JP2000310312A - Lockup apparatus of torque converter - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce problems caused by two drive plates in a damper mechanism of a lockup apparatus. SOLUTION: This lockup apparatus 4 is arranged in a space between a front cover 2 and a turbine 11, and mechanically connects and disconnects the both in response to the fluctuation of the hydraulic oil pressure. The lockup apparatus 4 has a first piston 43, a driven plate 53, and a plurality of torsion springs 52. The first piston 43 is made of a disk-like member, and has a first friction connecting portion 49 forming a clutch connecting portion 40 in association with the front cover 2, and a plurality of spring supporting portions 60 arranged in a circumferential direction. The driven plate 53 is unrotatably engaged with the turbine 11. A plurality of the torsion springs 52 are supported on the spring supporting portions 60 and resiliently connect the first piston 43 and the driven plate 53 in the rotation direction.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a lockup device for a torque converter.

[0002]

2. Description of the Related Art Generally, a torque converter can smoothly perform acceleration and deceleration because power is transmitted by a fluid. However, slippage of the fluid causes energy loss, resulting in poor fuel economy. Therefore, some conventional torque converters are provided with a lock-up device for mechanically connecting the input-side front cover and the output-side turbine. The lockup device is disposed in a space between the front cover and the turbine. The lockup device, for example, elastically connects the friction connection plate to the front cover, a piston for pressing the friction connection plate against the front cover friction surface, and the friction connection plate and the turbine in the rotational direction. And a damper mechanism. The damper mechanism includes two drive plates fixed to the friction connection plate, a driven plate disposed therebetween and non-rotatably connected to the turbine, and a torsion for elastically connecting the drive plate and the driven plate in the rotational direction. And a spring. The torsion spring is supported at both ends in the rotational direction by a drive plate and a driven plate, and is supported at both axial sides by two drive plates.

[0003]

In the conventional lock-up device, since two drive plates are provided, the number of parts increases and the axial dimension increases. This means that it is difficult to increase the size of the torsion spring in a limited space.

[0004] It is an object of the present invention to reduce problems caused by two drive plates in a damper mechanism of a lock-up device.

[0005]

According to a first aspect of the present invention, there is provided a lock-up device comprising: a front cover, an impeller that forms a fluid chamber together with the front cover, and a front cover that is disposed in the fluid chamber so as to face the impeller. Used in a torque converter including a turbine for securing a space. The lock-up device is located in the space and mechanically connects the front cover and the turbine by changing the pressure in the space.
This is for releasing the connection. The lockup device includes an input member, an output member, and a plurality of springs. The input member is a disk-shaped member arranged in the space, and has a friction connecting portion that forms a clutch connecting portion together with the front cover, and a plurality of spring support portions arranged in the circumferential direction.
The output member engages the turbine in a relatively non-rotatable manner. The plurality of springs are supported by the spring support portion, and elastically connect the input member and the output member in the rotation direction.

[0006] In this lockup device, the input member has a frictional connection portion and a plurality of spring support portions, so that it functions as one of the conventional drive plates. As a result, the number of components of the lockup device is reduced. In the lock-up device for a torque converter according to claim 2, in claim 1, the plurality of spring support portions are:
The spring supports both ends in the circumferential direction and one side in the axial direction.

According to a third aspect of the present invention, there is provided a lock-up device for a torque converter, further comprising a support member fixed to the input member and supporting an opposite side of one side in the axial direction of the spring.

[0008]

FIG. 1 shows a torque converter 1 employing an embodiment of the present invention. In FIG. 1, a torque converter 1 mainly includes a front cover 2
A fluid operating unit 3 including three types of impellers (impeller 10, turbine 11, and stator 12) concentrically arranged with the front cover 2, the front cover 2 and the turbine 11
Lock-up device 4 arranged in a space C in the axial direction between
It is composed of The outer periphery of the front cover 2 and the impeller shell 15 of the impeller 10 are fixed by welding, and both form a fluid chamber A filled with hydraulic oil. A portion of the impeller shell 15 further extending from the impeller blade 16 is arranged on the outer peripheral side of the turbine 11 and is integrated with the outer peripheral tubular portion 8 of the front cover 2.

The front cover 2 is a member to which a torque is input from a crankshaft (not shown) of the engine. The front cover 2 mainly includes a disk-shaped main body 5. A boss 6 is fixed to the center of the main body 5.
A plurality of nuts 7 are fixed to the outer peripheral side of the main body 5 on the side of the engine. An outer peripheral cylindrical portion 8 extending toward the transmission is formed on an outer peripheral portion of the main body 5. Outer cylindrical part 8
Are formed with projections and depressions that alternately project in the radial direction over the entire circumference. A lug or a spline 9 is formed inside the outer peripheral cylindrical portion 8 due to the unevenness. Further, an annular and flat friction surface 70 is formed on the outer peripheral portion inside the main body 5 of the front cover 2. The friction surface 70 faces the transmission side in the axial direction.

The fluid operating section 3 is disposed in the fluid chamber A on the transmission side in the axial direction. Thus, the inside of the fluid chamber A is divided into a fluid working chamber B including the fluid working section 3 and a space C formed between the main body 5 of the front cover 2 and the turbine 11. The impeller 10 includes an impeller shell 15, a plurality of impeller blades 16 fixed inside the impeller shell 15, an impeller core 17 fixed inside the impeller blade 16, and an impeller fixed to the inner peripheral edge of the impeller shell 15. And a hub 18.

The turbine 11 is located inside the fluid chamber A in the impeller 1.
0. The turbine 11 includes a turbine shell 20, a plurality of turbine blades 21 fixed to the turbine shell 20, a turbine core 22 fixed inside the turbine blade 21, and a turbine shell 2.
And a turbine hub 23 fixed to the inner peripheral edge of the turbine hub 23. The turbine hub 23 is a cylindrical member, and has a flange 26 on the outer peripheral side. The flange 26 is fixed to the inner peripheral portion of the turbine shell 20 by a plurality of rivets 24. Further, a spline 25 is formed on the inner peripheral edge of the turbine hub 23. The spline 25 is engaged with a shaft (not shown) extending from the transmission side. Thus, the torque from the turbine hub 23 is output to a shaft (not shown).

The stator 12 is disposed between the inner periphery of the impeller 10 and the inner periphery of the turbine 11. Stator 12 is a mechanism for rectifying the flow of hydraulic oil returning from turbine 11 to impeller 10. The stator 12 includes a stator carrier 27, a plurality of stator blades 28 fixed to an outer peripheral surface thereof, and a stator core 29 fixed inside the stator blade 28. Further, the stator carrier 27 is supported by a fixed shaft (not shown) via a one-way clutch 30.

A first thrust bearing 32 is arranged between the main body 5 of the front cover 2 and the turbine hub 23 in the axial direction. A plurality of grooves extending in the radial direction are formed on the end face on the engine side in the axial direction of the turbine hub 23, and these grooves allow hydraulic oil to flow on both radial sides of the first thrust bearing 32. A second thrust bearing 33 is disposed between the turbine hub 23 and the one-way clutch 30. A plurality of grooves extending in the radial direction are formed on a member constituting the one-way clutch 30 on the engine side in the axial direction. These grooves allow the hydraulic oil to flow between both sides in the radial direction of the second thrust bearing 33.

Stator carrier 27 and impeller hub 1
A third thrust bearing 34 is arranged between the third thrust bearing 34 and the axial direction. A plurality of grooves extending in the radial direction are formed on the transmission side of the stator carrier 27 in the axial direction. These grooves allow hydraulic oil to flow between both sides in the radial direction of the third thrust bearing 34. In this embodiment, the impeller hub 18 and the stator 1
The first oil passage of the hydraulic operating mechanism is connected in the axial direction between
A second oil passage of the hydraulic operation mechanism is connected between the stator 12 and the turbine hub 23 in the axial direction, and a third oil passage of the hydraulic operation mechanism is connected between the turbine hub 23 and the inner peripheral portion of the front cover 2. ing. The first oil passage and the second oil passage are usually connected to a common hydraulic circuit, and both supply the hydraulic oil to the fluid operating unit 3 or discharge the hydraulic oil from the fluid operating unit 3. The third oil passage is formed inside the shaft, and is capable of supplying hydraulic oil between the front cover 2 and the turbine hub 23, that is, the inner peripheral portion of the space C, or discharging the hydraulic oil from the space C. .

Next, the space C will be described. The space C is an annular space formed between the main body 5 of the front cover 2 and the turbine 11 in the axial direction. The space C is formed by the main body 5 of the front cover 2 on the engine side in the axial direction and by the turbine shell 20 of the turbine 11 on the transmission side in the axial direction. Further, the outer peripheral side of the space C is mainly formed by the inner peripheral surface of the outer cylindrical portion 8, and the inner peripheral side is formed by the outer peripheral surface of the turbine hub 23. As described above, the space C is connected to an external hydraulic operating mechanism on the inner circumferential side, that is, between the inner circumferential portion of the front cover 2 and the turbine hub 23. Further, the space C communicates with the fluid working chamber B through a gap between the impeller 10 outlet and the turbine 11 inlet at the outer peripheral portion.

The lock-up device 4 is arranged in the space C, and mechanically connects and disconnects the front cover 2 and the turbine 11 by a change in hydraulic pressure in the space C. The lock-up device 4 mainly includes a piston mechanism 41 and a piston 42. The piston mechanism 41 itself has a piston function that operates in the space C by a change in oil pressure, and a damper function for absorbing and attenuating torsional vibration in the rotational direction.

The piston mechanism 41 comprises a first piston 43 and a damper mechanism 44. First piston 4
Numeral 3 is a disk-shaped member arranged in the space C close to the main body 5 side of the front cover 2. First piston 4
Reference numeral 3 mainly includes a disk-shaped plate 45, and divides the space C into a first space D on the front cover 2 side and a second space E on the turbine 11 side. The outer peripheral portion of the plate 45 is a first friction connecting portion 49 arranged on the axial transmission side of the friction surface 70 of the front cover 2. The first friction connecting portion 49 is an annular and flat plate-like portion, and annular friction members 46 are attached to both sides in the axial direction.
The friction member 46 facing the friction surface 70 is a first member.
The friction member 46a, the opposite one of which is the second friction member 4
6b.

The first piston 43 has an inner peripheral portion located closer to the transmission in the axial direction than an outer peripheral portion. That is, as shown in FIG. 4, the inner peripheral portion of the first piston 43 is formed as a protruding portion 56 that protrudes in the axial direction by drawing. The protruding portion 56 includes a cylindrical portion 50 and a disk-shaped portion 51. On the inner peripheral edge of the first piston 43, that is, on the inner peripheral edge of the disc-shaped portion 51, an inner peripheral tubular portion 71 extending toward the transmission in the axial direction is provided. Inner circumference tubular part 71
Are radially supported on the outer peripheral surface of the turbine hub 23. Thus, the first piston 43 can be rotated relative to the turbine hub 23 and moved in the axial direction. An annular groove is formed on the outer peripheral surface 65 of the turbine hub 23, and a seal ring 57 is provided in the groove. The seal ring 57 is in contact with the inner peripheral surface of the inner peripheral cylindrical portion 71. This seal ring 57 allows the first space D
And the second space E are sealed. An annular contact portion 48 is formed on the outer peripheral surface of the turbine hub 23 on the axial transmission side of the inner cylindrical portion 71. This restricts the movement of the plate 45 toward the transmission in the axial direction.

The disc-shaped portion 51 is formed with a spring support portion 60 which constitutes a part of a damper mechanism 44 described later. A plurality of spring support portions 60 are formed in a line in the circumferential direction. The spring support portion 60 is formed so as to protrude in the axial direction by drawing, is convex on the axial transmission side, and concave on the axial engine side. No holes or cutouts are formed in the spring supporting portion 60 in the axial direction. Each spring support extends long in the circumferential direction. The concave side of the spring support portion 60 is provided with abrasion measures such as hardening by heat treatment and improvement in lubricity with a lubricant. Therefore, even if the torsion spring 52 slides on the spring support portion 60, the wear is small.

The inner peripheral portion of the first space D communicates with the third oil passage, and is isolated from the second space E by the inner peripheral edge of the first piston 43 and the outer peripheral surface 65 of the turbine hub 23.
The outer peripheral portion of the first space D has a friction surface
And is in communication with the second space E in a state of being cut off from the second space E in a state of contact with the second space E and in a state of being separated therefrom. The damper mechanism 44 includes a first
This is a mechanism for transmitting torque from the piston 43 to the turbine 11 side and for absorbing and attenuating torsional vibration. The damper mechanism 44 is disposed on the engine side of the inner peripheral portion of the first piston 43 in the axial direction, that is, in the first space D. In other words, the damper mechanism 44 is housed in the protrusion 56. The damper mechanism 44 includes the drive plate 54, the torsion spring 52, and the driven plate 5
And 3. The outer periphery of the drive plate 54 is fixed to the first piston 43 by rivets 75. The drive plate 54 is arranged to face the disk-shaped portion 51 of the first piston 43 in the axial direction.
The drive plate 54 is formed with a plurality of spring support portions 35 corresponding to the spring support portions 60. Spring support 3
5 is cut and raised toward the engine in the axial direction. The first piston 43 has a plurality of holes 80 through which the rivets 75 pass.

The driven plate 53 is an annular plate, and its outer peripheral portion is disposed between the drive plate 54 and the disk-shaped portion 51 in the axial direction. A window hole 58 is formed in the driven plate 53 at a position corresponding to the spring support 35 of the drive plate 54 and the spring support 60 of the first piston 43. The window hole 58 is a hole penetrating in the axial direction. The torsion spring 52 is arranged in the window hole 58. The torsion spring 52 is a coil spring extending in the rotation direction. The torsion spring 52 is supported at both ends in the rotational direction by the window hole 58 and the spring support portions 35 and 60 described above. Further, the torsion spring 52 is connected to the spring support 3 of the drive plate 54.
5 supports the engine side in the axial direction, and the spring support portion 60 of the first piston 43 supports the transmission side in the axial direction.

The driven plate 53 has a plurality of teeth 116 on the inner periphery. The teeth 116 are engaged with teeth 117 provided on the outer periphery of the turbine hub 23 so as to be relatively rotatable and movable in the axial direction. In addition, a clearance penetrating in the axial direction is secured at the engagement portion between the teeth 116 and the teeth 117. The driven plate 53 has its outer peripheral surface 74 supported in the radial direction by the inner peripheral surface of the cylindrical portion 50 of the first piston 43.

In the second space E, the piston 42
The piston 43 is disposed on the transmission side in the axial direction of the outer peripheral portion and on the outer peripheral side of the damper mechanism 44. The piston 42 is an annular plate.
9 has a second friction coupling portion 68 adjacent to the axial transmission side. As shown in FIG. 2, the second friction coupling portion 68 has an annular and flat shape, and has a pressing surface 69 on the engine side in the axial direction. The pressing surface 69 faces the second friction member 46b in the axial direction. Piston 42
An outer peripheral cylindrical portion 62 extending toward the transmission in the axial direction is formed on the outer peripheral edge of the transmission. The outer cylindrical portion 62 is disposed close to the inner peripheral surface of the outer cylindrical portion 8 of the front cover 2. The outer cylindrical portion 62 has teeth 64 that protrude alternately on both sides in the radial direction. The teeth 64 are engaged with lugs or splines 9 formed on the outer cylindrical portion 8 of the front cover 2. By this engagement, the piston 42 is not rotatable relative to the front cover 2 and is movable in the axial direction. An annular groove is formed in a portion of the lug or spline 9 on the transmission side in the axial direction, and a snap ring 67 is arranged in the groove.
The axial transmission end face of the outer cylindrical portion 62 of the piston 42 abuts against the snap ring 67, thereby restricting the movement of the piston 42 toward the axial transmission. A gap is formed in the engagement portion between the tooth 64 and the lug or spline 9 so that the hydraulic oil can move in the axial direction.

An inner peripheral cylindrical portion 63 extending toward the transmission in the axial direction is formed on the inner peripheral edge of the piston 42. The inner peripheral edge of the inner peripheral cylindrical portion 63 is supported by the outer peripheral surface 73 of the cylindrical portion 50 of the first piston 43, is positioned in the radial direction, and can move in the rotation direction and the axial direction. Further, an annular groove is formed in the outer peripheral surface 73, and a seal ring 66 is disposed therein. The seal ring 66 is in contact with the inner peripheral surface of the inner cylindrical portion 63. The space on both sides in the axial direction at the inner peripheral edge of the piston 42 is sealed by the seal ring 66. Thus, the third space F is formed mainly between the outer peripheral portion of the first piston 43 and the piston 42 in the axial direction. The third space F is isolated from other parts of the second space E by the above-described seal ring 66. Further, the third space F is closed on the outer peripheral side when the first frictional connection portion 49 and the second frictional connection portion 68 are in contact with each other, and is open when the two are away from each other. Since the third space F is formed between the piston 42 and the plate 45, the number of components is reduced and the structure is simplified. Further, in the plate 45, the first frictional connection portion 49
A plurality of holes 4 penetrating in the axial direction
7 are formed. The first space D and the third space F communicate with each other by the holes 47.

A summary of the above description will be given of the clutch connecting portion 40 of the lockup device 4. The clutch connecting portion 40 includes a friction surface 70 of the front cover 2, a first friction connecting portion 49 of the first piston 43, and a piston 42.
And the pressing surface 69 of the second friction coupling portion 68. Thus, the clutch connecting portion 40 has two friction surfaces. The piston 42 and the first piston 43
Rotates relative to each other with the clutch connecting portion 40 disconnected. However, in a state where the clutch connecting portion 40 is connected, the two rotate integrally, and the inner peripheral cylindrical portion 63 and the cylindrical portion 50 do not slide in the rotational direction.

In this case, since the first frictional connection portion 49 and the second frictional connection portion 68 are each a piston that moves in the axial direction, the first piston is located between the friction surface 70 and the friction member 46. 43, the friction member 4
The pressing force from the piston 42 acts between 6 and the pressing surface 69. In this clutch connecting portion 40, a piston 42
Is the inner diameter of the first piston 43 (ID1)
By being larger, the first frictional connection 4
The pressing force acting on 9 is smaller than when the inner diameter of the piston 42 is equal to the inner diameter of the first piston 43. Therefore, a smaller pressing force can be generated as compared with the case where the friction surface is simply doubled, and wear and breakage of the friction member 46 and the like can be suppressed. Further, by changing the size of the piston 42, the pressing force acting on the clutch connecting portion 40 can be easily changed. It can be said that the inner diameter of the piston 42 is larger than the inner diameter of the first piston 43. Such a structure exhibits the above-described excellent effects when the piston mechanism 41 is not provided with the damper mechanism 44.

Since the piston 42 is arranged on the outer peripheral side of the damper mechanism 44 as an input member which rotates integrally with the front cover 2, more specifically, the inner diameter of the piston 42 is larger than the outer diameter of the damper mechanism 44 and Are arranged on the outer periphery of the damper mechanism 44, so that the space on one side in the axial direction of the damper mechanism 44 is not restricted.
Therefore, the axial dimension of the torsion spring 52 in the damper mechanism 44 can be increased. Thereby, the design becomes easy, and the high functionality of the torsion spring 52 such as lower rigidity can be realized.

Further, the piston 42 as a piston member which moves in the axial direction by itself is supported in a radial direction by a part of the damper mechanism 44, in particular, by the first piston 43 constituting a drive member, thereby supporting the piston 42. This eliminates the need for special members and configurations, and simplifies the overall structure of the lockup device 4. Next, the operation will be described. In the clutch disengaged state, hydraulic oil is supplied from the third oil passage to the inner peripheral side of the first space D. The hydraulic oil in the first space D flows radially outward, and the friction surface 7
It flows between the first friction member 46a and the first friction member 46a and further flows through the gap between the lug or spline 9 and the teeth 64 to the outer peripheral side of the second space E. The hydraulic oil in the second space E passes through the gap between the impeller shell 15 and the turbine shell 20 and flows into the fluid working chamber B from the gap between the impeller 10 outlet and the turbine 11 inlet. The hydraulic oil that moves in the first space D passes through a hole 47 formed in the first piston 43,
It flows into the space F. The hydraulic oil in the third space F is
9 and the second friction member 46b flows radially outward. The hydraulic oil also includes lugs or splines 9 and teeth 64
Flows to the outer peripheral side of the second space E through the gap between

Here, the first piston 43 and the piston 4
2 function as pistons that move in the axial direction due to changes in oil pressure in the space C, so that the axial movement of both members is stable. Therefore, the clutch connecting portion 40
, Each member is difficult to contact with each other. Specifically, the movement of the piston 42 toward the transmission in the axial direction is restricted by the snap ring 67, and the movement of the first piston 43 in the axial direction is restricted by the turbine hub 23. As a result, as shown in FIG.
A predetermined clearance is secured between the friction member 46a and between the second friction member 46b and the pressing surface 69.

Next, the clutch connecting operation will be described. The hydraulic oil in the first space D is drained from the third oil passage.
Thus, the hydraulic oil in the first space D flows toward the inner peripheral side, and the hydraulic oil in the third space F flows into the first space D through the hole 47. As a result, the first piston 43 moves to the engine side in the axial direction, and the first frictional connecting portion 49 is moved to the front cover 2.
Abuts on the friction surface 70. Further, the piston 42 also moves toward the engine side in the axial direction, and the pressing surface 69 moves to the second friction member 46.
b. Thus, the first space D is formed by the hole 47.
And the third space F communicate with each other, whereby the operation of the piston 42 becomes smooth.

Next, the clutch release operation will be described.
When the hydraulic oil is supplied from the third oil passage into the first space D, the hydraulic oil moves to the outer peripheral side, and further passes through the hole 47 to the third oil passage.
It flows into the space F. As a result, the first piston 43 and the piston 42 move toward the transmission in the axial direction. Thus, the operation of the piston 42 is smoothened by the hole 47. [Functions of First Piston 43] The functions of the above-described first piston 43 will be summarized and described. (1) The first piston 43 functions as an input member that transmits torque to the damper mechanism 44. (2) The first piston 43 has a first friction connection part 49,
The clutch connecting portion 40 is formed together with the front cover 2 as a clutch plate. (3) The first piston 43 has a spring support portion 60 and constitutes a part of the damper mechanism 44. (4) The first piston 43 has a function as a piston that can move by itself due to a change in oil pressure in the torque converter 1. (5) The first piston 43 supports the second piston 42 and the driven plate 53 in the radial direction by the cylindrical portion 50.

As described above, the first piston 43 realizes a plurality of functions by one disk-shaped member. For this reason, the number of parts is reduced, and the overall structure is simple and compact. In particular, by simultaneously having the functions (1) to (3), “an input member having a clutch plate constitutes a spring support portion of a damper mechanism” can be achieved, so that one conventional drive plate can be omitted. The excellent effect of is obtained. (A) The number of parts is reduced, and a structure for disposing and mounting the drive plate is not required. (B) The space on both sides in the axial direction of the torsion spring 52 can be increased, so that the coil diameter of the torsion spring 52 can be increased. Thereby, the vibration absorbing performance of the torsion spring 52 can be improved. Second Embodiment A lock-up device 4 shown in FIG. 5 will be described in detail only for parts different from the first embodiment.

The inner peripheral surface of the piston 42 is
, The space on both axial sides communicates with the inner peripheral portion of the piston 42. The outer peripheral portion of the piston 42 is connected to the first frictional connecting portion 49 of the first piston 43.
It extends further outward and is located in the vicinity of the outer cylindrical portion 8 of the front cover 2. An annular fourth space G is provided between the main body 5 of the front cover 2 and the outer peripheral portion of the piston 42 on the outer peripheral side of the first piston 43. Further, on the outer peripheral surface of the piston 42, an annular seal member 95 which is in contact with the inner peripheral surface of the outer cylindrical portion 8 is fixed, and both sides in the axial direction are sealed between the inner cylindrical portion 8 and the piston 42. ing. As described above, the outer peripheral portion of the fourth space G has the sealing member 95.
, And the inner peripheral portion is closed with the clutch connecting portion 40 connected. A cone spring 97 is disposed in the fourth space G. The cone spring 97 is elastically deformed in the axial direction in a state where at least the piston 42 has moved to the engine side in the most axial direction (a clutch connected state). That is, the cone spring 97 is at least connected to the piston 4 in the clutch connected state.
2 is applied to the front cover 2 in a direction away from the front cover 2.

The first friction member 46a and the second friction member 96 adhered to the first friction connecting portion 49 of the first piston 43 will be described. The first friction member 46a is the same as in the first embodiment. The second friction member 96 has the same inner diameter as the first friction member 46a, but has a smaller outer diameter. As a result,
The radial width of the second friction member 96 is about half the width of the first friction member 46a. That is, in the clutch engagement state, the pressing surface 69 of the piston 42
It is in contact with the friction member 96, and its outer peripheral side has a gap between the first frictional connection portion 49 and a portion where the friction member is not fixed. This gap forms a part of the fourth space G described above.

In the first embodiment, lugs or splines are formed on the front cover 2, but in this embodiment, lugs or splines 100 are formed on the impeller shell 15. Further, the impeller shell 15 is formed with a spigot portion 101 axially facing the outer cylindrical portion 62 of the piston 42. The first piston 43 is a substantially flat disk-shaped member. An inner peripheral cylindrical portion 7 extending toward the transmission in the axial direction is provided on an inner peripheral edge of the first piston 43.
1 is provided. The inner cylindrical portion 71 is a turbine hub 2
3 is supported in the radial direction on the outer peripheral surface 65. Thus, the first piston 43 can be rotated relative to the turbine hub 23 and moved in the axial direction. An annular groove is formed on the outer peripheral surface 65 of the turbine hub 23,
A seal ring 57 is provided in the groove. The seal ring 57 is in contact with the inner peripheral surface of the inner peripheral cylindrical portion 71. The seal ring 57 seals between the first space D and the second space E. An annular contact portion 48 is formed on the outer peripheral surface of the turbine hub 23 on the axial transmission side of the inner cylindrical portion 71. This restricts the movement of the first piston 43 toward the transmission in the axial direction.

The first piston 43 is provided with a spring support 102 which constitutes a part of a damper mechanism 44 described later. A plurality of the spring support portions 102 are formed side by side in the circumferential direction. The spring support part 102 is formed so as to protrude in the axial direction by drawing, and is convex toward the engine side in the axial direction and concave toward the transmission side in the axial direction. No holes or cutouts are formed in the spring support 102 in the axial direction. Each spring support 102 extends long in the circumferential direction. The concave side of the spring support 102 is provided with abrasion measures such as hardening by heat treatment and improvement in lubricity with a lubricant. For this reason, even if the torsion spring 52 slides on the spring support part 102, wear is small.

As described above, the first piston 43 functions as a damper casing of the damper mechanism 44, and one of the conventional drive plates can be omitted. As a result, the number of parts is reduced, and the overall structure is simplified. The damper mechanism 44 transmits the torque from the first piston 43 to the turbine 1
This is a mechanism for transmitting to the first side and absorbing and attenuating torsional vibration. The damper mechanism 44 includes the first piston 43
Is disposed in the axial direction on the transmission side of the inner peripheral portion, that is, in the second space E. The damper mechanism 44 includes a drive plate 54, a torsion spring 52, and a driven plate 53. Drive plate 5
4 has an outer peripheral portion fixed to the first piston 43 by a rivet 75. The drive plate 54 is arranged to face the first piston 43 in the axial direction. The drive plate 54 is formed with a plurality of spring support portions 35 corresponding to the spring support portions 102. The spring support portion 35 is formed by being cut and raised toward the transmission in the axial direction. The first piston 43 has a plurality of holes 80 through which the rivets 75 pass. The driven plate 53 is an annular plate, and its outer peripheral portion is disposed between the drive plate 54 and the first piston 43 in the axial direction. Window holes 58 are formed in the driven plate 53 at positions corresponding to the spring support portions 35 of the drive plate 54 and the spring support portions 102 of the first piston 43.
The window hole 58 is a hole penetrating in the axial direction. The torsion spring 52 is arranged in the window hole 58. The torsion spring 52 is a coil spring extending in the rotation direction. The torsion spring 52 is supported at both ends in the rotation direction by the window hole 58 and the spring support portions 35 and 102 described above. Further, the torsion spring 52 is supported on the axial transmission side by a spring support portion 35 of a drive plate 54 (support member), and is supported on the axial engine side by a spring support portion 60 of the first piston 43.

On the inner peripheral edge of the driven plate 53, an inner peripheral cylindrical portion 77 protruding toward the transmission in the axial direction is formed. The inner peripheral cylindrical portion 77 has a plurality of claw portions 61 formed side by side in the circumferential direction. The inner peripheral surface of the inner peripheral cylindrical portion 77, that is, the claw portion 61 is radially supported by the second outer peripheral surface 105 of the turbine hub 23, and as a result,
The driven plate 53 is movable in the axial direction with respect to the turbine 11. An engaging portion 1 extending further inward from the rivet 24 portion on the inner peripheral portion of the turbine shell 20.
03 is formed. The engaging portion 103 extends toward the transmission in the axial direction, and a plurality of claws 104 extending inward in the radial direction are formed at the tip thereof. The claw 104 is engaged with the claw portion 61. As a result, the driven plate 53 can move in the axial direction with respect to the turbine 11 and cannot rotate relative to the turbine 11.

In the lockup connection release operation state, the third
Hydraulic oil is supplied from the oil passage into the first space D. The hydraulic oil in the first space D moves to the outer peripheral side, and from the space between the friction surface 70 of the front cover 2 and the first friction member 46a, the fourth space G
Flows into. The hydraulic oil in the fourth space G is the second friction member 9
The fluid flows radially inward through the space between the pressing surface 6 and the pressing surface 69.
The hydraulic oil is further supplied to the inner peripheral portion of the piston 42 and the damper mechanism 4.
4 flows into the second space E from the gap between the second space E and the second space E.

In this state, the movement of the piston 42 toward the engine in the axial direction is restricted by the cone spring 97. Therefore, drag torque hardly occurs when the clutch is disconnected. Next, when the hydraulic oil in the first space D is drained from the third oil passage, the first piston 43 and the piston 42 move toward the engine in the axial direction. Thereby, the first friction member 46a is pressed against the friction surface 70, and the pressing surface 69 is pressed against the second friction member 46b. Here, the second friction member 96
Of the second friction member 96 because the effective radius of the
May be smaller than in the first embodiment. However, in this embodiment, the second friction member 96
, The pressure receiving area of the piston 42 is increased. Therefore, depending on the pressure acting on the piston 42, the transmission torque of the second friction member 96 can be made equal to or larger than that of the conventional friction member.

Next, when hydraulic oil is supplied from the third oil passage into the first space D, the first piston 43 and the piston 42 move toward the transmission in the axial direction, and the clutch connection is interrupted. At this time, the piston 42 is reliably and smoothly moved toward the transmission in the axial direction by the cone spring 97. [Functions of First Piston 43] The functions of the above-described first piston 43 will be summarized and described. (1) The first piston 43 functions as an input member that transmits torque to the damper mechanism 44. (2) The first piston 43 has a first friction connection part 49,
The clutch connecting portion 40 is formed together with the front cover 2 as a clutch plate. (3) The first piston 43 forms a part of the damper mechanism 44 by having the spring support portion 102. (4) The first piston 43 has a function as a piston that can move by itself due to a change in oil pressure in the torque converter 1.

As described above, the first piston 43 realizes a plurality of functions by one disk-shaped member. For this reason, the number of parts is reduced, and the overall structure is simple and compact. In particular, by simultaneously having the functions (1) to (3), “an input member having a clutch plate constitutes a spring support portion of a damper mechanism” can be achieved, so that one conventional drive plate can be omitted. The excellent effect of is obtained. (A) The number of parts is reduced, and a structure for disposing and mounting the drive plate is not required. (B) The space on both sides in the axial direction of the torsion spring 52 can be increased, so that the coil diameter of the torsion spring 52 can be increased. Thereby, the vibration absorbing performance of the torsion spring 52 can be improved.

[0043]

In the lock-up device according to the present invention, the input member has a frictional connection portion and a plurality of spring support portions, so that it functions as one of the conventional drive plates. As a result, the number of components of the lockup device is reduced.

[Brief description of the drawings]

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

FIG. 2 is a partially enlarged view of FIG. 1, showing a clutch connecting portion of the lock-up device.

FIG. 3 is a partially enlarged view of FIG. 1, showing support of a piston by a damper mechanism.

FIG. 4 is a perspective view of a piston.

FIG. 5 is a schematic longitudinal sectional view of a torque converter according to a second embodiment.

FIG. 6 is a perspective view of a piston.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Torque converter 2 Front cover 3 Fluid operating part 4 Lockup device 5 Main body 8 Outer peripheral cylindrical part 9 Inner peripheral tooth 10 Impeller 11 Turbine 12 Stator 20 Turbine shell 21 Turbine blade 23 Turbine hub 41 Piston mechanism 42 Piston 43 First piston 45 Plate 46 friction member 52 torsion spring 53 driven plate 54 drive plate 60 spring support 102 spring support

Claims (3)

[Claims] A torque converter including a front cover, an impeller that forms a fluid chamber together with the front cover, and a turbine that is disposed in the fluid chamber so as to face the impeller and that secures a space between the front cover and the turbine. A lock-up device disposed in the space and mechanically connecting and disconnecting the front cover and the turbine by a pressure change in the space, wherein the disk shape is disposed in the space. An input member (43) having a friction connection portion (49) forming a clutch connection portion (40) together with the front cover, and a plurality of spring support portions (60, 102) arranged in a circumferential direction.
An output member (5) engaged with the turbine so as to be relatively non-rotatable.
3) and a plurality of springs (52) supported by the spring support portion and elastically connecting the input member and the output member in a rotational direction.
And a lockup device (4) for a torque converter comprising: 2. The lock-up device for a torque converter according to claim 1, wherein said plurality of spring support portions support both ends in the circumferential direction of said spring and one side in the axial direction. 3. The lock-up device for a torque converter according to claim 2, further comprising a support member fixed to said input member and supporting an opposite side of said spring in said one axial direction.