JP2019090428A - Damper disc assembly - Google Patents

Abstract

To provide a damper disc assembly capable of reducing its size in an axis direction.SOLUTION: In a clutch disc assembly 1, a first damper structure 3 substantially actuates in a high angle of torsion region [0157]HR. Torque is transmitted from the first damper structure 3 to a second damper structure 5. The second damper structure 5 is arranged in the first damper structure 3 as a single unit. The second damper structure 5 substantially actuates in a low angle of torsion region HR.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a damper disk assembly, and more particularly to a damper disk assembly for damping and transmitting torque fluctuations input from an engine to the transmission side.

  During idling and traveling, vibrations and noise may occur in the vehicle. In order to solve this problem, a damper disk assembly is provided. In particular, in the damper disk assembly, the pre-damper (second damper structure) may be assembled to the main damper (first damper structure) in order to suppress vibration and noise during idling (see Patent Document 1). ).

JP, 2016-145614, A

  In the conventional damper disk assembly, since the pre-damper is disposed outside the main damper, there is a problem that the axial length of the damper disk assembly is increased. In addition, since it is necessary to prepare a member for mounting the pre-damper to the main damper, for example, a support plate, there is a problem that the number of parts increases. Further, since it is necessary to assemble each member constituting the pre-damper into the main damper one by one, there is also a problem that the assembling time of the damper disk assembly becomes long.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a damper disk assembly which can be miniaturized in the axial direction. Another object of the present invention is to provide a damper disk assembly capable of reducing the number of parts. Furthermore, an object of the present invention is to provide a damper disk assembly in which the second damper structure can be easily assembled to the first damper structure.

  A damper disk assembly according to one aspect of the present invention is for damping and transmitting torque fluctuations input from an engine to the transmission side.

  The damper disk assembly has a first damper structure, a second damper structure, and an output portion. The first damper structure receives torque from the engine. The first damper structure operates substantially in the high twist angle region. The second damper structure transmits torque from the first damper structure. The second damper structure is disposed as a unit inside the first damper structure. The second damper structure operates substantially in the low twist angle region.

  The output unit is configured to be connectable to the transmission. Torque is output from the first damper structure to the output receiving portion in the high torsion angle region. The torque is output from the second damper structure to the output receiving portion in the low torsion angle region.

  In this damper disk assembly, since the second damper structure is disposed inside the first damper structure, the damper disk assembly can be miniaturized in the axial direction, and the number of parts of the damper disk assembly can be reduced. Further, in the damper disk assembly, the second damper structure is disposed as a unit inside the first damper structure, so that the second damper structure can be easily assembled to the first damper structure.

  The damper disk assembly according to another aspect of the present invention is preferably configured as follows. The first damper structure outputs torque to the output portion in the high torsion angle region. The first damper structure transmits torque to the second damper structure in the low torsion angle region.

  With this configuration, the second damper structure can be suitably operated in the low torsion angle region, together with the above-mentioned effects.

  The damper disk assembly according to another aspect of the present invention is preferably configured as follows. The first damper structure has a first rotating member. The first rotating member has a first input rotating member to which torque is input from the engine, and a second input rotating member configured to be integrally rotatable opposite to the first input rotating member. The second damper structure is disposed between the first input rotary member and the second input rotary member in the rotation axis direction.

  By being configured in this manner, the second damper structure can be suitably incorporated in the first damper structure together with the above effects.

  The damper disk assembly according to another aspect of the present invention is preferably configured as follows. The first damper structure has a second rotating member and a first damper portion. The second rotation member is disposed between the first input rotation member and the second input rotation member in the rotation axis direction. The second rotation member is configured to be rotatable relative to the first input rotation member and the second input rotation member. The first damper unit relatively rotatably couples the first and second input rotary members and the second rotary member. The second damper structure is disposed between any one of the first input rotary member and the second input rotary member and the second rotary member in the rotation axis direction.

  By being configured in this manner, the second damper structure can be suitably incorporated in the first damper structure together with the above effects.

  The damper disk assembly according to another aspect of the present invention is preferably configured as follows. The second rotating member is configured to be integrally rotatable with the output portion in the high torsion angle region. The second rotating member is configured to be rotatable relative to the output portion in the low torsion angle region.

  With this configuration, in addition to the above-described effects, torque can be suitably transmitted from the first damper structure to the second damper structure in the low torsion angle region.

  The damper disk assembly according to another aspect of the present invention is preferably configured as follows. The first damper portion has a first hysteresis torque generating mechanism disposed between the first rotating member and the second rotating member in the rotation axis direction. The first hysteresis torque generation mechanism has a first sliding portion that generates a first hysteresis torque by sliding with at least one of the first rotating member and the second rotating member.

  With this configuration, the vibration and noise can be suitably reduced along with the above effects.

  The damper disk assembly according to another aspect of the present invention is preferably configured as follows. The first hysteresis torque generating mechanism generates the first hysteresis torque only in the high torsion angle region.

  With such a configuration, in addition to the above effects, vibration and noise can be suitably reduced in the high torsion angle region.

  The damper disk assembly according to another aspect of the present invention is preferably configured as follows. The second damper structure has a third rotating member, a fourth rotating member, and a second damper portion. Torque is transmitted to the third rotating member from the first damper structure. The fourth rotating member is configured to be rotatable relative to the third rotating member. The second damper unit relatively rotatably connects the third rotating member and the fourth rotating member.

  With this configuration, the second damper structure can be suitably operated with the above-described effects.

  The damper disk assembly according to another aspect of the present invention is preferably configured as follows. The second damper portion has a sliding portion disposed between the third rotating member and the fourth rotating member in the rotation axis direction, and a second hysteresis torque generating mechanism. The second hysteresis torque generating mechanism generates a second hysteresis torque by sliding between the sliding portion and at least one of the third rotating member and the fourth rotating member.

  By this configuration, the durability of the second damper structure can be improved as compared to the case where the second hysteresis torque occurs in both the low torsion angle region and the high torsion angle region. Also, the above effects can be obtained simultaneously.

  The damper disk assembly according to another aspect of the present invention is preferably configured as follows. The second hysteresis torque generation mechanism generates the second hysteresis torque only in the low torsion angle region.

  With this configuration, in addition to the above-described effects, vibration and noise can be suitably reduced in the low torsion angle region.

  The damper disk assembly according to another aspect of the present invention is preferably configured as follows. The first damper structure has a first rotating member and a second rotating member. Torque is input to the first rotating member from the engine. The second rotating member is configured to be rotatable relative to the first rotating member. The third rotating member is configured to be integrally rotatable with the second rotating member. The fourth rotating member is configured to be integrally rotatable with the output receiving portion.

  With this configuration, in addition to the above-described effects, torque can be suitably transmitted from the first damper structure to the second damper structure in the low torsion angle region.

  The damper disk assembly according to another aspect of the present invention is preferably configured as follows. The third rotating member has a pair of opposing members disposed opposite to each other and integrally rotatable with each other by the connecting member. The fourth rotating member is disposed between the pair of opposing members and configured to be rotatable relative to the pair of opposing members.

  The second sliding portion is disposed between the facing member and the fourth rotating member. The second sliding portion contacts at least one of the opposing member and the fourth rotating member by the biasing member, and slides the second hysteresis torque by sliding with at least one of the opposing member and the fourth rotating member. Occur.

  With this configuration, in addition to the above-described effects, vibration and noise can be suitably reduced in the low torsion angle region.

  According to the present invention, the damper disk assembly can be miniaturized in the axial direction, and the number of parts of the damper disk assembly can be reduced. Further, in the present invention, the second damper structure can be easily assembled to the first damper structure.

FIG. 3 is a cross-sectional view of a clutch disk assembly according to an embodiment of the present invention (II cross section in FIG. 2). The front view of FIG. Partially expanded sectional view of a 2nd damper structure. The disassembled sectional view for demonstrating the 2nd damper structure. The schematic diagram for demonstrating a torsion characteristic.

[overall structure]
FIG. 1 shows a clutch disk assembly 1 (an example of a damper disk assembly) according to an embodiment of the present invention.

  FIG. 1 is a cross-sectional view of the clutch disk assembly 1, and FIG. 2 is a front view thereof. The clutch disc assembly 1 is used for a clutch device of a vehicle. The clutch disc assembly 1 has a clutch function and a damper function.

  In FIG. 1, OO is the rotation axis or rotation center line of the clutch disk assembly 1. Moreover, in the following, the direction away from the rotation axis O is described as the radial direction, and the direction along the rotation axis is described as the axial direction (rotational axis direction). Furthermore, in the following, the direction around the rotation axis O is referred to as a circumferential direction or a rotation direction.

  An engine and a flywheel (not shown) are disposed on the left side of FIG. 1, and a transmission (not shown) is disposed on the right side of FIG. The R1 side in FIG. 2 is the rotational direction drive side (positive side) of the clutch disk assembly 1, and the R2 side is the opposite side (negative side).

  The clutch disk assembly 1 attenuates torque fluctuation input from the engine and transmits it to the transmission side. As shown in FIG. 1, the clutch disk assembly 1 includes a first damper structure 3, a second damper structure 5, and a hub 7 (an example of a portion to be output).

<First damper structure>
The torque from the engine is input to the first damper structure 3. The first damper structure 3 operates substantially in the high torsional angle region HR (see FIG. 5) of the torsional characteristic. Torque is input to the first damper structure 3 from the engine. The first damper structure 3 operates substantially in the high torsion angle region HR. The first damper structure 3 outputs torque to the hub 7 in the high torsion angle region HR. The first damper structure 3 transmits torque to the second damper structure 5 in the low torsion angle region LR.

  As shown in FIGS. 1 and 2, the first damper structure 3 includes a first input side member 11 (an example of a first rotating member), a first output side member 13 (an example of a second rotating member), and And a damper unit 15.

-First input side member-
Torque is input to the first input side member 11 from the engine. In detail, torque is input to the first input side member 11 from a flywheel (not shown). As shown in FIGS. 1 and 2, the first input side member 11 includes a clutch plate 17 (an example of a first input rotary member), a retaining plate 19 (an example of a second input rotary member), and a clutch disc 21. And have. The clutch disc 21 may be interpreted as an example of the first input rotary member.

  The clutch plate 17 and the retaining plate 19 are substantially annularly formed. The clutch plate 17 and the retaining plate 19 are spaced apart in the axial direction. Here, the clutch plate 17 is disposed on the engine side, and the retaining plate 19 is disposed on the transmission side. The clutch plate 17 and the retaining plate 19 are integrally rotatably coupled to each other by a fixing member, for example, a first pin member 16.

  On each of the clutch plate 17 and the retaining plate 19, a plurality of (for example, four) first storage frame portions 17a and 19a are formed at intervals in the circumferential direction. A first high rigidity spring portion 33 (described later) is disposed in each of the first storage frame portions 17a and 19a. Both end portions of the first high rigidity spring portion 33 are in contact with the wall portions facing each other in the circumferential direction in each of the first storage frame portions 17a and 19a.

  Further, on each of the clutch plate 17 and the retaining plate 19, a plurality of (for example, four) second storage frame portions 17b and 19b are formed at intervals in the circumferential direction. A second high rigidity spring portion 35 (described later) is disposed in each of the second storage frame portions 17 b and 19 b. Both end portions of the second high rigidity spring portion 35 are in contact with the wall portions facing each other in the circumferential direction in each of the second storage frame portions 17 b and 19 b.

  Further, a plurality of (for example, seven) first holding holes 17 c are formed in the clutch plate 17. The plurality of first holding holes 17 c are used to hold a first hysteresis torque generation mechanism 37 (described later). The first protrusion 39c of the first hysteresis torque generating mechanism 37 is fitted in each first holding hole 17c.

  The retaining plate 19 has a plurality of (for example, ten) second holding holes 19c. The plurality of second holding holes 19 c are used to position the second damper structure 5. The second protrusion 20b of the second positioning member (for example, the ring member 20) for holding the second damper structure 5 is fitted in each second holding hole 19c.

  The clutch disc 21 is a portion pressed against a flywheel (not shown). The clutch disc 21 is fixed to the clutch plate 17. The clutch disc 21 includes a cushioning plate 21a fixed to the clutch plate 17 and friction facings 21b fixed to both sides of the cushioning plate 15a. The clutch disc 21 has the same structure as that of a known structure, and thus the detailed description of the clutch disc 21 is omitted.

-First output side member-
The first output side member 13 is configured to be rotatable relative to the first input side member 11. In detail, the first output side member 13 is configured to be rotatable relative to the clutch plate 17 and the retaining plate 19. The first output member 13 is configured to be rotatable relative to the hub 7 in the low torsion angle region LR. The first output member 13 is configured to be integrally rotatable with the hub 7 in the high torsion angle region HR.

  Specifically, as shown in FIGS. 1 and 2, the first output side member 13 is disposed at the outer peripheral portion of the hub 7. The first output member 13 is formed in a substantially annular shape in the circumferential direction, and is disposed radially outward of the hub 7. The first output side member 13 is formed separately from the hub 7.

  The first output member 13 is rotatable relative to the hub 7 in a predetermined twist angle range, for example, a low twist angle region LR (see FIG. 5). Further, the first output side member 13 can rotate integrally with the hub 7 outside the predetermined range of the twist angle, for example, in the high twist angle region HR.

  Here, the twisting angle A is defined, for example, by the twisting angle (relative rotation angle) of the first output member 13 with respect to the hub 7. As described later, since the second input side member 51 (the first holder plate 57 and the second holder plate 59) is configured to be integrally rotatable with the first output side member 13, the torsion angle A is For example, it can be said that it is defined by the twisting angle (relative rotation angle) of the second input-side member 51 (the first holder plate 57 and the second holder plate 59) with respect to the hub 7.

  Specifically, as shown in FIG. 1, the first output member 13 is disposed between the clutch plate 17 and the retaining plate 19 in the axial direction. As shown in FIGS. 1 and 2, the first output member 13 includes a first hole 23, a plurality of (for example, four) third storage frame portions 25, and a plurality (for example, four) fourth accommodations. A frame portion 27, a plurality of (for example, four) first engagement recesses 29, and a plurality (for example, four) stopper recesses 31 are provided.

  The first hole portion 23 is formed at the central portion of the first output side member 13. The hub 7 can be inserted into the first hole 23. In the first hole portion 23, a plurality of internal teeth 23a are formed. The plurality of external teeth 83a formed in the large diameter portion 83 of the hub 7 engage with the plurality of internal teeth 23a. Specifically, the external teeth 83a of the hub 7 are disposed between the internal teeth 23a adjacent to each other in the circumferential direction. Further, a gap is formed between the inner teeth 23a and the outer teeth 83a adjacent to the inner teeth 23a in the circumferential direction. Due to this gap, the first output member 13 and the hub 7 can rotate relative to each other in the low torsion angle region LR.

  The plurality of third storage frame portions 25 are formed in the first output side member 13 at intervals in the circumferential direction. The respective third storage frame portions 25 are disposed to axially face the respective first storage frame portions 17 a and 19 a of the clutch plate 17 and the retaining plate 19. The first high rigidity spring portions 33 are disposed in the third storage frame portions 25. Both end portions of the first high rigidity spring portions 33 are in contact with the wall portions facing each other in the circumferential direction in the third storage frame portions 25.

  The plurality of fourth storage frame portions 27 are formed in the first output side member 13 at intervals in the circumferential direction. Each fourth storage frame portion 27 is disposed between the third storage frame portions 25 adjacent to each other in the circumferential direction. The fourth storage frame portions 27 are disposed to axially face the second storage frame portions 17 b and 19 b of the clutch plate 17 and the retaining plate 19. Each second high rigidity spring portion 35 is disposed in each fourth storage frame portion 27. The wall portions facing each other in the circumferential direction in each of the fourth storage frame portions 27 are disposed at an interval from both end portions of the second high rigidity spring portions 35.

  The claws 57b (described later) of the first holder plate 57 engage with the plurality of first engagement recesses 29 respectively. Each first engagement recess 29 is formed at an edge on the inner peripheral side of each third storage frame 25. Each of the first engagement recesses 29 is formed in a concave shape toward the rotation axis O at the inner circumferential edge of each of the third storage frame portions 25.

  The stopper recess 31 is formed on the outer peripheral portion of the first output side member 13. The first pin member 16 for fixing the clutch plate 17 and the retaining plate 19 can be in contact with the stopper recess 31. For example, the abutment of the stopper recess 31 and the first pin member 16 restricts the rotation of the clutch plate 17 and the retaining plate 19 with respect to the first output member 13. That is, the stopper recess 31 and the first pin member 16 function as a stopper mechanism for stopping the relative rotation of the first input side member 11 and the first output side member 13.

-1st damper part-
The first damper portion 15 couples the first input side member 11 and the first output side member 13 so as to be capable of relative rotation. In detail, the first damper portion 15 couples the clutch plate 17 and the retaining plate 19 with the first output member 13 so as to be relatively rotatable.

  As shown in FIGS. 1 and 2, the first damper portion 15 includes a plurality of (for example, four) first high rigidity spring portions 33, a plurality of (for example four) second high rigidity spring portions 35, and And a hysteresis torque generating mechanism 37. The overall stiffness combining the stiffness of the plurality of first high stiffness spring portions 33 and the stiffness of the plurality of second high stiffness spring portions 35 is higher than the stiffness of the plurality of low stiffness spring portions 71.

(First high rigidity spring part)
The plurality of first high rigidity spring portions 33 elastically connect the first input side member 11 and the first output side member 13 in the rotational direction. Specifically, the plurality of first high rigidity spring portions 33 elastically connect the clutch plate 17 and the retaining plate 19 and the first output side member 13 in the rotational direction. The stiffness of the plurality of first high stiffness spring portions 33 is higher than the stiffness of the plurality of low stiffness spring portions 71.

  As shown in FIGS. 1 and 2, each first high rigidity spring portion 33 has a high rigidity first spring 33 a and a high rigidity second spring 33 b. The second spring 33b for high rigidity is disposed on the inner peripheral portion of the first spring 33a for high rigidity. Here, the second spring 33b for high rigidity has substantially the same length as the first spring 33a for high rigidity.

  The first spring 33 a for high rigidity and the second spring 33 b for high rigidity are the first storage frame portions 17 a and 19 a of the clutch plate 17 and the retaining plate 19, and the third storage frame of the first output side member 13. It is arranged in the section 25.

  Both end portions of the high rigidity first spring 33 a and both end portions of the high rigidity second spring 33 b are circumferentially opposed walls of the first storage frame portions 17 a and 19 a of the clutch plate 17 and the retaining plate 19. It is in contact with the part. Further, both end portions of the first spring 33 a for high rigidity and both end portions of the second spring 33 b for high rigidity are on wall portions facing in the circumferential direction in the third storage frame portions 25 of the first output side member 13. , Is in contact.

  Here, when the twist angle A of the clutch plate 17 and the retaining plate 19 with respect to the first output side member 13 becomes equal to or more than a predetermined first twist angle A1 (see FIG. 5), the first and second high rigidity The springs 33a and 33b operate.

(2nd high rigidity spring part)
The plurality of second high rigidity spring portions 35 elastically connect the first input side member 11 and the first output side member 13 in the rotational direction. In detail, the plurality of second high rigidity spring portions 35 elastically connect the clutch plate 17 and the retaining plate 19 and the first output member 13 in the rotational direction.

  As shown in FIGS. 1 and 2, each second high rigidity spring portion 35 has a high rigidity third spring 35 a. The third spring 35 a for high rigidity is disposed in each of the second storage frame portions 17 b and 19 b of the clutch plate 17 and the retaining plate 19 and the fourth storage frame portion 27 of the first output side member 13. .

  As shown in FIG. 2, both end portions of the high rigidity third spring 35 a abut against circumferentially opposed wall portions of the second storage frame portions 17 b and 19 b of the clutch plate 17 and the retaining plate 19. ing. Further, both end portions of the high rigidity third spring 35 a are disposed at an interval from the circumferentially facing wall portion in each of the fourth storage frame portions 27 of the first output side member 13.

  Here, both ends of the third spring 35a for high rigidity, in which the twisting angles A of the clutch plate 17 and the retaining plate 19 with respect to the first output side member 13 reach a predetermined second twisting angle A2, It abuts on the wall portion of each of the third storage frame portions 25 of the one output side member 13. Thus, when the twisting angle A becomes equal to or more than the predetermined second twisting angle A2 (see FIG. 5), the first to third springs 33a, 33b, 35a for high rigidity operate.

(First hysteresis torque generation mechanism)
The first hysteresis torque generation mechanism 37 damps torque fluctuations in the high torsion angle region HR. For example, the first hysteresis torque generation mechanism 37 generates the first hysteresis torque H1 only in the high torsion angle region HR (see FIG. 5).

  As shown in FIG. 1, the first hysteresis torque generation mechanism 37 is disposed between the first input side member 11 and the first output side member 13 in the axial direction.

  As shown in FIG. 3, the first hysteresis torque generation mechanism 37 generates a first hysteresis torque by sliding with at least one of the first input side member 11 and the first output side member 13. It has member 39 (an example of the 1st sliding part).

  In detail, the first hysteresis torque generating mechanism 37 has a first sliding member 39 and a first biasing member 41.

  The first sliding member 39 is configured to be slidable with the first output side member 13. The first sliding member 39 is configured to be integrally rotatable with the first input side member 11.

  For example, the first sliding member 39 is disposed between the clutch plate 17 of the first input side member 11 and the first output side member 13 in the axial direction. Specifically, the first sliding member 39 is disposed between the first biasing member 41 and the first output member 13 in the axial direction. The first sliding member 39 is mounted on the clutch plate 17 so as to be integrally rotatable with the clutch plate 17.

  The first sliding member 39 has a first annular portion 39a, a sliding portion 39b, and a plurality (for example, seven) of first projecting portions 39c. The first annular portion 39a is substantially annularly formed. The first annular portion 39 a is disposed between the first biasing member 41 and the first output side member 13 in the axial direction.

  The plurality of first protrusions 39c are provided on the first annular portion 39a. Each first protrusion 39 c protrudes from the first annular portion 39 a toward the clutch plate 17 from the first annular portion 39 a. The first projecting portions 39 c are inserted through the through holes 41 a provided in the first biasing member 41 and fitted in the first holding holes 17 c of the clutch plate 17.

  The sliding portion 39 b is substantially annularly formed. The sliding portion 39 b is fixed to the first annular portion 39 a. Specifically, the sliding portion 39 b is disposed axially between the first annular portion 39 a and the first output side member 13, and is fixed to the surface where the first annular portion 39 a faces the first output side member 13. ing. The sliding portion 39 b is in contact with the first output side member 13 and is slidable with the first output side member 13.

  The first biasing member 41 is configured to be capable of biasing the first sliding member 39 toward the first output side member 13. The first biasing member 41 is disposed between the clutch plate 17 and the first sliding member 39 in the axial direction. The first biasing member 41 is provided with a plurality of (for example, seven) through holes 41 a. The first projecting portions 39c of the first sliding member 39 are inserted into the through holes 41a.

  The first biasing member 41 is, for example, a cone spring. The outer peripheral portion of the first biasing member 41 is in contact with the first sliding member 39, and the inner peripheral portion of the first biasing member 41 is in contact with the clutch plate 17. In this state, the first biasing member 41 biases the first sliding member 39 toward the first output member 13. Thereby, the first sliding member 39 is pressed against the first output side member 13. Then, when the first input side member 11 rotates relative to the first output side member 13, the first sliding member 39 (sliding portion 39b) slides on the first output side member 13, and the first hysteresis torque H1 occurs (see FIG. 5).

  The first damper portion 15 having the above-described configuration operates substantially within the range of the high torsion angle region HR (see FIG. 5) of the torsion characteristic. Specifically, the plurality of first high stiffness spring portions 33 operate substantially at the first torsion angle A1 or more and less than the second torsion angle A2 in the high torsion angle region HR. The plurality of second high rigidity spring portions 35 operate substantially at the second torsion angle A2 or more and the third torsion angle A3 in the high torsion angle region HR. The first hysteresis torque generating mechanism 37 operates substantially at the first torsion angle A1 or more and the third torsion angle A3 in the high torsion angle region HR.

<Second damper structure>
The torque is transmitted from the first damper structure 3 to the second damper structure 5. The second damper structure 5 is configured to be less rigid than the first damper structure 3. The second damper structure 5 operates substantially in the low torsion angle region LR of the torsion characteristic (see FIG. 5). For example, the second damper structure 5 engages with the first damper structure 3 and functions as a pre-damper of the first damper structure 3. When the first damper structure 3 substantially starts its operation, the second damper structure 5 substantially stops its operation.

  The second damper structure 5 is disposed as a unit inside the first damper structure 3. That is, the unitized second damper structure 5 is disposed inside the first damper structure 3. As shown in FIG. 3, the second damper structure 5 is disposed between the clutch plate 17 and the retaining plate 19 in the axial direction. In detail, the second damper structure 5 is disposed between the first output member 13 and either the clutch plate 17 or the retaining plate 19 in the axial direction.

  Here, the second damper structure 5 is disposed between the retaining plate 19 and the first output member 13 in the axial direction. The second damper structure 5 is disposed radially inward of the first and second high rigidity spring portions 33 and 35 and axially between the retaining plate 19 and the first output member 13.

  Further, the second damper structure 5 is disposed on the outer peripheral portion of the hub 7. For example, the second damper structure 5 is positioned with respect to the hub 7 by the first positioning member, for example, the snap ring 18 in a state where the second damper structure 5 is disposed on the outer peripheral portion of the hub 7.

  Furthermore, the second damper structure 5 is positioned by the second positioning member, for example, the ring member 20, with respect to the second input side member 51, for example, the second holder plate 59 (described later). The ring member 20 has a second annular portion 20a and a plurality of second protrusions 20b. The ring member 20 may be interpreted as a member included in the first damper structure 3.

  The second annular portion 20a is substantially annularly formed. The second annular portion 20 a is disposed between the second damper structure 5 and the retaining plate 19 in the axial direction. In detail, the second annular portion 20 a is disposed between the second holder plate 59 and the retaining plate 19 in the axial direction.

  The plurality of second protrusions 20 b are provided on the second annular portion 20 a. Each second projecting portion 20 b protrudes from the second annular portion 20 a from the second annular portion 20 a toward the retaining plate 19. Each second protrusion 20 b is fitted in each second holding hole 19 c of the retaining plate 19. Thereby, the ring member 20 rotates integrally with the retaining plate 19.

  As shown in FIGS. 3 and 4, the second damper structure 5 includes a second input side member 51 (an example of a third rotating member), a second output side member 53 (an example of a fourth rotating member), and And 2 damper portion 55. The second input-side member 51, the second output-side member 53, and the second damper portion 55 are assembled as one unit, and are mounted axially between the retaining plate 19 and the first output-side member 13.

-Second input side member-
Torque is transmitted to the second input side member 51 from the first damper structure 3. Specifically, torque is transmitted from the first damper structure 3 to the second input side member 51 in the low torsion angle region LR. The second input side member 51 is configured to be integrally rotatable with the first output side member 13 of the first damper structure 3. The second input side member 51 is configured to be rotatable relative to the second output side member 53.

  As shown in FIGS. 3 and 4, the second input-side member 51 includes a first holder plate 57 (an example of an opposing member) and a second holder plate 59 (an example of an opposing member). Torque is input to the first holder plate 57 from the first damper structure 3. For example, the first holder plate 57 is configured to be engageable with the first output side member 13.

  The first holder plate 57 is substantially annularly formed. The first holder plate 57 is disposed between the first output member 13 and the retaining plate 19 in the axial direction. In detail, the first holder plate 57 is disposed between the first output member 13 and the second output member 53 in the axial direction. The first holder plate 57 is spaced apart from the hub 7 in the radial direction.

  The first holder plate 57 has a plurality of claws 57b. Each of the plurality of (for example, four) claws 57 b is configured to be engageable with the first engagement recess 29 of the first output member 13. Each claw portion 57 b extends in the axial direction from the outer peripheral portion of the first holder plate 57 toward the first output member 13. The first holder plate 57 can rotate integrally with the first output member 13 by the claws 57 b engaging with the first engagement recesses 29.

  The second holder plate 59 is disposed to face the first holder plate 57 in the axial direction, and is configured to be integrally rotatable with the first holder plate 57. The second holder plate 59 is substantially annularly formed. The second holder plate 59 is disposed between the first output member 13 and the retaining plate 19 in the axial direction. In detail, the second holder plate 59 is disposed between the second output member 53 and the retaining plate 19 in the axial direction.

  The second holder plate 59 is spaced apart from the hub 7 in the radial direction. The second holder plate 59 is disposed to face the first holder plate 57 in the axial direction. The second holder plate 59 is integrally rotatably connected to the first holder plate 57 by fixing means, for example, the second pin member 22 so as to be able to rotate integrally with the first holder plate 57.

  On each of the first holder plate 57 and the second holder plate 59, a plurality of (for example, four) fifth storage frame portions 57a, 59a are formed at intervals in the circumferential direction. A low rigidity spring portion 71 is disposed in each of the fifth storage frame portions 57a and 59a. Both end portions of the low rigidity spring portion 71 are in contact with the wall portions facing each other in the circumferential direction in the fifth storage frame portions 57a and 59a.

-Second output side member-
The second output side member 53 is configured to be rotatable relative to the second input side member 51. In detail, the second output side member 53 is disposed between the first holder plate 57 and the second holder plate 59 in the axial direction. The second output side member 53 is configured to be rotatable relative to the first holder plate 57 and the second holder plate 59. Further, the second output side member 53 is configured to be integrally rotatable with the hub 7. The second output member 53 is axially positioned relative to the hub 7 by means of a snap ring 18 (see FIG. 3).

  As shown in FIGS. 3 and 4, the second output side member 53 has a second hole 61, a plurality of (for example, four) sixth storage frame portions 63, and a plurality (for example, four) first lengths. A hole 65 and a plurality of (for example, four) second long holes 67 are provided.

  The second hole portion 61 is formed at the central portion of the second output side member 53. The hub 7 is inserted into the second hole 61. In the second hole 61, a plurality of internal teeth 61a are formed. The plurality of internal teeth 61 a are engaged with the plurality of external teeth 87 a formed in the second small diameter portion 87 of the hub 7. As a result, the second output member 53 can rotate integrally with the hub 7.

  The plurality of sixth storage frame portions 63 are formed in the second output side member 53. In detail, the plurality of sixth storage frame portions 63 are formed at intervals in the circumferential direction. The sixth storage frame portions 63 are disposed to face the fifth storage frame portions 57a and 59a in the axial direction. A low rigidity spring portion 71 is disposed in each of the sixth storage frame portions 63. Both end portions of each low rigidity spring portion 71 are in contact with the wall portions facing each other in the circumferential direction in each of the sixth storage frame portions 63.

  The plurality of first elongated holes 65 are formed on the inner peripheral side of the second output side member 53. The respective first elongated holes 65 are provided in the second output member at intervals in the circumferential direction. Each first long hole 65 is a hole extending in the circumferential direction. Each second pin member 22 is inserted into each first elongated hole 65, and each second pin member 22 is movable in the circumferential direction inside each first elongated hole 65.

  As shown in FIG. 4, the plurality of second elongated holes 67 are formed on the outer peripheral side of the second output side member 53. The respective second elongated holes 67 are provided in the second output side member 53 at intervals in the circumferential direction. Each second long hole 67 is a hole extending in the circumferential direction. The third pin members 24 are inserted into the second long holes 67, and the third pin members 24 are movable in the circumferential direction in the second long holes 67.

-Second damper section-
The second damper portion 55 damps torque fluctuations in the low torsion angle region LR. The second damper 55 couples the second input side member 51 and the second output side member 53 in a relatively rotatable manner. In detail, the second damper portion 55 couples the first holder plate 57 and the second holder plate 59 with the second output side member 53 so as to be relatively rotatable.

  As shown in FIGS. 3 and 4, the second damper 55 includes a plurality of low rigidity spring portions 71, a second hysteresis torque generating mechanism 79, and a third hysteresis torque generating mechanism 81 (the second aspect described in the claims). And an example of a hysteresis torque generating mechanism).

(Low rigidity spring part)
The plurality of low rigidity spring portions 71 elastically connect the second input side member 51 and the second output side member 53. Further, the plurality of low rigidity spring portions 71 can slide with at least one of the second input side member 51 and the second output side member 53. The stiffness of the plurality of low stiffness spring portions 71 is lower than the overall stiffness combining the stiffness of the plurality of first high stiffness spring portions 33 and the stiffness of the plurality of second high stiffness spring portions 35.

  Specifically, as shown in FIG. 3 and FIG. 4, each low rigidity spring portion 71 has a low rigidity spring 71 a. The respective low rigidity springs 71 a are disposed in the fifth storage frame portions 57 a and 59 a of the first and second holder plates 57 and 59 and the sixth storage frame portions 63 of the second output side member 53. .

  Both ends of each low rigidity spring 71 a are the walls of the fifth storage frame portions 57 a and 59 a of the first and second holder plates 57 and 59, and the sixth storage frame portions 63 of the second output side member 53. In contact with the wall of the In this state, the low rigidity springs 71a elastically connect the first holder plate 57 and the second holder plate 59 to the second output member 53. Further, the outer peripheral portion of each low rigidity spring 71a can slide with each fifth storage frame portion 57a, 59a and each sixth storage frame portion 63.

(2nd hysteresis torque generation mechanism)
The second hysteresis torque generation mechanism 79 generates the second hysteresis torque H2 only in the low torsion angle region LR (see FIG. 5). The second hysteresis torque generation mechanism 79 generates a second hysteresis torque H2 by sliding between the plurality of low rigidity spring portions 71 and at least one of the second input side member 51 and the second output side member 53. .

  Here, as shown in FIG. 3, the second hysteresis torque generation mechanism 79 is configured such that the second hysteresis torque is generated by the sliding of the plurality of low rigidity spring portions 71 and the second input side member 51 and the second output side member 53. Generate H2.

  Specifically, the second hysteresis torque H2 is generated by the sliding of the low rigidity spring portions 71 with the first and second holder plates 57 and 59 and the second output member 53. Generate. More specifically, the second hysteresis torque generation mechanism 79 operates the low rigidity spring portions 71 to operate the low rigidity spring portions 71, the fifth storage frame portions 57a and 59a, and the sixth storage frame portions 63. The second hysteresis torque H2 is generated by the sliding with the

  From this, the second hysteresis torque generation mechanism 79 may be interpreted as being configured from the plurality of low rigidity spring portions 71, the second input side member 51, and the second output side member 53.

(3rd hysteresis torque generation mechanism)
The third hysteresis torque generation mechanism 81 generates the third hysteresis torque H3 only in the low torsion angle region LR. The third hysteresis torque generation mechanism 81 is configured such that the third hysteresis torque generation mechanism 81 slides the third sliding member 73, the third sliding member 75, and at least one of the second input side member 51 and the second output side member 53. A hysteresis torque H3 is generated.

  Here, as shown in FIG. 3, the third hysteresis torque generation mechanism 81 is configured to generate the third hysteresis torque by sliding between the second sliding member 73 and the third sliding member 75 and the second output side member 53. Generate H3.

  The third hysteresis torque generation mechanism 81 is disposed between the second input side member 51 and the second output side member 53 in the axial direction. The third hysteresis torque generation mechanism 81 generates a third hysteresis torque H3 by sliding with at least one of the second input side member 51 and the second output side member 53, and the second and third sliding members 73, 75 (an example of a 2nd sliding part). In detail, the third hysteresis torque generation mechanism 81 includes second and third sliding members 73 and 75 and a second biasing member 77.

-Second sliding member and third sliding member-
The second and third sliding members 73 and 75 are configured to be slidable with at least one of the second input side member 51 and the second output side member 53. Here, the second and third sliding members 73 and 75 are configured to be slidable with the second output side member 53.

  As shown in FIGS. 3 and 4, the second and third sliding members 73 and 75 are disposed between the second input side member 51 and the second output side member 53 in the axial direction. The second and third sliding members 73 and 75 are disposed radially outward of the plurality of low rigidity spring portions 71.

  Specifically, the second sliding member 73 is substantially annularly formed. The fixing member, for example, the second pin member 22 passes the inner peripheral side of the second sliding member 73. The second sliding member 73 is disposed between the first holder plate 57 and the second output member 53 in the axial direction. Specifically, the second sliding member 73 is disposed radially spaced from the hub 7 and axially disposed between the first holder plate 57 and the second output member 53. More specifically, the second sliding member 73 is disposed radially spaced from the hub 7 and disposed axially between the second biasing member 77 and the second output side member 53. The second sliding member 73 contacts the second output side member 53.

  The third sliding member 75 is substantially annularly formed. The fixing member, for example, the third pin member 22 passes the inner peripheral side of the third sliding member 75. The third sliding member 75 is disposed between the second output side member 53 and the second holder plate 59 in the axial direction. In detail, the third sliding member 75 is disposed at a distance from the hub 7 in the radial direction, and is disposed axially between the second output side member 53 and the second holder plate 59. The third sliding member 75 contacts the second output side member 53.

  The second sliding member 73 and the third sliding member 75 are configured to be integrally rotatable with the second input side member 51, for example, the first holder plate 57 and the second holder plate 59. Here, the second sliding member 73 and the third sliding member 75 are fixed to the first holder plate 57 and the second holder plate 59 by fixing means, for example, the third pin member 24. The second sliding member 73 and the third sliding member 75 are provided with a plurality of pin holes 73 a and 75 a for inserting the third pin member 24.

-Second biasing member-
The second biasing member 77 is configured to be capable of biasing the second sliding member 73 toward the second output side member 53. The second biasing member 77 is configured to be capable of biasing the second output side member 53 toward the third sliding member 75. The axial movement of the third sliding member 75 is restricted by the second holder plate 59.

  As shown in FIGS. 3 and 4, the second biasing member 77 is disposed between the second input side member 51 and the second output side member 53 in the axial direction. The second biasing member 77 is disposed radially outward of the plurality of low rigidity spring portions 71. The second biasing member 77 is formed in a substantially annular shape. The fixing means, for example, the second pin member 22 passes the inner circumferential side of the second biasing member 77.

  The second biasing member 77 is, for example, a cone spring. The outer peripheral portion of the second biasing member 77 is in contact with the second sliding member 73, and the inner peripheral portion of the second biasing member 77 is in contact with the second input side member 51, for example, the first holder plate 57. . In this state, the second biasing member 77 biases the second sliding member 73 toward the second output side member 53. Then, the second sliding member 73 is pressed against the second output side member 53 by the second biasing member 77, and the second output side member 53 is pressed against the third sliding member 75. As a result, the second sliding member 73 and the third sliding member 75 separately contact the both surfaces of the second output side member 53.

  As described above, the second sliding member 73 and the third sliding member 75 are configured to be integrally rotatable with the second input side member 51 (the first holder plate 57 and the second holder plate 59). Further, the second sliding member 73 and the third sliding member 75 are in contact with the second output side member 53. In this state, when the second input member 51 rotates relative to the second output member 53, the second sliding member 73 and the third sliding member 75 slide on the second output member 53. Thereby, a third hysteresis torque H3 is generated.

  From this, the third hysteresis torque generation mechanism 81 may be interpreted as being configured of the second sliding member 73, the third sliding member 75, and the second output side member 53.

<Hub>
The hub 7 is configured to be connectable to a transmission. Torque is output from the first damper structure 3 to the hub 7 in the high torsion angle region HR. Torque is output from the second damper structure 5 to the hub 7 in the low torsion angle region LR.

  As shown in FIGS. 1 to 4, the hub 7 is substantially cylindrically formed. As shown in FIGS. 3 and 4, on the outer peripheral surface of the hub 7, a large diameter portion 83 formed at the axial center, and a first small diameter portion 85 and a second small diameter formed at both end portions in the axial direction. And a part 87.

  The first small diameter portion 85 is provided on the clutch plate 17 side in the axial direction with respect to the large diameter portion 83. The first hysteresis torque generation mechanism 37 is disposed outside the first small diameter portion 85. The second small diameter portion 87 is provided on the retaining plate 19 side in the axial direction with reference to the large diameter portion 83. The second damper structure 5 is disposed on the outer peripheral portion of the second small diameter portion 87.

  On the outer peripheral surface of the large diameter portion 83, a plurality of external teeth 83a are formed. The internal teeth 61a of the first output side member 13 are engaged with the external teeth 83a. A gap is provided between each external tooth 83a and an internal tooth 61a adjacent to each external tooth 83a.

  At a predetermined twist angle, for example, less than the first twist angle A1 (see FIG. 5), each inner tooth 61a is movable circumferentially between adjacent outer teeth 83a. In this state, the first output member 13 is rotatable relative to the hub 7. The torsion angle region in this state corresponds to the low torsion angle region LR.

  At a predetermined twist angle, for example, the second twist angle A1 or more (see FIG. 5), each inner tooth 61a abuts on any one of the adjacent outer teeth 83a. In this state, the first output member 13 can rotate integrally with the hub 7. The torsion angle region in this state corresponds to the high torsion angle region HR.

  The outer peripheral surface of the second small diameter portion 87 is formed with a plurality of external teeth 87 a and a plurality of positioning recesses 87 b. The internal teeth 61a of the second output side member 53 engage with the external teeth 87a. Each inner tooth 18a (see FIG. 3) of the snap ring 18 engages with each positioning recess 87b. In this state, the snap ring 18 abuts against the inner peripheral side surface of the second output side member 53 to position the second output side member 53 on the hub 7.

[Assembly of second damper structure, and attachment of second damper structure to first damper structure]
The second damper structure 5 is configured as one unit. Here, the assembly of the second damper structure will be described with reference to FIG.

  First, the second biasing member 77 and the second sliding member 73 are disposed axially between the first holder plate 57 and the second output member 53. Next, a plurality of low rigidity spring portions 71 are disposed on the first holder plate 57 and the second output side member 53.

  Subsequently, the third sliding member 75 is disposed axially between the second output side member 53 and the second holder plate 59. In this state, the first holder plate 57 and the second holder plate 59 are connected by the second pin member 22 and the third pin member 24. Thus, the second damper structure 5 is unitized.

  The unitized second damper structure 5 is attached to the first damper structure 3 as follows. The second damper structure 5 is attached to the first output member 13 and the hub 7 in a state where the portion of the first damper structure 3 excluding the retaining plate 19 is assembled.

  For example, as shown in FIG. 3, the claws 57 b of the first holder plate 57 are engaged with the first engagement recesses 29 of the first output member 13. The internal teeth 61 a of the second output side member 53 are engaged with the external teeth 87 a of the second small diameter portion 87 of the hub 7. In this state, the snap ring 18 is fitted in the positioning recess 87 b of the hub 7. Thus, the second damper structure 5 is attached to the first damper structure 3.

  Thereafter, the ring member 20 is attached to the retaining plate 19, and the retaining plate 19 in this state is fixed to the clutch plate 17 by the first pin member 16 (see FIG. 1). Thereby, the clutch disc assembly 1 is assembled.

[Operation of clutch disc assembly]
The clutch disc assembly 1 having the above configuration will be described with reference to the torsional characteristics shown in FIG. First, when torque input to the clutch disk assembly 1 is started, the first damper structure 3 rotates relative to the hub 7 due to the above-mentioned gap. In this state, the torque transmitted to the first damper structure 3 is transmitted to the second damper structure 5. Then, the second damper structure 5 operates.

  Here, the first damper structure 3 is higher in rigidity than the second damper structure, and between the internal teeth 23 a of the first output side member 13 in the first damper structure 3 and the external teeth 83 a of the hub 7, Since the above-mentioned gap is formed, the first damper structure 3 is substantially inoperative.

  On the other hand, since the second damper structure is less rigid than the first damper structure 3, the second damper structure 5 operates. That is, since the plurality of low rigidity spring portions 71 in the second damper structure 5 operate, the plurality of low rigidity spring portions 71 form the first stage torsional rigidity K1. The range in which the first stage torsional rigidity K1 is formed (0 <torsion angle A <first torsion angle A1) corresponds to the low torsion angle region LR.

  In the low torsion angle region LR, second and third hysteresis torques H2 and H3 are generated in the second hysteresis torque generation mechanism 79 and the third hysteresis torque generation mechanism 81. That is, the torque fluctuation input to the second damper structure 5 is attenuated by the second hysteresis torque generating mechanism 79 and the third hysteresis torque generating mechanism 81. Thus, only the second and third hysteresis torque generating mechanisms 81 operate in the low torsion angle region LR.

  Next, when the torque input to the clutch disk assembly 1 increases and the torsion angle A reaches the first torsion angle A1, the internal teeth 23a of the first output member 13 in the first damper structure 3 become the hub 7 Abuts on the external teeth (the above clearance becomes zero). Then, the first input side member 11 and the first output side member 13 of the first damper structure 3 rotate relative to each other in the range where the twist angle A is equal to or greater than the first twist angle A1 and less than the third twist angle A3. Structure 3 starts to operate.

  For example, the plurality of first high rigidity spring portions 33 in the first damper structure 3 operate in a range in which the twist angle A is in the range of the first twist angle A1 to the second twist angle A2. Thereby, the second stage torsional rigidity K2 is formed. Then, the plurality of first and second high rigidity spring portions 33, 35 in the first damper structure 3 operate in the range where the twist angle A is in the range of the second twist angle A2 to the third twist angle A3. Thereby, the third stage torsional rigidity K3 is formed.

  Here, a range in which the second stage torsional rigidity K2 is formed (first torsion angle A1 ≦ twist angle A <second torsion angle A2), and a range in which the third stage torsional rigidity K3 is formed (second torsion Angle A2 ≦ twist angle A <third twist angle A3) corresponds to the high twist angle region HR.

  In the high torsion angle region HR, the first hysteresis torque H1 is generated in the first hysteresis torque generation mechanism 37. That is, the torque fluctuation input to the first damper structure 3 is attenuated by the first hysteresis torque generating mechanism 37. Thus, only the first hysteresis torque generation mechanism 37 operates in the high torsion angle region HR.

  In the high torsion angle region HR, the first output side member 13 of the first damper structure 3 is integrally rotated with the hub 7. Further, the second input side member 51 of the second damper structure 5 is integrally rotated with the first output side member 13 of the first damper structure 3. Furthermore, the second output side member 53 of the second damper structure 5 rotates integrally with the hub 7. That is, in the second damper structure 5, since the second input side member 51 and the second output side member 53 are integrally rotated with the hub 7, in this state, the second damper structure 5 stops its operation.

  Finally, when the torque input to the clutch disk assembly 1 increases and the torsion angle A reaches the third torsion angle A3, the first pin member 16 abuts on the wall of the stopper recess 31. As a result, the first input side member 11 can not rotate relative to the first output side member 13, and the first damper structure 3 stops its operation.

[Summary]
In the present clutch disc assembly 1, the second damper structure 5 is disposed inside the first damper structure 3. Therefore, the clutch disc assembly 1 can be miniaturized in the axial direction, and the number of parts of the clutch disc assembly 1 is reduced. it can.

  Further, in the present clutch disc assembly 1, since the second damper structure 5 is disposed as one unit inside the first damper structure 3, the second damper structure 5 can be easily assembled to the first damper structure 3. .

  Further, in the clutch disc assembly 1, only the first hysteresis torque generating mechanism 37 operates in the high torsion angle region HR, and only the third hysteresis torque generating mechanism 81 operates in the low torsion angle region LR. Therefore, the durability of the second damper structure 5 can be improved as compared with the case where the first hysteresis torque generation mechanism 37 occurs in both the low torsion angle region LR and the high torsion angle region HR.

[Other embodiments]
The present invention is not limited to the embodiments as described above, and various changes or modifications are possible without departing from the scope of the present invention.

  (A) In the embodiment, the hysteresis torque due to the first and second high rigidity spring portions 33 and 35 sliding with the first input side member 11 and the first output side member 13 has not been described. However, it may be interpreted that this sliding generates a hysteresis torque.

  (B) In the above embodiment, an example in which the first damper structure 3 includes two high rigidity spring portions (first and second high rigidity spring portions 33 and 35) has been described. May be composed of one high stiffness spring portion (the first high stiffness spring portion 33 or the second high stiffness spring portion 35).

  (C) In the above embodiment, the first high rigidity spring portion 33 has two springs (the first spring 33a for high rigidity and the second spring 33b for high rigidity). The high rigidity spring portion 33 may be configured of one spring (a first spring 33a for high rigidity or a second spring 33b for high rigidity).

  (D) In the above embodiment, the first and second sliding members 39 and 73 slide on the second output side member 53, but the first and second sliding members 39 and 73 are illustrated. However, it may be configured to slide on the second input side member 51. In this case, the first and second sliding members 39 and 73 are configured to be integrally rotatable with the second output side member 53, and slide with the second input side member 51.

DESCRIPTION OF SYMBOLS 1 clutch disc assembly 3 first damper structure 5 second damper structure 7 hub 11 first input side member 13 first output side member 15 first damper portion 17 clutch plate 19 retaining plate 21 clutch disk 51 second input side member 53 second output side member 55 second damper portion 71 low rigidity spring portion 73 second sliding member 75 third sliding member 79 second hysteresis torque generating mechanism 81 third hysteresis torque generating mechanism H2 second hysteresis torque H3 third Hysteresis torque HR high torsion angle region LR low torsion angle region

Claims (12)

A damper disk assembly for attenuating and transmitting torque fluctuation input from an engine to a transmission side,
A first damper structure that receives torque from the engine and operates substantially in a high torsion angle region;
A second damper structure, to which torque is transmitted from the first damper structure, disposed as a unit inside the first damper structure and substantially operating in a low torsion angle region;
An output portion configured to be connectable to the transmission, the torque being output from the first damper structure in the high torsion angle region, and the torque being output from the second damper structure in the low torsion angle region;
Damper disk assembly comprising:
The first damper structure outputs a torque to the output target in the high torsion angle region, and transmits the torque to the second damper structure in the low torsion angle region.
The damper disk assembly according to claim 1.
The first damper structure has a first rotating member,
The first rotating member includes a first input rotating member to which torque is input from the engine, and a second input rotating member configured to be integrally rotatable opposite to the first input rotating member,
The second damper structure is disposed between the first input rotary member and the second input rotary member in the rotation axis direction.
The damper disk assembly according to claim 1.
The first damper structure includes a second rotating member and a first damper portion,
The second rotation member is disposed between the first input rotation member and the second input rotation member in the rotation axis direction, and is configured to be rotatable relative to the first input rotation member and the second input rotation member. And
The first damper unit relatively rotatably connects the first input rotary member and the second input rotary member to the second rotary member,
The second damper structure is disposed between any one of the first input rotary member and the second input rotary member and the second rotary member in the rotation axis direction.
The damper disk assembly according to claim 3.
The second rotating member is configured to be integrally rotatable with the output portion in the high torsion angle region, and configured to be rotatable relative to the output portion in the low torsion angle region.
The damper disk assembly according to claim 3 or 4.
The first damper portion has a first hysteresis torque generating mechanism disposed between the first rotating member and the second rotating member in the rotation axis direction,
The first hysteresis torque generating mechanism has a first sliding portion that generates a first hysteresis torque by sliding with at least one of the first rotating member and the second rotating member.
The damper disk assembly according to claim 4 or 5.
The first hysteresis torque generating mechanism generates the first hysteresis torque only in the high torsion angle region.
The damper disk assembly according to claim 6.
The second damper structure includes a third rotating member, a fourth rotating member, and a second damper portion.
Torque is transmitted to the third rotating member from the first damper structure,
The fourth rotating member is configured to be rotatable relative to the third rotating member,
The second damper unit relatively rotatably connects the third rotating member and the fourth rotating member.
The damper disk assembly according to any one of claims 1 to 7.
The second damper portion has a second hysteresis torque generating mechanism disposed between the third rotating member and the fourth rotating member in the rotation axis direction,
The second hysteresis torque generating mechanism has a second sliding portion that generates a second hysteresis torque by sliding with at least one of the third rotating member and the fourth rotating member.
The damper disk assembly according to claim 8.
10. The damper disk assembly according to claim 9, wherein the second hysteresis torque generating mechanism generates the second hysteresis torque only in the low torsion angle region.
The first damper structure includes a first rotating member and a second rotating member,
Torque is input from the engine to the first rotating member;
The second rotating member is configured to be rotatable relative to the first rotating member,
The third rotation member is configured to be integrally rotatable with the second rotation member.
The fourth rotating member is configured to be integrally rotatable with the output receiving portion.
The damper disk assembly according to any one of claims 8 to 10.
The third rotating member includes a pair of opposing members disposed opposite to each other and configured to be integrally rotatable with each other by the coupling member,
The fourth rotating member is disposed between the pair of opposing members and configured to be rotatable relative to the pair of opposing members.
The second sliding portion is disposed between the facing member and the fourth rotation member.
The second sliding portion is in contact with at least one of the opposing member and the fourth rotating member by the biasing member, and is slid by at least one of the opposing member and the fourth rotating member. Generating the second hysteresis torque,
A damper disk assembly according to any one of claims 9 to 11.

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