JPH0849757A - Fluid transmission gear - Google Patents

Abstract

PURPOSE:To provide a fluid transmission gear that can reduce the number of part items and prevent the damage of a spring. CONSTITUTION:A fluid transmission gear has a lock-up clutch piston 21, a drive plate receiving transmitted rotation, a driven plate extended radially outward and provided with an axially extended locking part, and a spring. A stopper ST for regulating the movement of the locking part is integrally formed at the peripheral edge of the driven plate, along the spring. When the spring is bent by the set quantity, the movement of the locking part is regulated by the stopper ST. Each coil of the spring is not therefore placed in the closely adhering state so as to prevent the damage of the spring. Interference preventing parts ST1, ST2 for preventing interference with the spring are formed at the end parts of the stopper ST, so that there is no interference between the end part of the stopper ST and the spring.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic power transmission device having a lockup clutch device.

[0002]

2. Description of the Related Art Conventionally, an automatic transmission is provided with a torque converter as a fluid transmission device, and has a structure for transmitting the rotation of an engine taken out by a crankshaft to an input shaft of a transmission mechanism via the torque converter. There is.
The torque converter includes a pump impeller, a turbine runner, a stator, a lockup clutch device, and a damper device. Then, the rotation from the engine is transmitted to the pump impeller through the front cover,
The turbine runner is rotated by the flow of oil generated by the rotation of the pump impeller, and the rotation of the turbine runner is transmitted to the input shaft.

In this case, when the vehicle speed set in advance is obtained after the vehicle has started, the lockup clutch device is engaged and the rotation of the engine is transmitted to the input shaft without passing through the torque converter. By the way, if the rotation from the engine is transmitted to the input shaft as it is at the same time as the engagement of the lockup clutch device, the rapid fluctuation of the output torque of the engine is transmitted as it is, and vibration, noise and the like are generated. Therefore, a damper device is arranged between the lockup clutch device and the turbine hub. The damper device is locked to the lock-up clutch piston of the lock-up clutch device, one of the two drive plates receiving rotation of the lock-up clutch piston is fixed to the other, and the other is fixed to the turbine hub. And a driven plate, and a spring arranged between the drive plate and the driven plate to absorb a sudden change in the transmission torque. The spring is sandwiched by the two driven plates (see Japanese Patent Application Laid-Open No. 61-252962).

Therefore, when the transmission torque is rapidly transmitted to the lockup clutch piston due to the engagement of the lockup clutch device, the spring bends.
In the bent state, the transmission torque is transmitted to the input shaft, and abrupt changes in the transmission torque are absorbed.

[0005]

However, in the above-mentioned conventional fluid transmission device, the damper device requires the lock-up clutch piston, the drive plate and the two driven plates, so that the number of parts is large. Further, after the vehicle has started, the lockup clutch device cannot be engaged until the preset vehicle speed is obtained, so the rotation of the engine is transmitted to the input shaft via the torque converter. Therefore, the fuel consumption is deteriorated accordingly.

Therefore, while reducing the number of parts of the damper device and using a spring having a small spring constant, the engagement region of the lock-up clutch device can be set to the low speed side to improve fuel efficiency. Possible fluid transmissions are conceivable. However, when a spring having a small spring constant is used, when the torque transmitted to the spring increases, the spring is in a completely contracted state. Therefore, the windings of the spring may come into close contact with each other, and the stress may suddenly increase to damage the spring.

Therefore, it is conceivable to dispose a stopper in order to prevent the spring from being in a close contact state. However, since a space for disposing the stopper is required in the torque converter, the torque is reduced. The overall length and outer diameter of the converter will increase. Further, even if the stopper is provided in the torque converter, the installation location is integrally formed with the press working member. Therefore, since it is necessary to form the stopper by press working, the press working becomes complicated and the durability deteriorates.

When the stopper is arranged on the outer peripheral edge of the lock-up clutch piston, since the plate thickness of the lock-up clutch piston is large, it becomes difficult to perform press working, and the accuracy can be increased. Can not. Furthermore, the spring cannot be attached when the damper device is assembled. On the other hand, if the stopper is arranged integrally with the drive plate, the stopper may interfere with the spring and the spring may be damaged.

The present invention solves the above-mentioned problems of the conventional fluid transmission device, can reduce the number of parts, can improve the fuel consumption, and can reduce the durability.
It is an object of the present invention to provide a fluid transmission device that can improve accuracy and that does not damage a spring.

[0010]

Therefore, in the fluid transmission device of the present invention, the rotation of the engine is transmitted to the pump impeller through the front cover, and the oil flow generated as the pump impeller rotates. The turbine runner is rotated by and is transmitted to the output member.

A lock-up clutch piston, which is disposed so as to face the front cover and is engaged and disengaged with the front cover via a friction material, is fixed to the lock-up clutch piston and is transmitted to the lock-up clutch piston. Drive plate that receives rotation, a driven plate that includes a locking portion that extends radially outward from the output member and that extends in the axial direction, a drive plate at one end, and a locking portion of the driven plate at the other end And a spring that absorbs fluctuations in the transmission torque.

Further, on the periphery of the drive plate,
A stopper that restricts the movement of the locking portion is integrally formed along the spring, and an interference prevention portion that prevents interference with the spring is formed at an end portion of the stopper. In another fluid transmission device of the present invention, the interference prevention portion is formed by deforming the end portion of the stopper and floating it from the spring.

In still another fluid transmission device of the present invention, the interference prevention portion is formed by chamfering a surface of the end portion of the stopper facing the spring.

[0014]

According to the present invention, as described above, in the fluid transmission device, the rotation from the engine is transmitted to the pump impeller through the front cover, and the oil generated by the rotation of the pump impeller is transmitted. Is used to rotate the turbine runner and transmit it to the output member.

A lock-up clutch piston, which is disposed so as to face the front cover and is engaged and disengaged with the front cover via a friction material, is fixed to the lock-up clutch piston and is transmitted to the lock-up clutch piston. Drive plate that receives rotation, a driven plate that includes a locking portion that extends radially outward from the output member and that extends in the axial direction, a drive plate at one end, and a locking portion of the driven plate at the other end And a spring that absorbs fluctuations in the transmission torque.

In this case, when the preset vehicle speed is obtained after the vehicle has started, the lock-up clutch piston and the front cover are engaged. Therefore, the rotation of the engine is transmitted to the output member without passing through the fluid transmission device, so that the fuel consumption can be improved. Further, the rotation transmitted from the front cover via the friction material is transmitted to the output member via the spring, but in this case, the spring contracts, and fluctuations in the transmission torque when the rotation is transmitted are suppressed. Absorb. Therefore,
It is possible to prevent vibration, noise, and the like from occurring due to transmission of abrupt fluctuations in the output torque of the engine.

In this case, since the driven plate has no function of holding the spring, only one driven plate needs to be used. Therefore, the number of parts of the damper device can be reduced. In addition, a stopper that restricts the movement of the locking portion is integrally formed along the spring at the periphery of the drive plate.

In this case, when the spring is bent by a set amount, the stopper restricts the movement of the locking portion, so that the windings of the spring are not brought into close contact with each other, and the spring is prevented from being damaged. be able to. Moreover, since a stopper can be formed on the periphery of the drive plate, no special space is required. Therefore, the overall length and outer diameter of the fluid transmission can be reduced.

Further, an interference preventing portion for preventing interference with the spring is formed at the end of the stopper. Therefore, when the spring is bent, the end portion of the stopper does not interfere with the spring, so that the spring can be prevented from being damaged.
In another fluid transmission device of the present invention, the interference prevention portion is formed by deforming the end portion of the stopper and floating it from the spring. In this case, since the end of the stopper floats from the spring, the end of the stopper does not interfere with the spring.

In still another fluid transmission device of the present invention, the interference prevention portion is formed by chamfering a surface of the end portion of the stopper facing the spring. In this case, since the end of the stopper is chamfered, the end of the stopper does not interfere with the spring.

[0021]

Embodiments of the present invention will now be described in detail with reference to the drawings. 1 is a front view of a fluid transmission device according to an embodiment of the present invention, FIG. 2 is a sectional view of a fluid transmission device according to an embodiment of the present invention, FIG. 3 is a sectional view taken along line XX of FIG. 1, and FIG. FIG. 5 is a sectional view taken along line YY, FIG. 5 is a first operational state diagram of the stopper in the embodiment of the present invention, and FIG. 6 is a second operational state diagram of the stopper in the embodiment of the present invention.

In the figure, the torque converter as a fluid transmission device is composed of 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. Then, the rotation of the engine transmitted via a crankshaft (not shown) is transmitted to the front cover 16 and is transmitted to the pump impeller 11 fixed to the front cover 16. In this case, when the pump impeller 11 rotates, a flow of oil in the torus rotating around the shaft is generated, and a centrifugal force is applied to the flow of the oil to cause the pump impeller 11 and the turbine runner 1 to rotate.
2 and the stator 13 to circulate.

When the vehicle starts, the pump impeller 11 is used.
When the engine has just started rotating and the difference in rotational speed from the turbine runner 12 is large, the oil flowing out from the turbine runner 12 flows in a direction in which the rotation of the pump impeller 11 is hindered.
Therefore, a stator 13 is arranged between the pump impeller 11 and the turbine runner 12, and when the rotational speed difference between the two is large, the stator 13 converts the oil flow in a direction that assists the rotation of the pump impeller 11.

Then, the rotation speed of the turbine runner 12 becomes high, and the turbine runner 12 and the pump impeller 1
When the difference in rotational speed from 1 becomes small, the oil hitting the front side of the blade 31 of the stator 13 hits the back side, and the oil flow is obstructed. 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 comes into contact with the back side of the blade 31, the stator 13 naturally rotates, so that the oil can circulate smoothly. The outer race 18 of the one-way clutch 17 is fixed to the stator 13, and the inner race 19 is fixed to a case of an automatic transmission (not shown).

As described above, the torque converter acts as a torque converter when the rotational speed difference between the pump impeller 11 and the turbine runner 12 is large, amplifies the torque, and acts as a fluid coupling when the rotational speed difference becomes small. Next, the lockup clutch device 14 will be described.
After the vehicle has started, when the preset vehicle speed is obtained, the lockup clutch device 14 is engaged. Therefore, the rotation of the engine is transmitted to the input shaft of the transmission mechanism without passing through the torque converter, so that the fuel consumption can be improved. The lock-up clutch device 14 operates by switching the oil supply by a lock-up relay valve (not shown), and the lock-up clutch piston 21 moves in the axial direction so that the friction material 20 and the front cover 16 are engaged with each other. Removal is performed.

Therefore, the release side oil chamber R is provided between the lock-up clutch piston 21 and the front cover 16.
1, an engagement side oil chamber R2 is formed between the lockup clutch piston 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.

When the front cover 16 and the lockup clutch piston 21 are engaged with each other via the friction material 20, the rotation of the crankshaft causes the front cover 16, the lockup clutch piston 21, the damper device 15 and the output member to rotate. It is directly transmitted to an input shaft (not shown) via the turbine hub 23 as. Therefore, the spline groove 23a is formed on the inner circumference of the turbine hub 23.
The turbine hub 23 and the input shaft are spline-fitted by the spline groove 23a.

Reference numeral 61 is an annular friction plate as a damping member arranged between the turbine hub 23 and the front cover 16, 65 is a thrust bearing arranged between the stator 13 and the turbine hub 23, 66 is the stator 13
And a sleeve 67, which is a thrust bearing. The damper device 15 is for absorbing the fluctuation of the transmission torque generated when the lockup clutch device 14 is engaged and disengaged, and is fixed to the lockup clutch piston 21 by the rivet 58 and integrated with the lockup clutch piston 21. A drive plate 57 which is rotated in a vertical direction, a driven plate 32 which is disposed so as to face the drive plate 57 and is rotated integrally with the turbine runner 12, and springs 33 to 35. The springs 33 and 35 are for the first stage, and both occupy a circumferential length of 85% or more in the circumferential direction of the lockup clutch piston 21 to form a long stroke damper. In this embodiment, they are arranged at two locations in the circumferential direction.

The springs 34 are for the second stage and are arranged at four positions in the circumferential direction. The spring 34 starts to bend after the transmission torque reaches the bending point torque when the torsion (twisting) angle of the springs 33 and 35 reaches a set value. Therefore, the front cover 16
The rotation transmitted from the friction member 20 to the turbine hub 23 is transmitted to the turbine hub 23 via the damper device 15. In this case, the springs 33 to 35 contract and the torque transmitted when the rotation is transmitted. Absorb fluctuations. As a result, it is possible to prevent the generation of vibration, noise, etc. due to the transmission of a sudden change in the output torque of the engine.

The pump impeller 11 and the turbine runner 12 have blades 41 and 42, respectively, and the blade 4
The outer shells 43 and 44 and the inner cores 45 and 46 are disposed on both sides of the first and the second 42, respectively. And
The outer shell 44 of the turbine runner 12 is connected to the turbine hub 23 by the rivets 47 together with the driven plate 32.

The lock-up clutch piston 21 extends in the axial direction and slides in the axial direction along the sliding surface formed on the turbine hub 23. First flat plate portion 52 extending radially outward from the first rising portion 51, first flat plate portion 5
2, a second flat plate portion 53 extending radially outward, a third flat plate portion 54 extending radially outward from the second flat plate portion 53,
And a second rising portion 55 extending in the axial direction from the third flat plate portion 54.

Then, the second flat plate portion 53 is slightly projected to the engine side in the axial direction from the first flat plate portion 52 and the third flat plate portion 54, and the first flat plate portion 52 and the second flat plate portion The spring 35 is disposed on the stepped portion P1 formed between the stepped portion P1 and the portion 53, and the spring 34 is disposed on the stepped portion P2 formed between the second flat plate portion 53 and the third flat plate portion 54. Is provided. In addition, the second rising portion 55
Is slightly curved inward in the radial direction, and the curved portion P
3 is formed, and the bent portion P4 and the curved portion P3 are formed between the third flat plate portion 54 and the second rising portion 55.
And form an outer holding portion of the spring 33.

In this case, since the spring 33 can be arranged at the outermost peripheral portion of the lockup clutch piston 21, it is possible to fully utilize the space formed between the front cover 16 and the torus. Therefore, the diameter of the spring 33 can be set large. Therefore, the spring constant of the spring 33 can be reduced to reduce the natural frequency. In this embodiment, the spring constant of the spring 33 is, for example, 130.
It is set below [kg · m / rad].

In this case, the natural frequency of the damper device 15 can be reduced, and the lockup clutch device 14 can be used.
It is possible to set the engagement area of No. 1 to the low speed side accordingly. Therefore, fuel efficiency can be improved. Also,
The lock-up clutch piston 21 is surrounded and held by the springs 33 to 35, and the rotation of the lock-up clutch piston 21 is rotated by the springs 33 to 35.
A drive plate 57 is provided for transmission to
Lock-up clutch piston 2 with rivets 58
Fixed to 1. The drive plate 57 includes a curved portion Q1 formed corresponding to the stepped portion P1, curved portions Q2 and Q3 formed corresponding to the stepped portion P2, and the bent portion P4 and the curved portion. It has a rising portion Q4 formed corresponding to P3.

The curved portion Q1 forms the outer holding portion of the spring 35, the curved portions Q2 and Q3 form the inner and outer holding portions of the spring 34, and the rising portion Q4 forms the inner holding portion of the spring 33. . Further, when the lock-up clutch device 14 is engaged with the bending portion Q1 and the lock-up clutch piston 21 rotates in the forward direction (counterclockwise direction in FIG. 1) (hereinafter, referred to as "during forward drive"). ) Spring 35
The spring 35 is held when the lock-up clutch piston 21 rotates in the reverse direction (clockwise direction in FIG. 1) during engine braking or the like (hereinafter, referred to as “reverse driving”). The spring pressing portion M2 is formed. Similarly, the bending portions Q2, Q3 are formed with spring pressing portions M3, M5 for holding the spring 34 during forward driving and spring pressing portions M4, M6 for holding the spring 34 during reverse driving. Further, the rising portion Q4 includes a spring pressing portion M7 that holds the spring 33 when the lock-up clutch piston 21 is normally driven to engage the lock-up clutch device 14, and a lock-up clutch piston 21 during engine braking or the like. A spring pressing portion M8 that holds the spring 33 during reverse driving is formed.

The spring pressing portions M1 and M2 are then
In the stepped portion P1 of the lock-up clutch piston 21, spring pressing portions N1 and N2 integrated with the lock-up clutch piston 21 are provided. Also, in correspondence with the spring pressing portions M7 and M8, Spring pressing portions N3 and N4 integral with the lockup clutch piston 21 are formed at the bent portion P4.

On the other hand, the driven plate 32 extends in the radial direction along the turbine runner 12, and locking portions T1 to T3 are provided at three radial positions of the driven plate 32 in correspondence with the springs 33 to 35. Is formed. Each of the locking portions T1 to T3 extends in the axial direction with the tip end facing the engine side, and the lockup clutch piston 2
At the time of forward drive or reverse drive of 1, one end of the springs 33 to 35 is pressed and bent by the locking portions T1 to T3.

As described above, since the driven plate 32 does not have a function of holding the springs 33 to 35, only one driven plate 32 needs to be used. Therefore, the number of parts of the damper device 15 is reduced, and not only the structure of the torque converter can be simplified, but also the size can be reduced and the weight can be reduced.

By the way, the lock-up clutch device 14
When the lock-up clutch piston 21 is normally driven, the engaging portion T3 bends the spring 33 toward the spring pressing portion M7, and when the lock-up clutch piston 21 is reversely driven during engine braking or the like, The locking portion T3 bends the spring 33 toward the spring pressing portion M8.

However, since a spring having a small spring constant is used as the spring 33, when the torque transmitted to the spring 33 is large, the spring 33 is in a completely contracted state. In this case, each winding of the spring 33 may be in a close contact state, the stress may suddenly increase, and the spring 33 may be damaged. Therefore, in order to prevent the spring 33 from being in a close contact state, a stopper ST is formed integrally with the rising portion Q4 at a position where the spring 33 is bent by a set amount in the peripheral portion of the drive plate 57. . The stopper ST is formed by further raising a part of the rising portion Q4 along the outer diameter of the spring 33, and holds the spring 33.

Even when the spring 33 is bent toward the spring pressing portion M7 side, the spring pressing portion M
The stopper ST extends in the circumferential direction along the rising portion Q4 by a set distance so that the stopper ST can restrict the movement of the locking portion T3 even when the stopper ST is bent to the 8th side. The spring pressing portion M8
The end portion STa of the lock-up clutch piston 21 restricts the movement of the locking portion T3 when the lock-up clutch piston 21 is normally driven, and the end portion STb of the spring pressing portion M7 side locks the locking portion T3 when the lock-up clutch piston 21 is reversely driven.
Are regulated to move.

In this case, the windings of the spring 33 are not brought into close contact with each other, and the spring 33 can be prevented from being damaged. In addition, the rising portion Q4
Can be formed by further raising part of the spring 33 along the outer diameter of the spring 33, so that no special space is required. Therefore, the overall length and outer diameter of the torque converter can be reduced.

In this embodiment, the stopper S
Although T extends integrally from the end portion STa on the spring pressing portion M8 side to the end portion STb on the spring pressing portion M7 side, the end portion STa on the spring pressing portion M8 side and the end portion on the spring pressing portion M7 side are integrated. It is also possible to separate the part STb and separate it. Further, since the stopper ST is formed by further raising a part of the rising portion Q4 along the outer diameter of the spring 33, it is possible to prevent the spring 33 from jumping out due to the centrifugal force.

By the way, if the ends STa and STb of the stopper ST interfere with the spring 33 when the spring 33 is bent, the spring 33 may be damaged. Therefore, by floating the vicinity of the end portion STa of the stopper ST from the spring 33, the interference prevention portion ST1 becomes
The interference prevention portion ST2 is formed by floating the vicinity of b from the spring 33.

In this case, the interference prevention portions ST1 and ST2 are formed by deforming the vicinity of the respective end portions STa and STb inward in the radial direction. Also, the interference prevention units ST1 and ST
2 is a spring 3 near each end STa, STb
It can also be formed by chamfering the surface opposite to 3. In this way, the end portion ST of the stopper ST is
Since the interference prevention portions ST1 and ST2 are formed in the vicinity of a and STb, when the spring 33 is bent, the ends STa and STb do not interfere with the spring 33, so that the spring 33 is damaged. Can be prevented.

The present invention is not limited to the above-mentioned embodiments, but various modifications can be made based on the spirit of the present invention, and they are not excluded from the scope of the present invention.

[Brief description of drawings]

FIG. 1 is a front view of a fluid transmission device according to an embodiment of the present invention.

FIG. 2 is a sectional view of a fluid transmission device according to an embodiment of the present invention.

FIG. 3 is a sectional view taken along line XX of FIG. 1;

FIG. 4 is a sectional view taken along line YY of FIG.

FIG. 5 is a first operational state diagram of the stopper according to the embodiment of the present invention.

FIG. 6 is a second operational state diagram of the stopper according to the embodiment of the present invention.

[Explanation of symbols]

 11 Pump Impeller 12 Turbine Runner 14 Lockup Clutch Device 16 Front Cover 20 Friction Material 33-35 Spring 57 Drive Plate ST Stopper ST1, ST2 Interference Preventing Part T3 Locking Part

Claims (3)

[Claims] 1. A fluid transmission device in which rotation from an engine is transmitted to a pump impeller through a front cover, and a turbine runner is rotated and transmitted to an output member by a flow of oil generated with the rotation of the pump impeller. ,
A lock-up clutch piston that is disposed so as to face the front cover and that is engaged with and disengaged from the front cover via a friction material, and a drive that is fixed to the lock-up clutch piston and receives the rotation transmitted to the lock-up clutch piston. A driven plate that extends outwardly in the radial direction from the output member and has an engaging portion that extends in the axial direction; one end is engaged with the drive plate; the other end is engaged with the engaging portion of the driven plate; A spring that absorbs fluctuations in the transmission torque is provided, and a stopper that restricts the movement of the locking portion is integrally formed along the spring at the peripheral edge of the drive plate, and the spring is provided at the end of the stopper. A fluid transmission device, characterized in that an interference prevention portion is formed to prevent interference between the fluid transmission device. 2. The fluid transmission device according to claim 1, wherein the interference prevention portion is formed by deforming an end portion of the stopper and floating the stopper from the spring. 3. The fluid transmission device according to claim 1, wherein the interference prevention portion is formed by chamfering a surface of an end portion of the stopper facing the spring.