JPH11141617A - Damper device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress forming hysteresis to torque to be transmitted, to prevent changing a characteristic at the time of acceleration and deceleration. SOLUTION: This device is arranged between a clutch plate 21, for engaging/ disengaging a lock-up clutch device 14, and an output member, and absorbs the variation of torque and has a driving plate 57 fixed to the clutch plate 21; driven plates 31 and 32 fixed to the output member and a torque transmitting means arranged between the driving plate 57 and the driven plates 31 and 32, and for transmitting torque following the engaging/disengaging of the clutch device 14. A torque transmitting means is equipped with at least two springs, and an intermediate member 66 floating-freely arranged, and positioned in the outer periphery of the output member. A positioning diameter can be shortened, thereby lessening hysteresis.

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 an engine output to a crankshaft is transmitted to an input shaft of a transmission via the torque converter. The torque converter includes a pump impeller, a turbine runner, a stator,
It is composed of a lock-up clutch device, a damper device and the like. The rotation transmitted from the engine is transmitted to the pump impeller via the front cover, and the turbine runner is rotated by the flow of oil 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.

[0003] Further, the lock-up clutch device includes:
A clutch plate is provided movably in the axial direction, and a friction material is attached to the clutch plate. Then, when a preset vehicle speed is obtained after the vehicle starts, the clutch plate and the front cover are brought into contact, and the lock-up clutch device is engaged. As a result, the rotation of the engine is directly transmitted to the input shaft without passing through the oil.

[0004] By the way, the torque transmitted to the input shaft via the torque converter may fluctuate with the engagement and disengagement of the lock-up clutch device. Therefore, a damper device is provided between the lock-up clutch device and the turbine hub so as to absorb fluctuations in torque transmitted by the damper device. for that reason,
The damper device includes springs disposed at a plurality of positions in a circumferential direction of a clutch plate, a drive plate fixed to the clutch plate, holding each spring, and being in contact with one end of the spring, and the turbine hub. A driven plate is fixed and is brought into contact with the other end of the spring.

In this case, in the damper device, when the torque fluctuates, the spring is compressed,
The torque is transmitted to the input shaft via the turbine hub in a compressed state. Therefore, a sudden change in torque can be absorbed. By the way, in the damper device, an intermediate member is disposed between the drive plate and the driven plate to increase the compression amplitude of the spring, and between the drive plate and the intermediate member, and between the drive member and the driven member. There is provided a spring in which a spring is disposed between the plate and the plate (see JP-A-59-222624).

FIG. 2 is a schematic view of a conventional damper device.
In this case, the two drive plates 111 form a plurality of windows 114 for accommodating a pair of springs including two springs 112 and 113. Further, a driven plate 116 is disposed radially inward from the springs 112 and 113, and hub arms 117 are formed at a plurality of positions in the circumferential direction of the driven plate 116 so as to protrude radially outward from the boss portion 118. The spring pair is disposed between the hub arms 117.

An annular intermediate member 121 is disposed radially outward from each of the springs 112 and 113. Arms 122 project radially inward at a plurality of locations in the circumferential direction of the intermediate member 121. It is formed. The arm 12
2 is a pair of springs 112, 1
13 to transmit torque.

[0008]

However, in the conventional damper device, since the intermediate member 121 is positioned by the rivet of the drive plate 111 on the outer peripheral side of the damper device, it is necessary to absorb the fluctuation of the transmitted torque. When the springs 112 and 113 are compressed at the same time, the intermediate member 121 and the drive plate 111 slide (slide) to generate a relatively large frictional force, and hysteresis is formed in the transmitted torque. Therefore, the characteristics of the damper device change between acceleration and deceleration.

Further, since the torque transmitted from the springs 112 and 113 is received by each of the hub arms 117, the thickness of the root portion P1 of each of the hub arms 117 and the boss portion 118 is increased to increase the strength. Need to be higher. As a result, the weight of the damper device increases and the space for disposing the springs 112 and 113 is restricted.

The present invention solves the problems of the conventional damper device, suppresses the formation of hysteresis in the transmitted torque, and prevents the characteristics from changing between acceleration and deceleration. It is another object of the present invention to provide a damper device that does not increase the weight or restrict the space for disposing the spring.

[0011]

To this end, a damper device according to the present invention is provided between a clutch plate for engaging and disengaging a lock-up clutch device and an output member, and absorbs fluctuations in torque. I have. The drive plate fixed to the clutch plate, the driven plate fixed to the output member, and the drive plate and the driven plate are arranged between the drive plate and the driven plate. And torque transmitting means for transmitting.

The torque transmitting means is provided so as to be freely movable between the at least two springs and the drive plate and the driven plate, and is disposed between the springs so that the springs act in series. In addition, an intermediate member positioned on the outer periphery of the output member is provided. In another damper device according to the present invention, the drive plate further includes a locking portion formed to protrude radially inward.

[0013] In still another damper device of the present invention,
Further, the intermediate member includes a locking portion formed to protrude radially outward.

[0014]

Embodiments of the present invention will be described below in detail with reference to the drawings. FIG. 1 is a longitudinal sectional view of a torque converter according to an embodiment of the present invention, and FIG.
FIG. 4 is a front view of the damper device according to the embodiment of the present invention, and FIG. 4 is a hysteresis characteristic diagram according to the embodiment of the present invention. In FIG. 4, the horizontal axis represents the angle, and the vertical axis represents the torque.

As shown in FIG. 1, the torque converter includes a pump impeller 11, a turbine runner 12, a stator 13, a lock-up clutch device 14, a damper device 15 and the like, which constitute a torus together with the pump impeller 11. The rotation of the engine (not shown) is controlled by a front cover 16 via a crankshaft (not shown).
And 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 circulates between the pump impeller 11, the turbine runner 12, and the stator 13 by applying centrifugal force.

When the pump impeller 11 has just started to rotate, for example, when the vehicle starts moving, the pump impeller 1
When the rotation speed difference between the turbine runner 1 and the turbine runner 12 is large,
The oil flowing out of the turbine runner 12 flows in a direction that hinders rotation of the pump impeller 11. Therefore, a stator 13 is provided between the pump impeller 11 and the turbine runner 12, and the stator 13 controls the flow of the oil when the rotation speed difference between the pump impeller 11 and the turbine runner 12 is large. Convert to a direction that helps the rotation of.

When the rotation speed of the turbine runner 12 increases and the difference in rotation speed between the pump impeller 11 and the turbine runner 12 decreases, the stator 1
The oil that has hit the front side of the third blade 13a now hits the back side, thereby impeding the flow of oil. Therefore, a one-way clutch 17 that allows the stator 13 to rotate only in a certain direction is provided on the inner peripheral side of the stator 13. Therefore, when the oil hits the back side of the blade 13a, the stator 13 is spontaneously rotated by the one-way clutch 17, so that the oil circulates smoothly. The one-way clutch 17
It comprises an outer race 18 and an inner race 19. And the outer race 18 is fixed to the stator 13,
The inner race 19 is fixed to a case of an automatic transmission (not shown).

As described above, the torque converter is operated as a torque converter when the rotational speed difference between the pump impeller 11 and the turbine runner 12 is large, and amplifies the torque. When the rotational speed difference is small, the torque converter Actuated as a joint. Next, the lock-up clutch device 14 will be described.

In this case, when a preset vehicle speed is obtained after the vehicle starts, the lock-up clutch device 14 is engaged. When the lock-up clutch device 14 is engaged, the rotation of the engine is directly transmitted to the input shaft of the transmission (not shown) without the intervention of oil, so that fuel efficiency can be improved. Further, the lock-up clutch device 14
Is operated by switching the oil supply by a lock-up relay valve (not shown), and the clutch plate 21 is moved in the axial direction.
1 and the front cover 16 are separated from each other via a friction material 20.

For this purpose, a release-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 lock-up clutch device 14 is released, and when oil is supplied to the engagement-side oil chamber R2, the lock-up clutch device 14 is engaged. .

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

Reference numeral 91 denotes a thrust bearing disposed between the turbine hub 23 and the front cover 16, 95 denotes a thrust bearing disposed between the stator 13 and the turbine hub 23, and 96 denotes a stator. 13 is a thrust bearing disposed between the sleeve 13 and the sleeve 97. Further, the clutch plate 21 extends in the axial direction, and slides in the axial direction along a sliding surface formed on the turbine hub 23.
A first flat plate portion 52 extending radially outward from the first rising portion 51, a curved portion 53 extending radially outward from the first flat plate portion 52, and extending radially inward from the curved portion 53 It comprises a second flat plate portion 54 and a cylindrical second rising portion 55 extending from the second flat plate portion 54 in the axial direction.

Next, the damper device 15 will be described.
The damper device 15 is for absorbing fluctuations in torque, is fixed to the clutch plate 21, is fixed to the annular drive plate 57 that is rotated integrally with the clutch plate 21, and is fixed to the turbine hub 23, Driven plates 31, 32, springs 33 to 35, which are rotated integrally with the turbine runner 12, are provided between the drive plates 57 and the driven plates 31, 32 so as to be freely movable and between the springs 33, 34. , And an intermediate member 66 for transmitting torque by operating the springs 33 and 34 in series. Torque transmitting means is constituted by the springs 33 to 35 and the intermediate member 66. The drive plate 57
The intermediate member 66 is sandwiched between the driven plates 31 and 32 from both sides. A sleeve-like spacer 81 is provided between the driven plates 31 and 32 so that the drive plate 57 and the intermediate member 66 and the driven plates 31 and 32 can be relatively rotated. Driven plates 31, 32 are connected by rivets 82 passing through 81.

The drive plate 57 has an annular portion 61 extending along the second rising portion 55 and a plurality of, for example, three, radially inwardly projecting portions of the annular portion 61 in the circumferential direction. It comprises a substantially trapezoidal locking portion 62 formed. A groove 63 is formed at a plurality of positions, for example, six positions, on the outer peripheral edge of the annular portion 61, and the groove 63 and a locking piece 64 formed on the second rising portion 55 are locked.

The springs 33 and 34 are provided in the first
It is for a stage, and is arranged adjacently in the circumferential direction via an intermediate member 66 in order to increase the compression amplitude, and forms a spring pair. The spring pair includes the drive plate 57 and the driven plate 3.
1, 32 are provided at a plurality of locations in the circumferential direction, for example, at three locations. Each of the springs 33 and 34 includes a large-diameter outer spring S1 and a small-diameter inner spring S2 disposed on the same axis in the outer spring S1.

The springs 35 are for the second stage, and are provided at a plurality of positions, for example, three positions, in the circumferential direction of the drive plate 57 and the driven plates 31, 32. Meanwhile, on the drive plate 57 side, the locking portion 62 is used when the lock-up clutch device 14 is engaged and the clutch plate 21 is rotated in the forward direction (counterclockwise in FIG. 3) (hereinafter referred to as “forward drive”). ), And when the clutch plate 21 is rotated in the reverse direction (clockwise direction in FIG. 3) during engine braking or the like (hereinafter, referred to as "reverse drive").
Compress 35.

For this purpose, on the drive plate 57 side, each spring pair is disposed between the locking portions 62, and the outer end 33a of the spring 33 and one end M1 of the locking portion 62 contact each other. Then, the outer end 34a of the spring 34 is brought into contact with the other end M2 of the locking portion 62. Further, on the driven plate 31, 32 side, each pair of springs is connected to the driven plate 31, 3
2 and is held by holding portions Q1 and Q2 formed on the periphery of each window 36. The outer end 33a of the spring 33 and the holding portion Q
1, the one end R1 of Q2 is brought into contact, and the outer end 34a of the spring 34 is brought into contact with the other end R2 of the holding parts Q1, Q2.

Further, on the drive plate 57 side, the spring 35 is housed in a hole 71 formed in the root portion P3 of the locking portion 62, and one end 35a of the spring 35 and one end of the hole 71 are provided. The other end 35b of the spring 35 and the other end N2 of the hole 71 are brought into contact with each other. On the driven plate 31, 32 side, each spring 35 is accommodated in a window 37 formed in the driven plate 31, 32, and a holding portion Q3 formed on the periphery of each window 37,
It is held by Q4. Then, one end 35a of the spring 35 and one end V1 of the holding portions Q3, Q4 are opposed to each other so as to freely contact and separate, and the other end 35b of the spring 35 and the other end of the holding portions Q3, Q4. The part V2 is opposed to the part V2 so as to be able to freely contact and separate. The spring 35 is
It is set shorter than the window 37 and the end 35 of the spring 35
a, 35b abut against the ends V1, V2 of the holding portions Q3, Q4, and start to be compressed after the torque of the springs 33, 34 reaches the bending point torque.

Therefore, the driven plates 31, 32
Side, the holding portions Q3, Q4
1 at the time of forward drive, the springs 33 to 3
5 and receives the pressing force of the springs 33 to 35 by the end portion V2 when the clutch plate 21 is driven in the reverse direction. The intermediate member 66 includes an annular portion 72 extending along the turbine hub 23 and the annular portion 72.
, A substantially dovetail-shaped locking portion 73 formed so as to protrude radially inward at a plurality of locations in the circumferential direction, for example, at three locations. The locking portion 73 is disposed between the spring 33 and the spring 34 in each spring pair, and transmits the torque by causing the spring 33 and the spring 34 to act in series. Also, the inner end 33b of the spring 33 and one end T1 of the locking portion 73
And the inner end 34b of the spring 34
And the other end T2 of the locking portion 73 are brought into contact with each other.

The annular portion 72 is formed integrally with a positioning portion 85 extending in the axial direction.
5 and the outer peripheral surface of the turbine hub 23 are slidably brought into contact with each other. Therefore, the intermediate member 66 is positioned on the outer periphery of the turbine hub 23. In addition,
The pump impeller 11 includes a blade 41, an outer shell 43, and an inner core 45, and the turbine runner 12 includes a blade 42, an outer shell 44, and an inner core 46. The outer shell 44 of the turbine runner 12 is connected to the turbine hub 23 by rivets 47 together with the driven plate 32.

Incidentally, the springs 33 and 34 are
The outer spring S1 includes an outer spring S1 and an inner spring S2 having the same length. The inner spring S2 is disposed in the outer spring S1.
In the vicinity of both ends that do not affect the spring characteristics of No. 2, the coil diameter is increased, and the coil is brought into close contact with the outer spring S1.

In this case, since both ends of the inner spring S2 are supported by the outer spring S1 and a clearance can be secured between the outer spring S1 and the inner spring S2, the inner spring S2 is rotated with the rotation of the damper device 15. Is bent outward in the radial direction (warp)
However, outer spring S1 and inner spring S2
And do not interfere.

In the damper device 15 having the above structure, when the clutch plate 21 is driven forward, the end M2 of each locking portion 62 and the end R1 of each holding portion Q1, Q2 push the springs 33, 34 from both sides. Compressed, followed by each hole 7
1 end N2 and the end V1 of each holding portion Q3, Q4 press each spring 35 to compress. Also, when the clutch plate 21 is driven in reverse, the end M1 of each locking portion 62 and the end R2 of each holding portion Q1, Q2 press the springs 33, 34 from both sides to be compressed. End N1 and end V2 of each holding portion Q3, Q4 press each spring 35 to be compressed. Therefore, the fluctuation of the torque can be absorbed by the damper device 15, so that the fluctuation of the torque is not transmitted to the input shaft as it is, and the generation of vibration, noise, and the like can be prevented.

By the way, the torque is transmitted to the springs 33 and 34 by the locking portion 62 when the clutch plate 21 is driven forward and when the clutch plate 21 is driven reversely. Since it is arranged radially outward from the pair, the circumferential dimension of each locking portion 62 can be made large. Moreover, the width of each locking portion 62 is increased as it goes radially outward.

Therefore, the strength of the root portion P3 of the locking portion 62 and the annular portion 61 can be sufficiently ensured, and it is not necessary to increase the thickness of the root portion P3 of the locking portion 62 and the annular portion 61. . As a result, the weight of the damper device 15 does not increase, and the space for disposing the springs 33 to 35 is not restricted. The intermediate member 66
When the clutch plate 21 is driven forward and reversely, the spring 33,
The torque is transmitted between the two. In this case, since the forces applied from the springs 33 and 34 cancel each other, it is not necessary to increase the thickness of the root portion of the locking portion 73 and the thickness of the annular portion 72.

When the springs 33 to 35 are compressed, the intermediate member 66 and the driven plate 3
1 and 32 are relatively rotated, so that the inner peripheral surface of the positioning portion 85 and the outer peripheral surface of the turbine hub 23 slide to generate frictional force, and the torque transmitted through the damper device 15. Hysteresis is formed. In this case, centrifugal force is generated in the springs 33 and 34 with the rotation of the damper device 15, and the centrifugal force causes the intermediate member 66 to be eccentric with respect to the turbine hub 23, and a friction force proportional to the eccentric amount at this time is generated. Will happen.

Therefore, assuming that half of the centrifugal force generated in the springs 33 and 34 is received by the locking portion 62, the amount of eccentricity is δ, the mass of the intermediate member 66 is m ₁ , The total mass is m ₂ , the rotational angular velocity is ω, and the springs 33 and 34 are
A radial force that occurs when pressing the 6 and F ', when the eccentric force when the intermediate member 66 is eccentric with respect to the turbine hub 23 and F, the eccentric force _{F, F = (m 1 + m} 2 / 2) δ · ω ² + F '

Accordingly, if the friction coefficient between the inner peripheral surface of the positioning portion 85 and the outer peripheral surface of the turbine hub 23 is μ, and the friction force is G, the friction force G becomes G = μ · F. . And the diameter of the outer peripheral surface of the turbine hub 23,
That is, assuming that the positioning diameter for positioning the intermediate member 66 is r and the hysteresis generated based on the frictional force G is H, the hysteresis H becomes H = r · G.

In this embodiment, the positioning of the intermediate member 66 is performed on the outer peripheral surface of the turbine hub 23,
Since the inner peripheral surface of the positioning portion 85 and the outer peripheral surface of the turbine hub 23 slide radially inward of the spring pair, the positioning diameter r can be reduced. Therefore, the formation of the hysteresis H in the transmitted torque can be suppressed. As a result, it is possible to prevent the characteristics of the damper device 15 from changing during acceleration and deceleration.

In FIG. 4, L1 is a line indicating the hysteresis characteristic when the positioning diameter r is increased,
Reference numeral 2 denotes a line indicating a hysteresis characteristic when the positioning diameter r is reduced. It should be noted that the present invention is not limited to the above-described embodiment, but can be variously modified based on the gist of the present invention, and they are not excluded from the scope of the present invention.

[0041]

As described above in detail, according to the present invention, the damper device is disposed between the clutch plate for disengaging the lock-up clutch device and the output member,
It is designed to absorb fluctuations in torque. And a drive plate fixed to the clutch plate;
A driven plate fixed to the output member, disposed between the drive plate and the driven plate,
And a torque transmitting unit that transmits torque when the lock-up clutch device is disengaged.

The torque transmitting means is provided so as to be free to move between at least two springs and the drive plate and the driven plate, and to be arranged between the springs so that the springs act in series. In addition, an intermediate member positioned on the outer periphery of the output member is provided. In this case, when the torque transmitted to the damper device changes, each spring is pressed and compressed by the drive plate and the driven plate. Therefore, the fluctuation of the torque can be absorbed by the damper device, so that the fluctuation of the torque is not transmitted to the input shaft of the transmission as it is, and the generation of vibration, noise, and the like can be prevented.

Further, when the spring is compressed, the intermediate member and the output member slide to generate a frictional force, thereby suppressing the formation of hysteresis in the torque transmitted through the damper device. be able to. However,
Since the intermediate member is positioned on the outer periphery of the output member,
The positioning diameter can be reduced. Therefore, the hysteresis can be reduced, so that the characteristics of the damper device can be prevented from changing between acceleration and deceleration.

[0044] In another damper device of the present invention, the drive plate further includes a locking portion formed to protrude radially inward. In this case, since the drive plate is disposed radially outward of each spring, the circumferential dimension of each locking portion can be made large. Therefore, the strength of the root portion of the locking portion can be sufficiently ensured, and it is not necessary to increase the thickness of the root portion of the locking portion. As a result, there is no increase in the weight of the damper device and no restriction on the space for disposing the spring.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a torque converter according to an embodiment of the present invention.

FIG. 2 is a schematic view of a conventional damper device.

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

FIG. 4 is a hysteresis characteristic diagram according to the embodiment of the present invention.

[Explanation of symbols]

 14 Lock-up Clutch Device 15 Damper Device 21 Clutch Plate 23 Turbine Hub 31, 32 Driven Plate 33-35 Spring 57 Drive Plate 62, 73 Locking Portion 66 Intermediate Member

Continued on the front page (72) Inventor Masashi Hattori 10 Takane, Fujii-machi, Anjo, Aichi Prefecture Inside Aisin AW Co., Ltd. (72) Inventor Naohisa Mogi 10, Takane, Fujii-cho, Anjo, Aichi Prefecture Aisin Ai Within the AW Inc. (72) Inventor Takeshi Furuya 10th Takane, Fujii-machi, Anjo, Aichi Prefecture Inside AW Co., Ltd. (72) Takashi Hori 10th Takane, Fujii-cho, Anjo-city, Aichi Prefecture Aisin Ai In GW Corporation

Claims (3)

[Claims] 1. A damper device disposed between a clutch plate for engaging and disengaging a lock-up clutch device and an output member and absorbing torque fluctuation, wherein a drive plate fixed to the clutch plate and the output member are provided. A driven plate fixed to the drive plate and a driven plate, and a torque transmitting unit that transmits torque with engagement and disengagement of the lock-up clutch device, and the torque transmitting unit includes: At least two springs, and are arranged freely between the drive plate and the driven plate and between the springs so that the respective springs act in series and are positioned at the outer periphery of the output member. A damper device comprising an intermediate member. 2. The damper device according to claim 1, wherein the drive plate includes a locking portion formed to protrude radially inward. 3. The damper device according to claim 1, wherein the intermediate member includes a locking portion formed to protrude radially outward.