JP4684347B1 - Damper device - Google Patents

Abstract

In a damper device with a wide twist angle, a stopper mechanism is realized with a simple configuration.
The damper device includes first and second retaining plates 38, 39, an outer peripheral torsion spring 44 supported by the retaining plates 38, 39, a pair of clutch plates 43, And an inner peripheral side torsion spring 45 supported by the clutch plate 43. The first and second retaining plates 38 and 39 and the pair of clutch plates 43 are formed with stopper portions 65 that engage with each other when both plates exceed a predetermined relative rotation angle range.
[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

  In the damper device, in order not to apply excessive stress to the torsion spring, a stopper mechanism is provided so that the relative rotation angle (torsion angle) between the input side member and the output side member is regulated within a predetermined angle. It has been. For example, in the damper device disclosed in Patent Document 1, a stopper mechanism is formed by inserting a rivet into a notch. Here, the relative rotation between the input side member and the output side member is allowed within the angle range where the notch is formed, and if the rivet comes into contact with the end of the notch, the relative rotation between the two is prohibited.

  As described above, the conventional damper device requires a plurality of rivets or pins in order to constitute the stopper mechanism.

  An object of the present invention is to realize a stopper mechanism with a simple configuration, particularly in a damper device with a wide twist angle.

  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 are arranged at a predetermined interval from each other, and torque is input from a member on the engine side. 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 are arranged at a predetermined interval from each other and can be connected to a member on the transmission side. 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. An intermediate member is arrange | positioned between the axial directions of a pair of input plates, and makes an outer peripheral side elastic member and an inner peripheral side elastic member act in series. The pair of input plates and the pair of output plates are formed with stopper portions that engage with each other when both plates exceed a predetermined relative rotation angle range.

  In this damper device, when torque is input from a member on the engine side to a pair of input plates, this torque is paired via a plurality of outer peripheral side elastic members, intermediate members, and a plurality of inner peripheral side elastic members. To the output plate and further to the transmission side member. Here, when the plurality of outer peripheral side elastic members and inner peripheral side elastic members are elastically deformed, the input plate and the output plate rotate relative to each other (twisted in the rotation direction). This twist angle is regulated by a stopper portion formed on the pair of input plates and the pair of output plates.

  Here, since the torsion angles of both plates are regulated by the stopper portions formed on the input plate and the output plate, members such as rivets and pins in the conventional apparatus are not necessary. Therefore, the stopper mechanism can be realized with a simple configuration.

  The damper device according to claim 2 is the device according to claim 1, wherein each of the pair of input plates and the pair of output plates is formed in an annular shape, and the pair of output plates is on the inner peripheral side of the input plate Is arranged. The pair of input plates has a plurality of input side locking portions formed at predetermined intervals in the rotation direction at the inner peripheral end portion. Moreover, a pair of output plate is formed in the outer peripheral edge part at predetermined intervals in the rotation direction, and has a plurality of output side locking portions that are locked to the plurality of input side locking portions.

  Here, since the output plate is disposed on the inner peripheral side of the input plate, the stopper portion is configured using the inner peripheral end portion and the outer peripheral end portion of each plate.

  The damper device according to a third aspect is the device according to the second aspect, wherein the input side locking portion is a first protruding portion that protrudes outward in the axial direction, and the first protruding portion is first in the axial direction. It has the 1st space of a rotation angle range. The output side latching portion is a second projecting portion that protrudes outward in the axial direction and is inserted into the first space, and the second projecting portion is rotated outward in the axial direction by a second rotation smaller than the first rotation angle range. It is formed over an angular range.

  The “axially outer side” is “transmission side” in the transmission side input plate and “engine side” in the engine side input plate of the pair of input plates.

  Here, the first protrusion and the second protrusion can be formed by pressing each plate. Therefore, the stopper portion can be easily formed.

  According to a fourth aspect of the present invention, there is provided the damper device according to the third aspect, wherein a part of the inner peripheral end part of the pair of input plates and a part of the outer peripheral end part of the pair of output plates are the outer peripheral elastic member and the inner peripheral part. The sliding contact is made by elastic deformation of the side elastic member.

  Here, hysteresis torque can be generated by sliding a part of the input plate and the output plate. For this reason, a special member for generating hysteresis torque is not necessary.

  The damper device according to claim 5 is the device according to claim 2, wherein the input side locking portion is a plurality of claws formed at predetermined intervals on the inner peripheral end portion, and the output side locking portion is the outer peripheral end portion. Each of the plurality of claws is formed into a notch that can be inserted and rotated within a predetermined angle range.

  Here again, as described above, the stopper portion can be formed by pressing each plate, which facilitates the manufacture.

  According to the present invention as described above, the stopper mechanism of the damper device can be realized with a simple configuration.

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. The figure equivalent to FIG. 1 of other embodiment of this invention. The figure equivalent to FIG. 2 of other embodiment of this invention.

  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>
As shown in FIGS. 1 and 2, the damper device 35 includes first and second retaining plates (a pair of input plates) 38 and 39, a hub flange (intermediate member) 41, a turbine hub 42, 1 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 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. The plurality of protrusions 50 are arranged at predetermined intervals in the circumferential direction, and the protrusions 50 are engaged with grooves formed on the outer peripheral portion of the torque transmission plate 34.

  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.

  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, 45 are compressed, a difference in rotation occurs between the first and second retaining plates 38, 39 and the pair of clutch plates 43. In this portion, hysteresis torque is generated.

[Stopper part]
Here, as shown in the developed view of FIG. 3, the first and second retaining plates 38 and 39 and the clutch plate 43 are provided with a stopper portion 65 for restricting the relative rotation (twisting angle) of both plates. Is formed. In FIG. 3, only one stopper portion 65 (left side in FIG. 1) is shown, but the configuration of the other stopper portion is the same.

  The stopper portion 65 has an input side locking portion 66 formed on the retaining plates 38 and 39 and an output side locking portion 67 formed on the clutch plate 43.

The input side locking portion 66 is formed in a wave shape so that the inner peripheral end portions of the retaining plates 38 and 39 are uneven in the axial direction by pressing. Specifically, the inner peripheral ends of the retaining plates 38 and 39 are formed so as to protrude outward in the axial direction (the first retaining plate 38 is on the transmission side and the second retaining plate 39 is on the engine side). One protrusion 66a is formed. The first protrusion 66a has a first space 66b having a first rotation angle range R1 on the inner side in the axial direction. And
Moreover, the output side latching | locking part 67 is the 2nd protrusion part 67a formed by pushing out a part of outer peripheral edge part of the clutch plate 43 to an axial direction outer side by press work. More specifically, the second projecting portion 67a is inserted into the first space 66b of the retaining plates 38 and 39. And this 2nd protrusion part 67a is continuously formed in the axial direction outer side over 2nd rotation angle range R2 smaller than 1st rotation angle range R1.

  In such a stopper portion 65, the retaining plates 38 and 39 and the clutch plate 43 can rotate relative to each other over an angular range in which the second projecting portion 67a can move in the first space 66b. And when the 2nd protrusion part 67a contact | abuts the edge part of the 1st space 66b, both relative rotation is prohibited.

[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 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, depending on the setting of the clearance between the inner peripheral portion of the first and second retaining plates 38 and 39 and the outer peripheral portion of the clutch plate 43, both are brought into sliding contact and a hysteresis torque is generated. .

  Further, when excessive torque is input to the damper device 35, the torsion angles of the first and second retaining plates 38, 39 with respect to the output side member, that is, the clutch plate 43, become very large. Then, the 2nd protrusion part 67a formed in the clutch plate 43 contact | abuts to the edge part of the 1st space 66b of the retaining plates 38 and 39. FIG. Therefore, further relative rotation of the retaining plates 38 and 39 and the clutch plate 43 is prohibited.

[Characteristic]
In the embodiment as described above, the stopper portion is formed at the portion where the inner peripheral end portions of the retaining plates 38 and 39 and the outer peripheral end portion of the clutch plate 43 overlap in the axial direction. A mechanism can be realized.

  Since a member such as a rivet or a stop pin is not required as in the conventional apparatus, the apparatus can be further downsized. Further, since the hub flange is not used as a stopper mechanism, the stress acting on the hub flange is relieved.

[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.

  4 and 5 show another embodiment of the stopper portion. In the embodiment shown in FIGS. 4 and 5, the members constituting the stopper portion are different from those in the above embodiment, but other configurations are completely the same.

  In this embodiment, a plurality of claws 70 are formed at predetermined intervals in the circumferential direction at the inner peripheral ends of the retaining plates 68 and 69. The plurality of claws 70 protrude to the inner peripheral side. On the other hand, a plurality of notches 71 that open to the outer peripheral side are formed at the outer peripheral end of the clutch plate 73. Each of the plurality of claws 70 is inserted into the notch 71 of the clutch plate 73. The width of the claw 70 in the rotation direction is sufficiently smaller than the width of the notch 71 in the rotation direction. For this reason, in the angle range in which the claw 70 can move within the notch 71, the retaining plates 68 and 69 and the clutch plate 73 can be rotated relative to each other, and when the claw 70 contacts the end of the notch 71. The relative rotation (twisting) of the two is prohibited.

  Also according to the embodiment as described above, it is possible to obtain the same effect as that of the embodiment. In this case, a hysteresis torque generation mechanism by sliding contact between the retaining plates 68 and 69 and the clutch plate 73 cannot be realized.

1 Torque Converter 2 Front Cover 6 Torque Converter Body 35 Damper Device 38, 39, 68, 69 Retaining Plate (Input Plate)
41 Hub flange (intermediate member)
42 Turbine hub 43, 73 Clutch plate (output plate)
50 Projection 65 Stopper portion 66 Input side locking portion 66a First protrusion 66b First space 67 Output side locking portion 67a Second protrusion 70 Claw 71 Notch

Claims (5)

A damper device that transmits torque input from a member on an engine side to a member on a transmission side,
A pair of input plates that are arranged at a predetermined distance from each other and to which torque is input from the engine-side member;
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 arranged at a predetermined distance from each other and connectable to the transmission side member;
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
The pair of input plates and the pair of output plates are formed with stopper portions that engage with each other when both plates exceed a predetermined relative rotation angle range.
Damper device. Each of the pair of input plates and the pair of output plates is formed in an annular shape, and the pair of output plates are arranged on the inner peripheral side of the input plate,
The pair of input plates have a plurality of input side locking portions formed at predetermined intervals in the rotation direction at the inner peripheral end portions,
The pair of output plates have a plurality of output side locking portions that are formed at a predetermined interval in the rotation direction at outer peripheral end portions and locked to the plurality of input side locking portions,
The damper device according to claim 1. The input side locking portion is a first protruding portion that protrudes outward in the axial direction, and the first protruding portion has a first space in a first rotation angle range on the inner side in the axial direction,
The output side locking portion is a second protruding portion that protrudes outward in the axial direction and is inserted into the first space, and the second protruding portion is smaller than the first rotation angle range outward in the axial direction. Formed over a range of two rotation angles,
The damper device according to claim 2.   A part of the inner peripheral end portion of the pair of input side plates and a part of the outer peripheral end portion of the pair of output side plates are in sliding contact with each other by elastic deformation of the outer peripheral side elastic member and the inner peripheral side elastic member; The damper device according to claim 3. The input side locking portion is a plurality of claws formed at predetermined intervals on the inner peripheral end portion,
The output side locking portion is a notch that is formed at an outer peripheral end portion, and each of the plurality of claws is inserted and the plurality of claws can be rotated within a predetermined angle range.
The damper device according to claim 2.

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