JP6545972B2 - Damper disc assembly - Google Patents

Description

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

  A damper disk assembly used in a clutch disk assembly or the like has a pair of input plates, a hub flange disposed axially between the pair of input plates, and a pair of input plates and hub flanges. And a plurality of torsion springs elastically coupled in a direction.

  Further, Patent Document 1 discloses a clutch disk assembly provided with a pre-damper unit for damping torsional vibration in a range of small torque separately from the main damper unit. The pre-damper unit has a pair of input side plates to which torque is input from the main damper unit, and an output side plate disposed so as to be sandwiched between the plates. The pair of input plates are fixed to one another by rivets. The pair of input side plates and the output side plate are elastically connected by a torsion spring.

Unexamined-Japanese-Patent No. 2003-277891

  In the clutch disk assembly shown in Patent Document 1, a pre-damper is provided separately from the main damper unit.

  However, in the conventional pre-damper unit, the range of the twist angle is narrow, and the twist characteristic is one step. For this reason, it is not possible to effectively suppress the torsional vibration particularly at the time of idling. Moreover, in the conventional pre-damper unit, the space for the pre-damper unit is large, which is an obstacle in shortening the axial dimension in particular. For this reason, there is a problem that the possibility of interference with other members becomes high at the time of mounting on a vehicle, and the mounting property is lowered.

  An object of the present invention is to realize widening of the pre-damper unit and to shorten the axial dimension to improve vehicle mountability.

  Another object of the invention is to enable multistage characterization of the pre-damper unit.

  A damper disk assembly according to a first aspect of the present invention is for transmitting torque from an engine to an input shaft of a transmission, and includes a main damper unit and a pre-damper unit. The main damper unit has an input side member to which torque from the engine is input, and an output side member connected to the input shaft of the transmission, and the torsional vibration from the engine is attenuated and input to the input side member Torque is transmitted to the output side member. The pre-damper unit receives torque from the main damper unit, attenuates torsional vibration in a range where the torque is smaller than that of the main damper unit, and outputs the torque to the output side member. The pre-damper unit has a plurality of outer peripheral side elastic members, an output side plate, a plurality of inner peripheral side elastic members, and an intermediate plate. The plurality of outer peripheral elastic members engage with the input side member of the main damper unit, and torque is input from the input side member. The output side plate is connected to the output side member of the main damper unit. The plurality of inner peripheral elastic members are disposed on the inner peripheral side of the plurality of outer peripheral elastic members, engage with the output side plate, and transmit torque to the output side sub plate. The intermediate plate is disposed so as to be rotatable relative to the input side member and the output side plate of the main damper unit, and operates the plurality of outer peripheral elastic members and the plurality of inner peripheral elastic members in series.

  Here, the pre-damper unit includes an outer peripheral elastic member and an inner peripheral elastic member that operate in series. Therefore, the operating angle of the elastic member is increased, and widening of the pre-damper unit portion can be realized. In addition, since the plurality of outer peripheral elastic members of the pre-damper unit are engaged with the output-side plate of the main damper unit, the plate on the input side becomes unnecessary as compared with the conventional pre-damper unit, It can be shortened compared to the conventional device. This improves the mountability to a vehicle.

  The damper disk assembly according to the second aspect of the present invention is the damper disk assembly according to the first aspect, wherein the intermediate plate is provided with an outer peripheral storage portion for housing a plurality of outer peripheral elastic members, and a plurality of inner peripheral elastic members. And an inner peripheral side first storage section for storing the

  The outer peripheral side elastic member and the inner peripheral side elastic member are operated in series by the intermediate plate, and the outer peripheral side elastic member and the inner peripheral side elastic member are supported by the housing portion formed in the intermediate plate.

  The damper disk assembly according to the third aspect of the present invention is the damper disk assembly of the second aspect, wherein the output side plate is formed in a disk shape, and is formed on the inner peripheral portion and the outer peripheral portion of the output side member And an inner peripheral second storage portion for storing a plurality of inner peripheral elastic members together with an inner peripheral first storage portion of the intermediate plate.

  The damper disk assembly according to the fourth aspect of the present invention is the damper disk assembly according to any one of the first to third aspects, wherein the output side plate is restricted within a predetermined angular range relative to the intermediate plate. There is.

  Here, since relative rotation of the output side plate with respect to the intermediate plate is restricted within a predetermined angle range, multistage formation of the pre-damper unit can be realized.

  A damper disk assembly according to a fifth aspect of the present invention is the damper disk assembly according to the fourth aspect, wherein the intermediate member has an arc-shaped hole having a predetermined length in the rotational direction, and the output side plate is arc-shaped And a projection inserted through a predetermined gap in the hole of.

  As described above, according to the present invention, the wide angle of the pre-damper unit can be realized, and the axial dimension can be shortened to improve the vehicle mountability. Furthermore, in the present invention, multistage characterization of the pre-damper unit can be realized.

FIG. 2 is a cross-sectional view of a clutch disc assembly according to an embodiment of the present invention. The front view of a clutch disc assembly. The perspective view of a flange. FIG. 3 is an enlarged partial view of FIG. 2 showing the connection between the output hub and the flange. The figure which expands and shows a pre-damper unit. The figure which expands and shows the stopper mechanism part of a pre-damper unit.

  A clutch disk assembly 1 as one embodiment of the present invention is shown in FIG. The clutch disc assembly 1 is a device for transmitting and blocking torque from an engine (not shown) disposed on the left side of FIG. 1 to a transmission (not shown) disposed on the right side of FIG. . In FIG. 1, OO is the rotation axis of the clutch disk assembly 1.

[overall structure]
The clutch disc assembly 1 includes a plurality of clutch discs 2, a clutch plate 3 and a retaining plate 4 (input side members), first and second flanges 5 and 6, an output hub (output side member) 7, The torsion spring 8, the hysteresis torque generating mechanism 9, and the pre-damper unit 10 are provided.

[Clutch disc 2]
The clutch disc 2 is, as shown in FIGS. 1 and 2, an annular cushioning plate 12 having a plurality of mounting portions arranged in a circumferential direction, and an annular cushion fixed to both sides of the cushioning plate 12 by rivets 13. And friction facings 14. The inner periphery of the cushioning plate 12 is fixed to the outer periphery of the clutch plate 3 by rivets (not shown). Note that a flywheel (not shown) on the engine side is disposed on the left side of the friction facings 14 in FIG. 1 and torque on the engine side of the clutch disc assembly 1 is obtained by pressing the friction facings 14 against the flywheels. Is input.

[Clutch plate 3 and retaining plate 4]
The clutch plate 3 and the retaining plate 4 are formed in a disk shape, and are disposed to face each other in the axial direction across the first and second flanges 5 and 6. The two plates 3 and 4 are fixed by the stud pins 16 so as not to be relatively rotatable.

  As shown in FIGS. 1 and 2, the clutch plate 3 and the retaining plate 4 include four first storage portions 3a and 4a for storing the torsion spring 8 and four second storage portions. 3b and 4b are formed. The four first storage portions 3a, 4a are arranged at an interval of 90 °, and the second storage portions 3b, 4b are arranged between them. Each of the storage portions 3a, 3b, 4a and 4b is formed to expand axially outward (the clutch plate 3 is on the engine side and the retaining plate 4 is on the transmission side), and an opening is formed in the central portion There is.

[First and second flanges 5, 6]
The first and second flanges 5 and 6 are disposed so as to be sandwiched between the clutch plate 3 and the retaining plate 4. Both flanges 5 and 6 have the same shape, and the first flange 5 will be specifically described here.

  As shown in FIG. 3, the first flange 5 is a disk-like plate, and has four first openings 5 a and four second openings 5 b arranged in the circumferential direction. The first opening 5a is formed larger in the radial direction and the rotational direction than the second opening 5b. The first opening 5 a is formed at a position corresponding to the clutch plate 3 and the first storage portions 3 a and 4 a of the retaining plate 4. Further, the second opening 5 b is formed at a position corresponding to the clutch plate 3 and the second accommodation portions 3 b and 4 b of the retaining plate 4.

  The stud pins 16 axially pass through the inner peripheral portions of the first openings 5a, 6a of the flanges 5, 6 (see FIG. 2).

  Spring support portions (protrusions) 5c protruding in both axial directions are formed on one end surface of the four first openings 5a in the rotational direction. The spring support portion 5c has a substantially rectangular shape, and the end faces of the first coil spring 8a and the second torsion spring 8b among the plurality of torsion springs 8 are in contact with the spring support portion 5c. Further, the surface of the spring support 5c opposite to the surface receiving the torsion spring 8 abuts on one end surface of the clutch plate 3 and the first storage portions 3a and 4a of the retaining plate 4 in the rotational direction.

  With the above configuration, the spring support portion 5c of the first flange 5 is located between one end face of the torsion spring 8 and one end face of the clutch plate 3 and the first storage portions 3a and 4a of the retaining plate 4 It is pinched. Therefore, when the clutch plate 3 and the retaining plate 4 rotate in the + R direction of FIGS. 2 to 4, relative rotation of the first flange 5 with the clutch plate 3 and the retaining plate 4 is prohibited. It will rotate integrally with both plates 3 and 4. When the clutch plate 3 and the retaining plate 4 rotate in the -R direction, the first flange 5 is allowed to rotate relative to the clutch plate 3 and the retaining plate 4 within a predetermined angular range.

  Further, as shown in FIG. 4 which is an enlarged partial view of FIG. 3 and FIG. 2, a plurality of notches 5 d opening toward the inner peripheral side are formed in the inner peripheral portion of the first flange 5.

  As mentioned above, the second flange 6 has the same shape as the first flange 5. With respect to the second flange 6, the spring support portion 6c is held between the other end face of the torsion spring 8 and the other end faces of the clutch plate 3 and the first storage portions 3a and 4a of the retaining plate 4 ing. Therefore, when the clutch plate 3 and the retaining plate 4 rotate in the -R direction, relative rotation between the second flange 6 and the clutch plate 3 and the retaining plate 4 is prohibited, and both plates 3 and 4 are prevented. It will rotate with it. When the clutch plate 3 and the retaining plate 4 rotate in the + R direction, the second flange 5 is allowed to rotate relative to the clutch plate 3 and the retaining plate 4 within a predetermined angle range.

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

  As shown in FIGS. 2 and 4, the notches 5d and 6d in the inner peripheral portions of both the flanges 5 and 6 are assembled with their phases shifted in the rotational direction.

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

  Further, as shown in FIGS. 1, 2 and 4, a plurality of first teeth 7b are formed on the outer peripheral surface of the output hub 7, and further, a plurality of second teeth 7c are formed on the outer peripheral surface of the end portion on the transmission side. It is formed. Each of the plurality of first teeth 7b is inserted into the inside of the notches 5d, 6d of the both flanges 5, 6 via a predetermined gap.

  Specifically, as described above, the first and second flanges 5 and 6 are disposed out of phase with each other in the rotational direction. Therefore, as shown in FIG. 4, in the neutral state where no torque is input, a first gap G1 is formed between the first teeth 7b of the output hub 7 and the end face of the notch 5d of the first flange 5 in the rotational direction. Is formed, and a second gap G2 wider than the first gap G1 is formed between the first teeth 7b and the end surface of the notch 6d of the second flange 6 in the rotational direction.

[Torsion spring 8]
The torsion spring 8 has first to third coil springs 8a, 8b and 8c. The first coil spring 8 a and the second coil spring 8 b are disposed in the first openings 5 a and 6 a of the first and second flanges 5 and 6, and are formed by the clutch plate 3 and the first storage portions 3 a and 4 a of the retaining plate 4. It is supported. The second coil spring 8b is disposed on the inner peripheral portion of the first coil spring 8a. Further, the third coil spring 8c is disposed in the second openings 5b and 6b of the first and second flanges 5 and 6, and is supported by the clutch plate 3 and the second accommodation portions 3b and 4b of the retaining plate 4 .

[Hysteresis torque generation mechanism 9]
Hysteresis torque generation mechanism 9 is disposed between the clutch plate 3 and the first flange 5, between the first flange 5 and the second flange 6, and at the inner peripheral portion between the second flange 6 and the retaining plate 4. There is. Although detailed description of this mechanism 9 is omitted, a friction washer whose relative rotation beyond the predetermined angle range with the clutch plate 3 is prohibited, a friction plate abutted against the side surface of the first flange 5, and a friction plate It is comprised from the cone spring pressed to the side of 5.

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

  As shown in FIG. 5, a plurality of notches 4 c for storing a spring are formed on the transmission side of the retaining plate 4. The outer circumferential side pre-torsion spring 23 is accommodated in the plurality of notches 4 c, and the end face of the outer circumferential side pre-torsion spring 23 is engaged with the end face of the notch 4 c. Note that a part of the notch 4c on the engine side is open.

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

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

  The second storage portion 21 b is formed to expand toward the engine side, and stores and holds a part of the inner circumferential side pre-torsion spring 24. Further, the end face of the inner circumferential side pre-torsion spring 24 is engaged with the end face in the rotational direction of the second accommodation portion 21 b.

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

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

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

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

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

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

  Here, when the torsional vibration is small, only the inner peripheral side torsion spring 24 or the inner peripheral side torsion spring 24 and the outer peripheral side torsion spring 23 expand and contract. Then, when the torsional vibration further increases and the elastic deformation of the inner peripheral side torsion spring 24 increases, the engaging protrusion 22 d of the second sub plate 22 abuts on the end face of the arc-shaped hole 21 c of the first sub plate 21. Therefore, after that, only the outer peripheral side torsion spring 23 is further elastically deformed.

  By the operation as described above, in the pre-damper unit 10, it is possible to achieve widening of the torsional characteristics and two stages.

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

  In such a situation, when the clutch plate 3 and the retaining plate 4 rotate in the -R direction, the first flange 5 can rotate relative to the two plates 3 and 4, but the second flange 6 The relative rotation between both plates 3 and 4 is prohibited and they rotate integrally. Therefore, when both plates 3 and 4 rotate in the -R direction, torque is transmitted from both plates 3 and 4 to the pre-damper unit 10 and is also transmitted to the first flange 5 via the torsion spring 8 and further the output hub It is transmitted to 7.

  At this time, the output hub 7 and the first flange 5 relatively rotate by the twist angle corresponding to the gap G1 shown in FIG. 4 by the operation of the pre-damper unit 10 as described above. Then, when the first teeth 7 b of the output hub 7 abut on the end surface of the notch 5 d of the first flange 5 in the + R direction, the output hub 7 and the first flange 5 rotate integrally. After that, when the torsion spring 8 is elastically deformed and both plates 3 and 4 and the second flange 6 and the first flange 5 and the output hub 7 relatively rotate by an angle corresponding to the gap G2, One tooth 7b abuts on the + R direction end face of the notch 6d of the second flange 6, and their relative rotation is prohibited. That is, the end face of the notch 6d of the second flange 6 functions as a stopper.

  In addition, when the clutch plate 3 and the retaining plate 4 rotate in the + R direction, the relative rotation of the first flange 5 with the clutch plate 3 and the retaining plate 4 is prohibited contrary to the above. Becomes relatively rotatable. Therefore, when the pre-damper unit 10 operates and the first teeth 7b of the output hub 7 abut the end face of the notch 6d of the second flange 6 in the -R direction, the output hub 7 and the second flange 6 are integrated. To rotate. Thereafter, when the torsion spring 8 is elastically deformed and both plates 3 and 4 and the first flange 5 and the second flange 6 and the output hub 7 rotate relative to each other by an angle corresponding to the gap G2, One tooth 7b abuts on the end surface of notch 5d of fifth flange 5 in the + R direction, and their relative rotation is prohibited. That is, the end face of the notch 5d of the first flange 5 functions as a stopper.

[Feature]
(1) The pre-damper unit 10 has the outer peripheral side torsion spring 23 and the inner peripheral side torsion spring 24 which operate in series. Therefore, widening of the pre-damper unit 10 can be realized.

  (2) A part of the retaining plate 4 is made to function as the input side plate of the pre-damper unit 10. Therefore, the plate on the input side is not required compared to the conventional pre-damper unit, and the axial dimension can be shortened as compared with the conventional device.

  (3) The outer side torsion springs 23 and 24 are supported by the first sub plate 21 connecting the outer side torsion spring 23 and the inner side torsion spring 24. Therefore, the wide angle can be realized with a small number of parts.

  (4) The rotation angle range of the second sub plate 22 is regulated by the first sub plate 21. Therefore, two stages of torsional characteristics can be realized in the pre-damper unit 10.

  (5) A stopper mechanism is realized by the output hub 7 and the two flanges 5 and 6. Therefore, it is not necessary to provide a stopper mechanism including a stop pin at the flange outer peripheral portion as in the conventional device. Therefore, a large space for the torsion spring can be secured, and high torque and wide angle can be easily realized.

  (6) Since the end faces of the torsion spring 8 are supported by the spring support portions 5c, 6c formed on the flanges 5, 6, the flanges 5, 6 are rotated relative to the plates 3, 4 on the input side. The configuration for prohibiting can function as a spring seat.

  (7) Since the two flanges 5 and 6 have the same shape, the manufacturing cost can be reduced.

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

  (A) The configuration for restricting the relative rotation angle range of the first sub plate 21 and the second sub plate 22 is not limited to the above embodiment.

  (B) The rigidity of the outer peripheral side torsion spring 23 and the inner peripheral side torsion spring 24 in the pre-damper unit 10 is an example, and is not limited to the above embodiment.

1 clutch disc assembly 2 clutch disc 3 clutch plate (input side member)
4 Retaining plate (input side member)
7 Output hub (output side member)
8 torsion spring 10 pre-damper unit 21 first sub plate (intermediate plate)
21c Arc-shaped hole 22 second sub plate (output side plate)
22 d Protuberance 23 Outer peripheral side torsion spring 24 Inner peripheral side torsion spring 24

Claims (4)

A damper disk assembly for transmitting torque from an engine to an input shaft of a transmission,
It has an input side member to which torque from the engine is input, and an output side member connected to the input shaft of the transmission, and the torque input to the input side member is attenuated by torsional vibration from the engine A main damper unit for transmitting to the output side member;
A pre-damper unit that receives torque from the main damper unit, attenuates torsional vibration in a range where the torque is smaller than that of the main damper unit, and outputs the torque to the output side member;
Equipped with
The pre-damper unit is
A plurality of outer peripheral elastic members engaged with the input side member of the main damper unit and torque is input from the input side member;
An output side plate connected to an output side member of the main damper unit;
A plurality of inner circumferential elastic members disposed on the inner circumferential side of the plurality of outer circumferential elastic members and engaged with the output plate to transmit torque to the output member;
An intermediate piece of the plurality of outer peripheral elastic members and the plurality of inner peripheral elastic members arranged in series so as to be rotatable relative to the input side member and the output side plate of the main damper unit. Plate,
Equipped with
The intermediate plate is formed in a disk shape, and includes an outer peripheral storage portion for storing the plurality of outer peripheral elastic members formed in the outer peripheral portion, and the plurality of inner peripheral elastic members formed in the inner peripheral portion. And an inner peripheral side first storage section for storing
Damper disc assembly. The output side plate is formed in a disk shape, and is formed on an inner peripheral portion and engaged with an outer peripheral portion of the output side member, and the inner peripheral first storage portion of the intermediate plate. has an inner peripheral side second housing section for housing a plurality of inner peripheral side elastic member, the damper disk assembly according to claim 1. The output-side plate, the relative rotation with respect to the intermediate plate is restricted within a predetermined angular range, the damper disk assembly according to claim 1 or 2. The intermediate plate has an arc-shaped hole having a predetermined length in the rotational direction,
The output side plate has a projection inserted into the arc-shaped hole through a predetermined gap.
The damper disk assembly according to claim 3.

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