JP4684348B1 - Damper device - Google Patents

Abstract

In a damper device with a wide damper twist angle, a hysteresis torque can be easily adjusted with a simple configuration.
The damper device includes first and second retaining plates, a plurality of outer torsion springs, a pair of clutch plays, and a plurality of inner torsion springs. A hub flange 41. The first and second retaining plates 38 and 39 are arranged at a predetermined interval from each other, and support the outer peripheral side torsion spring 44. The pair of clutch plates 43 are arranged at a predetermined interval from each other and support the inner peripheral torsion spring 45. The inner peripheral end portions of the retaining plates 38 and 39 and the outer peripheral end portion of the clutch plate 43 are in sliding contact with the elastic deformation of the torsion springs 44 and 45.
[Selection] Figure 1

Description

  The present invention relates to a damper device, and more particularly to a damper device for transmitting torque input from a member on an engine side to a member on a transmission side.

  The damper device is employed in a clutch disk assembly for an automobile and a lock-up device for a torque converter. Here, in the damper device, in order to absorb and attenuate the torque fluctuation input from the engine, it is necessary to reduce the rigidity and widen the twist angle of the torsion spring. Therefore, as shown in Patent Document 1, torsion springs are arranged on the outer peripheral part and the inner peripheral part, respectively, and the outer peripheral side torsion spring and the inner peripheral side torsion spring act in series by an intermediate member. Has already been proposed.

JP 2001-82577 A

  According to the damper device of the lockup device disclosed in Patent Document 1, the outer periphery side torsion spring and the inner periphery side torsion spring act in series via the intermediate member. Moreover, in the torsion spring on the inner peripheral side, two coil springs are arranged so as to act in series. For this reason, the damper twist angle is wide.

  Further, in order to effectively absorb and attenuate the torque fluctuation, it is necessary to widen the damper torsion angle. For this purpose, the coil diameters of the inner and outer torsion springs must be enlarged. Here, the distance from the holding portion of each plate holding each torsion spring to the tip of the plate needs to ensure a predetermined distance from the point of strength. However, when the coil diameter of the inner and outer torsion springs is enlarged, both springs approach each other, and there is a problem that it is difficult to secure the distance between the torsion spring holding portion and the plate tip portion of each plate. Furthermore, in consideration of compatibility with vehicle characteristics, it is necessary to set hysteresis torque with appropriate characteristics in the damper device. And it is calculated | required that these characteristics can be easily changed now according to the vehicle applied.

  An object of the present invention is to employ a torsion spring having a large coil diameter as an elastic member, thereby making it possible to widen a damper twist angle.

  Another object of the present invention is to make it possible to easily adjust the hysteresis torque with a simple configuration.

  A damper device according to claim 1 is a device that transmits torque input from a member on an engine side to a member on a transmission side, and includes a pair of input plates, a plurality of outer peripheral elastic members, and a pair of outputs. A plate, a plurality of inner peripheral elastic members, and intermediate members are provided. The pair of input plates receives torque from an engine-side member and is disposed at a predetermined interval from each other. The plurality of outer peripheral elastic members are supported by a pair of input plates, and torque is input from the pair of input plates. The pair of output plates can be connected to a member on the transmission side, and are arranged at a predetermined interval from each other. The plurality of inner peripheral elastic members are supported by a pair of output plates on the inner peripheral side of the plurality of outer peripheral elastic members, and transmit torque to the pair of output plates. The intermediate member is a member that is disposed between the pair of input plates and causes the outer peripheral side elastic member and the inner peripheral side elastic member to act in series. A part of the pair of input plates and a part of the pair of output plates face each other in the rotation axis direction.

  In this damper device, torque input from the engine-side member to the pair of input plates is transmitted to the pair of output plates via the plurality of outer peripheral side elastic members, the intermediate member, and the plurality of inner peripheral side elastic members. And further transmitted to a member on the transmission side.

  Here, a part of the pair of input plates and the pair of output plates are arranged so as to face each other in the rotation axis direction. That is, it is arrange | positioned so that the position of the rotating shaft direction of a part of both plates may shift | deviate, and interference of both plates can be avoided. For this reason, in each plate, the distance between the portion holding the elastic member and the tip portion of the plate can be increased. Therefore, when a torsion spring is used as the inner peripheral side elastic member and the outer peripheral side elastic member, these coil diameters can be increased, and the damper twist angle can be further increased.

  A damper device according to a second aspect is the device according to the first aspect, wherein each of the pair of input plates is formed in an annular shape and has a window hole for supporting the outer peripheral side elastic member. Each of the pair of output plates is disposed on the inner peripheral side of the pair of input plates, is formed in an annular shape, and has a window hole for supporting the inner peripheral elastic member. And the outer peripheral part of a pair of output plate is inserted in the inner peripheral part of a pair of input plate, and a part of output plate and input plate have overlapped with the rotating shaft direction.

  For this reason, as described above, a torsion spring having a large coil diameter can be used as the elastic member while sufficiently securing the strength of the input / output plate.

  The damper device according to a third aspect further includes an output hub fixed to the pair of output plates in the device according to the first or second aspect, wherein the intermediate member and the output hub are capable of relative rotation within a predetermined angular range. is there.

The damper device according to claim 4 is the device according to any one of claims 1 to 3, wherein the portions of the pair of input plates and the pair of output plates facing each other in the rotation axis direction are in sliding contact with each other.
Here, when the input plate and the output plate rotate relative to each other, a part of the input plate and the output plate come into sliding contact, and hysteresis torque is generated. Thus, since the hysteresis torque is generated using the input plate and the output plate, a hysteresis torque generating mechanism can be realized with a simple configuration. Further, the hysteresis torque can be arbitrarily adjusted by changing specifications such as rigidity, arrangement, and dimensions of each plate.

  According to the present invention as described above, the strength required for holding the elastic member can be easily ensured particularly in the damper device in which the damper twist angle is widened. Further, the hysteresis torque can be easily adjusted as necessary using the constituent members of the damper device.

1 is a partial cross-sectional view of a torque converter including a damper device according to an embodiment of the present invention. The front fragmentary view of the said damper apparatus.

  FIG. 1 is a partial cross-sectional view of a torque converter 1 provided with a damper device as an embodiment of the present invention. An engine (not shown) is arranged on the left side of FIG. 1, and a transmission (not shown) is arranged on the right side of the figure. FIG. 2 is a partial front view of the damper device. In FIG. 2, the torsion spring as an elastic member and some members are omitted. Note that OO shown in FIG. 1 is the rotational axis of the torque converter.

[Overall configuration of torque converter]
The torque converter 1 is a device for transmitting torque from a crankshaft (not shown) on the engine side to an input shaft of a transmission. The torque converter 1 includes a front cover 2 fixed to a member on the engine side, a torque converter body 6 including three types of impellers (an impeller 3, a turbine 4, and a stator 5), a power transmission device 7, and a lock-up. The apparatus 8 is comprised.

  The front cover 2 is a disk-shaped member, and an outer peripheral cylindrical portion 10 that protrudes toward the axial transmission side is formed on the outer peripheral portion thereof. The impeller 3 includes an impeller shell 12 fixed to the outer peripheral cylindrical portion 10 of the front cover 2 by welding, a plurality of blades 13 fixed to the inside thereof, a core 14 provided inside the blade 13, and an impeller shell. 12 and a cylindrical impeller hub 15 provided on the inner peripheral side. The turbine 4 is disposed to face the impeller 3 in the fluid chamber. The turbine 4 includes a turbine shell 16, a plurality of blades 17 fixed to the turbine shell 16, a core 18 provided inside the blade 17, a turbine support 19 fixed to the inner peripheral side of the turbine shell 16, It is composed of The turbine support 19 is a disk-shaped plate, and the turbine shell 16 and the turbine support 19 are fixed by a plurality of rivets 20.

  The stator 5 is a mechanism for rectifying hydraulic fluid that is disposed between the impeller 3 and the inner peripheral portion of the turbine 4 and returns from the turbine 4 to the impeller 3. The stator 5 includes a disk-shaped stator carrier 24, a plurality of blades 25 provided on the outer peripheral surface thereof, and a core 26 provided on the outer peripheral portion of the blade. The stator carrier 24 is supported by a fixed shaft (not shown) via a one-way clutch 27. Thrust bearings 28 and 29 are provided between the turbine support 19 and the one-way clutch 27 and between the stator carrier 24 and the impeller shell 12, respectively.

[Power transmission device]
The power transmission device 7 includes a torque transmission plate 34 fixed to the turbine support 19 and a damper device 35.

<Torque transmission plate>
The torque transmission plate 34 is formed in a disk shape, and an inner peripheral end thereof is fixed to the turbine support 19 together with the turbine shell 16 by a rivet 20. On the outer periphery of the torque transmission plate 34, a plurality of grooves are formed at predetermined intervals in the circumferential direction.

<Damper device>
1 and 2, the damper device 35 includes first and second retaining plates 38 and 39 (a pair of input plates), a hub flange (intermediate member) 41, a turbine hub 42, A pair of clutch plates (output plates) 43 and outer and inner torsion springs (elastic members) 44 and 45 are provided.

  The first and second retaining plates 38 and 39 are formed in a disc shape, and are arranged at intervals in the axial direction. Moreover, as shown in FIG. 2, both the retaining plates 38 and 39 are formed with narrowed portions 38a and 39a at a plurality of locations on the outer peripheral portion. In FIG. 2, only the throttle portion 38 a of the first retaining plate 38 appears, but the throttle portion 39 a having the same shape is also formed at the same position on the second retaining plate 39. The narrowing portions 38 a and 39 a of both the retaining plates 38 and 39 are in contact with each other at their opposing surfaces, and the narrowing portions 38 a and 39 a are connected by a rivet 48. Therefore, both the retaining plates 38 and 39 rotate synchronously. In addition, a plurality of window holes 38b and 39b are formed in both retaining plates 38 and 39 at predetermined intervals in the circumferential direction. The outer peripheral side torsion spring 44 is supported by the window holes 38b and 39b, and the torque input to both the retaining plates 38 and 39 is transmitted to the outer peripheral side torsion spring 44 through the window holes 38b and 39b. .

  In addition, a plurality of protrusions 50 that protrude toward the axial transmission side (to the right in FIG. 1) are formed at the inner peripheral end of the first retaining plate 38. As shown in FIG. 2, the plurality of protrusions 50 are arranged at predetermined intervals in the circumferential direction, and the protrusions 50 engage with grooves formed on the outer peripheral portion of the torque transmission plate 34. Yes. In FIG. 2, the torque transmission plate 34 is removed.

  As described above, the engaging portion 51 is configured by the plurality of grooves formed on the outer periphery of the torque transmission plate 34 and the plurality of protrusions 50 formed on the first retaining plate 38. By these engagements, torque is transmitted from the turbine 4 to the first and second retaining plates 38 and 39. The engaging portion 51 is located on the inner peripheral side of the torus center C (see FIG. 1) of the torque converter body 6 and further on the inner peripheral side of the outer peripheral torsion spring 44. The center C of the torus is the center of the space surrounded by the cores 14, 18, and 26 of the impeller 3, the turbine 4, and the stator 5. As is clear from FIG. 1, the torque converter main body 6 generally has the impeller 3 and the turbine 4 formed in an arc shape in cross section. In each of the shells 12 and 16 of the impeller 3 and the turbine 4, the portion located at the same radial position as the center of the torus protrudes to the outermost side (the transmission side in the impeller 3 and the engine side in the turbine 4). Therefore, on the turbine side, a relatively wide space is formed between the damper device 35 and the inner peripheral side of the torus center.

  Therefore, here, the engaging portion 51 between the turbine 4 and the damper device 35 is arranged using a relatively wide space on the inner peripheral side of the torus center C.

  Further, a plurality of notches 38c and 39c that are opened outward are formed at equal angular intervals on the outer peripheral ends of the first and second retaining plates 38 and 39. The notches 38c and 39c are portions that function as engaging portions with the lockup device 8.

  The hub flange 41 is formed in a disc shape, and is disposed so as to be sandwiched between the first retaining plate 38 and the second retaining plate 39.

  As is apparent from FIG. 2, a plurality of outer peripheral long holes 41a that are relatively long in the circumferential direction are formed on the outer peripheral side of the hub flange 41, and the inner peripheral side is more circumferential than the outer peripheral long hole 41a. A plurality of inner peripheral long holes 41b having a short direction length are formed. The outer peripheral side long hole 41 a is formed at the same position as the window holes 38 b and 39 b of the first and second retaining plates 38 and 39. Moreover, the outer peripheral side long hole 41a and the inner peripheral side long hole 41b are formed so that the center of the circumferential direction may shift | deviate and it may become alternate in the circumferential direction. An outer peripheral side torsion spring 44 is stored in the outer peripheral side long hole 41a, and an inner peripheral side torsion spring 45 is stored in the inner peripheral side long hole 41b.

  In addition, a plurality of notches 41 c that open to the outer peripheral side are formed at equiangular intervals at the outer peripheral end of the hub flange 41. In the notch 41c, the narrowed portions 38a and 39a of the first and second retaining plates 38 and 39 connected to each other by the rivet 48 are disposed. Therefore, when the first and second retaining plates 38 and 39 rotate relative to the hub flange 41, the throttle portions 38a and 39a come into contact with the circumferential ends of the notches 41c, thereby restricting the relative rotation. . That is, the notch 41c and the narrowed portions 38a and 39a constitute a stopper mechanism.

  At the inner peripheral end of the hub flange 41, a plurality of notches 41d that open to the inner peripheral side are formed at equal angular intervals.

  The turbine hub 42 is disposed on the inner peripheral side of the hub flange 41, and has a boss portion 42a and a flange portion 42b. In FIG. 2, only the flange portion 42b of the turbine hub 42 is shown.

  The boss portion 42a is a cylindrical member, and supports an inner peripheral end of the turbine support 19 at an end portion on the transmission side so as to be relatively rotatable. A spline hole 42c is formed on the inner peripheral surface of the boss portion 42a, and the spline hole 42c can be engaged with a transmission shaft.

  The flange portion 42b extends radially outward from the boss portion 42a and is formed in a disk shape. As shown in FIG. 2, a plurality of teeth 42d are formed on the outer peripheral end of the flange portion 42b. The teeth 42d are located in the notches 41d of the turbine hub 41. The circumferential length of the tooth 42d is shorter than the circumferential length of the notch 41d. Accordingly, the hub flange 41 and the turbine hub 42 can rotate relative to each other until the teeth 42d abut on the circumferential end of the notch 41d.

  The pair of clutch plates 43 are formed in a disc shape and have the same shape. A plurality of window holes 43 a are formed in the clutch plate 43 at the same position as the inner peripheral long hole 41 b of the hub flange 41. The inner periphery side torsion spring 45 is supported by the window hole 43a. The pair of clutch plates 43 are fixed to the hub flange 42 so as not to rotate relative to each other by a plurality of rivets 52.

  Further, the outer peripheral end portions of the pair of clutch plates 43 are inserted into the inner peripheral portions of the first and second retaining plates 38 and 39. More specifically, the outer peripheral end of the transmission-side clutch plate 43 is inserted between the inner peripheral end of the first retaining plate 38 and the hub flange 41. The outer peripheral end of the engine-side clutch plate 43 is inserted between the inner peripheral end of the second retaining plate 39 and the hub flange 41. Here, when the torsion springs 44 and 45 are compressed, a difference in rotation occurs between the first and second retaining plates 38 and 39 and the pair of clutch plates 43. The sliding portion comes into sliding contact, and hysteresis torque is thereby generated. The hysteresis torque will be described in detail later.

[Lock-up device]
The lockup device 8 is disposed in an annular space between the front cover 2 and the damper device 35. The lockup device 8 mainly includes a piston 55, a drive plate 56 and a driven plate 57 provided between the front cover 2 and the piston 55, and a clutch ring 58.

  The piston 55 is a disk-shaped plate member, and is disposed so as to divide the space between the front cover 2 and the turbine 4 into two in the axial direction. The outer peripheral portion of the piston 55 is a flat friction connecting portion 55a. Further, a flat friction surface is formed on the front cover 2 so as to face the friction coupling portion 55 a of the piston 55. An inner peripheral cylindrical portion 55 b extending toward the axial engine side is provided on the inner peripheral edge of the piston 55. The inner peripheral surface of the inner peripheral cylindrical portion 55 b is supported so as to be movable in the axial direction and the rotational direction with respect to the outer peripheral surface of the cylindrical portion 42 a of the turbine hub 42. A seal ring 60 is provided between the inner peripheral cylindrical portion 55 b and the outer peripheral surface of the cylindrical portion 42 a of the turbine hub 42.

  The drive plate 56 is an annular member and is fixed to the intermediate portion in the radial direction of the front cover 2. The outer peripheral portion of the drive plate 56 is bent toward the axial transmission side, and a plurality of protrusions are formed in the bent portion. On the other hand, the drive plate 57 is an annular member, and is fixed to the intermediate portion in the radial direction of the piston 55 by a rivet 62. A plurality of grooves are formed on the outer peripheral portion of the drive plate 57, and the grooves and the protrusions of the drive plate 56 are engaged with each other. By the drive plate 56 and the driven plate 57 as described above, the piston 55 is connected to the front cover 2 so as not to rotate relative to the front cover 2 and to be movable in the axial direction.

  The clutch ring 58 is an annular member, and includes a disk part 58a and an engagement part 58b extending from the outer peripheral end of the disk part 58a to the axial transmission side. The disc part 58a is disposed between the frictional connection part 55a of the piston 55 and the frictional connection surface of the front cover 2, and friction facings are fixed on both sides. The engaging portion 58b has a plurality of protrusions at the tip. The protrusions of the engaging portion 58b are engaged with the notches 38c and 39c of the first and second retaining plates 38 and 39.

[Operation]
Next, the operation will be described. Torque from the crankshaft on the engine side is input to the front cover 2. As a result, the impeller 3 rotates and hydraulic oil flows from the impeller 3 to the turbine 4. The turbine 4 is rotated by the flow of the hydraulic oil, and the torque transmission plate 34 fixed to the turbine 4 is similarly rotated.

  In the low speed range, the lockup device 8 is off (disconnected state), and in this case, the torque output from the turbine 4 is output to the transmission side via the torque transmission plate 34 and the damper device 35.

  Further, when the speed ratio of the torque converter 1 increases and reaches a predetermined speed range, the hydraulic fluid in the space between the front cover 2 and the piston 55 is drained. As a result, the piston 55 is moved to the front cover 2 side. As a result, the friction facing of the clutch ring 58 is sandwiched between the piston 55 and the friction connecting surface of the front cover 2, and the lockup device 8 is turned on (connected state). For this reason, the torque of the front cover 2 is transmitted to the damper device 35 via the piston 55 and the clutch ring 58 and is output to the transmission side without passing through the impeller 3 and the turbine 4.

  As described above, the torque input to the front cover 2 from the engine side is input to the damper device 35 via the torque converter body 6 and the torque transmission plate 34 when the lockup device 8 is off, and the lockup device When 8 is on, the signal is input to the damper device 35 via the lockup device 8.

  In the damper device 35, torque from the turbine 4 is transmitted from the torque transmission plate 34 to the first and second retaining plates 38, 39, and further, the outer peripheral side torsion spring 44, the hub flange 41, and the inner peripheral side torsion. It is transmitted to the spring 45. At this time, the torsion springs 44 and 45 transmit torque to the turbine hub 42 while being compressed.

  The characteristics of the damper device 35 at this time will be described statically. When torque is input to the damper device 35 and the torsion springs 44 and 45 are compressed, the hub flange 41 and the turbine hub 42 rotate relative to each other. When the relative rotation angle (torsion angle) increases, the teeth 42d of the turbine hub 42 abut on the circumferential ends of the notches 41d of the hub flange 41. For this reason, thereafter, the hub flange 41 and the turbine hub 42 rotate integrally.

  If the torque from the engine further increases after the teeth 42d of the turbine hub 42 abuts the end of the notch 41d of the hub flange 41, the twist angles of the first and second retaining plates 38, 39 with respect to the hub flange 41 Becomes larger and the outer peripheral side torsion spring 44 is further compressed. In this case, since the turbine hub 42 and the clutch plate 43 and the hub flange 41 rotate integrally, the inner peripheral side torsion spring 45 is not compressed, and only the outer peripheral side torsion spring 44 is compressed.

  When excessive torque is input to the damper device 35, the torsion angles of the first and second retaining plates 38 and 39 with respect to the hub flange 41 become very large. Accordingly, the narrowed portions 38a, 39a formed on the both retaining plates 38, 39 abut against the circumferential ends of the notches 41c formed on the outer periphery of the hub flange 41, and further relative rotation is prohibited.

[Hysteresis torque]
When the damper device 35 operates as described above, when the torsion springs 44 and 45 are compressed and expanded, relative rotation occurs between the input side and the output side. Specifically, the first and second retaining plates 38 and 39 and the clutch plate 43 fixed to the turbine hub 42 rotate relative to each other according to torque fluctuation. For this reason, in a dynamic state, when the inner peripheral portion of the first and second retaining plates 38 and 39 and the outer peripheral portion of the clutch plate 43 are in contact with each other, the sliding contact occurs, and hysteresis torque is generated. Therefore, desired hysteresis torque characteristics can be obtained by variously changing the specifications such as the rigidity and dimensions of the retaining plates 38 and 39 and the clutch plate 43. Examples of the characteristics are shown below.

(I) High hysteresis at low rotation In order to obtain a high hysteresis torque in a low rotation speed range, the rigidity of the retaining plates 38 and 39 may be lowered and the rigidity of the clutch plate 43 may be increased. Then, at the time of stopping, both plates 38, 39, 43 are set so as to come into strong pressure contact with each other.

  In this case, since the press contact force between the retaining plates 38 and 39 and the clutch plate 43 is strong in the low rotational speed range, a high hysteresis torque is generated. On the other hand, when the rotational speed is increased, the retaining plates 38 and 39 having low rigidity are elastically deformed so that the inner peripheral ends are opened outward by centrifugal force. Further, the highly rigid clutch plate 43 is not easily deformed. For this reason, the pressure contact force between the retaining plates 38 and 39 and the clutch plate 43 is reduced, and the hysteresis torque is reduced.

(Ii) High hysteresis at high rotation In order to obtain high hysteresis torque in a high rotation speed region, the rigidity of the retaining plates 38 and 39 may be increased and the rigidity of the clutch plate may be decreased. At the time of stopping, the plates 38, 39, and 43 are set so that the pressure contact force is weakened.

  In this case, since the pressure contact force between the retaining plates 38 and 39 and the clutch plate 43 is weak in the low speed range, a low hysteresis torque is generated. On the other hand, when the rotational speed is increased, the highly rigid retaining plates 38 and 39 are not easily deformed even if centrifugal force is generated. On the contrary, the clutch plate 43 having low rigidity opens the outer peripheral end of the plate itself by centrifugal force, and the inner peripheral torsion spring 45 moves outward by the centrifugal force. Is elastically deformed to open outward. For this reason, the press contact force between the retaining plates 38 and 39 and the clutch plate 43 is increased, and the hysteresis torque is increased.

[Characteristic]
In the above embodiment, since the hysteresis torque generating mechanism is realized using the retaining plates 38 and 39 and the clutch plate 43, a special member for generating the hysteresis torque becomes unnecessary. Further, by changing the specifications of the retaining plates 38 and 39 and the clutch plate 43, the hysteresis torque can be arbitrarily adjusted.

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

  (A) In the above-described embodiment, the retaining plates 38 and 39 and the clutch plate 43 are directly slidably contacted, but a friction facing may be attached to any of the plates. A predetermined clearance may be provided between both plates. However, in this case, hysteresis torque due to sliding contact between both plates does not occur.

  (B) Although the present invention is applied to the power transmission device of the torque converter in the above embodiment, the present invention can be similarly applied to other power transmission devices.

1 Torque Converter 2 Front Cover 6 Torque Converter Body 35 Damper Device 38, 39 Retaining Plate (Input Plate)
41 Hub flange (intermediate member)
42 Turbine hub 43 Clutch plate (output plate)
44 Outer peripheral side torsion spring 45 Inner peripheral side torsion spring

Claims (4)

A damper device that transmits torque input from a member on an engine side to a member on a transmission side,
Torque is input from the engine side member, and a pair of input plates arranged at a predetermined interval from each other;
A plurality of outer peripheral elastic members supported by the pair of input plates and receiving torque from the pair of input plates;
A pair of output plates that are connectable to the transmission side member and are spaced apart from each other;
A plurality of inner peripheral elastic members supported by the pair of output plates on the inner peripheral side of the plurality of outer peripheral elastic members, and transmitting torque to the pair of output plates;
An intermediate member disposed between the pair of input plates in the axial direction, for causing the outer peripheral side elastic member and the inner peripheral side elastic member to act in series;
With
A part of the pair of input plates and a part of the pair of output plates are opposed to each other in the rotation axis direction.
Damper device. Each of the pair of input plates is formed in an annular shape and has a window hole for supporting the outer peripheral side elastic member,
Each of the pair of output plates is disposed on the inner peripheral side of the pair of input plates, is formed in an annular shape, and has a window hole for supporting the inner peripheral elastic member,
The outer peripheral portion of the pair of output plates is inserted into the inner peripheral portion of the pair of input plates, and the output plate and a part of the input plate overlap in the rotation axis direction,
The damper device according to claim 1. An output hub fixed to the pair of output plates;
The intermediate member and the output hub are capable of relative rotation within a predetermined angle range.
The damper device according to claim 1 or 2. The damper device according to any one of claims 1 to 3, wherein portions of the pair of input plates and the pair of output plates facing each other in a rotation axis direction are in sliding contact with each other.

Images