CN213206445U

CN213206445U - Vibration damping device

Info

Publication number: CN213206445U
Application number: CN202021253430.1U
Authority: CN
Inventors: 佐伯智洋; 岩崎靖久
Original assignee: Aisin Seiki Co Ltd
Current assignee: Aisin Corp
Priority date: 2019-08-09
Filing date: 2020-07-01
Publication date: 2021-05-14
Anticipated expiration: 2030-07-01
Also published as: JP2021028522A; JP7287176B2; DE202020104108U1

Abstract

Provided is a vibration damping device which has a compact shaft length and can stably generate various varying hysteresis torques. The vibration damping device is provided with: a first rotating body having at least a first plate and a second plate that rotate around a rotation axis; a second rotating body that rotates relative to the first rotating body; a first thrust member having a first elastic body, a fitting portion fitted to the first rotating body, and a first sliding surface sliding on the second rotating body, the first sliding surface being pressed against the second rotating body by the urging member to generate a first sliding torque; a control plate having a second sliding surface sliding on the first plate, a radially extending portion, and an axially extending portion, and generating a second sliding torque; and a second thrust member having an engagement portion that receives an end portion of the axially extending portion and a third sliding surface that slides on the second plate and generates a third sliding torque.

Description

Vibration damping device

Technical Field

The technology disclosed in the present application relates to a vibration damping device.

Background

In a vehicle or the like, a vibration damping device that absorbs vibration of torque transmitted from a drive source such as an engine to a transmission is provided in a torque transmission path between the drive source and the transmission, and the vibration damping device is incorporated in, for example, a clutch device.

As a general structure of the vibration damping device, the following techniques are known: the coil spring is interposed between a disk plate as an input member and a hub as an output member which are rotatable relative to each other, and absorbs and attenuates torque fluctuations due to elastic deformation of the coil spring. In addition to elastic deformation of the coil spring, a technique is known in which a slip torque (hysteresis torque) due to relative rotation between the disk plate and the hub is generated, and this torque variation is further absorbed.

For example, patent document 1 discloses a vibration damping device including, as main components, a first rotating member (reference numeral 1 in patent document 1) on an input side of power transmission, a second rotating member (reference numeral 2 in patent document 1) on an output side of the power transmission, two control plates (reference numerals 31 and 32 in patent document 1), first sliding members (reference numerals 6 and 7 in patent document 1) that generate a first sliding torque, second sliding members (reference numerals 8 and 9 in patent document 1) that generate a second sliding torque larger than the first sliding torque, and an elastic member 57 using a conical spring.

Documents of the prior art

Patent document

Patent document 1: japanese patent No. 6471486 Specification

Technical problem to be solved by the utility model

However, in the damper device described in patent document 1, two control plates, a first slide member, a second slide member, and an elastic member 57 are accommodated between the first rotating member and the second rotating member in the axial direction, and therefore, the axial length of the damper device becomes long, which causes a technical problem when the damper device is mounted on a vehicle or the like.

SUMMERY OF THE UTILITY MODEL

Therefore, according to the embodiments, a vibration damping device having a compact shaft length and capable of stably generating various varying hysteresis torques is provided.

Means for solving the problems

The vibration damping device of one aspect includes: a first rotating body having at least a first plate that rotates about a rotation axis and a second plate that is disposed opposite to the first plate and rotates integrally with the first plate about the rotation axis; a second rotating body that relatively rotates with respect to the first rotating body about the rotation axis; a first elastic body elastically connecting the first rotating body and the second rotating body in a rotational direction; a first thrust member that has a fitting portion fitted to the first rotating body and a first sliding surface that slides on the second rotating body and that rotates integrally with the first rotating body, the first sliding surface being pressed against the second rotating body by a biasing member supported by the first rotating body, and that generates a first sliding torque when the first rotating body and the second rotating body rotate relative to each other; a control plate having a second sliding surface that slides on the first plate, a radially extending portion that is disposed between the first plate and the second rotating body in the axial direction and extends in the radial direction so as to be in contact with the first elastic body, and an axially extending portion that penetrates the second rotating body and extends in the axial direction, and that generates a second sliding torque by rotating the first rotating body relative to the second rotating body in a predetermined direction only when the first rotating body and the second rotating body rotate relative to each other in the predetermined direction; and a second thrust member having an engagement portion that receives an end portion of the axially extending portion and a third sliding surface that slides on the second plate, the second thrust member being configured to rotate in the predetermined direction integrally with the control plate relative to the first rotating body to generate a third sliding torque.

According to this configuration, the number of parts can be reduced by providing one control plate, and the vibration damping device having a compact axial length can be provided. Further, in the vibration damping device of this configuration, the first slip torque that is small is always generated when the first rotating body and the second rotating body relatively rotate, and the second slip torque and the third slip torque are additionally generated in a particular case where the first rotating body and the second rotating body relatively rotate in a predetermined direction, and in this particular case, a large hysteresis torque obtained by summing up the first slip torque, the second slip torque, and the third slip torque can be generated. Therefore, the vibration damping device of this configuration can generate a hysteresis torque that varies in various ways depending on the situation. The large hysteresis torque (the total torque of the first slip torque, the second slip torque, and the third slip torque) can be used, for example, when large vibration and noise generated when an engine of a vehicle or the like (particularly, a hybrid vehicle) is started are suppressed.

In the vibration damping device according to one aspect, it is preferable that the axially extending portion is compressed in advance in the axial direction, the second sliding surface is pressed against the first plate by the axially extending portion compressed in advance, and the third sliding surface is pressed against the second plate by the axially extending portion compressed in advance.

With this configuration, it is possible to provide a vibration damping device that effectively generates the second slip torque and the third slip torque.

In the vibration damping device according to one aspect, it is preferable that a second elastic body compressed in advance is further disposed between the second rotating body and the second thrust member.

With this configuration, it is possible to provide a vibration damping device that more efficiently generates the third slip torque.

In the vibration damping device according to one aspect, it is preferable that the second rotating body includes a guide portion that comes into contact with the axially extending portion and guides the relative rotation of the control plate in the predetermined direction when the second rotating body rotates relative to the first rotating body in the predetermined direction by a predetermined torsion angle or more.

With this configuration, when the first rotating body and the second rotating body rotate relatively in a predetermined direction, the control plate can stably rotate relatively in the predetermined direction with respect to the first rotating body. As a result, the second slip torque and the third slip torque can be generated stably.

In the vibration damping device according to one aspect, it is preferable that the second sliding surface is provided radially outward of the radially extending portion.

With this configuration, since the distance between the rotation shaft and the second sliding surface is increased, the centrifugal force acting on the first rotating body and the control plate affects the second sliding torque, and the magnitude of the second sliding torque can be increased. Further, by adjusting the position of the second sliding surface, the magnitude of the second sliding torque can be varied.

In the vibration damping device according to one aspect, it is preferable that the second rotating body includes a cylindrical portion extending in the axial direction and a disc portion extending in the radial direction from the cylindrical portion, the fitting portion of the first thrust member is fitted to the second plate, and the first sliding surface faces a radially inner end portion of the disc portion of the second rotating body.

With this configuration, the first sliding torque generated constantly when the first rotating body and the second rotating body relatively rotate can be made to be a small hysteresis torque in conjunction with the decrease in the distance between the rotating shaft and the first sliding surface. The first slip torque can be used to suppress small vibration, noise, and the like generated during normal running of the vehicle and the like.

Effect of the utility model

According to the embodiments, a vibration damping device having a compact shaft length and capable of stably generating various varying hysteresis torques can be provided.

Drawings

Fig. 1 is a schematic plan view schematically showing the structure of a vibration damping device according to an embodiment.

Fig. 2 is a schematic plan view schematically showing a configuration in which a part of the components of the vibration damping device shown in fig. 1 is omitted.

Fig. 3 is a schematic cross-sectional view schematically showing the structure of the vibration damping device shown in fig. 1 viewed from the X-X' line to the R side.

Fig. 4 is a schematic perspective view showing the vibration damping device according to the embodiment in an exploded manner.

Fig. 5 is an enlarged perspective view of a control plate and a second thrust member of the vibration damping device according to the embodiment.

Fig. 6A is a schematic plan view schematically showing a state in which the first rotating body and the second rotating body do not rotate relative to each other in the damper device according to the first embodiment.

Fig. 6B is a schematic plan view schematically showing a state in which the second rotating body is rotated by a torsion angle θ 1 ° relative to the first rotating body in the positive direction in the vibration damping device according to the embodiment.

Fig. 6C is a schematic plan view schematically showing a state in which the second rotating body is rotated by a torsion angle θ 2 ° relative to the first rotating body in the positive direction in the vibration damping device according to the first embodiment.

Fig. 6D is a schematic plan view schematically showing a state in which the second rotating body is rotated by a torsion angle θ 3 ° in a negative direction with respect to the first rotating body in the damper device according to the first embodiment.

Fig. 6E is a schematic plan view schematically showing a state in which the second rotating body is rotated by a torsion angle θ 4 ° in the negative direction with respect to the first rotating body in the vibration damping device according to the embodiment.

Fig. 6F is a schematic plan view schematically showing a state in which the relative rotation of the second rotating body with respect to the first rotating body is eliminated from the state of fig. 6E in the damper device according to the embodiment.

Fig. 7 is a schematic characteristic diagram schematically showing torsional characteristics in the vibration damping device according to the embodiment.

Fig. 8 is a schematic cross-sectional view schematically showing the structure of a vibration damping device according to a second embodiment.

Fig. 9 is a schematic plan view schematically showing the structure of the vibration damping device according to the second embodiment (a part of the components is omitted).

Fig. 10 is a schematic plan view showing an enlarged scale of a control plate of the damper device according to the second embodiment.

Fig. 11 is a schematic cross-sectional view schematically showing the structure of a vibration damping device according to a third embodiment.

Fig. 12 is an enlarged schematic front view of a second elastic body used in a vibration damping device according to a third embodiment.

Fig. 13 is an enlarged perspective view of a control plate, a second thrust member, and an elastic member used in the damper device according to the fourth embodiment.

Description of the symbols

1 vibration damping device

2 flywheel

100 first rotating body (disc plate)

100A first plate

100B second plate

101 liner plate

105 incision

106 restriction part

200 second rotating body (hub)

202 cylindrical part

205 circular plate part

206 a-206 d aperture

207a to 207d protrusions

208a to 208d groove portions

209a to 209d guide

300 control panel

301 second sliding surface

302a to 302d radial extension

303a to 303d axial extension

400 first elastomer

500 first thrust member

501 fitting part

502a first sliding surface

600 second thrust component

601 joint

602 third sliding surface

700 force applying member

800 second elastomer

O-shaped rotating shaft

Detailed Description

Hereinafter, embodiments will be described with reference to the drawings. In the drawings, the same reference numerals are given to the common components. Note that, for convenience of description, components shown in a certain drawing may be omitted in other drawings. Note that the drawings are not necessarily drawn to a correct scale.

1. Structure of vibration damper

An outline of the overall structure of the vibration damping device according to the embodiment will be described with reference to fig. 1 to 5. Fig. 1 is a schematic plan view schematically showing the structure of a vibration damping device 1 according to an embodiment. Fig. 2 is a schematic plan view schematically showing a configuration in which a part of the components of the vibration damping device 1 shown in fig. 1 is omitted. Fig. 3 is a schematic cross-sectional view schematically showing the structure of the vibration damping device 1 shown in fig. 1 viewed from the X-X' line to the R side. Fig. 4 is a schematic perspective view showing the vibration damping device 1 according to the embodiment in an exploded manner. Fig. 5 is an enlarged perspective view of the control plate 300 and the second thrust member 600 of the damper device 1 according to the embodiment.

A damper device 1 according to an embodiment is provided in a power transmission path between a drive source (not shown) such as an engine or a motor and a transmission or the like, and the damper device 1 transmits (outputs) power from the drive source to the transmission or the like via a flywheel 2 (see fig. 3).

The vibration damping device 1 absorbs and damps the torque vibration. As shown in fig. 1 to 5, the vibration damping device 1 mainly includes: a disc plate 100 as a first rotating body to which power from a flywheel is transmitted, a hub 200 as a second rotating body, a control plate 300, a first elastic body 400, a first thrust member 500, a second thrust member 600, and a biasing member 700. In the present specification, the axial direction means a direction extending parallel to the rotation axis O, the radial direction means a direction perpendicular to the rotation axis O, and the circumferential direction means a direction around the rotation axis O.

The flywheel 2 is an annular plate member fixed to a drive shaft Z connected to a drive source by a bolt 3.

As shown in fig. 3, the power transmitted from the drive shaft Z to the flywheel 2 is transmitted to the disk plate 100 via the cover plate 10 and the first friction member 20, and the cover plate 10 is fixed to the flywheel 2 by the bolts 4 and rotates integrally with the flywheel 2. Further, the pressure plate 30 is fixed to the cover plate 10, and the cover plate 10 and the pressure plate 30 are configured to rotate integrally. The support plate 11 together with the cover plate 10 is also fastened to the flywheel 2 by means of bolts 4, the support plate 11 supporting the disk spring 40. The disc spring 40 biases the pressure plate 30 via the second friction member 21 so as to press the pressure plate 30 against a backing plate 101 of a disc plate 100 described later, and transmits the power transmitted to the flywheel 2 to the disc plate 100 (backing plate 101) together with the cover plate 10.

In addition, when the damper device 1 cannot completely absorb torque variation in the torsional direction, the support plate 11, the pressure plate 30, and the disc springs 40 can function as limiters that generate slip (block the transmission of power from the cover plate 10 and the pressure plate 30 to the disc plate 100). In addition, the limiter may be combined with a conventionally known structure.

1-1. disc plate 100

In the damper device 1, as described above, power from a drive source such as an engine or a motor is transmitted to the disc plate 100, which is the first rotating body, disposed on the most upstream side in the power transmission path via the flywheel 2. The disc plate 100 is formed of, for example, a metal material, and as shown in fig. 1 to 4, the disc plate 100 is provided so as to be rotatable about the rotation axis O with a hub 200 or the like as a second rotating body described later interposed therebetween. The disk plate 100 includes a first plate 100A and a second plate 100B (the second plate 100B is disposed to face the first plate 100A in the axial direction) as a pair of substantially disk-shaped plate members provided on both sides of the hub 200 in the axial direction. As shown in fig. 3 and 4, the first plate 100A and the second plate 100B are provided to have a symmetrical shape in the axial direction, and a substantially annular backing plate 101 is interposed between the two, and the backing plate 101 is capable of appropriately adjusting the positions in the axial direction of the two, and the first plate 100A and the second plate 100B are coupled near the outer periphery by a plurality of rivets 120 so as to be integrally rotatable.

When power from a drive source such as an engine or a motor is transmitted from the cover plate 10 and the pressure plate 30 to the lining plate 101 via the first friction material 20 and the second friction material 21 provided on the lining plate 101, the power is transmitted from the lining plate 101 to the first plate 100A and the second plate B near the rivet 120.

The first plate 100A and the second plate 100B cooperate with each other, and as shown in fig. 1 and 4, the first plate 100A and the second plate 100B have shapes bulging in the axial direction so as to form housing areas (four housing areas are shown in the example shown in fig. 1) for housing a first elastic body 400 described later, respectively, in correspondence with the areas I to IV. Each of the housing regions extends substantially linearly or substantially in an arc shape along the circumferential direction of the disc plate 100 to house the elastic body 410 extending along the circumferential direction of the disc plate 100. As shown in fig. 1, the regions I to IV are four regions each having a fan shape of substantially 90 degrees when the vibration damping device 1 is viewed from the top surface.

This will be described in detail with reference to fig. 1. The first plate 100A and the second plate 100B are formed with a first housing area 102a, a second housing area 102B, a third housing area 102c, and a fourth housing area 102d extending in the circumferential direction, respectively, corresponding to the areas I to IV. As will be described later, in the hub 200,

window holes

206a, 206b, 206c, and 206d corresponding to the first housing area 102a, the second housing area 102b, the third housing area 102c, and the fourth housing area 102d are provided in the respective areas.

As shown in fig. 1, focusing on the region IV, the first plate 100A and the second plate 100B include one end surface (fourth end surface) 104d as a sidewall surrounding the fourth housing region 102d₁And the other end face (fourth other end face) 104d opposed thereto₂. These fourth end faces 104d₁And a fourth other end face 104d₂For example, the axis of the disc plate 100 is aligned withAnd extend the same.

Similarly, focusing on the region I, the first plate 100A and the second plate 100B include one end surface (first end surface) 104a as a side wall surrounding the first housing region 102a₁And the other end face (first other end face) 104a opposed thereto₂Focusing on the region II, the first plate 100A and the second plate 100B include one end surface (second end surface) 104B as a sidewall surrounding the second housing region 102B₁And the other end face (second other end face) 104b opposed thereto₂Focusing on the region III, the first plate 100A and the second plate 100B include one end surface (third end surface) 104c as a sidewall surrounding the third housing region 102c₁And the other end face (third other end face) 104c opposite thereto₂. These side walls abut (engage) with a first elastic body 400 described later.

As shown in fig. 3, the liner plate 101 of the disc plate 100 is disposed at a position coaxial with the hub 200 (on the same straight line in the radial direction). Therefore, as shown in fig. 2 and 4, a slit 105 is provided in each of the regions I to IV of the backing plate 101, and the slit 105 allows movement (relative rotation) in the circumferential direction of the hub 200. The outer edge of the notch 105 functions as a restricting portion 106, and the restricting portion 106 restricts excessive relative rotation of the hub 200.

The first plate 100A is provided with a first fitting hole 111, the first fitting hole 111 accommodates a support member 130, and the support member 130 supports the first plate 100A in the axial direction and the radial direction and supports a control plate 300, which will be described later, in the radial direction. The support member 130 is fitted into the first fitting hole 111 to support the first plate 100A, and rotates integrally with the first plate 100A (disk plate 100) about the rotation axis O.

Further, it is preferable that the concave-convex surface 110x is provided on the surface of the inner surface 110A of the first plate 100A facing the second sliding surface 301 of the control plate 300, corresponding to the shape of the second sliding surface 301. The concave-convex surface 110x will be described in detail later.

The second plate 100B is provided with a second fitting hole 112 for receiving a first thrust member 500 described later. The fitting portion 501 of the first thrust member 500 is fitted into the second fitting hole 112, and the first thrust member 500 and the second plate 100B (the disk plate 100) rotate integrally.

Further, it is preferable that the concave-convex surface 110y is provided on the surface of the inner surface 110B of the second plate 100B facing the third sliding surface 602 of the second thrust member 600 in correspondence with the shape of the third sliding surface 602. The concave-convex surface 110y will be described in detail later.

The inner surface 110B of the second plate 100B supports a biasing member 700 described later.

1-2. hub 200

The hub 200 as the second rotating body functions as an output member in the damper device 1, is formed of, for example, a metal material, has a substantially disc-like shape as a whole, and is provided so as to be sandwiched between the first plate 100A and the second plate 100B and to be rotatable relative to the disc plate 100 (the first plate 100A and the second plate 100B) about the rotation axis O. As shown in fig. 3 and 4, the hub 200 is configured to be spline-coupled to an input shaft (not shown) of the transmission by inserting the input shaft into a through hole 203 formed in a substantially cylindrical portion 202. Further, the hub 200 is provided with a circular plate portion 205 extending radially outward from the cylindrical portion 202.

As described above, the

window holes

206a, 206b, 206c, and 206d corresponding to the first housing area 102a, the second housing area 102b, the third housing area 102c, and the fourth housing area 102d are provided at equal intervals in the disk portion 205. These window holes 206a to 206d provided in the hub 200 are provided to correspond to a first elastic body 400 described later. That is, the first elastic body 400 is housed in each of the windows 206a to 206 d.

As shown in fig. 2, the window hole 206a has an engagement portion (a first engagement portion) 206a on one end side corresponding to the region I₁And an engaging portion (first other end engaging portion) 206a on the other end side opposed thereto₂The window 206a is engaged with the first elastic body 400. Similarly, the window 206b has an engagement portion (second engagement portion) 206b on one end side corresponding to the region II₁And an engaging portion (second other end side engaging portion) 206b on the other end side opposite thereto₂ Window 206b and first bulletThe body 400 is engaged. In addition, the window hole 206c has an engagement portion (a third engagement portion) 206c on one end side corresponding to the region III₁And an engaging portion (third other end side engaging portion) 206c on the other end side opposed thereto₂The window 206c is engaged with the first elastic body 400. In addition, the window hole 206d has an engagement portion (fourth engagement portion) 206d on one end side corresponding to the region IV₁And an engaging portion (fourth other end engaging portion) 206d on the other end side opposed thereto₂The window 206d is engaged with the first elastic body 400.

At the radial end of the disk portion 205,

projections

207a, 207b, 207c, and 207d are provided corresponding to the regions I to IV. The projections 207a to 207d are accommodated in the notches 105 provided in the liner plate 101 so that the hub 200 can rotate relative to the disc plate 100. When the hub 200 is relatively rotated by a predetermined torsion angle, the protrusions 207a to 207d abut against the restricting portion 106, which is the outer edge portion of the notch 105, and excessive relative rotation of the hub 200 is restricted.

As shown in fig. 2 to 4,

groove portions

208a, 208b, 208c, and 208d for accommodating axially extending portions 303a to 303d of the control plate 300, which will be described later, are provided radially inward of the

respective windows

206a, 206b, 206c, and 206 d. In the damper device 1 according to the embodiment, the grooves 208a to 208d are provided continuously with the windows 206a to 206d, but the present invention is not limited thereto, and may be provided in any portion of the circular plate portion 205.

As shown in fig. 2 and 4, the hub 200 is provided with

guide portions

209a, 209b, 209c, and 209d, and the

guide portions

209a, 209b, 209c, and 209d define the shapes (outer edges) of the

groove portions

208a, 208b, 208c, and 208d and can abut on the axially extending portions 303a to 303d of the control plate 300, which will be described later. The

guide portions

209a, 209b, 209c, and 209d have a step-like shape defining the

groove portions

208a, 208b, 208c, and 208d, and when the hub 200 is rotated relative to the disc plate 100 in a predetermined direction (in fig. 2, in the L direction (counterclockwise)) by a predetermined torsion angle, the

guide portions

209a, 209b, 209c, and 209d come into contact with the

axially extending portions

303a, 303b, 303c, and 303 d. Conversely, the

guide portions

209a, 209b, 209c, and 209d do not abut against the

axially extending portions

303a, 303b, 303c, and 303d except in the above case.

As described above, the control plate 300 rotates in a predetermined direction (L direction in fig. 2) relative to the disc plate 100 together with the hub 200 by the

guide portions

209a, 209b, 209c, and 209d coming into contact with the

axially extending portions

303a, 303b, 303c, and 303d (guided by the guided

portions

209a, 209b, 209c, and 209 d).

1-3 control board 300

The control plate 300 is formed of a metal material such as spring steel, for example, and has a substantially annular shape as a whole, and as shown in fig. 3 and the like, most part of the control plate 300 is axially provided between the first plate 100A and the hub 200. As shown in fig. 2 to 5, the control board 300 mainly has: a second sliding surface 301, the second sliding surface 301 being provided in a substantially annular shape and sliding on the first plate 100A; radially extending portions 302a to 302d, which are disposed between the first plate 100A and the hub 200 in the axial direction, extend in the radial direction from the vicinity of the second sliding surface 301, and abut against a first elastic body 400 described later; and axial extension portions 303a to 303d, the axial extension portions 303a to 303d extending in the axial direction so as to penetrate the hub 200.

As shown in fig. 3 and the like, the second sliding surface 301 always abuts on the first plate 100A, and when the control plate 300 rotates relative to the first plate 100A (disc plate 100), the second sliding surface 301 slides on the first plate 100A, and a second sliding torque is generated. The detailed operation of the control plate 300 relative to the disc plate 100 will be described later.

As shown in fig. 2 and the like, the radially extending portions 302a to 302d are provided so as to correspond to the regions I to IV, the radially extending portion 302a is provided so as to abut against the first elastic body 400 housed in the first housing region 102a (the window hole 206a), the radially extending portion 302b is provided so as to abut against the first elastic body 400 housed in the second housing region 102b (the window hole 206b), the radially extending portion 302c is provided so as to abut against the first elastic body 400 housed in the third housing region 102c (the window hole 206c), and the radially extending portion 302d is provided so as to abut against the first elastic body 400 housed in the fourth housing region 102d (the window hole 206 d).

The length of the radial extensions 302a to 302d extending in the radial direction is set longer than the outer diameter of the first elastic body 400 so as to be able to ensure a sufficient contact area with respect to the first elastic body 400.

As shown in fig. 2 to 4, the axially extending portions 303a to 303d are provided so as to correspond to the regions I to IV, the axially extending portion 303a is provided so as to penetrate through the groove portion 208a provided radially inward of the window hole 206a, the axially extending portion 303b is provided so as to penetrate through the groove portion 208b provided radially inward of the window hole 206b, the axially extending portion 303c is provided so as to penetrate through the groove portion 208c provided radially inward of the window hole 206c, and the axially extending portion 303d is provided so as to penetrate through the groove portion 208d provided radially inward of the window hole 206 d. Note that the axially extending portions 303a to 303d are not engaged or fitted with the corresponding groove portions 208a to 208d by some means, and the control plate 300 does not always rotate integrally with the hub 200.

As described above, when the hub 200 is rotated relative to the disc plate 100 in a predetermined direction (in fig. 2, in the L direction (counterclockwise direction)) by a predetermined torsion angle or more, the axially extending portions 303a to 303d come into contact with the

guide portions

209a, 209b, 209c, and 209d of the hub 200, respectively. Accordingly, only when hub 200 is rotated relative to disc plate 100 in a predetermined direction (L direction (counterclockwise direction) in fig. 2) by a predetermined torsion angle or more, control plate 300 is rotated relative to disc plate 100 in the predetermined direction (L direction in fig. 2) together with hub 200, and second sliding surface 301 slides on first plate 100A to generate a second sliding torque.

Further, the end portions of the axially extending portions 303a to 303d are engaged with engagement portions 601 provided on the second thrust member 600, which will be described later. Thereby, the control plate 300 and the second thrust member 600 can be rotated integrally.

Further, the axially extending portions 303a to 303d are preferably made of a metal material such as spring steel and are attached in a state of being compressed in advance. By attaching the axially extending portions 303a to 303d in a state of being compressed in advance, the second sliding surface 301 is pressed against the first plate 100A, and therefore, when the control plate 300 rotates relative to the first plate 100A (disc plate 100), a larger second sliding torque can be generated. Similarly, the axially extending portions 303a to 303d are attached in a pre-compressed state, and the pressing force based on the pre-compression is transmitted from the end portions of the axially extending portions 303a to 303d to the second thrust member 600, so that the third sliding surface 602 of the second thrust member 600 is pressed against the second plate 100B. This can increase a third slip torque described later.

1-4. first elastomer 400

As shown in fig. 1 to 4, the first elastic body 400 uses one coil spring in each of the regions I to IV. In addition, two or more coil springs may be arranged in series in each region.

In the embodiment shown in fig. 1 to 4, as an example, four housing areas, that is, the first housing area 102a, the second housing area 102b, the third housing area 102c, and the fourth housing area 102d are formed in the disc plate 100 (corresponding to these, the

window holes

206a, 206b, 206c, and 206d are provided in the hub 200 as described above), and therefore, one first elastic body 400 is housed in each of these four housing areas, that is, in correspondence to the respective areas I to IV. In each of the regions I to IV, the first elastic body 400 may be configured such that both ends thereof are supported by a pair of sheet members (not shown) in each of the housing regions.

Here, focusing on the region I, one end of the first elastic body 400 is respectively connected to the first end surface 104a of the disc plate 100 (the

first plates

100A and 100B)₁And an engaging portion 206a provided on the first end side of the hub 200₁And (4) clamping. The other end of the first elastic member 400 is connected to the first other end surface 104a of the disc plate 100 (

first plates

100A and 100B)₂And an engaging portion 206a provided on the first other end side of the hub 200₂And (4) clamping. The same applies to regions II to IV, and the first elastic body 400 is engaged with the disk plate 100 and the hub 200.

With the above configuration, the first elastic body 400 can elastically couple the disc plate 100 and the hub 200 in the rotation direction. That is, after power from a drive source such as an engine or a motor is transmitted in the order of the disc plate 100, the first elastic body 400, and the hub 200, when the disc plate 100 and the hub 200 rotate relative to each other, the first elastic body 400 is compressed and deformed to absorb torque variation.

1-5. first thrust member 500

The first thrust member 500 is formed of, for example, a metal material, and has a substantially cylindrical fitting portion 501 and a main portion 502 having a substantially annular shape as a whole. As shown in fig. 2 to 4, the fitting portion 501 corresponds to the second fitting hole 112 provided in the second plate 100B, and is fitted (engaged) in the second fitting hole 112. Thereby, the first thrust member 500 is integrated with the second plate 100B (the disc plate 100), and rotates integrally with the disc plate 100 about the rotation axis O. The main portion 502 is disposed in contact with the hub 200 in the axial direction between the second plate 100B and the hub 200 via a biasing member 700 described later. Main portion 502 has a first slide surface 502a, and first slide surface 502a abuts on hub 200 and slides on the radially inner end of circular plate portion 205 of hub 200.

A biasing member 700 is provided between the main portion 502 and the second plate 100B, and the first thrust member 500 is pressed against the hub 200 by the biasing member 700. Thus, when the disc plate 100 (second plate 100B) and the hub 200 rotate relative to each other, the first sliding surface 502a of the main portion 502 slides on the disc portion 205 of the hub 200 (faces the disc portion 205) to generate a first sliding torque. This first slip torque is always generated when the disc plate 100 and the hub 200 rotate relative to each other, and is used as a small hysteresis torque in the damper device 1.

Further, the first thrust member 500 (the fitting portion 501 and the main portion 502) is preferably provided with a gap in the radial direction from the cylindrical portion 202 of the hub 200. Thus, the first sliding surface 502a can reliably generate the first sliding torque on the disc portion 205 of the hub 200.

1-6 second thrust component 600

The second thrust member 600 is formed of a resin material, for example, and has a substantially annular shape as a whole, as shown in fig. 3 and 4, and has a joint portion 601 and a third sliding surface 602, the joint portion 601 receiving end portions of the axially extending portions 303a to 303d in the control plate 300, and the third sliding surface 602 sliding on the second plate 100B. In addition, the control plate 300 and the second thrust member 600 can be rotated integrally by the axially extending portions 303a to 303d and the engaging portions 601 corresponding to these. Therefore, when control plate 300 rotates relative to disc plate 100 (when hub 200 rotates relative to disc plate 100 in a predetermined direction (in fig. 2, in the L direction (counterclockwise)) by a predetermined torsion angle or more as described above), third sliding surface 602 slides on second plate 100B, and a third sliding torque is generated.

In addition, as described above, when the axially extending portions 303a to 303d are mounted in a state of being compressed in advance, the pressing force based on the compression in advance is transmitted from the end portions of the axially extending portions 303a to 303d to the second thrust member 600, so that the third sliding face 602 of the second thrust member 600 is pressed against the second plate 100B. This can increase the third slip torque.

Further, the third sliding surface 602 is preferably disposed radially outward of the first sliding surface 502a of the first thrust member 500. That is, it is preferable that the outer diameter of the second thrust member 600 is larger than the outer diameter of the first thrust member 500. As a result, the third slip torque can be flexibly used as a hysteresis torque larger than at least the first slip torque.

Further, the second thrust member 600 may be formed of a metal material composed of a compound containing a 3d transition metal.

1-7. force applying member 700

As described above, the biasing member 700 is supported by the second plate 100B and is disposed between the second plate 100B and the main portion 502 of the first thrust member 500. A general disc spring can be used as the urging member 700. The urging member 700 urges the first thrust member 500 to press the first thrust member 500 toward the hub 200. As a result, the first sliding surface 502a of the first thrust member 500 slides on the hub 200 as described above, and a first sliding torque is generated. Further, by appropriately setting the spring constant of the disc spring, the magnitude of the first slip torque can be varied. Further, since the biasing member 700 according to an embodiment is used to generate the first slip torque used as a small hysteresis torque, a member having a limited axial expansion and contraction stroke can be used.

2. Operation of vibration damping devices

Next, the operation of the vibration damping device 1 having the above-described configuration will be described with reference to fig. 6A to 6F and fig. 7. Fig. 6A is a schematic plan view schematically showing a state where the first rotating member (disc plate 100) and the second rotating member (hub 200) do not rotate relative to each other in the damper device 1 according to the embodiment. Fig. 6B is a schematic plan view schematically showing a state in which the second rotating body (hub 200) is rotated relative to the first rotating body (disk plate 100) by a torsion angle θ 1 ° in the damper device 1 according to the embodiment. Fig. 6C is a schematic plan view schematically showing a state in which the second rotating body (hub 200) is rotated relative to the first rotating body (disk plate 100) by a torsion angle θ 2 ° in the positive side in the damper device 1 according to the embodiment. Fig. 6D is a schematic plan view schematically showing a state in which the second rotating body (hub 200) is rotated by a torsion angle θ 3 ° to the negative side with respect to the first rotating body (disk plate 100) in the damper device 1 according to the embodiment. Fig. 6E is a schematic plan view schematically showing a state in which the second rotating body (hub 200) is rotated by a torsion angle θ 4 ° to the negative side with respect to the first rotating body (disc plate 100) in the damper device 1 according to the embodiment. Fig. 6F is a schematic plan view schematically showing a state in which the relative rotation of the second rotating member (hub 200) with respect to the first rotating member (disc plate 100) is eliminated from the state of fig. 6E in the damper device 1 according to the embodiment. Fig. 7 is a schematic characteristic diagram schematically showing torsional characteristics in the damper device 1 according to the embodiment.

Fig. 6A shows a state (torsion angle 0 °) in which relative rotation is not generated between disc plate 100 and hub 200 although power from a drive source such as an engine or a motor is transmitted to damper device 1. In this case, the first sliding torque is not generated between the first sliding surface 502a in the first thrust member 500 and the hub 200, the second sliding torque is not generated between the second sliding surface 301 in the control plate 300 and the first plate 100A, and the third sliding torque is not generated between the third sliding surface 602 in the second thrust member 600 and the second plate 100B.

In addition, in a state where relative rotation is not generated between the disc plate 100 and the hub 200 shown in fig. 6A, the axially extending portions 303a to 303d in the control plate 300 are housed so as to penetrate through the groove portions 208a to 208d in the corresponding hub 200. At this time, gaps G are provided between the axially extending portions 303a to 303d and the guide portions 209a to 209d corresponding to these. That is, the axially extending portion 303a does not abut on the guide portion 209a (similarly, the axially extending portion 303b does not abut on the guide portion 209b, the axially extending portion 303c does not abut on the guide portion 209c, and the axially extending portion 303d does not abut on the guide portion 209 d).

Next, fig. 6B shows a case where relative rotation is generated between disc plate 100 and hub 200 from the state of fig. 6A, and a twist of θ 1 ° is generated to the positive side. Here, the positive side refers to, for example, a case where hub 200 rotates (moves) in the R direction (clockwise direction in fig. 6B) with respect to disc plate 100. In this case, the hub 200 rotates relative to the disc plate 100 while flexing the first elastic body 400. In addition, in the torsion angles 0 ° to θ 1 °, the gaps G between the axially extending portions 303a to 303d and the guide portions 209a to 209d corresponding thereto are gradually enlarged, and therefore, the two are not yet in contact with each other. Therefore, the control plate 300 does not affect the relative rotation of the hub 200 with respect to the disc plate 100, and the control plate 300 does not rotate relative to the disc plate 100.

In this case, a first sliding torque is generated between the first sliding surface 502a of the first thrust member 500 that rotates integrally with the disk plate 100 and the hub 200 (disk portion 205). On the other hand, since the control plate 300 does not rotate relative to the disc plate 100, the second slip torque and the third slip torque are not generated.

Next, fig. 6C shows a case where from the state of fig. 6B, hub 200 further rotates relative to disc plate 100, and a twist of θ 2 ° is generated to the positive side. In this case, the hub 200 rotates relative to the disc plate 100 while further flexing the first elastic body 400. At a torsion angle of θ 2 °, the protrusions 207a to 207d of the hub 200 abut against the restricting portions 106 provided on the backing plate 101. Accordingly, since the relative rotation of the hub 200 to the positive side by θ 2 ° or more is restricted, it can be understood that the torsion angle of θ 2 ° is the maximum torsion angle of the positive side.

Further, in the torsion angles θ 1 ° to θ 2 °, the gaps G between the axially extending portions 303a to 303d and the guide portions 209a to 209d corresponding thereto are further enlarged, and therefore, the two are not yet in contact. Therefore, the control plate 300 does not affect the relative rotation of the hub 200 with respect to the disc plate 100, and the control plate 300 does not rotate relative to the disc plate 100. In this case, a first sliding torque is generated between the first sliding surface 502a of the first thrust member 500 that rotates integrally with the disk plate 100 and the hub 200 (disk portion 205). On the other hand, since the control plate 300 does not rotate relative to the disc plate 100, the second slip torque and the third slip torque are not generated.

Next, fig. 6D shows a case where relative rotation is generated between disc plate 100 and hub 200 from the state of fig. 6A, and a twist of θ 3 ° is generated to the negative side. Here, the negative side refers to, for example, a case where the hub 200 rotates (moves) in the L direction (counterclockwise direction in fig. 6D) with respect to the disc plate 100. In this case, the hub 200 rotates relative to the disc plate 100 while flexing the first elastic body 400. In addition, in the torsion angles 0 ° to θ 3 °, the gap G between the axially extending portions 303a to 303d and the guide portions 209a to 209d corresponding thereto gradually decreases, and at the torsion angle θ 3 °, the two abut (the gap G disappears). Therefore, in the torsion angles 0 ° to θ 3 °, the control plate 300 does not affect the relative rotation of the hub 200 with respect to the disc plate 100, and the control plate 300 does not rotate relative to the disc plate 100.

At the torsion angle θ 3 °, a gap H is formed between the radial extensions 302a to 302d of the control plate 300 and the first elastic body 400. This is because, as described above, in conjunction with the disappearance of the gap G, in the torsion angles 0 ° to θ 3 °, the contact relationship between the radially extending portions 302a to 302d and the first elastic body 400 is eliminated due to the relative rotation of the hub 200 to the negative side while flexing the first elastic body 400, and the gap H is formed while gradually expanding. In addition, when the hub 200 does not rotate relative to the disc plate 100 (the state of fig. 6A) and when the hub 200 rotates relative to the disc plate 100 toward the front side (the states of fig. 6B and 6C), the radially extending portions 302a to 302d always abut against the first elastic body 400.

In this case, a first sliding torque is generated between the first sliding surface 502a of the first thrust member 500 that rotates integrally with the disk plate 100 and the hub 200 (disk portion 205). On the other hand, since control plate 300 does not rotate relative to disc plate 100, second slip torque and third slip torque are not generated.

Next, fig. 6E shows a case where from the state of fig. 6D, hub 200 further rotates relative to disc plate 100, and a twist of θ 4 ° is generated to the negative side. In this case, the hub 200 rotates relative to the disc plate 100 while further flexing the first elastic body 400. At a torsion angle of θ 4 °, the protrusions 207a to 207d of the hub 200 abut against the restricting portions 106 provided on the backing plate 101. Accordingly, since the relative rotation of the hub 200 to the negative side is limited to θ 4 ° or more, it can be understood that the torsion angle of θ 4 ° is the maximum torsion angle on the negative side. In this case, the gap H continues to be formed between the radial extensions 302a to 302D of the control plate 300 and the first elastic body 400 from the state of fig. 6D.

Further, in the torsion angles θ 3 ° to θ 4 °, the axially extending portions 303a to 303d abut on the guide portions 209a to 209d corresponding to these. Therefore, the control plate 300 (the axially extending portions 303a to 303d) is guided by the hub 200 (the guide portions 209a to 209d) to rotate relatively in the L direction together with the hub 200 with respect to the disc plate 100. In this case, a first sliding torque is generated between the first sliding surface 502a of the first thrust member 500 that rotates integrally with the disk plate 100 and the hub 200 (the disk portion 205). On the other hand, since the control plate 300 also rotates relative to the disc plate 100, a second sliding torque is generated between the second sliding surface 301 in the control plate 300 and the first plate 100A, and a third sliding torque is generated between the third sliding surface 602 in the second thrust member 600 and the second plate 100B. That is, in the torsion angles θ 3 ° to θ 4 °, the sum of the first slip torque, the second slip torque, and the third slip torque becomes the hysteresis torque.

Next, fig. 6F shows a state in which relative rotation of hub 200 with respect to disc plate 100 is eliminated and the negative side transitions from maximum torsion angle θ 4 ° to torsion angle 0 ° from the state of fig. 6E. In this case, the hub 200 moves relatively in the R direction toward the torsion angle of 0 ° while gradually eliminating the deflection of the first elastic body 400. That is, the torsion angle in the state of fig. 6F may be, for example, a torsion angle between θ 3 ° and θ 4 °.

In this case, first, when the hub 200 is relatively moved from the torsion angle θ 4 ° in the R direction (moved so as to cancel the relative rotation in the L direction), the contact relationship between the axially extending portions 303a to 303d and the guide portions 209a to 209d corresponding thereto is canceled, and the gap G is formed again therebetween. That is, the rotation of the control plate 300 in the R direction (relative rotation with respect to the disc plate 100) cannot be guided by the hub 200. Therefore, a slight time difference is generated between the timing of canceling the relative rotation of hub 200 to disc plate 100 on the negative side and the timing of canceling the relative rotation of control plate 300 to disc plate 100 on the negative side.

When hub 200 is relatively moved in the R direction by a predetermined angle (for example, the predetermined angle is α °) in order to cancel the negative relative rotation from torsion angle θ 4 ° before control plate 300 (without guiding control plate 300), gap H formed in the state of fig. 6D (and 6E) gradually decreases and finally disappears. Thereby, the radially extending portions 302a to 302d of the control plate 300 again abut the first elastic body 400. In this state, since the first elastic body 400 is still in a state of being deflected, the first elastic body 400 presses the control plate 300 in the R direction. Thus, in this case, the control plate 300 rotates in the R direction relative to the disc plate 100 based on the pressing force of the first elastic body 400.

To further explain the above flow, only the hub 200 rotates relative to the disc plate 100 in the R direction up to the torsion angle θ 4 ° to θ 4 — α °, and therefore only the first slip torque is generated. On the other hand, since control plate 300 rotates relative to disc plate 100 in the R direction in addition to hub 200 up to θ 4- α ° to 0 °, first slip torque, second slip torque, and third slip torque are generated.

As described above, based on the flow of the operation of the damper device 1 described with reference to fig. 6A to 6F, the torsional characteristics of the damper device 1 are as shown in fig. 7.

In addition, the large hysteresis torque generated only on the negative side as described above, that is, the hysteresis torque obtained by summing up the first slip torque, the second slip torque, and the third slip torque is suitable for use in a case where, for example, in a hybrid vehicle, the torque variation generated when the engine is started under a certain condition is absorbed in a state where the vehicle is driven only by the electric motor with the engine stopped. In addition, as described above, since only the first slip torque is generated on the positive side, a small hysteresis torque can be generated. As described above, the damper device 1 according to the embodiment can reduce the axial length of the damper device 1 by integrating the control plates 300 into one, and can generate a small hysteresis torque on the positive side and a large hysteresis torque on the negative side, thereby stably generating various hysteresis torques.

3. Modification example

3-1. second embodiment

Next, the structure of the vibration damping device 1 according to the second embodiment will be described with reference to fig. 8 to 10. Fig. 8 is a schematic cross-sectional view schematically showing the structure of the damper device 1 according to the second embodiment. Fig. 9 is a schematic plan view schematically showing the structure of the vibration damping device 1 according to the second embodiment (a part of the components is omitted). Fig. 10 is a schematic plan view showing an enlarged scale of a control plate 300 of the damper device 1 according to the second embodiment.

The damper device 1 according to the second embodiment has substantially the same configuration as the damper device 1 according to the first embodiment, but the position of the second sliding surface 301 of the control plate 300 is different from that of the first embodiment. In the damper device 1 according to the second embodiment, a detailed description of the same structure as the damper device 1 according to the first embodiment will be omitted.

As shown in fig. 8 to 10, the second sliding surface 301 of the control plate 300 in the vibration damping device 1 of the second embodiment is disposed radially outward of the radially extending portions 302a to 302 d. Specifically, the second sliding surface 301 of the second embodiment is continuous with the radially extending portions 302a to 302d, is provided radially outward, and has a substantially annular shape as a whole.

The second sliding surface 301 is pressed against the first plate 100A by the pre-compression force of the axially extending portions 303a to 303d, but by extending the distance separating the axially extending portions 303a to 303d from the second sliding surface 301 as long as in the second embodiment, the diameter of the action of the pre-compression force can be increased, and as a result, the pressing force of the second sliding surface 301 against the first plate 100A can be increased. This can further increase the second slip torque.

3-2. other modifications

Next, another modification of the vibration damping device 1 will be described with reference to fig. 11 to 13. Fig. 11 is a schematic cross-sectional view schematically showing the structure of a damper device 1 according to a third embodiment. Fig. 12 is an enlarged schematic front view of a second elastic body 800 used in the vibration damping device 1 according to the third embodiment. Fig. 13 is an enlarged perspective view of the control plate 300, the second thrust member 600, and the elastic member 1000 used in the damper device 1 according to the fourth embodiment.

As shown in fig. 11, in the damper device 1 according to the third embodiment which reliably exerts the third sliding torque, a second elastic body 800 compressed in advance is provided between the hub 200 and the second thrust member 600. As the second elastic body 800, for example, a disc spring or a wave washer having a general shape can be used. The second elastic body 800 is supported by a support plate 801 provided on the hub 200 (on the side surface of the hub 200), and biases the second thrust member 600 so as to press the second thrust member 600 against the second plate 100B (inner surface 110B).

As shown in fig. 12, as the shape (inner shape) of the second elastic body 800, it is preferable that the notches 800x for inserting the axially extending portions 303a to 303d in the axial direction are arranged in a substantially petal shape. This can increase the spring force acting as the second elastic body 800 (the spring portion 800y in the second elastic body 800), and thus the third sliding torque can be more reliably exerted.

As shown in fig. 13, in the damper device 1 according to the fourth embodiment that can be employed to further increase the second slip torque, an elastic member 1000 is provided between the second thrust member 600 and the control plate 300. In more detail, it is preferable that the elastic member 1000 extending in the axial direction is provided between the axially extending portions 303a to 303d and the second thrust member 600. As the elastic member 1000, a general coil spring can be used.

As another means for further increasing the second sliding torque, the second sliding surface 301 of the control plate 300 and the corresponding surface of the first plate 100A may be provided with concave and convex surfaces. It is assumed that the control plate 300 is formed with a concave-convex surface, and can press the first plate 100A in the axial direction when relative rotation at a predetermined torsion angle is generated between the disc plate 100 and the hub 200 (for example, when the relative rotation at the predetermined torsion angle is generated, the convex surface of the second sliding surface 301 presses the convex surface of the first plate 100A in the axial direction).

As another means for further increasing the third sliding torque, the third sliding surface 602 of the second thrust member 600 and the corresponding surface of the second plate 100B may be provided with concave-convex surfaces corresponding to each other, as described above.

As described above, the embodiments have been described, but the embodiments are merely examples and are not intended to limit the scope of the present invention. The above embodiment can be implemented by other various embodiments, and various omissions, substitutions, and changes can be made without departing from the spirit of the present invention. The structure, shape, size, length, width, thickness, height, number, and the like can be appropriately changed. Further, the above embodiments can be applied to a vibration damping device for an application that does not require the limiter function, such as a clutch disk.

Claims

1. A vibration damping device is characterized by comprising:

a first rotating body having at least a first plate that rotates about a rotation axis and a second plate that is disposed opposite to the first plate and rotates integrally with the first plate about the rotation axis;

a second rotating body that relatively rotates with respect to the first rotating body about the rotation axis;

a first elastic body elastically connecting the first rotating body and the second rotating body in a rotational direction;

a first thrust member that has a fitting portion fitted to the first rotating body and a first sliding surface that slides on the second rotating body and that rotates integrally with the first rotating body, the first sliding surface being pressed against the second rotating body by a biasing member supported by the first rotating body, and that generates a first sliding torque when the first rotating body and the second rotating body rotate relative to each other;

a control plate having a second sliding surface that slides on the first plate, a radially extending portion that is disposed between the first plate and the second rotating body in the axial direction and extends in the radial direction so as to be in contact with the first elastic body, and an axially extending portion that penetrates the second rotating body and extends in the axial direction, and that generates a second sliding torque by rotating the first rotating body relative to the second rotating body in a predetermined direction only when the first rotating body and the second rotating body rotate relative to each other in the predetermined direction;

and a second thrust member having an engagement portion that receives an end portion of the axially extending portion and a third sliding surface that slides on the second plate, the second thrust member being configured to rotate in the predetermined direction integrally with the control plate relative to the first rotating body to generate a third sliding torque.

2. The vibration damping device according to claim 1,

the axial extension is pre-compressed in the axial direction,

the second sliding surface is pressed against the first plate by the axially extending portion that is pre-compressed, and the third sliding surface is pressed against the second plate by the axially extending portion that is pre-compressed.

3. Damping device according to claim 1 or 2,

a second elastic body that is compressed in advance is further disposed between the second rotating body and the second thrust member.

4. The vibration damping device according to claim 1,

the second rotating body has a guide portion that comes into contact with the axially extending portion and guides the relative rotation of the control plate in the predetermined direction when the second rotating body is rotated relative to the first rotating body in the predetermined direction by a predetermined torsion angle or more.

5. The vibration damping device according to claim 1,

the second sliding surface is disposed radially outward of the radially extending portion.

6. The vibration damping device according to claim 1,

the second rotating body has a cylindrical portion extending in the axial direction and a disk portion extending in the radial direction from the cylindrical portion,

the fitting portion of the first thrust member is fitted to the second plate, and the first sliding surface faces a radially inner end of the circular plate portion of the second rotating body.