate receiving portions 38 houses a first spring assembly 41 and a second spring assembly 42 (see reference). Figure 2 ).

[0069] -Spring assembly 41, 42-

[0070] The first spring assembly 41 and the second spring assembly 42 are respectively housed in the output-side receiving portion 28 of the flange 22 and the intermediate receiving 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 assembly 41 and 42 has an R1 spring 411 and 421 arranged on a first side (hereinafter R1 side) in the circumferential direction, and an R2 spring 412 and 422 arranged on a second side (hereinafter R2 side) in the circumferential direction.

[0071] Furthermore, in a neutral state with no torsional angle of the input side plate 3 and the hub flange 4, at each spring assembly 41, 42, the R1 side end face of the R1 springs 411, 421 abuts against the R1 side end face of the window portions 11e, 12e and the output side receiving portion 28, and the R2 side end face abuts against the support portion 35 of the pair of support plates 31, 32. Additionally, the R1 side end face of the R2 springs 412, 422 abuts against the support portion 35 of the pair of support plates 31, 32, and the R2 side end face abuts against the R2 side end face of the window portions 11e, 12e and the output side receiving portion 28.

[0072] With the configuration of springs 411, 412, 421, and 422 as described above, and the two support plates 31 and 32, when the input side plate 3 and the hub flange 4 twist, springs R1 411 and R2 412 of the first spring group 41 work in series, and springs R1 421 and R2 422 of the second spring group 42 work in series. On the other hand, the first spring group 41 and the second spring group 42 work in parallel.

[0073] -Spacer 45-

[0074] A pair of spacers 45 are respectively disposed between the annular portion 34 of the first support plate 31 and the outer periphery of the flange 22 in the axial direction. The spacers 45 are annular with a predetermined width in the radial direction and are formed of a resin component with a low coefficient of friction. Although the spacers 45 are held between the outer periphery of each support plate 31, 32 and flange 22 and abut against the two components, they are able to rotate freely.

[0075] By providing this spacer 45, unintended hysteresis torque caused by direct contact between the support plates 31, 32 and flange 22 can be avoided. Furthermore, although the spacer 45 and each component 31, 32, 22 are in frictional contact, the spacer 45 is made of a resin with a low coefficient of friction, so the hysteresis torque caused by these frictional contacts can be suppressed to a small extent.

[0076] <Hysteresis Generating Mechanism 6>

[0077] like Figure 1 As shown, the hysteresis generating mechanism 6 has a first friction plate 51, a second friction plate 52, a first bushing 61, a second bushing 62, a support plate 63, an outer peripheral conical spring 64, and an inner peripheral conical spring 65.

[0078] A first friction plate 51 is disposed axially between the first input plate 11 and the flange 22. An annular resin component is fixed to the first friction plate 51, and this resin component contacts the flange 22. A plurality of protrusions 51a are formed at the outer peripheral end of the first friction plate, protruding toward the first input plate 11, and these protrusions 51a engage with engaging holes 11h formed in the first input plate 11. Therefore, the first friction plate 51 rotates synchronously with the first input plate 11.

[0079] The first bushing 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 circular plate portion 25 of the hub 21. Multiple protrusions projecting radially outward are formed on the outer circumferential surface of the first bushing 61, and these protrusions can abut against a portion of the inner circumferential end of the first friction plate 51. This restricts the movement of the first bushing 61 toward the second input plate 12. Furthermore, the first bushing 61 and the first input plate 11 partially engage with each other. Therefore, the first bushing 61 rotates synchronously with the first input plate 11 and the first friction plate 51.

[0080] The second friction plate 52 is disposed axially between the second input plate 12 and the flange 22. An annular resin component is fixed to the second friction plate 52, and this resin component contacts the flange 22. Four protrusions 52a are formed on the inner circumferential end of the second friction plate 52, protruding towards the second input plate 12, and these protrusions 52a engage with engaging holes 12h formed in the second input plate 12. Therefore, the second friction plate 52 rotates synchronously with the second input plate 12.

[0081] The second bushing 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 circular plate portion 25 of the hub 21. Multiple protrusions projecting radially outward are formed on the outer circumferential surface of the second bushing 62, and these protrusions engage with a portion of the second friction plate 52. Thus, the second bushing 62 rotates synchronously with the second friction plate 52 and the second input plate 12.

[0082] A support plate 63 and an outer peripheral conical spring 64 are disposed axially between the second friction plate 52 and the second input plate 12. More specifically, the support plate 63 is configured to contact the second friction plate 52, and the outer peripheral conical spring 64 is disposed between the support plate 63 and the second input plate 12. The support plate 63 is formed in a ring shape, and the outer peripheral conical spring 64 presses the second friction plate 52 toward the flange 22 via the support plate 63.

[0083] An inner circumferential conical spring 65 is disposed axially between the second bushing 62 and the second input plate 12. Through this inner circumferential conical spring 65, the second bushing 62 is pressed against the circular plate portion 25 of the hub 21.

[0084] [action]

[0085] When the input torque or torque variation is small, only the spring 29 disposed between the hub 21 and the flange 22 operates. That is, the input side plate 3 rotates integrally with the flange 22, and the flange 22 and the hub 21 rotate relative to each other at an angle equivalent to the gap between the tooth 25a and the engagement portion 26a. Here, the first bushing 61 and the second bushing 62 make frictional contact with the circular plate portion 25 of the hub 21, generating a hysteresis torque caused by them.

[0086] If the torque variation increases, the torsional angle between the flange 22 and the hub 21 increases, and the tooth 25a abuts against the wall of the engaging portion 26a. Then, the spring 29 stops working, and the hub 21 and flange 22 rotate as a unit. Furthermore, relative rotation occurs between the input side plate 3 and the hub flange 4. The two springs 411 and 412 of the first spring group 41 operate in series via the intermediate component 30 (first support plate 31 and second support plate 32), and the two springs 421 and 422 of the second spring group 42 also operate in series via the intermediate component 30. In addition, the first spring group 41 and the second spring group 42 operate in parallel. In this state, the first friction plate 51 and the second friction plate 52 rotate synchronously with the input side plate 3, so the two friction plates 51 and 52 come into frictional contact with the flange 22. Therefore, a hysteresis torque is generated due to these frictional contacts.

[0087] Furthermore, if the torsional angle between the input side plate 3 and the hub flange 4 increases further, the stop protrusion 27s formed on the outer peripheral surface of the flange 22 abuts against the stop surfaces 11s and 12s of the input side plate 3. As a result, relative rotation between the input side plate 3 and the flange 22 is prohibited.

[0088] Furthermore, during the above-described operation, the first support plate 31 and the second support plate 32 rotate relative to the flange 22. However, since a spacer 45 is provided between the two support plates 31, 32 and the flange 22, the hysteresis torque between them can be suppressed to a small extent.

[0089] [Other Implementation Methods]

[0090] The present invention is not limited to the above-described embodiments, and various modifications or variations can be made without departing from the scope of the present invention.

[0091] (a) The number of spring assemblies is not limited to the embodiment described above. Furthermore, the number of springs constituting each spring assembly is also not limited to the embodiment described above.

[0092] (b) In the embodiment described, the hub flange 4 is divided into a hub 21 and a flange 22, but the invention can also be applied to a one-piece hub flange.

[0093] (c) In the embodiment described above, a spacer is provided between each support plate and the flange, but the spacer can also be omitted.

[0094] (d) Regarding the structure of the hysteresis generating mechanism, it is not limited to the described embodiment, but can also apply the structure of various hysteresis generating mechanisms of general parallel-operating vibration damping devices.

Claims

1. A vibration damping device, comprising: First body of revolution; The second rotating body is capable of rotating relative to the first rotating body; Multiple elastic components are arranged along the circumferential direction to elastically connect the first rotating body and the second rotating body along the rotation direction. An intermediate component is rotatably disposed between the first rotating body and the second rotating body along their axial directions; as well as A hysteresis generating mechanism is disposed axially between the first rotating body and the second rotating body, and generates a hysteresis torque when the first rotating body and the second rotating body rotate relative to each other. The intermediate component has an annular portion and a supporting portion. The annular portion is disposed on the radially outer side of the plurality of elastic components. The support portion is formed by protruding radially inward from the annular portion and is disposed between at least two adjacent elastic members in the circumferential direction, so that the adjacent elastic members operate in series. The hysteresis generating mechanism has a friction member disposed axially between the first rotating body and the second rotating body, wherein a first axial side of the friction member contacts the first rotating body and a second axial side contacts the second rotating body. The first rotating body has a first input plate and a second input plate that are axially opposed to each other and fixed in the shape of circular plates. The second rotating body has a flange disposed axially between the first input plate and the second input plate. The intermediate component has: A first intermediate plate is disposed axially between the first input plate and the flange; and The second intermediate plate is disposed axially between the second input plate and the flange, and is fixed in the axial and rotational directions by rivets passing through fixing holes formed in the support portion, so that it cannot move relative to the first intermediate plate.

2. The vibration damping device according to claim 1, wherein, 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 outside the plurality of elastic members, and the first support portion is formed by protruding 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 by protruding radially inward from the second annular portion. The vibration damping device also includes: A first spacer is disposed axially between a first annular portion of the first intermediate plate and the outer periphery of the flange; and The second spacer is disposed axially between the second annular portion of the second intermediate plate and the outer periphery of the flange.

3. The vibration damping device according to claim 1 or 2, wherein, The friction component has a first friction plate disposed between the first input plate and the flange, and a second friction plate disposed between the second input plate and the flange.

4. The vibration damping device according to claim 1 or 2, wherein, The first rotating body has a plurality of arc-shaped retaining portions for holding the plurality of elastic components. The second rotating body has multiple receiving portions that are disposed corresponding to the multiple holding portions and accommodate the multiple elastic components. At least two of the elastic components, which are respectively housed and held in the plurality of the housing portions and the holding portions, operate in series through the intermediate component.

5. The vibration damping device according to claim 4, wherein, The first rotating body has multiple slits and multiple stops. The slits have a predetermined length in the circumferential direction on the radially outer side of the end region of the retaining part. The stops are disposed at positions corresponding to the slits in the circumferential direction and have a predetermined length in the circumferential direction. The second rotating body has a protrusion that protrudes radially outward from the outer peripheral surface of the flange and is formed at a position that overlaps with the stop in the axial direction. The protrusion restricts the relative rotation angle between the first rotating body and the second rotating body by abutting against the end face of the stop in the circumferential direction.

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