JP2018150957A - Damper disc assembly - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a damper disc assembly that can increase allowable torque.SOLUTION: A damper disc assembly includes: a clutch disc assembly 1, a clutch plate 13 and a retaining plate 14; a pin member 16; a flange part 11; and a high-rigidity spring unit 12. The high-rigidity spring unit 12 includes a first spring unit 23 and a second spring unit 24. The pin member 16 has a cross section of which circumferential length is longer than the radial length thereof, where a ratio of a second line segment connecting between an outermost point and a rotation axis of a first elastic member in a radial direction to a first line segment connecting between an outermost point and a rotation axis of a second elastic member in the radial direction is 0.85 or more and 1.0 or less.SELECTED DRAWING: Figure 2B

Description

  The present invention relates to a damper disk assembly.

  In a conventional damper disk assembly, for example, a damper disk assembly disclosed in Patent Document 1, a clutch plate and a retaining plate (first and second rotating members) are provided 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 first and second elastic members (30, 31). Here, the second elastic member (31) is arranged on the radially inner side of the stop pin.

JP 2009-19746 A

  In the conventional damper disk assembly, the stop pin has a circular cross section. Further, the second elastic member (31; corresponding to the first elastic member) is arranged on the radially inner side of the stop pin having a circular cross section. For this reason, it is difficult to arrange the second elastic member on the radially outer side. Thereby, it was difficult to improve the torque borne by the second elastic member. That is, it is 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) A damper disk 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 spaced apart from each other in the axial direction. The connecting member connects the first and second rotating members so as to be integrally rotatable. The connecting member has a cross section in which the circumferential length is longer than the radial length. The third rotating member is disposed 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 part includes a first elastic member disposed radially inward of the connecting member and a second elastic member that operates in parallel with the first elastic member. Here, the ratio of the second line segment connecting the outermost point of the first elastic member and the rotation axis in the radial direction to the first line segment connecting the outermost point of the second elastic member and the rotation axis in the radial direction is 0.85 or more and 1.0 or less.

  In this damper disk assembly, the connecting member has a cross section in which the circumferential length is longer than the radial length. A first elastic member is disposed inside the connecting member having the 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.

  In this way, by configuring the damper disk assembly, the first elastic member can be arranged on the radially outer side as compared with the prior art. Thereby, the torque (allowable torque of the first elastic member) borne by 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 another 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.

  By comprising in this way, the allowable torque of a 1st elastic member can be improved suitably. That is, the allowable torque of the damper disk assembly can be preferably improved.

  (3) In the damper disk 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 periphery of the first storage window to the third line segment connecting the rotation axis and the outermost periphery of the second storage window is 0.85. Above and below 1.0.

  In this structure, the 1st elastic member arrange | positioned at the 1st accommodation window can be operated on the radial direction outer side compared with a 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 another 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 in 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.

1 is a cross-sectional view of a clutch disk assembly according to an embodiment of the present invention. The front view of FIG. The front view of FIG. 1 for demonstrating arrangement | positioning of a highly rigid damper unit. The front view of a low-rigidity damper unit. The partial expanded sectional view of the 1st to 3rd hysteresis torque generation mechanism. The partial expanded sectional view of the 1st to 3rd hysteresis torque generation mechanism. The front view of a biasing member. The schematic diagram for demonstrating the formation form of a biasing member (figure seen from radial direction outer side). The schematic diagram for demonstrating the formation form of a biasing member (figure seen from radial direction outer side). The front view of the low-rigidity damper unit for demonstrating operation | movement of the 2nd and 3rd hysteresis torque generation mechanism. The front view of the low-rigidity damper unit for demonstrating operation | movement of the 2nd and 3rd hysteresis torque generation mechanism. The front view of the low-rigidity damper unit for demonstrating operation | movement of the 2nd and 3rd hysteresis torque generation mechanism. The front view of the low-rigidity damper unit for demonstrating operation | movement of the 2nd and 3rd hysteresis torque generation mechanism. FIG. 6 is a torsional characteristic diagram of a low-rigidity damper unit and a hysteresis torque generating mechanism. The front view of the low-rigidity damper unit for demonstrating operation | movement of the 2nd and 3rd hysteresis torque generation mechanism in the modification 1. The front view of the low-rigidity damper unit for demonstrating operation | movement of the 2nd and 3rd hysteresis torque generation mechanism in the modification 1. FIG. 11 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 disk assembly 1 having a damper disk assembly according to an embodiment of the present invention.

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

  In FIG. 1, OO is a rotation axis of the clutch disk assembly 1, that is, a rotation center line. Hereinafter, a direction away from the rotation axis O is referred to as a radial direction, and a direction along the rotation axis is referred to as an axial direction. Further, hereinafter, 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 arranged on the left side of FIG. 1, and a transmission (not shown) is arranged on the right side of FIG. R1 in FIG. 2 is the rotational drive direction (first rotational direction) of the clutch disk assembly 1, and R2 is the opposite direction (second rotational direction).

  The clutch disk assembly 1 transmits torque input from the engine to the transmission side. The clutch disk assembly 1 mainly includes a high-rigidity damper unit 2, a low-rigidity damper unit 3, a spline hub 4, and a hysteresis torque generating 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 a damper unit that operates during traveling, for example. 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 first and second rotating members), a pin member 16 (an example of a connecting member), and a flange portion 11 (a third rotating member). 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 disk 15. Have.

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

  Four window holes 13a, 14a are formed at equal intervals in the rotation direction on the outer peripheral portions of the clutch plate 13 and the retaining plate 14, respectively. A high-rigidity spring unit 12 is disposed in each of the window holes 13a and 14a. Both end portions 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. In each of the window holes 13a and 14a, raised portions are formed 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 14 b are for supporting the hysteresis torque generating mechanism 5. A first protrusion 45 of the first bush 40 in the hysteresis torque generating mechanism 5 described later is inserted into each support hole 14b.

  The clutch disc 15 is a portion that is pressed against a flywheel (not shown). The clutch disk 15 is composed of a cushioning plate 15a and friction facings 15b fixed to both surfaces of the cushioning plate 15a. Since the clutch disk 15 is the same as the conventional configuration, a detailed description of the clutch disk 15 is omitted.

-Pin member-
The pin member 16 connects the clutch plate 13 and the retaining plate 14 so as to be integrally rotatable. For example, as shown in FIGS. 1 and 2A, the plurality of pin members 16 are inserted into a plurality of (for example, four) long holes 13b and 14c formed in the clutch plate 13 and the retaining plate 14, respectively. The And it fixes to the clutch plate 13 and the retaining plate 14 by crimping the both ends of each pin member 16. FIG.

  Each pin member 16 is arrange | positioned between the spring accommodating parts 20 adjacent to 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 contact each stopper portion 22 of the flange portion 11.

  Each pin member 16 is a member having the following cross section and long in the axial direction. As shown in FIG. 2A, each pin member 16 has a cross section in which the circumferential length is longer than the 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 long in the circumferential direction. More specifically, the cross section of each pin member 16 is formed in a rectangular shape so as to be long in a direction perpendicular to the radial direction.

  The ratio of the length in the orthogonal direction of the pin member 16 to the length in the radial direction of the pin member 16 is, for example, 0.13 or more and 0.2 or less. In the present 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 disposed on the radially 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 disposed between the axial direction of the clutch plate 13 and the retaining plate 14. 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 (for example, four) spring accommodating portions 20, and a plurality (for example, four). ) Recesses 21 and a plurality of stopper portions 22.

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

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

  Each pair of second internal teeth 18b protrudes radially inward from the first hole portion 17. Each of the pair of second internal teeth 18b is provided at an interval in the circumferential direction. Each pair of second internal teeth 18b is disposed between the second external teeth 27b and the third external teeth 27c of the spline hub 4 in the circumferential direction. One of the pair of second internal teeth 18b is arranged to face the second external teeth 27b in the first rotation direction R1. The other of the second inner teeth 18b of each pair is disposed to face the third outer teeth 27c in the second rotation direction R2. A second spring of the low-rigidity spring unit 25 is disposed between the circumferential directions of each pair of second internal teeth 18b.

  Each third internal tooth 18 c protrudes radially inward from the first hole portion 17. Each third internal tooth 18c is provided between the first internal teeth 18a and the second internal teeth 18b adjacent in the circumferential direction in the circumferential direction. Each third internal tooth 18c is disposed between the third external teeth 27c of the spline hub 4 and the circumferential direction of the first external teeth 27a. That is, each third internal tooth 18c is disposed to face the third external tooth 27c in the first rotational direction R1, and is disposed to face the first external tooth 27a in the second rotational direction R2.

  The first contacted portion 19 is a portion that is in 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 radially outer side of the first hole portion 17. Specifically, the contacted portion is provided on the side surface on the second bush 43 (described later) side between the first hole portion 17 and the spring accommodating portion 20 in the radial direction.

  A fourth friction member 53 (described later) of the third hysteresis torque generating mechanism 63 contacts 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 generating 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 part 11 further has a plurality of (for example, four) openings 20a.

  Each of the plurality of openings 20 a is formed in each spring accommodating portion 20. As shown in FIG. 1, each opening 20 a is disposed to face each of the window holes 13 a and 14 a of the clutch plate 13 and the retaining plate 14 in the axial direction. The high-rigidity spring unit 12 is disposed in each opening 20a. Both end portions of the high-rigidity spring unit 12 are in contact with the wall portions facing each other in the circumferential direction in 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 (for example, two) second openings 20a2 (an example of a first storage window). have.

  The first opening 20 a 1 is for housing the first spring unit 23 of the high-rigidity spring unit 12. Each first opening 20a1 has a shaft relative to each window hole 13a of the clutch plate 13 in which the first spring unit 23 is disposed and each window hole 14a in the retaining plate 14 in which the first spring unit 23 is disposed. It is arranged to face the direction.

  Each first opening 20a1 is disposed adjacent to each second opening 20a2 in the circumferential direction. Each first opening 20a1 is disposed 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 relative to each of the window holes 13a of the clutch plate 13 in which the second spring unit 24 is disposed and each of the window holes 14a of the retaining plate 14 in which the second spring unit 24 is disposed. It is arranged to face the direction.

  Each second opening 20a2 is disposed adjacent to each first opening 20a1 in the circumferential direction. Each 2nd opening 20a2 is arrange | positioned between the 1st opening 20a1 adjacent to the circumferential direction. That is, the first openings 20a1 and the second openings 20a2 are alternately arranged in the circumferential direction.

  As shown in FIGS. 4A and 4B, a second protrusion 43 c (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 concave portion 21 is formed in a concave shape toward the rotation axis O at the circumferential central portion at 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 that fixes the clutch plate 13 and the retaining plate 14 can contact each stopper portion 22. For example, the rotation of the clutch plate 13 and the retaining plate 14 relative to the flange portion 11 is restricted by the contact of 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 rotation direction. Specifically, the plurality of high-rigidity spring units 12 elastically connect the clutch plate 13 and the retaining plate 14 to the flange portion 11 in the rotational direction.

  As shown in FIGS. 1 and 2, specifically, the high-rigidity spring unit 12 includes 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 a first elastic member).

  As shown in FIG. 2, the first spring units 23 and the second spring units 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 accommodated in each opening 20 a of the flange portion 11. Further, the movements in the radial direction and the axial direction are restricted by the window holes 13 a and 14 a 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 includes 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 disposed 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 end portions of the first large spring 23 a and both end portions of the first small spring 23 b are in contact with the wall portions facing each other in the circumferential direction in each opening 20 a of the flange portion 11. Both end portions of the first large spring 23a and both end portions of the first small spring 23b are 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, respectively. .

  The second spring unit 24 includes a second large spring 24a and a second small spring 24b. The second large spring 24a is formed with a larger diameter than the second small spring 24b. The second small spring 24b is disposed 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 end portions of the second large spring 24 a and both end portions of the second small spring 24 b are in contact with the wall portions facing each other in the circumferential direction in the respective openings 20 a of the flange portion 11. Both end portions of the second large spring 24a and both end portions of the second small spring 24b are in contact with the wall portions facing each other in the circumferential direction in the window holes 13a, 14a of the clutch plate 13 and the retaining plate 14, respectively. .

  As shown in FIG. 2A, the second spring unit 24 is disposed radially inward from 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 the present 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 and the retaining plate 14 to the flange portion 11 in the rotational direction.

  In the high-rigidity damper unit 2 having the above-described 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. 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 of the first spring unit 23 and the rotation axis O 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 at the circumferential central portion of the second spring unit 24 (second large spring 24a) with respect to the first line segment L1 at the circumferential central portion of the first spring unit 23 (first large spring 23a). The ratio of the minute L2 is 0.85 or more and 1.0 or less. In the present embodiment, the above ratio is set to 0.9.

  Here, the first line segment L1 is defined on a plane perpendicular to the rotation axis O and passing through the first outermost point E1. The second line segment L2 is defined on a plane perpendicular to the rotation axis O and passing 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 central portion in the circumferential direction 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 axis J1 of the first spring unit 23.

  The central portion in the circumferential direction 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 central portion in the circumferential direction 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 axis 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 shaft 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 middle point C2 on the operating shaft of the second spring unit 24.

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

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

  Thus, by comprising the highly rigid damper unit 2, the 2nd spring unit 24 can be arrange | positioned on a radial direction outer side compared with a prior art. Thereby, 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 disk assembly 1 can be improved.

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

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

  The low rigidity damper unit 3 includes a flange portion 11, a low rigidity spring unit 25, and a spline hub 4. Since the structure of the flange part 11 was demonstrated in the high-rigidity damper unit 2 mentioned above, description is abbreviate | 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 rotation direction. The low rigidity spring unit 25 has lower rigidity than the high rigidity spring unit 12. As shown in FIG. 1, the low-rigidity spring unit 25 is disposed 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 (for example, two) of third springs 25a and a plurality (for example, two) of fourth springs 25b. The third springs 25a and the fourth springs 25b are alternately arranged at intervals in the circumferential direction.

  The third spring 25a is disposed between the first outer teeth 27a and the second outer teeth 27b adjacent to each other in the circumferential direction. Specifically, both end portions of the third spring 25a are engaged with the respective pairs of first internal teeth 18a. Here, a spring seat is disposed at each of both ends of the third spring 25a, and both ends of the third spring 25a engage with each pair of first internal teeth 18a via the spring seat. .

  Hereinafter, 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.

  In addition, both end portions of the third spring 25a are respectively divided into a first engagement portion 28a (described later) of the first external tooth 27a and a second engagement portion 28b (described later) of the second external tooth 27b. Engage. Here, both ends of the third spring 25a are connected to a first engagement portion 28a of the first external tooth 27a and a second engagement portion 28b (described later) of the second external 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 connected to the first engaging portion 28a. The second engaging portion 28b and the pair of first internal teeth 18a are in contact with each other.

  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 disposed between the second outer teeth 27b and the third outer teeth 27c adjacent to each other in the circumferential direction and disposed between the second inner teeth 18b of each pair. Specifically, both end portions of the fourth spring 25b are engaged with the respective pairs of second internal teeth 18b. Here, a spring seat is disposed at each of both ends of the fourth spring 25b, and both ends of the fourth spring 25b engage with each pair of second internal teeth 18b via the spring seat. .

  Hereinafter, 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.

  In addition, both end portions of the fourth spring 25b are respectively divided into a third engagement portion 28c (described later) of the second external tooth 27b and a fourth engagement portion 28d (described later) of the third external tooth 27c. Engage. Here, both end portions of the fourth spring 25b are individually engaged with the third engagement portion 28c of the second external tooth 27b and the fourth engagement portion 28d of the third external tooth 27c via the spring seat. Match.

  Further, both end portions of the fourth spring 25b engage with a pair of claw portions 51 (described later) adjacent to each other in the circumferential direction. Here, both end portions of the fourth spring 25b engage with a pair of claw portions 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 generating 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 claws 51 via the spring seat. , Each abut.

  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 engagement portion 28c. Furthermore, 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 part 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 protrudes radially outward from the cylindrical portion 26. The external tooth portion 27 includes 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. In the second rotation direction R2, the external tooth portion 27 is disposed at intervals in the order of the first external tooth 27a, the second external tooth 27b, and the third external tooth 27c.

  Each pair of first internal teeth 18a is disposed between the circumferential directions of the first external teeth 27a and the second external teeth 27b. The third spring 25a of the low-rigidity spring unit 25 is disposed between the circumferential directions of the first external teeth 27a and the second external teeth 27b.

  Each pair of second internal teeth 18b is disposed between the circumferential directions of the second external teeth 27b and the third external teeth 27c. A fourth spring 25b of the low-rigidity spring unit 25 is disposed between the circumferential directions of the second external teeth 27b and the third external teeth 27c. Between the circumferential direction of the 3rd external tooth 27c and the 1st external tooth 27a, the 3rd internal tooth 18c is arrange | positioned.

  In the initial state described above, as shown in FIG. 6A, the third gap S3 is provided between the circumferential directions of the first internal teeth 18a and the second external teeth 27b. A fourth gap S4 is provided between the second inner teeth 18b and the second outer teeth 27b in the circumferential direction.

  In the initial state described above, the fifth gap S5 is provided between the second inner teeth 18b and the third outer teeth 27c in the circumferential direction. A sixth gap S6 is provided between the third inner teeth 18c and the third outer teeth 27c in the circumferential direction.

  In the initial state described above, the seventh gap S7 is provided between the third inner teeth 18c and the first outer teeth 27a in the circumferential direction. In addition, an eighth gap S8 is provided between the first outer teeth 27a and the first inner teeth 18a in the circumferential direction.

  As shown in FIG. 6A, the first external teeth 27a protrude from the cylindrical portion 26 to the outside in the radial direction. The first external teeth 27a are provided between the third external teeth 27c and the second external teeth 27b in the circumferential direction. A first engagement portion 28a is provided on the first external tooth 27a. For example, the first engagement portion 28a is provided at the end portion on the second rotation direction R2 side of the first external tooth 27a. The first engagement portion 28a engages with the end portion of the third spring 25a.

  The second external teeth 27b protrude outward in the radial direction from the cylindrical portion 26. The second external teeth 27b are provided between the first external teeth 27a and the third external teeth 27c in the circumferential direction. A second engagement portion 28b and a third engagement portion 28c are provided on the second external tooth 27b.

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

  The third external teeth 27c protrude from the cylindrical portion 26 to the outside in the radial direction. The third external teeth 27c are provided between the second external teeth 27b and the first external teeth 27a in the circumferential direction. A fourth engagement portion 28d is provided on the third external tooth 27c. For example, the fourth engagement 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.

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

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

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

  The first bush 40 is disposed between the retaining plate 14 and the flange portion 11 in the axial direction. The first bush 40 is biased from the retaining plate 14 toward the flange portion 11 by the first biasing 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 1st protrusion part 45 is provided in the outer peripheral part of the 1st bush 40 at intervals in the circumferential direction. Each first protrusion 45 is inserted through each support hole 14 b of the retaining plate 14. Accordingly, the first bush 40 is configured to be movable in the axial direction with respect to the retaining plate 14 and to be rotatable integrally with the retaining plate 14.

  The first friction member 41 is substantially annular. The first friction member 41 is disposed between the first bush 40 and the flange portion 11 in the axial direction. The first friction member 41 is attached to the first bush 40 so as to be rotatable integrally 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 formed with the first bush 40 made of resin by injection molding.

  The first friction member 41 contacts 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 while being in contact with the flange portion 11. Thereby, the first hysteresis torque is generated.

  The first urging member 42 is disposed between the first bush 40 and the retaining plate 14 in the axial direction. The first biasing member 42 biases 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 disposed between the clutch plate 13 and the flange portion 11 in the axial direction. The second bush 43 is biased toward the clutch plate 13 by the first biasing member 42 through 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 2nd protrusion part 43c is provided in the outer peripheral part of the 2nd bush 43 at intervals in the circumferential direction. Each 2nd protrusion part 43c is arrange | positioned at each recessed part 21 (refer FIG. 3) of the flange part 11. As shown in FIG. Thereby, the 2nd bush 43 is comprised so that integral rotation with respect to the flange part 11 is possible. The second bush 43 is also a member constituting a second hysteresis torque generating mechanism 62 described later.

  The second friction member 44 is formed in a substantially annular shape. The second friction member 44 is disposed between the second bush 43 and the clutch plate 13 in the axial direction. The second friction member 44 is attached to the second bush 43 so as to rotate together 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 formed with the first bush 40 made of resin by injection molding.

  The second friction member 44 contacts 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 while being in contact with the clutch plate 13. Thereby, the first hysteresis torque is generated.

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

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

  The second hysteresis torque generating mechanism 62 has the second bush 43, the third bush 46, and the second urging member 47 described above.

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

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

  Each of the plurality of second protrusions 43c protrudes in the axial direction from the outer cylinder part 43b. As described above, each second protrusion 43c is disposed in each recess 21 of the flange portion 11 as described above. Thereby, the 2nd bush 43 is comprised so that integral rotation with respect to the flange part 11 is possible.

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

  The first contact portion 43 e is a portion that contacts the spline hub 4. The 1st contact part 43e is provided in the inner peripheral part of the main-body part 43a. Specifically, the first contact portion 43e is provided on the side surface on the flange portion 11 side in the inner peripheral portion of the main body portion 43a.

  The first contact portion 43 e contacts the external tooth portion 27 of the spline hub 4. Specifically, the first contact portion 43 e 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 43 e slides with respect to the base end portion of the external tooth portion 27 in a state where the first contact portion 43 e is in contact with the base end portion of the external tooth portion 27. . Thereby, the second hysteresis torque is generated.

  The second contacted portion 43 f is a portion that is in contact with the third hysteresis torque generating mechanism 63. The second contacted portion 43f is provided on the radially outer side of the first contact portion 43e. Specifically, the second contacted portion 43f is provided on the side surface on the flange portion 11 side in the outer peripheral portion of the main body portion 43a. 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.

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

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

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

  The second urging member 47 is disposed between the third bushing 46 and the retaining plate 14 in the axial direction. The second urging member 47 urges the third bushing 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 generating mechanism 63 is, for example, a hysteresis torque generating mechanism that operates during idling.

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

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

  The third hysteresis torque generating mechanism 63 is configured to be rotatable with respect to the flange portion 11. The third hysteresis torque generating mechanism 63 is configured to be slidable with respect to the flange portion 11. Further, the third hysteresis torque generating 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 generating 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 disposed between the flange portion 11 and the second bush 43 in the axial direction. The wave spring 50 is disposed at a distance from the flange portion 11 in the axial direction. The wave spring 50 is disposed at a distance from the second bush 43 in the axial direction.

  The wave spring 50 is disposed 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 tube portion 43 b 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. Accordingly, 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 25 b of the low-rigidity spring unit 25. Specifically, each pawl 51 is held in the circumferential direction by the fourth spring 25b by contacting the end 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 with a spacing 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 in the axial direction from the first portion 51a. The first portion 51 a is disposed between the second bush 43 and the flange portion 11 in the axial direction.

  The second portion 51b extends from the distal end portion of the first portion 51a toward the retaining plate 14. The second portion 51 b is disposed on the inner peripheral side of the flange portion 11. Specifically, the second portion 51 b is disposed on the inner peripheral side of the second inner tooth 18 b of the flange portion 11. Further, the second portion 51b can contact the end of the fourth spring 25b. When the second portion 51b contacts the end 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 in a substantially annular shape. The third friction member 52 is disposed between the flange portion 11 and the wave spring 50 in the axial direction. The third friction member 52 is biased toward the flange portion 11 by the wave spring 50.

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

  The fourth friction member 53 is substantially annular. The fourth friction member 53 is disposed between the second bush 43 and the wave spring 50 in the axial direction. The fourth friction member 53 is biased toward the second bush 43 by the wave spring 50.

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

  In the third hysteresis torque generating mechanism 63 having the above configuration, the third contact portion 52 a of the third friction member 52 contacts the flange portion 11 (first contacted portion 19), and the fourth contact of the fourth friction member 53. The part 53a contacts the second bush 43 (second contacted part 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 are moved relative to the flange portion 11 and the second bush 43. Slide separately. As a result, a third hysteresis torque is generated.

[Operation of clutch disk assembly]
Here, the operation of the clutch disk assembly 1 will be described. In the clutch disk assembly 1, when torque is input to the input side member 10 (the clutch plate 13 and the retaining plate 14), the input side member 10 starts to rotate 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. In a state where the input side member 10 has started rotating, the high-rigidity spring unit 12 is substantially inoperative, and therefore the flange portion 11 rotates integrally with the input side member 10. For this reason, the first hysteresis torque generating mechanism 61 is substantially inoperative.

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

  When the relative rotation between the flange portion 11 and the spline hub 4 is further increased, the flange portion 11 is relatively moved 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 generating mechanism 63 further operates. 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 is further increased, 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 is impossible. Thereby, the flange part 11 and the spline hub 4 rotate integrally. Then, the second hysteresis torque generating mechanism 62 and the third hysteresis torque generating 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 rotated, the input side member 10 is moved relative to the flange portion 11 (spline hub 4). Rotate relatively. Then, the first hysteresis torque generating mechanism 61 is activated. Thereby, the first hysteresis torque is generated.

[Operation of Second and Third 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 are rotated relative to each other when the first hysteresis torque generating mechanism 61 is not operated. .

  The second hysteresis torque generating mechanism 62 generates a second hysteresis torque during the operation of the third spring 25a of the low-rigidity damper unit 3. The third hysteresis torque generating 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, first, when the flange portion 11 is rotated in the first rotation direction R1 from the initial state of FIG. 6A with respect to the spline hub 4, the third spring 25a is moved to the first inner teeth 18a and the first outer teeth 27a. Compressed by one engaging portion 28a. In this state, the third spring 25a operates and the fourth spring 25b does not operate. Thereby, the first rigidity K1 is formed at the twist angle of “0 to a1” in FIG.

  Here, the 4th spring 25b is rotating with respect to the spline hub 4 with the flange part 11 and the 3rd hysteresis torque generation mechanism 63 in the non-operation state. Specifically, the fourth spring 25b rotates with respect to the spline hub 4 in a state where it is disposed 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 proximal end portion of the external tooth portion 27 of the spline hub 4 (FIG. 4A and FIG. (See FIG. 4B). As a result, the second hysteresis torque H2 is generated at a twist angle of “0 to a1” in FIG.

  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 simultaneously with the third spring 25a operating.

  In this case, in a state where one of the pair of claws 51 is held (clamped) by the second external teeth 27b and the end of the fourth spring 25b, the fourth spring 25b is one of the pair of second internal teeth 18b. Compression is performed by the second internal teeth 18b between the end of the fourth spring 25b and the third external teeth 27c and the third engaging portion 28c of the second external teeth 27b. Accordingly, 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 (clamped) by the end portions of the second external teeth 27b and the fourth spring 25b, so that the wave spring 50 rotates integrally with the spline hub 4. Accordingly, 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) becomes the fourth friction member 53. It slides with respect to the fourth contact portion 53a (see FIGS. 4A and 4B). Thereby, the third hysteresis torque H3 is generated. In this state (the torsion angles “a1 to a2” in FIG. 7), both the second hysteresis torque H2 and the third hysteresis torque H3 are generated.

  As shown in FIG. 6C, the other of the pair of second internal teeth 18b (the second internal teeth 18b between the end of the fourth spring 25b and the second external teeth 27b) hits the second external teeth 27b. When contacting, the rotation of the flange portion 11 with respect to the spline hub 4 stops. Thereby, the rotation of the flange portion 11 with respect to the spline hub 4 in the first rotation direction R1 stops.

  In this state, when the flange portion 11 rotates in the second rotational direction R2 with respect to the spline hub 4, 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 becomes the second of the first inner teeth 18a and the second outer teeth 27b. It is compressed by the engaging portion 28b. In this state, the third spring 25a operates and the fourth spring 25b does not operate. Thereby, the first rigidity K1 is formed at the twist angle of “0 to b1” in FIG.

  Here, the 4th spring 25b is rotating with respect to the spline hub 4 with the flange part 11 and the 3rd hysteresis torque generation mechanism 63 in the non-operation state. Specifically, the fourth spring 25b rotates with respect to the spline hub 4 in a state where it is disposed 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 proximal end portion of the external tooth portion 27 of the spline hub 4 (FIG. 4A and FIG. (See FIG. 4B). As a result, the second hysteresis torque H2 is generated at a twist angle of “0 to b1” in FIG.

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

  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 claw portions 51 is held (clamped) by the third external teeth 27c and the end of the fourth spring 25b. And the fourth engaging portion 28d of the third external 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 (clamped) by the end portions of the third external teeth 27c and the fourth spring 25b, so that the wave spring 50 rotates integrally with the spline hub 4. Accordingly, 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) becomes the fourth friction member 53. It slides with respect to the fourth contact portion 53a (see FIGS. 4A and 4B). Thereby, the third hysteresis torque H3 is generated. In this state (twist angle of “b1 to b2” in FIG. 7), both the second hysteresis torque H2 and the third hysteresis torque H3 are generated.

  When one of the pair of second internal teeth 18b (the second internal teeth 18b between the end of the fourth spring 25b and the third external teeth 27c) comes into contact with the third external teeth 27c, the spline hub 4 is The rotation of the flange portion 11 stops. Thereby, the rotation to the 2nd rotation direction R2 of the flange part 11 with respect to the spline hub 4 stops.

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

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

[Modification]
In the modification, 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.

  Since 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, the description thereof is 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 comes into contact with the end of the fourth spring 25b, the flange portion 11 together with the third hysteresis torque generating mechanism 63 is spline hub. 4 starts to rotate in the second rotation direction R2.

  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 between “a2 → a1”, the first hysteresis torque H1 and the second hysteresis torque H2 are generated as in the above-described embodiment.

  Here, “one of the pair of second inner teeth 18 b” is the second inner teeth 18 b between the ends of the fourth spring 25 b and the second outer teeth 27 b in the circumferential direction. "Before one of the pair of second internal teeth 18b contacts the end of the fourth spring 25b" means "one of the pair of second internal teeth 18b contacts the end of the fourth spring 25b" No state ".

  In the above operation, before one of the pair of second internal teeth 18b comes into contact with the end of the fourth spring 25b, the extension force of the fourth spring 25b and the sliding resistance by the third hysteresis torque generating mechanism 63 are reduced. It is generated by balancing. Here, the extension force of the fourth spring 25 b corresponds to the pressing force with which the fourth spring 25 b presses the claw portion 51 provided on the wave spring 50.

  8A to 8B, when the flange portion 11 and the third hysteresis torque generating mechanism 63 further rotate in the second rotational direction R2 with respect to the spline hub 4, the twist angle is “a2 → b0 ".

  In this case, the other of the pair of claw portions 51 is held (clamped) by the third external teeth 27c and the end portions of the fourth spring 25b. In this state, when the flange portion 11 further rotates in the second rotational direction R2 with respect to the spline hub 4, within the range of the gap K between one of the pair of second internal teeth 18b and the end portion of the fourth spring 25b (see FIG. 9), the second hysteresis torque H2 and the third hysteresis torque H3 are generated.

  In this state (the torsion angle “b0 to b1” in FIG. 9), the third spring 25a operates and the fourth spring 25b does not operate, so the first rigidity K1 is formed. When the twist angle in 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 inner teeth 18b and the fourth engagement portion 28d of the third outer teeth 27c. As a result, the second rigidity K2 is formed at the twist angle of “b1 to b2” in FIG. 9.

  In this state, the claw portion 51, that is, the wave spring 50 rotates integrally with the spline hub 4. Accordingly, 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) becomes the fourth friction member 53. It slides with respect to the fourth contact portion 53a (see FIGS. 4A and 4B). Thereby, the third hysteresis torque H3 is generated. In this state (twist 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 inner teeth 18b comes into contact with the third outer teeth 27c, the rotation of the flange portion 11 with respect to the spline hub 4 is stopped. Thereby, the rotation to the 2nd rotation direction R2 of the flange part 11 with respect to the spline hub 4 stops.

  In this state (the twist angle “b2 → b1” in FIG. 7), when the flange portion 11 rotates in the first rotation direction R1 with respect to the spline hub 4, one of the pair of second internal teeth 18b It separates from the teeth 27c and abuts against the end of the fourth spring 25b. At this time, both the second hysteresis torque H2 and the third hysteresis torque H3 are generated.

  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 (non-actuated state) ) Together with the flange portion 11 and the third hysteresis torque generating mechanism 63, the spline hub 4 rotates in the first rotation direction R1. As a result, the initial state of FIG. 6A is restored. In this state (the twist angle “b1 → 0” in FIG. 7), 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 changes and modifications can be made without departing from the scope of the invention.

  (A) In the above-described embodiment, an example in which the high-rigidity spring unit 12 has two types of spring units, that is, the first spring unit 23 and the second spring unit 24 has been described. You may be comprised only from any one spring unit of the 1 spring unit 23 and the 2nd spring unit 24. FIG.

  (B) In the above-described embodiment, an example in which each of the first spring unit 23 and the second spring unit 24 is configured by large and small springs 23a, 23b, 24a, and 24b has been described. Instead of this, 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-described embodiment, an example in which the spring seats are disposed at both ends of the third spring 25a and the fourth spring 25b has been described, but the spring seats may not be used.

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

DESCRIPTION OF SYMBOLS 1 Clutch disc assembly 10 Input side member 11 Flange part 12 High rigidity spring unit 16 Pin member 23 1st spring unit 23a 1st big spring 24 2nd spring unit 24a 2nd big spring G1-G3 Center of gravity L1-L5 Line segment

Claims (4)

First and second rotating members that are spaced apart from each other in the axial direction;
Connecting the first and second rotating members so as to be integrally rotatable, and a connecting member having a circumferential length longer than a radial length;
A third rotating member disposed between the first and second rotating members in an 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 includes a first elastic member disposed radially inward of the connecting member, and a second elastic member that operates in parallel with the first elastic member,
The ratio of the second line segment connecting the outermost point of the first elastic member and the rotation axis in the radial direction to the first line segment connecting the outermost point of the second elastic member and the rotation axis in the radial direction is: 0.85 or more and 1.0 or less,
Damper disk assembly. 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.
The damper disk assembly according to claim 1. 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 connecting the rotation axis and the outermost periphery of the first storage window to the third line connecting the rotation axis and the outermost periphery of the second storage window is 0. 85 or more and 1.0 or less,
The damper disk assembly according to claim 1 or 2. The ratio of the outer diameter of the first elastic member to the outer diameter of the second elastic member is not less than 0.75 and not more than 1.0.
The damper disk assembly according to any one of claims 1 to 3.

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