WO2016129183A1

WO2016129183A1 - Damper disk assembly

Info

Publication number: WO2016129183A1
Application number: PCT/JP2015/085633
Authority: WO
Inventors: 喜隆窪田; 一樹橋本
Original assignee: 株式会社エクセディ
Priority date: 2015-02-10
Filing date: 2015-12-21
Publication date: 2016-08-18
Also published as: DE112015005923T5; JP6501295B2; CN107208707B; CN107208707A; JP2016148360A

Abstract

Provided is a damper disk assembly wherein a stopper mechanism can easily achieve high torque and a widened angle. This damper disk assembly is provided with input-side plates (3, 4), a first flange (5), a second flange (6), an output hub (7), and a stopper mechanism. The first flange (5) is capable of relative rotation when the input-side plates (3, 4) rotate in a first direction and is prohibited from relative rotation when the plates rotate in a second direction. The second flange (6) has a configuration that is opposite the configuration of the first flange (5). The output hub (7) can be connected to an input shaft of a transmission and is connected to the first and second flanges (5, 6) so as to be capable of relative rotatation within a prescribed angular range. The stopper mechanism is formed on a connecting part that connects the first and second flanges (5, 6) to the output hub (7) and restricts relative rotation between the input-side plates (3, 4) and the output hub (7) to a prescribed angular range.

Description

Damper disk assembly

The present invention relates to a damper disk assembly, and more particularly to a damper disk assembly for transmitting power from an engine to an input shaft of a transmission.

A damper disk assembly used for a clutch disk assembly or the like includes a plurality of input plates, an output hub having a flange on the outer periphery, and a plurality of elastically connecting the pair of input plates and the output hub in the circumferential direction. And a torsion spring. The pair of input plates are fixed to each other by a plurality of stop pins at the outer periphery. The stop pin is inserted into a notch cut out on the outer peripheral edge of the flange constituting the output hub (see FIG. 2 of Patent Document 1).

In such a configuration, the pair of input plates and the flange of the output hub can be rotated relative to each other within a predetermined angle range, but if the stop pin comes into contact with the edge of the notch, the relative rotation of the two is prohibited. Is done.

JP 2003-278791 A

In the conventional clutch disk assembly, the stop pin needs to have a certain diameter, and must be further arranged on the inner peripheral side than the outer peripheral edge of the pair of input plates. That is, in order to configure the stop mechanism, a considerable space is required on the outer periphery of the flange portion of the output hub.

In such a configuration, the relative torsion angle between the pair of input plates and the flange of the output hub cannot be sufficiently increased. Further, the space for the torsion spring is limited, which hinders the increase in torque capacity.

An object of the present invention is to obtain a damper disk assembly having a stopper mechanism that can easily realize high torque and wide angle.

A damper disk assembly according to a first aspect of the present invention is for transmitting power from an engine to an input shaft of a transmission, and includes an input member, a first flange, a second flange, and an output hub. And a plurality of elastic members and a stopper mechanism. The input member receives power from the engine. The first flange is disposed to face the input member in the axial direction, and is rotatable relative to the input member within a predetermined angle range when the input member rotates in the first direction, and the input member is in the second direction. When rotating, relative rotation with the input member is prohibited. The second flange is disposed so as to face the first flange in the axial direction. When the input member rotates in the second direction, the input member can rotate relative to the input member within a predetermined angle range. When rotating in the forward direction, relative rotation with the input member is prohibited. The output hub is connectable to an input shaft of the transmission, and is connected to the first and second flanges so as to be relatively rotatable within a predetermined angle range. The plurality of elastic members elastically connect the input member and the first and second flanges in the circumferential direction. The stopper mechanism is formed at a connecting portion between the first and second flanges and the output hub, and restricts relative rotation between the input member and the output hub within a predetermined angular range.

Here, when the input member rotates in the first direction, the rotation of the input member is transmitted to the first flange via the plurality of elastic members, and further transmitted to the transmission side via the output hub. At this time, relative rotation with the input member is prohibited, and the second flange rotates integrally with the input member. When the elastic member is elastically deformed and the torsion angle between the input member and the first flange becomes a predetermined angle, the output hub comes into contact with the second flange. Thereby, the twist angle of an input member and an output hub is controlled.

In such a configuration, there is no need to provide a stopper mechanism including a stop pin on the outer periphery of the flange as in the conventional device. Therefore, a wide space for the elastic member can be secured, and high torque and wide angle can be easily realized.

The damper disk assembly according to the second aspect of the present invention is the damper disk assembly according to the first aspect, wherein the first flange engages the input member so as not to rotate relative to the input member when the input member rotates in the second direction. It has an engaging part. In addition, the second flange has an engaging portion that engages with the input member so as not to be relatively rotatable when the input member rotates in the first direction.

Here, by providing an engaging portion on each flange, relative rotation with the input member can be prohibited.

The damper disk assembly according to the third aspect of the present invention is the damper disk assembly according to the second aspect, wherein the input member has a plurality of accommodating portions for accommodating the plurality of elastic members. And the engaging part of a 1st and 2nd flange is the protrusion part which protrudes in the axial direction pinched | interposed between the rotation direction end surface of the at least 1 accommodating part of a some accommodating part, and the rotation direction end surface of an elastic member. is there.

Here, the end surface in the rotation direction of the elastic member is supported by the protrusion. That is, the protrusion functions also as a sheet of the elastic member. Therefore, it is not necessary to prepare a sheet for supporting the end face of the elastic member.

The damper disk assembly according to the fourth aspect of the present invention is the damper disk assembly according to any one of the first to third aspects, wherein the first and second flanges are annular plate members. The stopper mechanism has a plurality of notches and a plurality of teeth. The plurality of notches are formed at predetermined intervals in the circumferential direction on the inner peripheral edges of the first and second flanges. The plurality of teeth are formed on the outer peripheral portion of the output hub, and are inserted into the cutouts of the first and second flanges through a predetermined gap in the rotational direction. The plurality of notches in the first flange and the plurality of notches in the second flange are arranged so that the phases in the rotational direction are shifted.

The damper disk assembly according to a fifth aspect of the present invention is the damper disk assembly according to any one of the first to fourth aspects, wherein the input members are first and second input plates arranged opposite to each other in the axial direction. It is. The first and second flanges are arranged between the first input plate and the second input plate in the axial direction.

As described above, according to the present invention, the conventional flange is divided into the one rotation side hub and the other rotation side hub, and the stopper mechanism is configured using the non-actuated flange. Thus, it is not necessary to configure a stopper mechanism on the flange outer periphery of the output hub, and high torque and wide angle can be easily realized.

1 is a cross-sectional view of a clutch disk assembly according to an embodiment of the present invention. The front view of a clutch disk assembly. The perspective view of a flange. The expanded partial view of FIG. 2 which shows the connection part of an output hub and a flange. The figure which expands and shows a pre-damper unit. The figure which expands and shows the stopper mechanism part of a pre-damper unit.

FIG. 1 shows a clutch disk assembly 1 as an embodiment of the present invention. The clutch disk assembly 1 is a device for transmitting and interrupting torque from an engine (not shown) arranged on the left side of FIG. 1 to a transmission (not shown) arranged on the right side of FIG. . In FIG. 1, OO is the rotational axis of the clutch disk assembly 1.

[overall structure]
The clutch disk assembly 1 includes a clutch disk 2, a clutch plate (first input plate) 3, a retaining plate (second input plate) 4, first and

second flanges

5, 6, and an output hub 7. A plurality of torsion springs 8, a hysteresis torque generating mechanism 9, and a pre-damper unit 10 are provided.

[Clutch disk 2]
As shown in FIGS. 1 and 2, the clutch disk 2 includes an annular cushioning plate 12 having a plurality of mounting portions arranged side by side in the circumferential direction, and an annular cushioning plate 12 fixed to both surfaces of the cushioning plate 12 by rivets 13. And a friction facing 14. The inner peripheral part of the cushioning plate 12 is fixed to the outer peripheral part of the clutch plate 3 by rivets (not shown). An engine-side flywheel (not shown) is disposed on the left side of the friction facing 14 in FIG. 1, and the friction-facing 14 is pressed against the flywheel, whereby the engine-side torque is applied to the clutch disc assembly 1. Is entered.

[Clutch plate 3 and retaining plate 4]
The clutch plate 3 and the retaining plate 4 are formed in a disc shape, and are disposed opposite to each other in the axial direction with the first and

second flanges

5 and 6 interposed therebetween. These two

plates

3 and 4 are fixed by a stud pin 16 so as not to be relatively rotatable.

As shown in FIGS. 1 and 2, the clutch plate 3 and the retaining plate 4 include four

first storage portions

3 a and 4 a for storing the torsion springs 8 and four second storage portions in portions facing each other. 3b and 4b are formed. The four

first storage portions

3a and 4a are arranged at intervals of 90 °, and the

second storage portions

3b and 4b are arranged between them. Each of the

storage portions

3a, 3b, 4a, 4b is formed so as to bulge outward in the axial direction (the clutch plate 3 is on the engine side and the retaining plate 4 is on the transmission side), and an opening is formed in the center portion. Yes.

[First and second flanges 5, 6]
The first and

second flanges

5 and 6 are disposed so as to be sandwiched between the clutch plate 3 and the retaining plate 4. Both the

flanges

5 and 6 have the same shape, and the first flange 5 will be specifically described here.

As shown in FIG. 3, the first flange 5 is a disk-like plate, and has four first openings 5a and four second openings 5b arranged in the circumferential direction. The first opening 5a is larger than the second opening 5b in the radial direction and the rotation direction. The first opening 5 a is formed at a position corresponding to the

first storage portions

3 a and 4 a of the clutch plate 3 and the retaining plate 4. The second opening 5 b is formed at a position corresponding to the

second storage portions

3 b and 4 b of the clutch plate 3 and the retaining plate 4.

In addition, the stud pin 16 has penetrated the inner peripheral part of 1st opening 5a, 6a of both the

flanges

5 and 6 to an axial direction (refer FIG. 2).

A spring support part (protrusion part) 5c is formed on one end face in the rotational direction of the four first openings 5a. The spring support portion 5c has a substantially rectangular shape, and the end surfaces of the first coil spring 8a and the second coil spring 8b among the plurality of torsion springs 8 are in contact with the spring support portion 5c. The surface of the spring support portion 5c opposite to the surface that receives the torsion spring 8 is in contact with one end surface of the clutch plate 3 and the retaining plate 4 in the rotational direction of the

first storage portions

3a and 4a.

With the configuration as described above, the spring support portion 5c of the first flange 5 is located between one end surface of the torsion spring 8 and one end surface of the

first storage portions

3a and 4a of the clutch plate 3 and the retaining plate 4. It is pinched. Therefore, when the clutch plate 3 and the retaining plate 4 rotate in the + R direction of FIGS. 2 to 4, the first flange 5 is prohibited from rotating relative to the clutch plate 3 and the retaining plate 4, and these It will rotate integrally with both

plates

3 and 4. When the clutch plate 3 and the retaining plate 4 rotate in the −R direction, the first flange 5 is allowed to rotate relative to the clutch plate 3 and the retaining plate 4 within a predetermined angle range.

Further, as shown in FIG. 4 which is an enlarged partial view of FIGS. 3 and 2, a plurality of cutouts 5 d that open toward the inner periphery are formed in the inner periphery of the first flange 5.

As described above, the second flange 6 has the same shape as the first flange 5. And about this 2nd flange 6, the spring support part 6c is clamped between the other end surface of the torsion spring 8, and the other end surface of the 1st

accommodating parts

3a and 4a of the clutch plate 3 and the retaining plate 4. FIG. ing. Therefore, when the clutch plate 3 and the retaining plate 4 rotate in the −R direction, the second flange 6 is prohibited from rotating relative to the clutch plate 3 and the retaining plate 4. Will rotate together. When the clutch plate 3 and the retaining plate 4 rotate in the + R direction, the second flange 5 is allowed to rotate relative to the clutch plate 3 and the retaining plate 4 within a predetermined angle range.

Further, a plurality of notches 6d that open toward the inner peripheral side are formed in the inner peripheral portion of the second flange 6.

As shown in FIGS. 2 and 4, the

notches

5d and 6d in the inner peripheral portions of the

flanges

5 and 6 are assembled with their phases shifted in the rotational direction.

[Output hub 7]
The output hub 7 is a cylindrical member, and as shown in FIG. 1, a spline hole 7a is formed in the inner periphery. The input shaft of the transmission can be spline engaged with the spline hole 7a.

As shown in FIGS. 1, 2 and 4, a plurality of first teeth 7b are formed on the outer peripheral surface of the output hub 7, and a plurality of second teeth 7c are formed on the outer peripheral surface of the end portion on the transmission side. Is formed. Each of the plurality of first teeth 7b is inserted into the

notches

5d and 6d of the

flanges

5 and 6 through a predetermined gap.

Specifically, as described above, the first and

second flanges

5 and 6 are arranged in a state where the phase is shifted in the rotation direction. Therefore, as shown in FIG. 4, in the neutral state where no torque is input, the first gap G1 is formed between the first tooth 7b of the output hub 7 and the end surface in the rotational direction of the notch 5d of the first flange 5. A second gap G2 wider than the first gap G1 is formed between the first teeth 7b and the end face in the rotational direction of the notch 6d of the second flange 6.

[Torsion spring 8]
The torsion spring 8 has first to

third coil springs

8a, 8b and 8c. The first coil spring 8 a and the second coil spring 8 b are disposed in the first openings 5 a and 6 a of the first and

second flanges

5 and 6, and are formed by the

first storage portions

3 a and 4 a of the clutch plate 3 and the retaining plate 4. It is supported. The second coil spring 8b is disposed on the inner periphery of the first coil spring 8a. The third coil spring 8 c is disposed in the second openings 5 b and 6 b of the first and

second flanges

5 and 6 and is supported by the

second storage portions

3 b and 4 b of the clutch plate 3 and the retaining plate 4. .

[Hysteresis torque generating mechanism 9]
The hysteresis torque generating mechanism 9 is arranged between the clutch plate 3 and the first flange 5, between the first flange 5 and the second flange 6, and between the second flange 6 and the retaining plate 4. Yes. Although a detailed description of the mechanism 9 is omitted, the friction washer that is prohibited from rotating relative to the clutch plate 3 beyond a predetermined angle range, the friction plate that contacts the side surface of the first flange 5, and the friction plate are connected to the first flange. It is comprised from the cone spring which presses to the 5 side.

[Pre-damper unit 10]
As shown in FIGS. 1 and 5, the pre-damper unit 10 is disposed on the inner peripheral portion of the retaining plate 4 and on the outer peripheral portion on the transmission side of the output hub 7. Torque is input to the pre-damper unit 10 via the retaining plate 4. The pre-damper unit 10 includes a first sub-plate (intermediate plate) 21, a second sub-plate (output-side plate) 22, a plurality of outer peripheral pre-torsion springs 23, and a plurality of inner peripheral pre-torsion springs 24 ,have. FIG. 5 is an enlarged partial view of FIG.

As shown in FIG. 5, a plurality of notches 4c for housing springs are formed on the side surface of the retaining plate 4 on the transmission side. The outer periphery side pre-torsion spring 23 is housed in the plurality of notches 4c, and the end surface of the outer periphery side pre-torsion spring 23 is engaged with the end surface of the notch 4c. A part of the notch 4c on the engine side is open.

The first sub-plate 21 is formed in a disc shape, and includes a plurality of first storage portions 21a formed on the outer peripheral portion and a plurality of second storage portions 21b formed on the inner peripheral portion. ing. The first sub-plate 21 is rotatable relative to the retaining plate 4 and the second sub-plate 22 within a predetermined angle range.

The first storage portion 21 a is formed so as to swell toward the transmission side, and stores and holds the outer peripheral side pre-torsion spring 23 together with the notch 4 c of the retaining plate 4. Further, the end face of the outer peripheral pre-torsion spring 23 is engaged with the end face in the rotation direction of the first storage portion 21a.

The second storage portion 21b is formed so as to swell toward the engine side, and stores and holds a part of the inner peripheral side pre-torsion spring 24. Further, the end face of the inner peripheral side pre-torsion spring 24 is engaged with the end face in the rotation direction of the second storage portion 21b.

The second sub plate 22 is disposed on the transmission side of the first sub plate 21 so as to face the first sub plate 21. The second sub plate 22 is formed with a plurality of storage portions 22b that swell toward the transmission side, and stores and holds the inner peripheral side pre-torsion spring 24 together with the second storage portion 21b of the first sub plate 21. . A plurality of teeth 22 c are formed on the inner peripheral portion of the second sub-plate 22, and the teeth 22 c mesh with the second teeth 7 c of the output hub 7.

In such a configuration, the outer peripheral side pre-torsion spring 23 and the inner peripheral side pre-torsion spring 24 act in series. In this example, the outer peripheral side pre-torsion spring 23 has higher rigidity than the inner peripheral side pre-torsion spring 24.

Further, an arc-shaped hole 21c having a predetermined length in the rotation direction is formed in the radial intermediate portion of the first sub-plate 21. On the other hand, an engagement protrusion 22d formed by bending toward the engine side is formed on a part of the outer peripheral portion of the second sub-plate 22, and the engagement protrusion 22d is formed in the first subreport via a predetermined gap. 21 is inserted into the arcuate hole 21c.

A snap ring 26 is provided on the transmission side in the inner periphery of the second sub-plate 22. The snap ring 26 prevents the pre-damper unit 10 from coming out to the transmission side.

[Operation]
When the friction facing 14 is pressed against the flywheel on the engine side, torque from the engine is transmitted to the clutch plate 3 and the retaining plate 4 via the clutch disk 2. This torque is transmitted through the path of the torsion spring 8 → the first flange 5 or the second flange 6 → the output hub 7. Further, the torque transmitted to the retaining plate 4 is output to the transmission-side shaft through the path of the retaining plate 4 → the pre-damper unit 10 → the output hub 7.

Specifically, when a torsional vibration with a small displacement angle is transmitted from the engine side to the clutch disc assembly 1 during idling, the torsional spring 8 and the hysteresis torque generating mechanism 9 do not absorb the torsional vibration. And transmitted to the pre-damper unit 10. In the pre-damper unit 10, the outer peripheral side pre-torsion spring 23 and the inner peripheral side pre-torsion spring 24 operate in series, and the relative relationship between the retaining plate 4 and the first and second sub-plates 21 and 22 is relative. Rotation occurs. Here, a small hysteresis torque generated by sliding of each member is generated (more specifically, a hysteresis torque generating mechanism is provided on the outer peripheral side of the output hub 7 of the main damper unit), and a screw having a small displacement angle. Vibration is attenuated.

Here, when the torsional vibration is small, only the inner peripheral side pre-torsion spring 24 or the inner peripheral side pre-torsion spring 24 and the outer peripheral side pre-torsion spring 23 expands and contracts. When the torsional vibration is further increased and the elastic deformation of the inner peripheral side pre-torsion spring 24 is increased, the engagement protrusion 22d of the second sub-plate 22 contacts the end surface of the arc-shaped hole 21c of the first sub-plate 21. . Therefore, thereafter, only the outer peripheral side pre-torsion spring 23 is further elastically deformed.

By the operation as described above, the pre-damper unit 10 can have a torsional characteristic with a wide angle and two stages.

Next, the case where torsional vibration having a larger displacement angle is transmitted to the clutch disc assembly 1 will be described below.

In such a situation, when the clutch plate 3 and the retaining plate 4 rotate in the -R direction, the first flange 5 can rotate relative to both the

plates

3 and 4, but the second flange 6 Relative rotation with both

plates

3 and 4 is prohibited, and the plates rotate integrally. Therefore, when both

plates

3 and 4 rotate in the -R direction, torque is transmitted from both

plates

3 and 4 to the pre-damper unit 10 and also to the first flange 5 via the torsion spring 8, and further to the output hub. 7 is transmitted.

At this time, the operation of the pre-damper unit 10 as described above causes the output hub 7 and the first flange 5 to relatively rotate by a torsion angle corresponding to the gap G1 shown in FIG. When the first teeth 7b of the output hub 7 come into contact with the + R direction end face of the notch 5d of the first flange 5, the output hub 7 and the first flange 5 rotate integrally. After that, when the torsion spring 8 is elastically deformed and the

plates

3, 4 and the second flange 6, the first flange 5 and the output hub 7 are relatively rotated by an angle corresponding to the gap G2, the output hub 7 One tooth 7b abuts against the end surface in the + R direction of the notch 6d of the second flange 6, and relative rotation thereof is prohibited. That is, the end surface of the notch 6d of the second flange 6 functions as a stopper.

Further, when the clutch plate 3 and the retaining plate 4 rotate in the + R direction, on the contrary, the first flange 5 is prohibited from rotating relative to the clutch plate 3 and the retaining plate 4, and the second flange 6. Can be rotated relative to each other. Accordingly, when the pre-damper unit 10 operates and the first teeth 7b of the output hub 7 abut on the end surface in the −R direction of the notch 6d of the second flange 6, the output hub 7 and the second flange 6 are integrated. Rotate to. Thereafter, when the torsion spring 8 is elastically deformed and the

plates

3, 4 and the first flange 5, the second flange 6 and the output hub 7 are relatively rotated by an angle corresponding to the gap G2, the output hub 7 The one tooth 7b comes into contact with the end surface in the + R direction of the notch 5d of the fifth flange 5, and relative rotation thereof is prohibited. That is, the end surface of the notch 5d of the first flange 5 functions as a stopper.

[Characteristic]
(1) A stopper mechanism is realized by the output hub 7 and the two

flanges

5 and 6. For this reason, it is not necessary to provide a stopper mechanism including a stop pin on the outer peripheral portion of the flange as in the conventional device. Therefore, a wide space for the torsion spring can be secured, and high torque and wide angle can be easily realized.

(2) Since the end surface of the torsion spring 8 is supported by the

spring support portions

5c and 6c formed on the

flanges

5 and 6, the

flanges

5 and 6 are rotated relative to the

plates

3 and 4 on the input side. The configuration for prohibition can function as a spring seat.

(3) Since the two

flanges

5 and 6 have the same shape, the manufacturing cost can be reduced.

(4) The pre-damper unit 10 includes an outer peripheral side pre-torsion spring 23 and an inner peripheral side pre-torsion spring 24 that operate in series. For this reason, the wide angle in the pre-damper unit 10 can be realized.

(5) A part of the retaining plate 4 is made to function as an input side plate of the pre-damper unit 10. This eliminates the need for an input-side plate as compared with the conventional pre-damper unit, and the axial dimension can be shortened as compared with the conventional device.

(6) The outer peripheral side and inner peripheral side pre-torsion springs 23 and 24 are supported by the first sub-plate 21 that connects the outer peripheral side pre-torsion spring 23 and the inner peripheral side pre-torsion spring 24. For this reason, a wide angle can be realized with a small number of parts.

(7) The first sub plate 21 regulates the rotation angle range of the second sub plate 22. For this reason, the pre-damper unit 10 can realize two-stage torsional characteristics.

[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) The configuration for fixing the two flanges to the input side plate is not limited to the above embodiment. For example, a protrusion may be provided on each flange, and the protrusion may be inserted into a notch or the like different from the first opening formed on the input side plate.

(B) In the above embodiment, the two flanges have the same shape, but each may have a different shape.

In the present invention, the conventional flange is divided into a hub on the one rotation side and a hub on the other rotation side, and the stopper mechanism is configured using the flange that is not in operation. It is not necessary to form a stopper mechanism on the outer peripheral portion of the flange of the hub, and high torque and wide angle can be easily realized.

1 Clutch disc assembly 2 Clutch disc 3 Clutch plate (first input plate)
4 retaining plate (second input plate)
5 1st flange 5d Notch 6 2nd flange 6d Notch 7 Output hub 7b 1st tooth 8 Torsion spring 9 Hysteresis torque generating mechanism 10 Pre-damper unit

Claims

A damper disk assembly for transmitting power from the engine to the input shaft of the transmission,
An input member to which power from the engine is input;
The input member is disposed facing the input member in the axial direction. When the input member rotates in the first direction, the input member can rotate relative to the input member within a predetermined angle range, and the input member rotates in the second direction. A first flange for which relative rotation with the input member is prohibited,
The first flange is disposed to face the first flange in the axial direction, and when the input member rotates in the second direction, the input member is rotatable relative to the input member within a predetermined angle range. A second flange that is prohibited from rotating relative to the input member when rotating in a direction;
An output hub that is connectable to an input shaft of the transmission and is connected to the first and second flanges so as to be relatively rotatable within a predetermined angle range;
A plurality of elastic members that elastically connect the input member and the first and second flanges in a circumferential direction;
A stopper mechanism that is formed at a connecting portion between the first and second flanges and the output hub, and restricts relative rotation between the input member and the output hub within a predetermined angular range;
Damper disk assembly with
The first flange has an engaging portion that engages with the input member so as not to rotate relative to the input member when the input member rotates in the second direction.
The second flange has an engaging portion that engages with the input member so as not to rotate relative to the input member when the input member rotates in the first direction.
The damper disk assembly according to claim 1.
The input member has a plurality of accommodating portions for accommodating the plurality of elastic members,
The engaging portions of the first and second flanges are protrusions protruding in an axial direction sandwiched between a rotation direction end surface of at least one of the plurality of storage portions and a rotation direction end surface of the elastic member. Is,
The damper disk assembly according to claim 2.
The first and second flanges are annular plate members;
The stopper mechanism is
A plurality of notches formed at predetermined intervals in the circumferential direction on the inner peripheral edges of the first and second flanges;
A plurality of teeth formed on the outer periphery of the output hub and inserted into the notches of the first and second flanges through a predetermined gap in the rotational direction;
The plurality of notches in the first flange and the plurality of notches in the second flange are arranged with a rotational phase shifted from each other.
The damper disk assembly according to any one of claims 1 to 3.
The input members are first and second input plates disposed opposite to each other in the axial direction;
The first and second flanges are disposed between the first input plate and the second input plate in the axial direction.
The damper disk assembly according to any one of claims 1 to 4.