JP3529955B2 - Damper device - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a damper device.

[0002]

2. Description of the Related Art Conventionally, an automatic transmission is provided with a torque converter, and the rotation of the engine output to the crankshaft is transmitted to the input shaft of the transmission through the torque converter. The torque converter includes a pump impeller, a turbine runner, a stator,
It is composed of a lockup clutch device and a damper device. Then, the rotation transmitted from the engine is transmitted to the pump impeller through the front cover, and the turbine runner is rotated by the oil flow generated with the rotation of the pump impeller, and the rotation of the turbine runner is transmitted to the input shaft. It is designed to communicate.

Further, the lock-up clutch device is
A clutch plate disposed so as to be movable in the axial direction is provided, and a friction material is attached to the clutch plate. Then, when the vehicle speed set in advance is obtained after the vehicle has started, the clutch plate and the front cover are brought into contact with each other, and the lockup clutch device is engaged. As a result, the rotation of the engine is directly transmitted to the input shaft without passing through oil.

By the way, as the lock-up clutch device is engaged or disengaged, the torque transmitted through the torque converter, that is, the transmitted torque varies. Also,
Even if the torque generated by the engine changes, the transmission torque also fluctuates. In this case, if the changed transmission torque is transmitted as it is to the input shaft, vibration, noise, etc. will occur.

Therefore, a damper device is arranged between the lock-up clutch device and the turbine hub, and the damper device absorbs fluctuations in the transmission torque. Therefore, the damper device, springs arranged at a plurality of positions in the circumferential direction of the clutch plate,
The drive plate is fixed to the clutch plate and holds each spring and is in contact with one end of the spring, and the driven plate is fixed to the turbine hub and is in contact with the other end of the spring.

When the transmission torque fluctuates, the spring bends (deflects) and transmits the transmission torque to the input shaft through the turbine hub in a bent state, and the transmission torque rapidly increases. Absorbs fluctuations. By the way, there is provided a damper device in which a drive plate is made into a piece and a plurality of plate pieces are fixed to a clutch plate in order to improve the yield.

In this case, spring driving claws are formed so as to project from both ends of each plate piece, and a spring accommodating portion is formed between the spring driving claws. Then, a fixing portion is formed at two positions in the circumferential direction of the damper device that are substantially the same as the spring driving pawls and inside the spring driving pawls in the radial direction of the damper device, and the plate is provided at the fixing portion. One piece is fixed to the clutch plate (Jitsuko Sho 61-28).
No. 126).

[0008]

However, in the above-mentioned conventional damper device, it is necessary to form the spring driving claws at both ends of the plate piece, and moreover, a large force is applied to the spring driving claws by the transmission torque. It is necessary to widen the width of the spring driving pawl, and as a result, the ratio of the length of the spring accommodating portion to the length of each plate piece in the circumferential direction of the damper device becomes smaller, and the free length of the spring is correspondingly reduced. It gets shorter.

Therefore, the twisting angle of the damper device cannot be increased and the fluctuation of the transmission torque cannot be sufficiently absorbed. Further, since the ratio of the length of the spring accommodating portion to the length of each plate piece in the circumferential direction of the damper device is small, the lines of the spring come into close contact at the maximum stroke, and the spring acts as a stopper, Excessive force is applied to the spring drive pawl. Therefore, the durability of the spring and the plate piece is reduced.

The present invention provides a damper device which solves the problems of the conventional damper device described above, can sufficiently absorb the fluctuation of the transmission torque, and can improve the durability of the spring and the plate piece. The purpose is to do.

[0011]

Therefore, in the damper device of the present invention, the damper device is disposed between the clutch plate for engaging and disengaging the lock-up clutch device and the output member.
It is designed to absorb fluctuations in transmission torque. And springs respectively arranged at a plurality of positions in the circumferential direction of the clutch plate, and fixed adjacent to each other at a plurality of positions in the circumferential direction of the clutch plate, holding each spring together with the clutch plate, and The lockup clutch device includes a plurality of plate pieces that press the springs when the lockup clutch device is engaged or disengaged, and a driven plate that is fixed to the output member and that receives the springs when the lockup clutch device is engaged or disengaged.

Further, each of the plate pieces is formed at both ends thereof, and has a fixing portion for fixing to the clutch plate, a connecting portion formed between the fixing portions in the circumferential direction, and an outer peripheral edge of the connecting portion. It has one formed spring driving claw and a stopper formed on the inner peripheral edge of the connecting portion for restricting compression of the spring. In another damper device of the present invention, the base portion of the stopper is further raised and biased toward the driven plate.

[0013]

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. 1 is an enlarged view of a plate piece according to an embodiment of the present invention, FIG. 2 is a vertical sectional view of a torque converter according to an embodiment of the present invention, and FIG. 3 is a front view of a damper device according to the embodiment of the present invention.
FIG. 4 is a first sectional view of the plate piece according to the embodiment of the present invention, and FIG. 5 is a second sectional view of the plate piece according to the embodiment of the present invention.

As shown in the figure, the torque converter comprises a pump impeller 11, a turbine runner 12, a stator 13, a lockup clutch device 14 and a damper device 15 which form a torus together with the pump impeller 11. The rotation of the engine (not shown) is controlled by the front cover 16 through the crankshaft (not shown).
Is transmitted to the pump impeller 11 fixed to the front cover 16. In this case, when the pump impeller 11 rotates, the oil in the torus rotates around the shaft of the torque converter, and centrifugal force is applied to circulate between the pump impeller 11, the turbine runner 12, and the stator 13.

When the vehicle is started, the pump impeller 11 has just started to rotate, and the pump impeller 1
1 and the turbine runner 12 have a large rotational speed difference,
The oil flowing out from the turbine runner 12 flows in a direction that hinders the rotation of the pump impeller 11. Therefore, a stator 13 is arranged between the pump impeller 11 and the turbine runner 12, and the stator 13 is a direction that assists the rotation of the pump impeller 11 when the rotational speed difference between the pump impeller 11 and the turbine runner 12 is large. Convert the oil flow into.

When the rotational speed of the turbine runner 12 increases and the rotational speed difference between the pump impeller 11 and the turbine runner 12 decreases, the stator 1
The oil hitting the front side of the blade 31 of No. 3 hits the back side and obstructs the oil flow. Therefore, a one-way clutch 17 that allows the stator 13 to rotate only in a fixed direction is arranged on the inner peripheral side of the stator 13.
Therefore, when the oil hits the back side of the blade 31, the stator 13 naturally rotates,
The oil circulates smoothly. The one-way clutch 17 is composed of an outer race 18 and an inner race 19. The outer race 18 is fixed to the stator 13, and the inner race 19 is fixed to a case of an automatic transmission (not shown).

Thus, the torque converter is operated as a torque converter to amplify the transmission torque when the rotational speed difference between the pump impeller 11 and the turbine runner 12 is large, and when the rotational speed difference is small, the torque converter is Operated as a joint. Next, the lockup clutch device 14 will be described.

In this case, when the vehicle speed set in advance is obtained after the vehicle has started, the lockup clutch device 14 is engaged. When the lockup clutch device 14 is engaged, the rotation of the engine is directly transmitted to the input shaft of the transmission (not shown) without passing through oil, so that the fuel consumption can be improved. In addition, the lock-up clutch device 14
Is operated by switching the supply of oil by a lock-up relay valve (not shown), and the clutch plate 21 moves in the axial direction.
1 and the front cover 16 are brought into contact with and separated from each other via the friction material 20.

Therefore, a disengagement side oil chamber R1 is formed between the clutch plate 21 and the front cover 16, and an engagement side oil chamber R2 is formed between the clutch plate 21 and the turbine runner 12. Therefore, when oil is supplied to the release side oil chamber R1, the lockup clutch device 14 is released, and when oil is supplied to the engagement side oil chamber R2, the lockup clutch device 14 is engaged. .

The lock-up clutch device 14
Is engaged, rotation of the crankshaft
It is directly transmitted to the input shaft via the front cover 16, the clutch plate 21, the damper device 15, and the turbine hub 23 as an output member. Therefore, a spline groove 23a is formed on the inner circumference of the turbine hub 23, and the turbine hub 23 and the input shaft are spline-fitted by the spline groove 23a.

Reference numeral 61 is a thrust bearing disposed between the turbine hub 23 and the front cover 16, 65 is a thrust bearing disposed between the stator 13 and the turbine hub 23, and 66 is the stator. The thrust bearing is arranged between the sleeve 13 and the sleeve 67. Next, the damper device 15 will be described.

The damper device 15 is for absorbing the fluctuation of the transmission torque, and is caulked by crushing (warming) the projection formed on the clutch plate 21 (hereinafter referred to as "dough caulking"). ) 58, which is fixed to the clutch plate 21 and is rotated integrally with the clutch plate 21,
The driven plate 32 is arranged so as to face the drive plate 57, and is composed of a driven plate 32, a spring 33 and the like which are rotated integrally with the turbine runner 12.

The springs 33 are for the first stage and are arranged at a plurality of positions in the circumferential direction of the clutch plate 21, for example, at eight positions. In addition, a plurality of positions in the circumferential direction of the clutch plate 21, for example, 4
A spring (not shown) for the second stage is arranged at every other position in the spring 33. The diameter of the spring for the second stage is set smaller than that of the spring 33, and the spring is set to be shorter, and starts to bend after the transmission torque of the spring 33 reaches the bending point torque.

Therefore, the rotation transmitted from the front cover 16 via the friction material 20 is transmitted to the turbine hub 23 via the damper device 15. In this case, the rotation for the spring 33 and the second stage is used. Since the spring contracts and absorbs the fluctuation of the transmission torque, vibration,
It is possible to prevent noise and the like from being generated. The pump impeller 11 includes a blade 41, an outer shell 43, and an inner core 45.
Is a blade 42, an outer shell 44 and an inner core 4
It consists of six. The outer shell 44 of the turbine runner 12 together with the driven plate 32 includes the rivet 47.
Is connected to the turbine hub 23.

By the way, the clutch plate 21 is
A cylindrical first rising portion 51 that extends in the axial direction and slides in the axial direction along a sliding surface formed on the turbine hub 23, and an outer side in the radial direction from the first rising portion 51. A first flat plate portion 52 that extends toward the outside, a curved portion 53 that extends radially outward from the first flat plate portion 52, a second flat plate portion 54 that extends radially outward from the curved portion 53, and It is composed of a cylindrical second rising portion 55 extending in the axial direction from the second flat plate portion 54.

The second rising portion 55 forms the outer holding portion Q1 of the spring 33. In this case, since the spring 33 is arranged on the outermost peripheral portion of the clutch plate 21, it is possible to fully utilize the space formed between the front cover 16 and the torus. The diameter of the spring 33 can be set large. Therefore, the spring 3
The spring constant of 3 can be reduced, and as a result, the natural frequency can be reduced.

A drive plate 57 is provided to surround and hold the spring 33 together with the clutch plate 21 and to transmit the rotation of the clutch plate 21 to the spring 33 and the spring for the second stage. . In the present embodiment, the drive plate 57 is made into pieces and is formed by eight plate pieces 74 having a substantially fan shape. And
By making the plate pieces 74 adjacent to each other at eight locations in the circumferential direction of the clutch plate 21, the entire drive plate 57 is formed in an annular shape.

Further, each plate piece 74 has balance weight holding portions 81 and 82 at both ends thereof, which is slightly closer to the center side than the respective balance weight holding portions 81 and 82, that is,
Fixed portions 75 and 76 are provided at both ends, and a connecting portion 86 that connects the balance weight holding portions 81 and 82 is provided at the center.
A hole 88 is formed in each of the fixing portions 75 and 76. Therefore, the plate piece 74 is fixed to the clutch plate 21 by the dowel caulking 58 through the hole 88.

A stopper 78 is formed upright on the inner peripheral edge of the connecting portion 86, and a spring driving pawl M is formed on the outer peripheral edge of the connecting portion 86 so as to project outward in the radial direction. Further, each balance weight holding unit 8
An inner holding portion Q2 that holds the spring 33 from the inside is formed upright on the outer peripheral edges of the first and the second fixing portions 75 and 76.

The balance weight holding portions 81 and 82
Respectively include quadrilateral ridges 81a and 82a,
When the plate pieces 74 are adjacent to each other, the respective ridges 8
1a and 82a form eight balance weight insertion grooves 83 that open inward in the radial direction. Therefore, by inserting and fixing the balance weight 84 in the predetermined balance weight insertion groove 83, it is possible to achieve the balance when the clutch plate 21 is rotated.

The spring drive claw M is engaged with the lock-up clutch device 14 and rotates the clutch plate 21 in the forward direction (counterclockwise direction in FIG. 3) (hereinafter referred to as "forward drive time"). .), And when the clutch plate 21 rotates in the reverse direction (clockwise direction in FIG. 3) during engine braking and the like (hereinafter referred to as “reverse driving”), the spring 33 is pressed. Therefore, the spring driving claw M extends along the end surface of the spring 33 so that the pressing surface Ma contacts the end surface of the spring 33 during the forward driving and the pressing surface Mb contacts during the reverse driving. Further, the width of the spring drive claw M is made wider toward the outer side in the radial direction.

As described above, the spring driving claws M of the two plate pieces 74 adjacent to each other and the outer holding portion Q1.
A spring accommodating portion 91 is formed by the inner holding portion Q2, and the spring 33 is accommodated and retained in the spring accommodating portion 91. On the other hand, the driven plate 32
Are formed along the turbine runner 12 and have eight spring contact claw portions T radially outwardly corresponding to the spring drive claws M at eight positions in the circumferential direction. The spring abutment claw portion T receives the spring 33 when the clutch plate 21 is driven forward and backward. Therefore, the spring contact claw portion T has a rising portion T1 that is raised toward the spring drive claw M, and the pressing surface Ta is in forward driving, and the pressing surface Tb is in reverse driving. Hit Further, like the spring driving pawl M, the width of the spring abutting pawl portion T is made wider toward the outer side in the radial direction.

In order to disperse the stress generated at the base of the spring abutment claw T by the transmission torque, the ridges Tc and Td protruding toward the turbine runner 12 are formed at the base of the spring abutment claw T. To be done. Further, in the driven plate 32, arcuate restriction holes 89 are formed inside the respective spring contact claws T in the radial direction so as to correspond to the respective stoppers 78. Then, when the spring 33 is compressed and the stopper 78 hits the ends 89a and 89b of the restriction hole 89, further compression of the spring 33 is restricted.

By the way, a notch 94 is formed between the fixing portions 75 and 76 of the plate pieces 74 as the stopper 78 is cut and raised, and the connecting portion 86 becomes thin accordingly. Therefore, the base portion 93 of the stopper 78 is raised to increase the strength of the connecting portion 86. Therefore, even if a large force is applied to the spring driving claw M by the transmission torque, the plate piece 74 is not deformed, and the durability of the plate piece 74 can be improved.

Further, when the base portion 93 is raised, the base portion 93 of the stopper 78 is biased toward the driven plate 32 side, so that the stopper 78 and the end portions 89a and 89b of the regulation hole 89 come into contact with each other. The distance to the base 93 can be shortened. Therefore, the moment applied to the stopper 78 by the transmission torque can be reduced, so that the plate piece 74 is not deformed and the durability of the plate piece 74 can be improved.

In the damper device 15 having the above-described configuration, the pressing surface Ma of each spring driving pawl M and the pressing surface Ta of each spring abutting pawl portion T press the springs 33 from both sides during normal driving. Therefore, the damper device 15
Since the fluctuation of the transmission torque can be absorbed by, the fluctuation of the transmission torque is not directly transmitted to the input shaft, and it is possible to prevent vibration, noise, and the like from occurring.

Further, at the time of reverse driving, each spring driving claw M
Pressing surface Mb of each spring and pressing surface Tb of each spring contact claw T
Pushes and compresses each spring 33 from both sides. Therefore, the damper device 15 can absorb the fluctuation of the transmission torque. And each of the springs 33
Since both ends are sandwiched by the spring driving claws M of the two plate pieces 74 adjacent to each other, one spring driving claw M is connected to the two springs 33.
Can be shared with. Therefore, since the number of spring driving pawls M can be reduced, the spring accommodating portion 91 with respect to the length of each plate piece 74 in the circumferential direction.
The ratio of the length of the spring 33 increases, and the free length of the spring 33 can be lengthened accordingly.

As a result, the torsion angle of the damper device 15 can be increased and the fluctuation of the transmission torque can be sufficiently absorbed. Further, not only is the ratio of the length of the spring accommodating portion 91 to the length of each plate piece 74 in the circumferential direction large, but the compression of the spring 33 is restricted by the stopper 78, so that the spring 33 moves at the maximum stroke. There is no close contact between the lines. Therefore, the spring 33 does not act as a stopper, and it is possible to prevent an excessive force from being applied to the spring 33 and the spring drive pawl M.
The durability of the spring 33 and the plate piece 74 can be improved.

Further, fixing parts 75, 7 are provided at both ends of the plate piece 74 with the spring driving claw M and the stopper 78 interposed therebetween.
6 is formed, the force applied to the spring drive claw M by the transmission torque and the stopper 7 at the maximum stroke
One of the fixing portions 75 and 76 receives the force applied to 8 as a compressive force. Therefore, the tensile force applied to the other of the fixing portions 75 and 76 can be reduced correspondingly, and the durability of the plate piece 74 can be improved.

The present invention is not limited to the above-mentioned embodiments, but can be variously modified within the scope of the present invention, and they are not excluded from the scope of the present invention.

[0041]

As described in detail above, according to the present invention, the damper device is disposed between the clutch plate for engaging and disengaging the lock-up clutch device and the output member to prevent fluctuations in the transmission torque. It is designed to absorb. And springs respectively arranged at a plurality of positions in the circumferential direction of the clutch plate, and fixed adjacent to each other at a plurality of positions in the circumferential direction of the clutch plate, holding each spring together with the clutch plate, and The lockup clutch device includes a plurality of plate pieces that press the springs when the lockup clutch device is engaged or disengaged, and a driven plate that is fixed to the output member and that receives the springs when the lockup clutch device is engaged or disengaged.

Further, each plate piece is formed at both ends, and has a fixing portion for fixing to the clutch plate, a connecting portion formed between both fixing portions in the circumferential direction, and an outer peripheral edge of the connecting portion. It has one formed spring driving claw and a stopper formed on the inner peripheral edge of the connecting portion for restricting compression of the spring. In this case, when the transmission torque fluctuates, the spring driving claws and the driven plate push and compress the springs. Therefore, since the damper device can absorb the fluctuation of the transmission torque, the fluctuation of the transmission torque is not directly transmitted to the input shaft, and it is possible to prevent vibration, noise, and the like from being generated.

Since both ends of each spring are sandwiched by the spring driving claws of two plate pieces adjacent to each other, one spring driving claw can be shared by the two springs. You can Therefore, since the number of spring driving pawls can be reduced, the ratio of the length of the spring accommodating portion to the length of each plate piece in the circumferential direction increases, and the free length of the spring can be increased accordingly. it can.

As a result, the torsion angle of the damper device can be increased and the fluctuation of the transmission torque can be sufficiently absorbed. Further, not only is the ratio of the length of the spring accommodating portion to the length of each plate piece in the circumferential direction large, but the compression of the spring is restricted by the stopper, so that the lines of the spring are in close contact at the maximum stroke. Will disappear. Therefore, the spring does not act as a stopper, and it is possible to prevent an excessive force from being applied to the spring and the spring driving claw, so that the durability of the spring and the plate piece can be improved.

Further, since the fixing portions are formed at both ends of the plate piece with the spring driving claw and the stopper interposed,
One of the fixing portions receives the force applied to the spring driving pawl by the transmitted torque and the force applied to the stopper during the stroke as a compressive force. Therefore, the tensile force applied to the other of the fixing portions can be reduced accordingly, and the durability of the plate piece can be improved.

In another damper device of the present invention, the base portion of the stopper is further raised and biased toward the driven plate side. In this case, since the strength of the connecting portion is increased, the plate piece is not deformed even if a large force is applied to the spring driving claw by the transmission torque, and the durability of the plate piece can be improved.

Further, since the base portion of the stopper is biased toward the driven plate side, the distance between the base portion and the position where the stopper contacts the regulating means can be shortened. Therefore, the moment applied to the stopper by the transmission torque can be reduced, so that the plate piece is not deformed and the durability of the plate piece can be improved.

[Brief description of drawings]

FIG. 1 is an enlarged view of a plate piece according to an embodiment of the present invention.

FIG. 2 is a vertical cross-sectional view of the torque converter according to the embodiment of the present invention.

FIG. 3 is a front view of the damper device according to the embodiment of the present invention.

FIG. 4 is a first plate piece according to an embodiment of the present invention.
FIG.

FIG. 5 is a second plate piece according to the embodiment of the present invention.
FIG.

[Explanation of symbols]

14 Lock-up clutch device 15 Damper device 21 clutch plate 23 turbine hub 32 driven plate 33 spring 74 plate pieces 75,76 Fixed part 78 Stopper 86 connection 93 base M spring drive claw

─────────────────────────────────────────────────── --- Continuation of the front page (72) Inventor Naohisa Kayayama 10 Takane, Fujii-cho, Anjo City, Aichi Prefecture Aisin AW Co., Ltd. Aisin AW Co., Ltd. (72) Inventor Shinji Kasuga 1 Toyota-cho, Toyota-shi, Aichi Toyota Motor Co., Ltd. (72) Inventor Kazuaki Watanabe 1 Toyota-cho, Aichi-ken Toyota Motor Co., Ltd. In-house (72) Inventor Kunihiro Iwatsuki 1 Toyota-cho, Toyota-shi, Aichi Toyota Motor Co., Ltd. (72) Inventor Hideo Tomomatsu 1 Toyota-cho, Toyota-shi, Aichi Toyota-car (56) References Japanese Unexamined Patent Publication No. 2-97754 (JP, A) Special Table 9-501484 (JP, A) (58) Fields investigated (Int.Cl. ⁷ , DB name) F16F 15/134 F16H 45/02

Claims (2)

(57) [Claims] 1. A damper device, which is arranged between a clutch plate for engaging and disengaging a lock-up clutch device and an output member, and absorbs fluctuations in transmission torque. The provided spring and the clutch plate are fixed adjacent to each other at a plurality of positions in the circumferential direction of the clutch plate, hold each spring together with the clutch plate, and press each spring with engagement / disengagement of the lockup clutch device. It has a plurality of plate pieces and a driven plate which is fixed to the output member and receives each spring as the lock-up clutch device is engaged and disengaged, and each plate piece is formed at both ends and fixed to the clutch plate. A fixing portion for connecting, a connecting portion formed between the both fixing portions in the circumferential direction, One formed on the outer peripheral edge of the connecting portion
A spring drive pawl, and a damper device that is formed on the inner peripheral edge of the connecting portion and that restricts the compression of the spring. 2. The base of the stopper is raised,
The damper device according to claim 1, wherein the damper device is biased toward the driven plate side.