JP6756645B2 - Damper disk assembly - Google Patents

Description

The present invention relates to a damper disk assembly.

In the conventional damper disc assembly, for example, the damper disc assembly disclosed in Patent Document 1, the clutch plate and the retaining plate (first and second rotating members) are formed by a stop pin (connecting member) having a circular cross section. It is connected so that it can rotate integrally. Further, the clutch plate and the retaining plate are elastically connected to the hub flange (third rotating member) by the coil spring set (8) . Here, the coil spring set (8) is arranged inside the stop pin in the radial direction.

Japanese Unexamined Patent Publication No. 2009-19746

In a conventional damper disk assembly, the stop pin has a circular cross section. Further, the coil spring set (8) is arranged inside the stop pin having a circular cross section in the radial direction. Therefore, it is difficult to arrange the second elastic member on the outer side in the radial direction. As a result, it was difficult to improve the torque borne by the second elastic member. That is, it was difficult to improve the allowable torque of the second elastic member.

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 capable of improving the allowable torque.

(1) The damper disc assembly according to one aspect of the present invention includes first and second rotating members, a connecting member, a third rotating member, and an elastic portion.

The first and second rotating members are arranged axially spaced apart from each other. The connecting member connects the first and second rotating members so as to be integrally rotatable. The connecting member has a cross section whose circumferential length is longer than its radial length. The third rotating member is arranged between the axial directions of the first and second rotating members and is rotatable with respect to the first and second rotating members. The elastic portion elastically connects the first and second rotating members and the third rotating member.

The elastic portion has a first elastic member arranged radially inside the connecting member and a second elastic member operating in parallel with the first elastic member. Here, the ratio of the second line segment connecting the outermost point and the rotation axis of the first elastic member in the radial direction to the first line segment connecting the outermost point and the rotation axis of the second elastic member in the radial direction is , 0.85 or more and 1.0 or less.

In the present damper disk assembly, the connecting member has a cross section in which the length in the circumferential direction is longer than the length in the radial direction. A first elastic member is arranged inside the connecting member having this cross section in the radial direction. In this configuration, the ratio of the second line segment to the first line segment is set to 0.85 or more and 1.0 or less. On the other hand, in the prior art, the ratio of the outermost diameter of the first elastic member to the outermost diameter of the second elastic member is, for example, less than 0.80.

By constructing the damper disk assembly in this way, the first elastic member can be arranged radially outside as compared with the prior art. Thereby, the torque borne by the first elastic member (allowable torque of the first elastic member) can be improved. That is, the allowable torque of the damper disk assembly can be improved.

(2) In the damper disk assembly according to the other aspect of the present invention, the ratio of the second line segment in the circumferential central portion of the first elastic member to the first line segment in the circumferential central portion of the second elastic member is , 0.85 or more and 1.0 or less is preferable.

With such a configuration, the allowable torque of the first elastic member can be suitably improved. That is, the allowable torque of the damper disk assembly can be suitably improved.

(3) In the damper disc assembly according to another aspect of the present invention, the third rotating member has a first storage window for storing the first elastic member and a second storage for storing the second elastic member. It is preferable to have a window. In this case, the ratio of the fourth line segment connecting the rotation axis and the outermost peripheral portion of the first storage window to the third line segment connecting the rotation axis and the outermost peripheral portion of the second storage window is 0.85. It is more than and less than 1.0.

In this configuration, the first elastic member arranged in the first storage window can be operated on the outer side in the radial direction as compared with the prior art. Thereby, the allowable torque of the first elastic member can be improved. That is, the allowable torque of the damper disk assembly can be improved.

(4) In the damper disk assembly according to the other aspect of the present invention, the outer diameter of the first elastic member with respect to the outer diameter of the second elastic member is preferably 0.75 or more and 1.0 or less.

In this configuration, the outer diameter of the first elastic member can be set larger than that of the prior art. Thereby, the allowable torque of the first elastic member can be improved. That is, the allowable torque of the damper disk assembly can be improved.

In the present invention, the allowable torque of the damper disk assembly can be improved.

Sectional drawing of the clutch disc assembly according to one Embodiment of this invention. Front view of FIG. The front view of FIG. 1 for demonstrating the arrangement of a high-rigidity damper unit. Front view of the low-rigidity damper unit. Partially enlarged cross-sectional view of the first to third hysteresis torque generation mechanisms. Partially enlarged cross-sectional view of the first to third hysteresis torque generation mechanisms. Front view of the urging member. The schematic diagram (the view seen from the outside in the radial direction) for demonstrating the formation form of the urging member. The schematic diagram (the view seen from the outside in the radial direction) for demonstrating the formation form of the urging member. The front view of the low-rigidity damper unit for demonstrating the operation of the 2nd and 3rd hysteresis torque generation mechanisms. The front view of the low-rigidity damper unit for demonstrating the operation of the 2nd and 3rd hysteresis torque generation mechanisms. The front view of the low-rigidity damper unit for demonstrating the operation of the 2nd and 3rd hysteresis torque generation mechanisms. The front view of the low-rigidity damper unit for demonstrating the operation of the 2nd and 3rd hysteresis torque generation mechanisms. The torsional characteristic diagram of the low-rigidity damper unit and the hysteresis torque generation mechanism. The front view of the low-rigidity damper unit for demonstrating the operation of the 2nd and 3rd hysteresis torque generation mechanisms in the first modification. The front view of the low-rigidity damper unit for demonstrating the operation of the 2nd and 3rd hysteresis torque generation mechanisms in the first modification. FIG. 5 is a torsional characteristic diagram of a low-rigidity damper unit and a hysteresis torque generation mechanism according to Modification 1.

[overall structure]
FIG. 1 shows a clutch disc assembly 1 having a damper disc assembly according to an embodiment of the present invention.

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

In FIG. 1, OO is the rotation axis, that is, the rotation center line of the clutch disc assembly 1. Further, in the following, the direction away from the rotation axis O is referred to as a radial direction, and the direction along the rotation axis is referred to as an axial direction. Further, in the following, the direction around the rotation axis O will be referred to as a circumferential direction or a rotation direction.

The engine and flywheel (not shown) are located on the left side of FIG. 1, and the transmission (not shown) is located on the right side of FIG. R1 in FIG. 2 is the rotation driving direction (first rotation direction) of the clutch disc assembly 1, and R2 is the opposite direction (second rotation direction).

The clutch disc assembly 1 transmits the torque input from the engine to the transmission side. The clutch disc assembly 1 mainly includes a high-rigidity damper unit 2, a low-rigidity damper unit 3, a spline hub 4, and a hysteresis torque generation mechanism 5.

<High rigidity damper unit>
Torque from the engine is input to the high-rigidity damper unit 2. The high-rigidity damper unit 2 is, for example, a damper unit that operates during traveling. The high-rigidity damper unit 2 is configured to have higher rigidity than the low-rigidity damper unit 3.

As shown in FIG. 1, the high-rigidity damper unit 2 includes an input side member 10 (an example of a first and second rotating member), a pin member 16 (an example of a connecting member), and a flange portion 11 (an example of a third rotating member). An example) and a high-rigidity spring unit 12 (an example of an elastic portion).

-Input side member-
Torque is input to the input side member 10 from the engine. Specifically, the input side member 10 is a portion to which torque from a flywheel (not shown) is input. As shown in FIGS. 1 and 2, the input side member 10 includes, for example, a clutch plate 13 (an example of a first rotating member), a retaining plate 14 (an example of a second rotating member), and a clutch disc 15. , Have.

The clutch plate 13 and the retaining plate 14 are substantially annular disc members. The clutch plate 13 and the retaining plate 14 are arranged at predetermined intervals in the axial direction. The clutch plate 13 is arranged on the engine side, and the retaining plate 14 is arranged on the transmission side. The clutch plate 13 and the retaining plate 14 are integrally rotatably connected to each other by a fixing member such as a pin member 16.

Four window holes 13a and 14a are formed on the outer peripheral portions of the clutch plate 13 and the retaining plate 14 at equal intervals in the rotation direction, respectively. A high-rigidity spring unit 12 is arranged in each of the window holes 13a and 14a. Both ends of the high-rigidity spring unit 12 are in contact with the wall portions facing each other in the circumferential direction in the window holes 13a and 14a. The window holes 13a and 14a are formed with raised portions on the inner peripheral side and the outer peripheral side, respectively.

The retaining plate 14 has a plurality of (for example, four) support holes 14b. The plurality of support holes 14b are for supporting the hysteresis torque generation mechanism 5. The first protruding portion 45 of the first bush 40 in the hysteresis torque generation mechanism 5, which will be described later, is inserted into each support hole 14b.

The clutch disc 15 is a portion pressed against a flywheel (not shown). The clutch disc 15 is composed of a cushioning plate 15a and friction facings 15b fixed on both sides of the cushioning plate 15a. Since the clutch disc 15 has the same configuration as the conventional configuration, detailed description of the clutch disc 15 will be omitted.

-Pin member-
The pin member 16 integrally rotatably connects the clutch plate 13 and the retaining plate 14. For example, as shown in FIGS. 1 and 2A, the plurality of pin members 16 are separately inserted into a plurality of (for example, four) elongated holes 13b and 14c formed in the clutch plate 13 and the retaining plate 14, respectively. To. Then, both ends of each pin member 16 are crimped to be fixed to the clutch plate 13 and the retaining plate 14.

Each pin member 16 is arranged between the spring accommodating portions 20 adjacent in the circumferential direction. Each pin member 16 can move in the rotational direction together with the clutch plate 13 and the retaining plate 14, and can come into contact with each stopper portion 22 of the flange portion 11.

Each pin member 16 has the following cross section and is a member long in the axial direction. As shown in FIG. 2A, each pin member 16 has a cross section whose circumferential length is longer than its radial length. For example, the cross section of each pin member 16 is formed in a substantially rectangular shape. Specifically, the cross section of each pin member 16 is formed in a rectangular shape so as to be elongated in the circumferential direction. More specifically, the cross section of each pin member 16 is formed in a rectangular shape so as to be elongated in a direction orthogonal to the radial direction.

The ratio of the orthogonal length of the pin member 16 to the radial length of the pin member 16 is, for example, 0.13 or more and 0.2 or less. In this embodiment, the above ratio is set to 0.17.

− Flange part −
The flange portion 11 is configured to be rotatable relative to the input side member 10. As shown in FIGS. 1 to 3, the flange portion 11 is arranged on the radial outer side of the spline hub 4. The flange portion 11 is formed in a substantially annular shape. The flange portion 11 is formed separately from the spline hub 4.

Specifically, as shown in FIG. 1, the flange portion 11 is arranged between the clutch plate 13 and the retaining plate 14 in the axial direction. The flange portion 11 is rotatable with respect to the clutch plate 13 and the retaining plate 14.

As shown in FIG. 3, the flange portion 11 includes a first hole portion 17, an internal tooth portion 18, a first contacted portion 19, a plurality of (for example, four) spring accommodating portions 20, and a plurality (for example, 4). It has a recess 21 and a plurality of stopper portions 22.

The first hole portion 17 is formed in the central portion of the flange portion 11. A spline hub 4 can be inserted into the first hole 17. An internal tooth portion 18 is provided in the first hole portion 17. The internal tooth portion 18 is composed of a plurality of internal teeth, and each internal tooth projects radially inward from the first hole portion 17. The internal tooth portion 18 includes a plurality of pairs (for example, two pairs) of the first internal tooth 18a, a plurality of pairs (for example, two pairs) of the second internal tooth 18b, and a plurality of pairs (for example, two pairs) of the third internal tooth 18c. , Have. The internal tooth portions 18 are arranged in the order of the pair of first internal teeth 18a, the pair of second internal teeth 18b, and the third internal teeth 18c at intervals in the second rotation direction R2.

Each of the first internal teeth 18a of each pair projects radially inward from the first hole 17. Each pair of first internal teeth 18a is provided at intervals in the circumferential direction. The first internal teeth 18a of each pair are arranged between the circumferential directions of the first external teeth 27a and the second external teeth 27b of the spline hub 4. One of the first internal teeth 18a of each pair is arranged so as to face the first external teeth 27a in the first rotation direction R1. The other of the first internal teeth 18a of each pair is arranged to face the second external teeth 27b in the second rotation direction R2. A third spring 25a of the low-rigidity spring unit 25 is arranged between the circumferential directions of the first internal teeth 18a of each pair.

Each of the pair of second internal teeth 18b projects radially inward from the first hole 17. Each pair of second internal teeth 18b is provided at intervals in the circumferential direction. The second internal tooth 18b of each pair is arranged between the second external tooth 27b and the third external tooth 27c of the spline hub 4 in the circumferential direction. One of the second internal teeth 18b of each pair is arranged so as to face the second external teeth 27b in the first rotation direction R1. The other of the second internal teeth 18b of each pair is arranged to face the third external teeth 27c in the second rotation direction R2. A fourth spring 25b of the low-rigidity spring unit 25 is arranged between the circumferential directions of the second internal teeth 18b of each pair.

Each third internal tooth 18c projects radially inward from the first hole 17. Each third internal tooth 18c is provided between the first internal tooth 18a and the second internal tooth 18b adjacent to each other in the circumferential direction in the circumferential direction. Each third internal tooth 18c is arranged between the third external tooth 27c and the first external tooth 27a of the spline hub 4 in the circumferential direction. That is, each of the third internal teeth 18c is arranged so as to face the third outer tooth 27c in the first rotation direction R1 and is arranged so as to face the first outer tooth 27a in the second rotation direction R2.

The first contacted portion 19 is a portion that comes into contact with the third hysteresis torque generating mechanism 63. As shown in FIGS. 4A and 4B, the first contacted portion 19 is provided on the radial outer side of the first hole portion 17. Specifically, the contacted portion is provided on the side surface on the side of the second bush 43 (described later) between the first hole portion 17 and the spring accommodating portion 20 in the radial direction.

The fourth friction member 53 (described later) of the third hysteresis torque generation mechanism 63 comes into contact with the first contacted portion 19. The relationship between the first contacted portion 19 and the fourth friction member 53 (described later) will be described in the third hysteresis torque generation mechanism 63.

As shown in FIG. 3, the plurality of spring accommodating portions 20 are formed on the outer peripheral portion of the flange portion 11. Specifically, the plurality of spring accommodating portions 20 are formed at equal intervals in the circumferential direction.

Here, the flange portion 11 further has a plurality of (for example, four) openings 20a.

Each of the plurality of openings 20a is formed in each spring accommodating portion 20. As shown in FIG. 1, the openings 20a are arranged so as to face the window holes 13a and 14a of the clutch plate 13 and the retaining plate 14 in the axial direction. A high-rigidity spring unit 12 is arranged in each opening 20a. Both ends of the high-rigidity spring unit 12 are in contact with the wall portions facing each other in the circumferential direction at each opening 20a.

Specifically, the plurality of openings 20a include a plurality of (for example, two) first openings 20a1 (an example of a second storage window) and a plurality of (for example, two) second openings 20a2 (an example of a first storage window). have.

The first opening 20a1 is for accommodating the first spring unit 23 of the high-rigidity spring unit 12. Each of the first openings 20a1 has a shaft with respect to each window hole 13a of the clutch plate 13 in which the first spring unit 23 is arranged and each window hole 14a of the retaining plate 14 in which the first spring unit 23 is arranged. They are arranged facing each other.

Each first opening 20a1 is arranged adjacent to each second opening 20a2 in the circumferential direction. Each first opening 20a1 is arranged between the second openings 20a2 adjacent in the circumferential direction.

The second opening 20a2 is for accommodating the second spring unit 24 of the high-rigidity spring unit 12. Each of the second openings 20a2 has a shaft with respect to each window hole 13a of the clutch plate 13 in which the second spring unit 24 is arranged and each window hole 14a of the retaining plate 14 in which the second spring unit 24 is arranged. They are arranged facing each other.

The second openings 20a2 are arranged adjacent to the first openings 20a1 in the circumferential direction. Each of the second openings 20a2 is arranged between the first openings 20a1 adjacent in the circumferential direction. That is, the first opening 20a1 and the second opening 20a2 are alternately arranged in the circumferential direction.

As shown in FIGS. 4A and 4B, the second protrusion 43c (described later) of the second bush 43 is engaged with each of the plurality of recesses 21. Each recess 21 is formed on the inner peripheral edge of each of the two openings 20a facing each other in the radial direction. Each recess 21 is formed in a concave shape toward the rotation axis O at the central portion in the circumferential direction on the inner peripheral edge of the opening 20a.

As shown in FIGS. 1 and 3, each of the plurality of stopper portions 22 is provided on the outer peripheral portion of the spring accommodating portion 20. A pin member 16 for fixing the clutch plate 13 and the retaining plate 14 can be brought into contact with each stopper portion 22. For example, the rotation of the clutch plate 13 and the retaining plate 14 with respect to the flange portion 11 is restricted by the contact between the stopper portion 22 and the pin member 16. That is, the stopper portion 22 and the pin member 16 function as a stopper mechanism.

-High rigidity spring unit-
The high-rigidity spring unit 12 elastically connects the input side member 10 and the flange portion 11 in the rotational direction. Specifically, the plurality of high-rigidity spring units 12 elastically connect the clutch plate 13, the retaining plate 14, and the flange portion 11 in the rotational direction.

As shown in FIGS. 1 and 2, specifically, the high-rigidity spring units 12 include a plurality of (for example, two) first spring units 23 (an example of a second elastic member) and a plurality (for example, two). The second spring unit 24 (an example of the first elastic member) is provided.

As shown in FIG. 2, the first spring unit 23 and the second spring unit 24 are alternately arranged at intervals in the circumferential direction. As shown in FIG. 1, each of the first spring unit 23 and the second spring unit 24 is housed in each opening 20a of the flange portion 11. Further, the movement in the radial direction and the axial direction is regulated by the window holes 13a and 14a of the clutch plate 13 and the retaining plate 14.

The first spring unit 23 operates in parallel with the second spring unit 24. The first spring unit 23 has a first large spring 23a and a first small spring 23b. The first large spring 23a is formed to have a larger diameter than the first small spring 23b. The first small spring 23b is arranged on the inner peripheral side of the first large spring 23a. Here, the first small spring 23b has substantially the same length as the first large spring 23a.

Both ends of the first large spring 23a and both ends of the first small spring 23b are separately in contact with the wall portions facing each other in the circumferential direction at each opening 20a of the flange portion 11. Both ends of the first large spring 23a and both ends of the first small spring 23b are separately in contact with the wall portions facing each other in the circumferential direction in the window holes 13a and 14a of the clutch plate 13 and the retaining plate 14. ..

The second spring unit 24 has a second large spring 24a and a second small spring 24b. The second large spring 24a is formed to have a larger diameter than the second small spring 24b. The second small spring 24b is arranged on the inner peripheral side of the second large spring 24a. Here, the second small spring 24b has substantially the same length as the second large spring 24a.

Both ends of the second large spring 24a and both ends of the second small spring 24b are separately in contact with the wall portions facing each other in the circumferential direction at each opening 20a of the flange portion 11. Both ends of the second large spring 24a and both ends of the second small spring 24b are separately in contact with the wall portions facing each other in the circumferential direction in the window holes 13a and 14a of the clutch plate 13 and the retaining plate 14. ..

As shown in FIG. 2A, the second spring unit 24 is arranged radially inside the pin member 16. Here, the ratio of the outer diameter of the second spring unit 24 to the outer diameter of the first spring unit 23 is set to 0.75 or more and 1.0 or less. More specifically, the ratio of the outer diameter of the second large spring 24a to the outer diameter of the first large spring 23a is set to 0.75 or more and 1.0 or less. In this embodiment, the above ratio is set to 0.78.

With this configuration, the first spring unit 23 and the second spring unit 24 elastically connect the clutch plate 13, the retaining plate 14, and the flange portion 11 in the rotational direction.

In the high-rigidity damper unit 2 having the above configuration, as shown in FIG. 2B, when the high-rigidity damper unit 2 (clutch disc assembly 1) is viewed from the outside in the axial direction in the axial direction, each configuration is as follows. Is placed in.

The second outermost point E2 and the rotation axis O of the second spring unit 24 in the radial direction with respect to the first line segment L1 connecting the first outermost point E1 and the rotation axis O of the first spring unit 23 in the radial direction. The ratio of the second line segment L2 to be connected is 0.85 or more and 1.0 or less.

Specifically, the second line in the circumferential center of the second spring unit 24 (second large spring 24a) with respect to the first line segment L1 in the circumferential center of the first spring unit 23 (first large spring 23a). The ratio of the line segment L2 is 0.85 or more and 1.0 or less. In this embodiment, the above ratio is set to 0.9.

Here, the first line segment L1 is defined on a plane that is perpendicular to the rotation axis O and passes through the first outermost point E1. The second line segment L2 is defined on a plane that is perpendicular to the rotation axis O and passes through the second outermost point E2.

The circumferential central portion of the first spring unit 23 (first large spring 23a) is the central portion of the first spring unit 23 (first large spring 23a) in the circumferential direction around the rotation axis O. Specifically, the circumferential central portion of the first spring unit 23 (first large spring 23a) is defined by the midpoint C1 of the first spring unit 23 on the operating shaft J1 of the first spring unit 23.

The circumferential central portion of the second spring unit 24 (second large spring 24a) is the central portion of the second spring unit 24 (second large spring 24a) in the circumferential direction around the rotation axis O. Specifically, the circumferential central portion of the second spring unit 24 (second large spring 24a) is defined by the midpoint C2 of the second spring unit 24 on the operating shaft J2 of the second spring unit 24.

The first outermost point E1 corresponds to the outermost point of the first spring unit 23 in the radial direction from the rotation axis O toward the midpoint C1 on the operating axis of the first spring unit 23. The second outermost point E2 corresponds to the outermost point of the second spring unit 24 in the radial direction from the rotation axis O toward the midpoint C2 on the operating axis of the second spring unit 24.

The ratio of the fourth line segment L4 connecting the rotation axis O and the outermost peripheral portion P2 of the second opening 20a2 to the third line segment L3 connecting the rotation axis O and the outermost peripheral portion P1 of the first opening 20a1 is It is 0.85 or more and 1.0 or less. In this embodiment, the above ratio is set to 0.88.

Here, the third and fourth line segments L3 and L4 are defined on a plane that is perpendicular to the rotation axis O and passes through the outermost peripheral portions P1 and P2. The outermost peripheral portion P1 of the first opening 20a1 is the outermost portion of the first opening 20a1 in the radial direction. For example, the outermost peripheral portion P1 of the first opening 20a1 is a central point in the circumferential direction on the outer peripheral side wall portion of the first opening 20a1. The outermost peripheral portion P2 of the second opening 20a2 is the outermost portion of the second opening 20a2 in the radial direction. For example, the outermost peripheral portion P2 of the second opening 20a2 is the central point in the circumferential direction of the wall portion on the outer peripheral side of the second opening 20a2.

By configuring the high-rigidity damper unit 2 in this way, the second spring unit 24 can be arranged radially outside as compared with the prior art. As a result, the torque borne by the second spring unit 24 (allowable torque of the second spring unit 24) can be improved. That is, the allowable torque of the high-rigidity damper unit 2, that is, the allowable torque of the clutch disc assembly 1, can be improved.

<Low rigidity damper unit>
The low-rigidity damper unit 3 is, for example, a damper unit that operates when idling. The low-rigidity damper unit 3 is configured to have lower rigidity than the high-rigidity damper unit 2.

As shown in FIG. 1, the low-rigidity damper unit 3 is arranged between the flange portion 11 and the spline hub 4 in the radial direction. Specifically, the low-rigidity damper unit 3 is arranged on the inner peripheral side of the high-rigidity spring unit 12 between the flange portion 11 and the spline hub 4 in the radial direction.

The low-rigidity damper unit 3 has a flange portion 11, a low-rigidity spring unit 25, and a spline hub 4. Since the configuration of the flange portion 11 has been described in the high-rigidity damper unit 2 described above, the description thereof will be omitted here.

-Low rigidity spring unit-
The low-rigidity spring unit 25 elastically connects the flange portion 11 and the spline hub 4 in the rotational direction. The low-rigidity spring unit 25 has a lower rigidity than the high-rigidity spring unit 12. As shown in FIG. 1, the low-rigidity spring unit 25 is arranged in a space formed between the flange portion 11 and the spline hub 4 in the radial direction.

As shown in FIG. 3, the low-rigidity spring unit 25 has a plurality of (for example, two) third springs 25a and a plurality of (for example, two) fourth springs 25b. The third spring 25a and the fourth spring 25b are alternately arranged at intervals in the circumferential direction.

The third spring 25a is arranged between the circumferential direction of each pair of first internal teeth 18a, and is arranged between the first external tooth 27a and the second external tooth 27b adjacent to each other in the circumferential direction. Specifically, both ends of the third spring 25a engage each pair of first internal teeth 18a separately. Here, spring seats are arranged at both ends of the third spring 25a, and both ends of the third spring 25a are separately engaged with the first internal teeth 18a of each pair via the spring seats. ..

In the following, the terms "both ends of the third spring 25a" and "ends of the third spring 25a" may be used as terms including a spring seat.

Further, both ends of the third spring 25a are separately divided into a first engaging portion 28a (described later) of the first outer tooth 27a and a second engaging portion 28b (described later) of the second outer tooth 27b. Engage. Here, both ends of the third spring 25a are formed into a first engaging portion 28a of the first outer tooth 27a and a second engaging portion 28b (described later) of the second outer tooth 27b via a spring seat. , Engage each separately.

As shown in FIG. 3, when the flange portion 11 and the spline hub 4 are in the initial state, the spring seats at both ends of the third spring 25a, for example, both ends of the third spring 25a, are combined with the first engaging portion 28a. The second engaging portion 28b and the pair of first internal teeth 18a are in contact with each other separately.

The initial state is a state in which the relative rotation of the flange portion 11 and the spline hub 4 is zero (see the origin in FIG. 7). The initial state is the state shown in FIG. 6A.

The fourth spring 25b is arranged between the circumferential direction of each pair of the second internal teeth 18b, and is arranged between the second outer tooth 27b and the third outer tooth 27c adjacent to each other in the circumferential direction. Specifically, both ends of the fourth spring 25b engage each pair of second internal teeth 18b separately. Here, spring seats are arranged at both ends of the fourth spring 25b, and both ends of the fourth spring 25b are separately engaged with the second internal teeth 18b of each pair via the spring seats. ..

In the following, the terms "both ends of the fourth spring 25b" and "ends of the fourth spring 25b" may be used as terms including a spring seat.

Further, both ends of the fourth spring 25b are separately divided into a third engaging portion 28c (described later) of the second outer tooth 27b and a fourth engaging portion 28d (described later) of the third outer tooth 27c. Engage. Here, both ends of the fourth spring 25b are separately engaged with the third engaging portion 28c of the second outer tooth 27b and the fourth engaging portion 28d of the third outer tooth 27c via the spring seat. It fits.

Further, both ends of the fourth spring 25b are separately engaged with a pair of claws 51 (described later) adjacent to each other in the circumferential direction. Here, both ends of the fourth spring 25b are separately engaged with a pair of claws 51 adjacent to each other in the circumferential direction via a spring seat. The claw portion 51 will be described in the third hysteresis torque generation mechanism 63.

As shown in FIG. 3, when the flange portion 11 and the spline hub 4 are in the initial state, both ends of the fourth spring 25b are connected to the pair of second internal teeth 18b and the pair of claw portions 51 via the spring seat. , Each is in contact with each other.

Further, in this case, as shown in FIG. 6A, a first gap S1 is provided between one end portion (spring seat) of the fourth spring 25b and the circumferential direction of the third engaging portion 28c. Further, in this case, a second gap S2 is provided between the other end portion (spring seat) of the fourth spring 25b and the circumferential direction of the fourth engaging portion 28d.

-Spline hub-
The spline hub 4 is configured to be connectable to a member on the transmission side. As shown in FIG. 3, the spline hub 4 has a cylindrical portion 26 and an external tooth portion 27. The cylindrical portion 26 is formed in a substantially cylindrical shape. The cylindrical portion 26 is connected to the transmission-side member by spline engagement so that it can rotate integrally with the transmission-side member.

The external tooth portion 27 is provided on the outer peripheral portion of the cylindrical portion 26. The external tooth portion 27 is composed of a plurality of external teeth, and each external tooth projects radially outward from the cylindrical portion 26. The external tooth portion 27 has a plurality of (for example, two) first external teeth 27a, a plurality of (for example, two) second external teeth 27b, and a plurality of (for example, two) third external teeth 27c. doing. The external tooth portions 27 are arranged in the second rotation direction R2 in the order of the first external tooth 27a, the second external tooth 27b, and the third external tooth 27c at intervals.

Each pair of first internal teeth 18a is arranged between the first external teeth 27a and the second external teeth 27b in the circumferential direction. A third spring 25a of the low-rigidity spring unit 25 is arranged between the first outer teeth 27a and the second outer teeth 27b in the circumferential direction.

A pair of second internal teeth 18b is arranged between the second external teeth 27b and the third external teeth 27c in the circumferential direction. A fourth spring 25b of the low-rigidity spring unit 25 is arranged between the second outer tooth 27b and the third outer tooth 27c in the circumferential direction. A third internal tooth 18c is arranged between the third external tooth 27c and the first external tooth 27a in the circumferential direction.

In the above-mentioned initial state, as shown in FIG. 6A, a third gap S3 is provided between the first internal tooth 18a and the second external tooth 27b in the circumferential direction. Further, a fourth gap S4 is provided between the second internal tooth 18b and the second external tooth 27b in the circumferential direction.

Further, in the above-mentioned initial state, a fifth gap S5 is provided between the second internal tooth 18b and the third external tooth 27c in the circumferential direction. Further, a sixth gap S6 is provided between the third internal tooth 18c and the third external tooth 27c in the circumferential direction.

Further, in the above-mentioned initial state, a seventh gap S7 is provided between the third internal tooth 18c and the first external tooth 27a in the circumferential direction. Further, an eighth gap S8 is provided between the first outer tooth 27a and the first inner tooth 18a in the circumferential direction.

As shown in FIG. 6A, the first external tooth 27a projects radially outward from the cylindrical portion 26. The first external tooth 27a is provided between the third external tooth 27c and the second external tooth 27b in the circumferential direction. The first external tooth 27a is provided with a first engaging portion 28a. For example, the first engaging portion 28a is provided at the end portion of the first external tooth 27a on the second rotation direction R2 side. The first engaging portion 28a engages with the end portion of the third spring 25a.

The second external tooth 27b projects radially outward from the cylindrical portion 26. The second external tooth 27b is provided between the first external tooth 27a and the third external tooth 27c in the circumferential direction. The second external tooth 27b is provided with a second engaging portion 28b and a third engaging portion 28c.

For example, the second engaging portion 28b is provided at the end portion of the second external tooth 27b on the first rotation direction R1 side. The second engaging portion 28b engages with the end portion of the third spring 25a. The third engaging portion 28c is provided at the end portion of the second external tooth 27b on the second rotation direction R2 side. The third engaging portion 28c engages with the end portion of the fourth spring 25b.

The third external tooth 27c projects radially outward from the cylindrical portion 26. The third external tooth 27c is provided between the second external tooth 27b and the first external tooth 27a in the circumferential direction. The third external tooth 27c is provided with a fourth engaging portion 28d. For example, the fourth engaging portion 28d is provided at the end portion of the third external tooth 27c on the first rotation direction R1 side.

<Hysteresis torque generation mechanism>
As shown in FIGS. 4A and 4B, the hysteresis torque generation mechanism 5 includes a first hysteresis torque generation mechanism 61, a second hysteresis torque generation mechanism 62, and a third hysteresis torque generation mechanism 63 .

-First hysteresis torque generation mechanism-
The first hysteresis torque generation mechanism 61 is, for example, a hysteresis torque generation mechanism that operates during traveling.

The first hysteresis torque generation mechanism 61 is arranged between the high-rigidity spring unit 12 and the spline hub 4 in the radial direction. The first hysteresis torque generating mechanism 61 is arranged on the inner peripheral side of the high-rigidity spring unit 12 between the input side member 10 (retaining plate 14 and the clutch plate 13) and the flange portion 11 in the axial direction.

The first hysteresis torque generation mechanism 61 includes a first bush 40, a first friction member 41, a first urging member 42, a second bush 43, and a second friction member 44.

The first bush 40 is arranged between the retaining plate 14 and the flange portion 11 in the axial direction. The first bush 40 is urged from the retaining plate 14 toward the flange portion 11 by the first urging member 42.

The first bush 40 is formed in a substantially annular shape. As shown in FIGS. 1 and 2, the first bush 40 is provided with a plurality of (for example, four) first protrusions 45. Each of the first protruding portions 45 is provided on the outer peripheral portion of the first bush 40 at intervals in the circumferential direction. Each of the first protrusions 45 is inserted into each of the support holes 14b of the retaining plate 14. As a result, the first bush 40 is configured to be movable in the axial direction with respect to the retaining plate 14 and to be integrally rotatable with the retaining plate 14.

The first friction member 41 is formed substantially in an annular shape. The first friction member 41 is arranged between the first bush 40 and the flange portion 11 in the axial direction. The first friction member 41 is mounted on the first bush 40 so as to be integrally rotatable with the first bush 40. Here, the first friction member 41 is fixed to the first bush 40. For example, the first friction member 41 is integrally molded with the resin first bush 40 by injection molding.

The first friction member 41 comes into contact with the flange portion 11. When the first bush 40 rotates with respect to the flange portion 11, the first friction member 41 slides with respect to the flange portion 11 in contact with the flange portion 11. As a result, the first hysteresis torque is generated.

The first urging member 42 is arranged between the first bush 40 and the retaining plate 14 in the axial direction. The first urging member 42 urges the first bush 40 toward the flange portion 11. The first urging member 42 is, for example, a cone spring.

The second bush 43 is arranged between the clutch plate 13 and the flange portion 11 in the axial direction. The second bush 43 is urged toward the clutch plate 13 by the first urging member 42 via the flange portion 11, the first friction member 41, and the first bush 40.

The second bush 43 is formed in a substantially annular shape. As shown in FIGS. 4A and 4B, the second bush 43 is provided with a plurality of (for example, two) second protrusions 43c. Each of the second protruding portions 43c is provided on the outer peripheral portion of the second bush 43 at intervals in the circumferential direction. Each second protrusion 43c is arranged in each recess 21 (see FIG. 3) of the flange portion 11. As a result, the second bush 43 is configured to be integrally rotatable with respect to the flange portion 11. The second bush 43 is also a member that constitutes the second hysteresis torque generation mechanism 62, which will be described later.

The second friction member 44 is formed substantially in an annular shape. The second friction member 44 is arranged between the second bush 43 and the clutch plate 13 in the axial direction. The second friction member 44 is mounted on the second bush 43 so as to be integrally rotatable with the second bush 43. Here, the second friction member 44 is fixed to the second bush 43. For example, the second friction member 44 is integrally molded with the resin first bush 40 by injection molding.

The second friction member 44 comes into contact with the clutch plate 13. When the second bush 43 rotates with respect to the clutch plate 13, the second friction member 44 slides with respect to the clutch plate 13 in contact with the clutch plate 13. As a result, the first hysteresis torque is generated.

-Second hysteresis torque generation mechanism-
The second hysteresis torque generation mechanism 62 is, for example, a hysteresis torque generation mechanism that operates during idling.

As shown in FIGS. 4A and 4B, the second hysteresis torque generating mechanism 62 is arranged between the high-rigidity spring unit 12 and the spline hub 4 in the radial direction. The second hysteresis torque generating mechanism 62 is arranged on the inner peripheral side of the high-rigidity spring unit 12 between the input side member 10 (retaining plate 14 and the clutch plate 13) and the flange portion 11 in the axial direction.

The second hysteresis torque generation mechanism 62 has the above-mentioned second bush 43, the third bush 46, and the second urging member 47.

The second bush 43 is arranged between the high-rigidity spring unit 12 and the spline hub 4 in the radial direction. The second bush 43 is arranged between the clutch plate 13 and the flange portion 11 in the axial direction.

The second bush 43 includes a main body portion 43a, an outer cylinder portion 43b, a plurality of (for example, four) second protruding portions 43c, an annular groove portion 43d, a first contact portion 43e, and a second contacted portion 43f. have.

The main body 43a is formed substantially in an annular shape. The main body portion 43a is arranged between the clutch plate 13 and the flange portion 11 in the axial direction. Specifically, the main body 43a is arranged between the clutch plate 13 and the third hysteresis torque generating mechanism 63 in the axial direction.

The outer cylinder portion 43b is provided on the outer peripheral portion of the main body portion 43a. For example, the outer cylinder portion 43b is provided on the outer peripheral portion of the main body portion 43a on the outer peripheral side of the third hysteresis torque generation mechanism 63. The outer cylinder portion 43b is formed in a substantially cylindrical shape.

Each of the plurality of second projecting portions 43c projects axially from the outer cylinder portion 43b. As described above, each of the second protruding portions 43c is arranged in each recess 21 of the flange portion 11. As a result, the second bush 43 is configured to be integrally rotatable with respect to the flange portion 11.

The annular groove portion 43d is provided in the main body portion 43a so as to face the clutch plate 13 in the axial direction. The annular groove portion 43d is formed in the main body portion 43a by being recessed in an annular shape. A second friction member 44 is arranged in the annular recess. For example, as described above, the second friction member 44 is integrally molded together with the second bush 43 and can rotate integrally with the second bush 43.

The first contact portion 43e is a portion that contacts the spline hub 4. The first contact portion 43e is provided on the inner peripheral portion of the main body portion 43a. Specifically, the first contact portion 43e is provided on the side surface of the main body portion 43a on the inner peripheral portion on the flange portion 11 side.

The first contact portion 43e contacts the external tooth portion 27 of the spline hub 4. Specifically, the first contact portion 43e contacts the proximal end portion of the external tooth portion 27 of the spline hub 4. When the second bush 43 rotates with respect to the spline hub 4, the first contact portion 43e slides with respect to the proximal end portion of the external tooth portion 27 in a state of being in contact with the proximal end portion of the external tooth portion 27. .. As a result, the second hysteresis torque is generated.

The second contacted portion 43f is a portion that comes into contact with the third hysteresis torque generating mechanism 63. The second contacted portion 43f is provided on the radial outer side of the first contacted portion 43e. Specifically, the second contacted portion 43f is provided on the side surface of the outer peripheral portion of the main body portion 43a on the flange portion 11 side. More specifically, the second contacted portion 43f is provided on the side surface of the main body portion 43a on the flange portion 11 side between the first contact portion 43e and the outer cylinder portion 43b in the radial direction.

The fourth friction member 53 (described later) of the third hysteresis torque generating mechanism 63 comes into contact with the second contacted portion 43f. The relationship between the second contacted portion 43f and the fourth friction member 53 will be described in the third hysteresis torque generation mechanism 63.

The third bush 46 is formed in a substantially annular shape. The third bush 46 is arranged between the retaining plate 14 and the flange portion 11 in the axial direction. The third bush 46 is urged from the retaining plate 14 toward the flange portion 11 by the second urging member 47.

The third bush 46 has a second contact portion 46a. The second contact portion 46a contacts the external tooth portion 27 of the spline hub 4. Specifically, the second contact portion 46a contacts the proximal end portion of the external tooth portion 27 of the spline hub 4. When the third bush 46 rotates with respect to the spline hub 4, the second contact portion 46a slides with respect to the proximal end portion of the external tooth portion 27 in a state of being in contact with the proximal end portion of the external tooth portion 27. .. As a result, the second hysteresis torque is generated.

The second urging member 47 is arranged between the third bush 46 and the retaining plate 14 in the axial direction. The second urging member 47 urges the third bush 46 toward the external tooth portion 27 of the spline hub 4. The second urging member 47 is, for example, a cone spring.

-Third hysteresis torque generation mechanism-
The third hysteresis torque generation mechanism 63 is, for example, a hysteresis torque generation mechanism that operates during idling.

As shown in FIGS. 4A and 4B, the third hysteresis torque generation mechanism 63 is arranged between the high-rigidity spring unit 12 and the spline hub 4 in the radial direction. The third hysteresis torque generation mechanism 63 is arranged on the inner peripheral side of the high-rigidity spring unit 12 between the input side member 10 (clutch plate 13) and the flange portion 11 in the axial direction.

The third hysteresis torque generation mechanism 63 is held in the circumferential direction by the fourth spring 25b of the low-rigidity spring unit 25.

The third hysteresis torque generation mechanism 63 is configured to be rotatable with respect to the flange portion 11. Further, the third hysteresis torque generation mechanism 63 is configured to be slidable with respect to the flange portion 11. Further, the third hysteresis torque generation mechanism 63 is configured to be slidable with respect to the second bush 43.

As shown in FIGS. 4A and 4B, the third hysteresis torque generation mechanism 63 includes a wave spring 50, a plurality of (for example, four) claw portions 51, a third friction member 52, and a fourth friction member 53. , Have.

The wave spring 50 is formed in a substantially annular shape. The wave spring 50 is a spring in which convex portions and concave portions are alternately and continuously formed in the circumferential direction. The wave spring 50 is arranged between the flange portion 11 and the second bush 43 in the axial direction. The wave spring 50 is arranged at a distance from the flange portion 11 in the axial direction. The wave spring 50 is arranged at a distance from the second bush 43 in the axial direction.

The wave spring 50 is arranged between the third friction member 52 and the fourth friction member 53 in the axial direction. The wave spring 50 is positioned in the radial direction by the outer cylinder portion 43b of the second bush 43. Specifically, as shown in FIG. 5, the wave spring 50 is formed by being compressed in the axial direction by the third friction member 52 and the fourth friction member 53. As a result, the third friction member 52 is urged toward the flange portion 11 by the wave spring 50, and the fourth friction member 53 is urged toward the second bush 43 by the wave spring 50.

As shown in FIGS. 4A and 4B and FIGS. 6A to 6D, each of the plurality of claw portions 51 is held in the circumferential direction by the fourth spring 25b of the low-rigidity spring unit 25. Specifically, each claw portion 51 is held in the circumferential direction by the fourth spring 25b by abutting on the end portion of the fourth spring 25b.

Each claw portion 51 is provided on the inner peripheral side of the wave spring 50. Specifically, each of the plurality of claw portions 51 is integrally formed on the inner peripheral portion of the wave spring 50 at intervals in the circumferential direction.

Each claw portion 51 has a first portion 51a extending radially inward from the inner peripheral portion of the wave spring 50, and a second portion 51b extending axially from the first portion 51a. The first portion 51a is arranged between the second bush 43 and the flange portion 11 in the axial direction.

The second portion 51b extends from the tip of the first portion 51a toward the retaining plate 14. The second portion 51b is arranged on the inner peripheral side of the flange portion 11. Specifically, the second portion 51b is arranged on the inner peripheral side of the second internal tooth 18b of the flange portion 11. Further, the second portion 51b can come into contact with the end portion of the fourth spring 25b. When the second portion 51b comes into contact with the end portion of the fourth spring 25b, each claw portion 51 is held in the circumferential direction by the fourth spring 25b.

The third friction member 52 is formed substantially in an annular shape. The third friction member 52 is arranged between the flange portion 11 and the wave spring 50 in the axial direction. The third friction member 52 is urged toward the flange portion 11 by the wave spring 50.

The third friction member 52 has a third contact portion 52a and a first pressed portion 52b. The third contact portion 52a is a portion that comes into contact with the flange portion 11. The third contact portion 52a is provided on the side surface of the third friction member 52 on the flange portion 11 side. The first pressed portion 52b is a surface pressed by the wave spring 50. The first pressed portion 52b is provided on the side surface of the third friction member 52 on the wave spring 50 side.

The fourth friction member 53 is formed substantially in an annular shape. The fourth friction member 53 is arranged between the second bush 43 and the wave spring 50 in the axial direction. The fourth friction member 53 is urged toward the second bush 43 by the wave spring 50.

The fourth friction member 53 has a fourth contact portion 53a and a second pressed portion 53b. The fourth contact portion 53a is a portion that comes into contact with the second bush 43. The fourth contact portion 53a is provided on the side surface of the fourth friction member 53 on the side of the second bush 43. The second pressed portion 53b is a surface pressed by the wave spring 50. The second pressed portion 53b is provided on the side surface of the fourth friction member 53 on the wave spring 50 side.

In the third hysteresis torque generation mechanism 63 having the above configuration, the third contact portion 52a of the third friction member 52 contacts the flange portion 11 (first contacted portion 19), and the fourth contact portion 53 of the fourth friction member 53 comes into contact with the flange portion 11. The portion 53a comes into contact with the second bush 43 (second contacted portion 43f). In this state, when the flange portion 11 and the second bush 43 rotate with respect to the third hysteresis torque generating mechanism 63, the third friction member 52 and the fourth friction member 53 refer to the flange portion 11 and the second bush 43. Each slides separately. As a result, a third hysteresis torque is generated.

[Operation of clutch disc assembly]
Here, the operation of the clutch disc assembly 1 will be described. In the clutch disc assembly 1, when torque is input to the input side member 10 (clutch plate 13 and the retaining plate 14), the input side member 10 starts rotating with respect to the spline hub 4.

Then, the torque is transmitted from the input side member 10 to the flange portion 11 via the high-rigidity spring unit 12. Since the high-rigidity spring unit 12 is substantially inactive when the input-side member 10 has started to rotate, the flange portion 11 rotates integrally with the input-side member 10. Therefore, the first hysteresis torque generation mechanism 61 is substantially inactive.

In this state, the flange portion 11 rotates relative to the spline hub 4 via the third spring 25a of the low-rigidity damper unit 3. Then, the second hysteresis torque generation mechanism 62 operates. As a result, the second hysteresis torque is generated.

Then, when the relative rotation of the flange portion 11 and the spline hub 4 becomes further large, the flange portion 11 becomes relative to the spline hub 4 via the third spring 25a and the fourth spring 25b of the low-rigidity damper unit 3. Rotate. Then, the third hysteresis torque generation mechanism 63 is further operated. As a result, a third hysteresis torque is generated. In this state, both the second hysteresis torque and the third hysteresis torque are generated.

Subsequently, when the relative rotation of the flange portion 11 and the spline hub 4 becomes larger, the flange portion 11 and the spline hub 4 are brought into contact with each other by the contact between the inner tooth portion 18 of the flange portion 11 and the outer tooth portion 27 of the spline hub 4. Relative rotation becomes impossible. As a result, the flange portion 11 and the spline hub 4 rotate integrally. Then, the second hysteresis torque generation mechanism 62 and the third hysteresis torque generation mechanism 63 stop operating.

As described above, when the high-rigidity spring unit 12 starts operating in a state where the flange portion 11 and the spline hub 4 are integrally rotating, the input side member 10 acts on the flange portion 11 (spline hub 4). And rotate relatively. Then, the first hysteresis torque generation mechanism 61 operates. As a result, the first hysteresis torque is generated.

[Operation of 2nd and 3rd hysteresis torque generation mechanism]
Here, the operations of the second hysteresis torque generating mechanism 62 and the third hysteresis torque generating mechanism 63 will be described with reference to FIGS. 6A to 6D.

As described above, the second hysteresis torque generating mechanism 62 and the third hysteresis torque generating mechanism 63 operate when the flange portion 11 and the spline hub 4 rotate relative to each other in a state where the first hysteresis torque generating mechanism 61 is not operating. ..

The second hysteresis torque generation mechanism 62 generates the second hysteresis torque during the operation of the third spring 25a of the low-rigidity damper unit 3. Further, the third hysteresis torque generation mechanism 63 generates the third hysteresis torque during the operation of the third spring 25a and the fourth spring 25b of the low-rigidity damper unit 3.

For example, when the flange portion 11 first rotates with respect to the spline hub 4 in the first rotation direction R1 from the initial state of FIG. 6A, the third spring 25a causes the first internal teeth 18a and the first external teeth 27a to rotate. 1 It is compressed by the engaging portion 28a. In this state, the third spring 25a is operating and the fourth spring 25b is not operating. As a result, the first rigidity K1 is formed at the twist angle of "0 to a1" in FIG.

Here, the fourth spring 25b is rotating with respect to the spline hub 4 together with the flange portion 11 and the third hysteresis torque generating mechanism 63 in the inactive state. Specifically, the fourth spring 25b rotates with respect to the spline hub 4 in a state of being arranged between each pair of claw portions 51 and each pair of second internal teeth 18b.

In this state, the first contact portion 43e of the second bush 43 and the second contact portion 46a of the third bush 46 slide with respect to the base end portion of the external tooth portion 27 of the spline hub 4 (FIGS. 4A and 4A). See FIG. 4B). As a result, the second hysteresis torque H2 is generated at the twist angle of “0 to a1” in FIG. 7.

Next, as shown in FIG. 6B, when the flange portion 11 further rotates in the first rotation direction R1 with respect to the spline hub 4, the fourth spring 25b operates at the same time with the third spring 25a operating.

In this case, the fourth spring 25b is one of the pair of second internal teeth 18b while one of the pair of claw portions 51 is held (sandwiched) by the ends of the second outer tooth 27b and the fourth spring 25b. It is compressed by (the second internal tooth 18b between the end of the fourth spring 25b and the third external tooth 27c) and the third engaging portion 28c of the second external tooth 27b. As a result, the second rigidity K2 is formed at the twist angle of “a1 to a2” in FIG.

In this state, as described above, the claw portion 51 is held (sandwiched) by the ends of the second outer teeth 27b and the fourth spring 25b, so that the wave spring 50 rotates integrally with the spline hub 4. As a result, the flange portion 11 and the second bush 43 that rotates integrally with the flange portion 11 rotate relative to the spline hub 4 and the wave spring 50.

Then, the flange portion 11 (first contacted portion 19) slides with respect to the third contact portion 52a of the third friction member 52, and the second bush 43 (second contacted portion 43f) slides on the fourth friction member 53. Sliding with respect to the fourth contact portion 53a of the above (see FIGS. 4A and 4B). As a result, the third hysteresis torque H3 is generated. In this state (twisting angle of "a1 to a2" in FIG. 7), both the second hysteresis torque H2 and the third hysteresis torque H3 are generated.

Then, as shown in FIG. 6C, the other of the pair of second internal teeth 18b (the second internal tooth 18b between the end of the fourth spring 25b and the second external tooth 27b) hits the second external tooth 27b. Upon contact, the rotation of the flange portion 11 with respect to the spline hub 4 stops. As a result, the rotation of the flange portion 11 with respect to the spline hub 4 in the first rotation direction R1 is stopped.

In this state, when the flange portion 11 rotates in the second rotation direction R2 with respect to the spline hub 4, the operations opposite to the above-described operations are performed in the order of FIGS. 6C, 6B, and 6A, and the initial state is restored. To do.

On the other hand, when the flange portion 11 rotates with respect to the spline hub 4 in the second rotation direction R2 from the initial state of FIG. 6A, the third spring 25a is the second of the first internal teeth 18a and the second external teeth 27b. It is compressed by the engaging portion 28b. In this state, the third spring 25a is operating and the fourth spring 25b is not operating. As a result, the first rigidity K1 is formed at the twist angle of "0 to b1" in FIG.

Here, the fourth spring 25b is rotating with respect to the spline hub 4 together with the flange portion 11 and the third hysteresis torque generating mechanism 63 in the inactive state. Specifically, the fourth spring 25b rotates with respect to the spline hub 4 in a state of being arranged between each pair of claw portions 51 and each pair of second internal teeth 18b.

In this state, the first contact portion 43e of the second bush 43 and the second contact portion 46a of the third bush 46 slide with respect to the base end portion of the external tooth portion 27 of the spline hub 4 (FIGS. 4A and 4A). See FIG. 4B). As a result, the second hysteresis torque H2 is generated at the twist angle of "0 to b1" in FIG. 7.

Next, when the flange portion 11 further rotates in the second rotation direction R2 with respect to the spline hub 4, the fourth spring 25b operates with the third spring 25a operating, as shown in FIG. 6D.

In this case, the fourth spring 25b is the other of the pair of second internal teeth 18b while the other of the pair of claws 51 is held (sandwiched) by the ends of the third outer tooth 27c and the fourth spring 25b. And the fourth engaging portion 28d of the third outer tooth 27c. As a result, the second rigidity K2 is formed at the twist angle of "b1 to b2" in FIG.

In this state, the claw portion 51 is held (sandwiched) by the ends of the third external tooth 27c and the fourth spring 25b, so that the wave spring 50 rotates integrally with the spline hub 4. As a result, the flange portion 11 and the second bush that rotates integrally with the flange portion 11 rotate relative to the spline hub 4 and the wave spring 50.

Then, the flange portion 11 (first contacted portion 19) slides with respect to the third contact portion 52a of the third friction member 52, and the second bush 43 (second contacted portion 43f) slides on the fourth friction member 53. Sliding with respect to the fourth contact portion 53a of the above (see FIGS. 4A and 4B). As a result, the third hysteresis torque H3 is generated. In this state (twisting angle of "b1 to b2" in FIG. 7), both the second hysteresis torque H2 and the third hysteresis torque H3 are generated.

Then, when one of the pair of second internal teeth 18b (the second internal tooth 18b between the end of the fourth spring 25b and the third external tooth 27c) comes into contact with the third external tooth 27c, the spline hub 4 The rotation of the flange portion 11 stops. As a result, the rotation of the flange portion 11 with respect to the spline hub 4 in the second rotation direction R2 is stopped.

In this state, when the flange portion 11 rotates in the first rotation direction R1 with respect to the spline hub 4, an operation opposite to the above-described operation is performed in the order of FIGS. 6D and 6A, and the initial state is restored.

By configuring the clutch disc assembly 1 as described above, the damper disc assembly can be miniaturized in the axial direction, and hysteresis torque can be generated in multiple stages.

[Modification example]
In the modified example, the operation when the flange portion 11 rotates in the second rotation direction R2 with respect to the spline hub 4 from the state of FIG. 6C is different from the above-described embodiment.

The operation (FIG. 6A → FIG. 6C) when the flange portion 11 rotates in the first rotation direction R1 with respect to the spline hub 4 is the same as the operation of the above embodiment, and thus the description thereof will be omitted.

In the first modification, when the flange portion 11 rotates in the second rotation direction R2 with respect to the spline hub 4 in the state of FIG. 6C, the twist angle changes from “a2 → a1 ′” in FIG.

In this case, as shown in FIG. 8A, before one of the pair of second internal teeth 18b abuts on the end of the fourth spring 25b, the flange portion 11 together with the third hysteresis torque generating mechanism 63 spline hub. It starts to rotate in the second rotation direction R2 with respect to 4.

In FIG. 9, the twist angle at which both the flange portion 11 and the third hysteresis torque generating mechanism 63 start to rotate in the second rotation direction R2 with respect to the spline hub 4 is “a1 ′”. When the twist angle is "a2 → a1", the second hysteresis torque H2 and the third hysteresis torque H3 are generated as in the above embodiment.

Here, "one of the pair of second internal teeth 18b" is the second internal tooth 18b between the end of the fourth spring 25b and the second external tooth 27b in the circumferential direction. "Before one of the pair of second internal teeth 18b abuts on the end of the fourth spring 25b" means "one of the pair of second internal teeth 18b abuts on the end of the fourth spring 25b". There is no state.

In the above operation, before one of the pair of second internal teeth 18b abuts on the end of the fourth spring 25b, the extension force of the fourth spring 25b and the sliding resistance by the third hysteresis torque generation mechanism 63 are generated. , Occurs by balancing. Here, the extension force of the fourth spring 25b corresponds to the pressing force of the fourth spring 25b pressing the claw portion 51 provided on the wave spring 50.

Subsequently, from FIG. 8A to FIG. 8B, when the flange portion 11 and the third hysteresis torque generation mechanism 63 further rotate in the second rotation direction R2 with respect to the spline hub 4, the twist angle is “a2 → →” in FIG. It changes to "b0".

In this case, the other of the pair of claws 51 is held (sandwiched) by the ends of the third external tooth 27c and the fourth spring 25b. In this state, when the flange portion 11 further rotates in the second rotation direction R2 with respect to the spline hub 4, it is within the range K of the gap K between one of the pair of second internal teeth 18b and the end of the fourth spring 25b (FIG. The second hysteresis torque H2 and the third hysteresis torque H3 are generated at the twist angle of “b0 to b1” of 9.

In this state (twisting angle of "b0 to b1" in FIG. 9), the third spring 25a is operated and the fourth spring 25b is not operated, so that the first rigidity K1 is formed. Then, when the twist angle of FIG. 9 reaches "b1", one of the pair of second internal teeth 18b comes into contact with the end of the fourth spring 25b. Then, the fourth spring 25b is compressed between one of the pair of second internal teeth 18b and the fourth engaging portion 28d of the third outer tooth 27c. As a result, the second rigidity K2 is formed at the twist angle of "b1 to b2" in FIG.

In this state, the claw portion 51, that is, the wave spring 50 rotates integrally with the spline hub 4. As a result, the flange portion 11 and the second bush that rotates integrally with the flange portion 11 rotate relative to the spline hub 4 and the wave spring 50.

Then, the flange portion 11 (first contacted portion 19) slides with respect to the third contact portion 52a of the third friction member 52, and the second bush 43 (second contacted portion 43f) slides on the fourth friction member 53. Sliding with respect to the fourth contact portion 53a of the above (see FIGS. 4A and 4B). As a result, the third hysteresis torque H3 is generated. In this state (twisting angle of "b1 to b2" in FIG. 9 ), both the second hysteresis torque H2 and the third hysteresis torque H3 are generated.

Then, when the other of the pair of second internal teeth 18b comes into contact with the third external tooth 27c, the rotation of the flange portion 11 with respect to the spline hub 4 is stopped. As a result, the rotation of the flange portion 11 with respect to the spline hub 4 in the second rotation direction R2 is stopped.

In this state (torsion angle "b2 → b1" in FIG. 9), the flange portion 11 rotates in the first rotational direction R1 relative to the spline hub 4 and the other of the pair of second internal teeth 18b, the third outer It separates from the tooth 27c and comes into contact with the end of the fourth spring 25b. At this time, both the second hysteresis torque H2 and the third hysteresis torque H3 are generated.

Then, when the flange portion 11 further rotates in the first rotation direction R1 with respect to the spline hub 4, the fourth spring 25b is held by the pair of second internal teeth 18b and the pair of claw portions 51 (inactive state). ), The flange portion 11 and the third hysteresis torque generation mechanism 63 rotate in the first rotation direction R1 with respect to the spline hub 4. As a result, the initial state of FIG. 6A is restored. In this state (twist angle of "b1 → 0" in FIG. 9 ), only the second hysteresis torque H2 is generated.

<Other embodiments>
The specific configuration of the present invention is not limited to the above-described embodiment, and various modifications and modifications can be made without departing from the gist of the invention.

(A) In the above embodiment, an example is shown in which the high-rigidity spring unit 12 has two types of spring units, the first spring unit 23 and the second spring unit 24, but the high-rigidity spring unit 12 is the first. It may be composed of only one spring unit of 1 spring unit 23 and 2nd spring unit 24.

(B) In the above embodiment, an example is shown in which the first spring unit 23 and the second spring unit 24 are each composed of large and small springs 23a, 23b, 24a, 24b. Instead, each of the first spring unit 23 and the second spring unit 24 may be composed of only one spring, for example, the large springs 23a and 24a.

(C) In the above embodiment, the case where the spring seats are arranged at both ends of the third spring 25a and the fourth spring 25b is shown, but the spring seats may not be used.

(D) In the above-described embodiment, the arrangement relationship of each configuration has been described with reference to FIG. 2B when the high-rigidity damper unit 2 (clutch disc assembly 1) is not operating, but the high-rigidity damper unit 2 (clutch) Even when the disk assembly 1) is in operation, the arrangement relationship of each configuration is established.

1 clutch disk assembly 10 input-side member 11 flange portion 12 rigid spring unit 16 the pin member 23 first spring unit 23a first large spring 24 second spring unit 24a second large sprint grayed
L1-L4 line segment

Claims (2)

The first and second rotating members, which are arranged at intervals in the axial direction,
A connecting member which is integrally rotatably connected to the first and second rotating members and has a cross section whose circumferential length is longer than the radial length.
A third rotating member arranged between the first and second rotating members in the axial direction and rotatable with respect to the first and second rotating members,
An elastic portion that elastically connects the first and second rotating members and the third rotating member,
With
The elastic portion has a first elastic member arranged radially inside the connecting member and a second elastic member operating in parallel with the first elastic member.
A first line segment connecting the outermost point where a straight line extending in the radial direction from the center of rotation toward the central portion in the circumferential direction of the second elastic member passes through the outermost portion of the second elastic member and the center of rotation. A straight line extending in the radial direction from the rotation axis toward the central portion in the circumferential direction of the first elastic member connects the outermost point passing through the outermost portion of the first elastic member and the rotation axis. The ratio of the second line segment is 0.85 or more and less than 1.0 .
The ratio of the outer diameter of the first elastic member to the outer diameter of the second elastic member is 0.75 or more and less than 1.0.
Damper disk assembly. The third rotating member has a first storage window for storing the first elastic member and a second storage window for storing the second elastic member.
The ratio of the fourth line segment connecting the rotation axis and the outermost peripheral portion of the first storage window to the third line segment connecting the rotation axis and the outermost peripheral portion of the second storage window is 0. 85 or more and less than 1.0,
The damper disk assembly according to claim 1 .

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