JP2002213567A - Lockup device for fluid torque transmission device - Google Patents

Lockup device for fluid torque transmission device

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Publication number
JP2002213567A
JP2002213567A JP2001011173A JP2001011173A JP2002213567A JP 2002213567 A JP2002213567 A JP 2002213567A JP 2001011173 A JP2001011173 A JP 2001011173A JP 2001011173 A JP2001011173 A JP 2001011173A JP 2002213567 A JP2002213567 A JP 2002213567A
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JP
Japan
Prior art keywords
piston
cover
axial
peripheral
torque
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
JP2001011173A
Other languages
Japanese (ja)
Inventor
Naoki Tomiyama
直樹 富山
Original Assignee
Exedy Corp
株式会社エクセディ
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Exedy Corp, 株式会社エクセディ filed Critical Exedy Corp
Priority to JP2001011173A priority Critical patent/JP2002213567A/en
Publication of JP2002213567A publication Critical patent/JP2002213567A/en
Pending legal-status Critical Current

Links

Abstract

PROBLEM TO BE SOLVED: To simplify a mechanism for connecting a piston to a front cover in a lockup device having the piston pressing the frictional connection section of a drive plate to the front cover. SOLUTION: The drive plate 72 of the lockup device 7 has the frictional connection section near the frictional face of the front cover and outputs torque to a plurality of springs 73. The piston 74 is coupled with the front cover relatively unrotatably and movably in the axial direction by oil pressure, and it is a member for pressing the frictional connection section to the frictional face. A piston connecting mechanism 75 allows the piston 74 to be coupled with the front cover relatively nonrotatably and to move in the axial direction, and it has a wire ring 80 capable of transmitting torque between the piston 74 and the front cover.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a lock-up device for a hydraulic torque transmitting device, and more particularly, to a drive plate having a frictional connection portion close to a front cover, and a piston capable of pressing the drive plate against the front cover. And a lock-up device having the lock-up device.

[0002]

2. Description of the Related Art A torque converter is a type of fluid torque transmission device having three types of impellers (impeller, turbine, and stator) inside and transmitting torque through internal working oil. The impeller is fixed to a front cover as an input-side rotating body. The turbine is located opposite the impeller in the fluid chamber. When the impeller rotates, hydraulic oil flows from the impeller to the turbine, and outputs torque by rotating the turbine.

[0003] The lock-up device is disposed in a space between the turbine and the front cover, and is a mechanism for directly transmitting torque from the front cover to the turbine by mechanically connecting the front cover and the turbine. .

Normally, this lock-up device has a disk-shaped piston that can be pressed against a front cover, a retaining plate fixed to the outer peripheral portion of the piston, and a rotational direction and an outer peripheral side by the retaining plate. It has a torsion spring that is supported and a driven plate that supports both ends of the torsion spring in the rotation direction. The driven plate is fixed to a turbine shell or the like of the turbine.

[0005] When the lock-up device is connected, torque is transmitted from the front cover to the piston, and further transmitted to the turbine via the torsion spring.
Further, in the elastic coupling mechanism of the lockup device, the torsion spring is compressed in the rotating direction between the retaining plate and the driven plate, and absorbs and attenuates torsional vibration.

[0006]

Further, as a lockup device having two friction surfaces to increase the torque transmission capacity, a damper mechanism connected to a turbine and an input portion of the damper mechanism are relatively non-rotatable. Some have a drive plate locked to be movable in the axial direction, and a piston for urging the frictional connection portion of the drive plate to the piston.

In the lock-up device disclosed in JP-T-11-509611, the piston 9 is attached to the shell wall 2 by a plurality of elastic tongues 40.
Specifically, one end of the elastic tongue 40 is fixed to the wall 2 via an annular member 44, a rivet 43 and the like. The other end of the elastic tongue 40 is fixed to the piston 9 via a rivet 41.

In the lock-up device disclosed in Japanese Patent Application Laid-Open No. Hei 10-47453, the piston 14
4 attaches to the converter cover 1. Specifically, one end of the leaf spring 34 is fixed to the converter cover 1 via a connecting disk 35, rivets 42, and the like. The other end of the leaf spring 34 is a bolt 38 and a nut 3
9, is fixed to the piston 14 via a washer 40 and the like. In this way, the piston 14 rotates integrally with the converter cover 1 while being movable in the axial direction.

If a leaf spring is used to connect the piston to the front cover as in the prior art, members such as rivets and bolts are required to fix both ends of the leaf spring. As a result, the number of parts increases, the structure becomes complicated, and the weight increases. Further, the number of manufacturing steps increases.

An object of the present invention is to simplify a mechanism for connecting a piston to a front cover in a lockup device having a piston for pressing a frictional connection portion of a drive plate against a front cover.

[0011]

According to a first aspect of the present invention, there is provided a lock-up device comprising: a front cover having a friction surface; an impeller fixed to the front cover to form a fluid chamber;
And a turbine disposed in the fluid chamber so as to face the impeller. The lockup device is disposed between the turbine and the front cover. The lockup device includes a plurality of elastic members, a driven member, a drive plate, a piston, and a connection mechanism. The plurality of elastic members are arranged side by side in the rotation direction. The driven member is fixed to the turbine, and torque is input from a plurality of elastic members. The drive plate has a friction coupling portion close to the friction surface of the front cover, and outputs torque to the plurality of elastic members. The piston is movable in the axial direction by hydraulic pressure, and is a member for pressing the frictional connection portion against the friction surface. The piston connection mechanism is a mechanism for connecting the piston to the front cover so as to be relatively non-rotatable and movable in the axial direction,
It has a ring member capable of transmitting torque between the piston and the front cover.

In this lockup device, the torque is transmitted from the front cover to the piston using the ring member, so that the structure is simplified. In the lock-up device for a hydraulic torque transmission device according to the second aspect, in the first aspect, the ring member includes a plurality of first portions capable of transmitting torque with the front cover; It has a piston and a plurality of second portions that are arranged alternately and are capable of transmitting torque.

In this lockup device, a portion between the first portion and the second portion of the ring member serves as a torque transmitting portion. In the lock-up device for a hydraulic torque transmitting device according to the third aspect, the first portion and the second portion in the second aspect.
At least one of the parts is a ring-shaped part. At least one of the piston and the front cover has a plurality of axial extensions extending axially and inserted into the ring-shaped portion.

In this lockup device, the protrusion is inserted into at least one of the first portion and the second portion,
Torque can be transmitted. In this configuration, parts can be easily assembled.

According to a fourth aspect of the present invention, in the lock-up device for a hydraulic torque transmission device, the ring member is arranged to move away from the frictional connection portion with respect to the piston at least when the clutch is engaged. Gives elastic force.

In this lockup device, since the ring member also has a function of returning the piston, the total number of parts is reduced.

[0017]

DESCRIPTION OF THE PREFERRED EMBODIMENTS First Embodiment (FIGS. 1 to 9) (1) Basic Structure of Torque Converter FIG. 1 is a schematic longitudinal sectional view of a torque converter 1 according to an embodiment of the present invention. The torque converter 1 is a device for transmitting torque from a crankshaft 2 of an engine to an input shaft 3 of a transmission.
An engine (not shown) is arranged on the left side of FIG. 1, and a transmission (not shown) is arranged on the right side of FIG.
OO shown in FIG. 1 is a rotation shaft of the torque converter 1.

The torque converter 1 mainly includes a flexible plate 4 and a torque converter body 5. The flexible plate 4 is a thin disk-shaped member that transmits torque and absorbs bending vibration transmitted from the crankshaft 2 to the torque converter body 5. Therefore, the flexible plate 4 has sufficient rigidity for transmitting torque in the rotation direction, but has low rigidity in the bending direction.

The torque converter body 5 comprises a torus-shaped fluid working chamber 6 composed of three types of impellers (impeller 21, turbine 22, and stator 23), and a lock-up device 7.

The front cover 11 is a disk-shaped member, and is disposed close to the flexible plate 4. At the center of the front cover 11, a cylindrical center boss 11c is formed. The center boss 11c extends in the axial direction and is inserted into the center hole of the crankshaft 2. A bottom 11d is formed at the tip of the center boss 11c.

A boss member 16 is fixed inside the center boss 11c. As shown in FIG. 3, the boss member 16 includes a cylindrical portion 16a and a flange 16b. The outer peripheral surface of the cylindrical portion 16a is in contact with the inner peripheral surface of the center boss 11c. Further, the inner peripheral surface of the axial transmission side portion of the cylindrical portion 16 a rotatably supports the input shaft 3 via a bush 91. Further, a seal ring 92 is arranged on the bush 91 on the engine side in the axial direction. The seal ring 92 has a cylindrical portion 16.
The input shaft 3 is disposed in an annular groove formed on the inner peripheral surface of the input shaft 3 and is in contact with the outer peripheral surface of the distal end of the input shaft 3.

The flange 16b is formed on the outer peripheral surface of the cylindrical portion 16a on the axial transmission side, and has an outer peripheral surface 16c and an inner peripheral surface 16d having a predetermined axial length by projecting toward the axial transmission side. ing. The flange 16b is in contact with the axial engine side surface of the inner peripheral portion of the front cover 11. In this state, the boss member 16 is fixed to the front cover 11 by welding. In that sense, the boss member 16 may be regarded as a part of the front cover.

The boss member 16 is formed with a plurality of communication passages 16f communicating inside and outside in the radial direction. Each of the communication passages 16f is a plurality of grooves extending in the axial direction on the outer peripheral surface of the cylindrical portion 16a. Each of the communication passages 16f is a radially extending groove formed on the engine side surface in the axial direction in the flange 16b. Each communication passage 16f forms a passage between itself and the front cover 11. This communication passage 1
6f, the space on the inner peripheral side of the center boss 11c and the boss member 16, that is, the center hole 3a of the input shaft 3,
The outer peripheral side of the boss member 16, that is, the space 9 (described later) in the fluid chamber is communicated. This communication path 16f is hereinafter referred to as a first port 17.

The inner peripheral portion of the flexible plate 4 is fixed to the distal end surface of the crankshaft 2 by a plurality of bolts 13. A plurality of nuts 12 are fixed to the outer peripheral side of the front cover 11 and the engine side surface at equal intervals in the circumferential direction. Bolts 14 screwed into the nuts 12 cover the outer periphery of the flexible plate 4 with the front cover 11.
It is fixed to.

On the outer peripheral portion of the front cover 11, an outer cylindrical portion 11a extending toward the transmission in the axial direction is formed. The outer peripheral edge of the impeller shell 26 of the impeller 21 is fixed to the tip of the outer peripheral side cylindrical portion 11a by welding. As a result, a fluid chamber filled with hydraulic oil is formed by the front cover 11 and the impeller 21. The impeller 21 mainly includes an impeller shell 26, a plurality of impeller blades 27 fixed inside the impeller shell 26, and an impeller hub 28 fixed to an inner peripheral portion of the impeller shell 26.

The turbine 22 is provided in the fluid chamber in the impeller 21.
And are arranged to face each other in the axial direction. The turbine 22
It mainly includes a turbine shell 30, a plurality of turbine blades 31 fixed to a surface on the impeller side thereof, and a turbine hub 32 fixed to an inner peripheral edge of the turbine shell 30. Turbine shell 30 and turbine hub 3
2 is fixed by a plurality of rivets 33.

A spline engaging with the input shaft 3 is formed on the inner peripheral surface of the turbine hub 32. Thus, the turbine hub 32 rotates integrally with the input shaft 3.

The stator 23 is a mechanism for rectifying the flow of hydraulic oil returning from the turbine 22 to the impeller 21. The stator 23 is a member integrally manufactured by casting with a resin, an aluminum alloy, or the like. Stator 23 is arranged between the inner peripheral portion of impeller 21 and the inner peripheral portion of turbine 22. The stator 23 mainly includes an annular stator carrier 35 and a plurality of stator blades 36 provided on the outer peripheral surface of the carrier 35. The stator carrier 35 is supported on a cylindrical fixed shaft 39 via a one-way clutch 37. The fixed shaft 39 extends between the outer peripheral surface of the input shaft 3 and the inner peripheral surface of the impeller hub 28. Although the one-way clutch 37 shown in the figure has a structure using a ratchet, it may have a structure using rollers and sprags.

The torus-shaped fluid working chamber 6 is formed in the fluid chamber by the shells 26, 30, and 35 of the impellers 21, 22, and 23 described above. An annular space 9 is provided between the front cover 11 and the fluid working chamber 6 in the fluid chamber.

A first thrust bearing 41 is provided between the flange 16b of the boss member 16 and the turbine hub 32 in the axial direction.
Is arranged. Further, a second thrust bearing 42 is arranged between the turbine hub 32 and the inner peripheral portion of the stator 23 (specifically, the one-way clutch 37). In the portion where the second thrust bearing 42 is disposed, the second port 18 through which the hydraulic oil can communicate is formed on both sides in the radial direction. That is, the second port 18
Communicates the oil passage between the input shaft 3 and the fixed shaft 39 with the fluid working chamber 6. Further, the stator 23 (specifically, the carrier 35) and the impeller 21
A third thrust bearing 43 is arranged axially with the impeller hub 28 (specifically, the impeller hub 28). This third
In the portion where the thrust bearing 43 is disposed, third ports 19 through which hydraulic oil can be communicated are formed on both sides in the radial direction. That is, the third port 19 allows the oil passage between the fixed shaft 39 and the impeller hub 28 to communicate with the fluid working chamber 6. In addition, each oil passage is connected to a hydraulic circuit (not shown), and supply and discharge of hydraulic oil to the first to third ports 17 to 19 can be performed independently. (2) Structure of Lock-Up Device The lock-up device 7 is disposed in the space 9 between the turbine 22 and the front cover 11, and is a mechanism for mechanically connecting the two as necessary.

The lock-up device 7 has the functions of a clutch and an elastic coupling mechanism, and mainly includes a driven plate 71.
, A drive plate 72, a plurality of torsion springs 73, a piston 74, and a piston connection mechanism 75.

The driven plate 71 is an annular plate member as shown in FIGS. 2 and 4, and is fixed to the outer peripheral side of the turbine shell 30. Driven plate 71
Is mainly composed of a disc-shaped portion 71a (axial support portion) and a tubular portion 71b (outer peripheral support portion) extending from the outer peripheral edge toward the engine in the axial direction. The disc-shaped portion 71a is fixed to the turbine shell 30 by welding. The tubular portion 71b extends substantially straight in the axial direction, but has a shape in which the tip is bent inward.

The disc-shaped portion 71a is formed with a plurality of first cut-and-raised portions 71c cut and raised in the axial direction.
The first cut-and-raised portions 71c are formed side by side in the rotation direction, and are arranged with a gap on the inner peripheral side of the tubular portion 71b. A plurality of second cut-and-raised portions 71d cut and raised in the axial direction are formed on the disc-shaped portion 71a. The second cut-and-raised portions 71d are arranged between the rotation directions of the first cut-and-raised portions 71c, and are located on the outer peripheral side of the radial position of the first cut-and-raised portions 71c. Further, the cylindrical portion 71
In b, a protruding portion 71e is formed at a portion corresponding to the second cut-and-raised portion 71d so as to protrude inward by drawing.

Each pair of the second cut-and-raised portion 71d and the protruding portion 71e has a function as a torque transmitting portion, and a spring accommodating portion is provided between the torque transmitting portions in the rotation direction. In this embodiment, six spring accommodating portions are formed.

In the present embodiment, the torsion springs 73 are a plurality of (six) coil springs extending in the circumferential direction. The torsion spring 73 is held by the driven plate 71. In particular,
Each torsion spring 73 is accommodated in each spring accommodating portion, and the radial inner side is supported by the outer peripheral surface of the first cut-and-raised portion 71c, and the radial outer side is supported by the inner peripheral surface of the cylindrical portion 71b. In addition, the end of each torsion spring 73 in the rotation direction is directly or through a spring seat, and a second cut-and-raised portion 71d as a torque transmitting portion
And is supported in contact with or close to the protruding portion 71e.
Further, the transmission side surface of each torsion spring 73 in the axial direction is supported by a disc-shaped portion 71a. Further, the bent portion at the tip of the cylindrical portion 71b also abuts against the axial engine side surface on the outer peripheral side of the torsion spring 73, thereby preventing the torsion spring 73 from dropping from the driven plate 71 to the axial engine side. ing. Thus, in the lock-up device 7, the annular driven plate 71 is
And holds a plurality of torsion springs 73. Therefore, the number of parts is reduced, the structure of the entire apparatus is simplified, and the overall weight is reduced.

The drive plate 72 is a member capable of inputting torque to the torsion spring 73, and is also a frictional connection member that connects to and separates from the front cover 11. The drive plate 72 is an annular and disk-shaped plate member.
1 and the front cover 11. The drive plate 72 mainly includes an annular disc-shaped main body 72a.
And a tubular portion 72b (outer peripheral tubular portion) extending from the outer peripheral edge toward the transmission in the axial direction. The inner peripheral portion of the disk-shaped main body 72a is a friction coupling portion 72c, and the outer peripheral portion is a pressure receiving portion 72d (a disk-shaped portion).
The frictional connection portion 72c has an annular and flat disk shape,
It is close to the friction surface 11b of the front cover 11. The friction surface 11b is a flat and annular surface facing the transmission side in the axial direction. In addition, friction facings 72e are attached to both surfaces of the friction coupling portion 72c. Pressure receiving part 7
2d is an annular and flat disk shape, and is arranged on the engine side of the torsion spring 73 in the axial direction. The cylindrical part 72b is located on the outer peripheral side of the cylindrical part 71b of the driven plate 71, and the inner peripheral surface of the cylindrical part 72b is the cylindrical part 71b.
b is in contact with the outer peripheral surface. Accordingly, the drive plate 72 can move in the axial direction and the rotation direction with the drive plate 72 positioned in the radial direction with respect to the driven plate 71. Therefore, the position and posture of the drive plate 72 are stabilized. In particular, since the drive plate 72 is supported by the driven plate 71 by abutting (inlay) between the cylindrical portions, the drive plate 72
Is hard to tilt. As a result, the friction coupling portion 72c of the drive plate 72 can maintain high parallelism with respect to the friction surface 11b of the front cover 11 and the pressing portion 74a (described later) of the piston 74. In other words, when the clutch is engaged, the pressing force acts evenly on the entire friction facing 72e.
Drag torque is less likely to occur when the clutch is released.

Further, a plurality of claws 72f (contact portions) are formed on the drive plate 72. Claw part 72f
Are formed by cutting and raising the pressure receiving portion 72d toward the transmission in the axial direction, and are formed at equal intervals in the rotational direction. The claw portion 72f is inserted between the second cut-and-raised portion 71d and the protruding portion 71e in the radial direction from the engine side, and both ends in the rotation direction abut directly on the both ends in the rotation direction of each torsion spring 73 or via a spring seat. Or close. The claw portion 72f rotates relative to the driven plate 71 to rotate the second cut-and-raised portion 71d and the protruding portion 71e.
Can compress the torsion spring 73.
In this lockup device 7, the drive plate 72 is directly engaged with the torsion spring 73 without any intervening other members (plates), so that the total number of parts is reduced.

The drive plate 72 is movable in the axial direction. Specifically, the drive plate 72 has a friction facing portion 72e on the axial engine side of the friction coupling portion 72c on the axial engine side.
Can move on the transmission side in the axial direction until the outermost peripheral portion of the pressure receiving portion 72d contacts the cylindrical portion 71b of the driven plate 71.

In the structure of the drive plate 72 described above, a pressure receiving portion 72d is formed on the outer periphery of the friction connecting portion 72c. The pressure receiving portion 72d extends further to the outer peripheral side than the outer peripheral edge of the piston 74, and further extends to the outer peripheral side than the driven plate 71, and functions as a portion of the drive plate 72 that receives the hydraulic pressure in the space 9.
In other words, the pressure receiving portion 72d is
The pressure receiving area is increased, and the piston function is improved. Therefore, when the clutch is engaged, the hydraulic pressure
In addition, the drive plate 72 acts on the drive plate 72 so that the drive plate 72 quickly moves to the friction surface 11 of the front cover 11.
Move to b side. In other words, the lock-up response of the lock-up device 7 is improved.

The piston 74 is a member for connecting and disconnecting the clutch. The piston 74 has a disk shape with a center hole formed. The outer periphery of the piston 74 is close to the inner periphery of the torsion spring 73, and the inner periphery is the boss member 1.
6 is close to the outer peripheral side. The outer peripheral portion of the piston 74 is a pressing portion 74a. The pressing portion 74a is a flat annular portion, and is disposed on the axial transmission side of the friction coupling portion 72c of the drive plate 72. Therefore, when the piston 74 moves toward the engine in the axial direction, the pressing portion 74a presses the friction connecting portion 72c against the friction surface 11b of the front cover 11.

On the inner peripheral edge of the piston 74, an inner peripheral cylindrical portion 74b extending toward the engine in the axial direction is formed. The inner peripheral surface of the cylindrical portion 74b is in contact with the outer peripheral surface 16c of the flange 16b of the boss member 16. Thereby, the piston 74
Can be rotated and moved in the axial direction while being positioned in the radial direction by the boss member 16. An annular groove is formed in the outer peripheral surface 16c of the flange 16b, and a seal ring 79 is disposed therein. The seal ring 79 is in contact with the inner peripheral surface of the piston 74 to seal both sides in the axial direction.

The stopper 78 is a member disposed between the boss member 16 and the first thrust bearing 41 in the axial direction, and is a member for restricting the movement of the piston 74 toward the transmission in the axial direction. The stopper 78 is
As shown in FIGS. 8 and 9, the annular thin plate member is composed of an annular and flat disk-shaped portion 78a and a plurality of legs 78b extending in the axial direction from the inner peripheral edge thereof. The disc-shaped portion 78a is sandwiched between the flange 16b and the turbine hub 32 in the axial direction. The leg 78b has a rectangular shape having a predetermined width in the circumferential direction, and has a flange 16b.
b and is supported in contact with the inner peripheral surface 16d. Each leg 7
8b is formed with a claw portion 78c. The claw portion 78c
It is cut and raised radially outward from the other portion of the leg portion 78b so as to have a tip on the axial transmission side. The claw portion 78c is disposed in a concave portion 16e formed on the inner peripheral surface 16d of the flange 16b. This prevents the stopper 78 from easily falling off the boss member 16 in the axial direction. The tip of the disc-shaped portion 78a extends further from the outer peripheral edge of the flange 16b to the outer peripheral side.
4 is located on the axial transmission side near the inner peripheral edge. As a result, when the piston 74, particularly the inner peripheral portion thereof, comes into contact with the disc-shaped portion 78a, it cannot move further in the axial direction. The stopper 78
Can have the bearing race function of the first thrust bearing 41.

The operation of attaching the stopper 78 to the boss member 16 will be described. Leg 78b of stopper 78
Into the inner peripheral side of the flange 16b. At this time, the leg 78b is moving along the inner peripheral surface 16d of the flange 16b with the claw 78c bent. Claw part 7
When 8c reaches the concave portion 16e, the claw portion 78c is in a free state (that is, a state in which the claw portion 78c is raised radially outward from the leg portion 78b).
Return to In this state, the disc-shaped portion 78a is in contact with the axial end surface of the flange 16b. As described above, the mounting of the stopper 78 can be performed by one operation of moving in the axial direction.

Next, the piston connecting mechanism 75 will be described. The piston connection mechanism 75 has a function of connecting the piston 74 so as to rotate integrally with the front cover 11 while being movable in the axial direction.

Hereinafter, a specific configuration of the piston connecting mechanism 75 will be described with reference to FIGS. The piston connection mechanism 75 is mainly configured by one wiring 80. The wiring 80 is made of, for example, steel,
It is a thin wire with a diameter of about 2 to 3 mm. The wiring 80 extends annularly and has an endless shape. The wiring 80 includes a first connecting portion 80a and a second connecting portion 80a.
and b are alternately formed in the rotation direction.

The first connecting portion 80a is connected to the front cover 11
As shown in FIG. 6, the first portion 80c includes second portions 80d formed at both ends of the first portion 80c. The first portion 80c has substantially the same diameter as the main body. The second portion 80d is wider than the first portion 80c as well as the main body portion. A drive pin 81 is provided at each part of the front cover 11 corresponding to the first connection portion 80a of the wiring 80. The drive pin 81 is fixed to the front cover 11 by welding. A groove 81a extending in the rotation direction is formed on a side surface of the drive pin 81 in the axial transmission. The first portion 80c of the wiring 80 is arranged in the groove 81a. The second portion 80d of the wiring 80
The two ends of the groove 1a are in contact with both side portions of the groove, so that the wiring 80 cannot rotate relative to the drive pin 81. In addition, a caulking portion 81b is formed on the side surface of the drive pin 81 in the axial direction of the engine. The caulking portion 81b deforms the two portions divided by the groove 81a inward to form the first portion 80 of the wiring 80.
It is a portion that is in contact with the upper surface of c. With this structure, the wiring 80 does not come off the drive pin 81 in the axial direction.

The second connecting portion 80b is a ring-shaped portion which is formed so that a part of the ring main body protrudes outwardly. However, even if it says a ring-shaped part, the end part of the inner peripheral side part is an open annular shape mutually separated. A driven pin 74c is provided in a portion of the piston 74 corresponding to each second connecting portion 80b. The driven pin 74c is
This member is fixed to the piston 74 and engages with the second connecting portion 80b of the wiring 80. As shown in FIG. 7, the driven pin 74c has an engaging portion 74d.
The engagement portion 74d is a cylindrical portion extending in the axial direction,
It is inserted into the second connecting portion 80b of the wiring 80. More precisely, the engaging portion 74d is disposed closer to the inner peripheral side of the second connecting portion 80b, and the radial center position of the engaging portion 74d substantially coincides with the radial position of the main body of the wiring 80. In this state, both ends in the rotational direction of the engaging portion 74d are in contact with both ends of the second connecting portion 80b, so that torque transmission is possible. The engaging portion 74d is relatively movable in the axial direction with respect to the second connecting portion 80b.

The driven pin 74c further includes a neck 74e.
And a head 74f. The neck 74 e is
d is provided on the transmission side in the axial direction. The neck portion 74e has a smaller diameter than the engagement portion 74d,
4 is inserted into the hole formed. The head 74f is
It is provided on the axial transmission side of the neck 74e. The head 74f has a larger diameter than the neck 74e, and abuts on the axial transmission side surface around the hole of the piston 74.

Further, in the piston 74, a contact portion 74g is formed on a radially outer portion of each driven pin 74c so that the main body portion is projected in the axial direction by drawing. The contact portion 74g is connected to the second connecting portion 8 of the wiring 80.
0b, especially the outer peripheral side portion thereof. FIG. 7 shows a clutch disengaged state in which the piston 74 has moved to the transmission side in the most axial direction. In this state, the contact portion 74g is in contact with the outer peripheral portion of the second connection portion 80b.
That is, when the piston 74 moves to the engine side in the axial direction to be in the clutch connected state, the abutting portion of the piston 74 pushes and deforms the outer peripheral portion of the second connecting portion 80b of the wiring 80. That is, when the clutch is engaged, the wiring 80 applies an elastic force to the piston 74 toward the transmission in the axial direction. In addition, the second connecting portion 8
Since the vicinity of 0b is a portion where the wiring main body is curved, the rigidity is lower than that of the main body. Therefore, elastic deformation by the piston 74 is easy.

The assembly of each member in the piston connection mechanism 75 will be described. First, the drive pin 81 is fixed to the front cover 11 by welding or the like. Next, the wiring 80 is set on the drive pin 81. Specifically, the first connecting portion 80a of the wiring 80 is inserted into the groove 81a of each drive pin 81. In this state, the head of the drive pin 81 is caulked next to form the caulked portion 81b. Finally, the piston 74 is moved closer to the wiring 80, and each driven pin 74c is inserted into the second connecting portion 80b of the wiring 80.

In the assembling process described above, the piston 74 can be assembled simply by moving the piston 74 relative to the wiring 80 in the axial direction. Therefore, the working process is simplified and the manufacturing cost is reduced.

Further, since the piston connecting mechanism is mainly constituted by one wiring 80, the structure is simplified and the number of parts is reduced. As a result, cost and weight are reduced. (3) Operation of Torque Converter Immediately after starting the engine, hydraulic oil is supplied into the torque converter main body 5 from the first port 17 and the third port 19, and hydraulic oil is discharged from the second port 18. The hydraulic oil supplied from the first port 17 flows between the front cover 11 and the piston 74 toward the outer periphery. The hydraulic oil further flows through both sides of the drive plate 72 in the axial direction, and finally flows into the fluid working chamber 6. At this time, the oil pressure on the front cover 11 side becomes higher than the oil pressure on the turbine 22 side of the piston 74, and the piston 74 moves toward the transmission in the axial direction by the urging force of the wiring 80. The piston 74 stops in a state where the inner peripheral edge abuts on the stopper 78.

The drive plate 72 is in contact with the cylindrical portion 71b of the driven plate 71, so that the movement of the drive plate 72 on the transmission side in the axial direction is restricted. Therefore, in the clutch connected state, the frictional connection portion 7 of the drive plate 72
A gap is provided between 2c and the pressing portion 74a of the piston 74. Therefore, drag torque hardly occurs.

When the lock-up is released as described above, torque transmission between the front cover 11 and the turbine 22 is performed by fluid drive between the impeller 21 and the turbine 22. (4) Operation of lockup device The speed ratio of the torque converter 1 increases, and the input shaft 3
Reaches a certain number of rotations, the space 9
Hydraulic oil inside is discharged. As a result, the hydraulic pressure of the piston 74 on the turbine 22 side becomes higher than the hydraulic pressure on the front cover 11 side, the piston 74 is moved to the front cover 11 side, and the pressing portion 74a connects the friction connecting portion 72c of the drive plate 72 to the front cover 11. To the friction surface 11b. Also, as described above, the drive plate 72
Is the friction surface 1 by the hydraulic pressure acting on the pressure receiving portion 72d.
It has moved to 1b side. As a result, the front cover 11
The torque of the piston 74 is transmitted from the drive plate 72 to the driven plate 71 via the torsion spring 73. Further, the torque is transmitted from the driven plate 71 to the turbine 22. That is, the front cover 11 is mechanically connected to the turbine 22, and the torque of the front cover 11 is directly output to the input shaft 3 via the turbine 22. The drive plate 7
Since both surfaces of the second frictional connection portion 72c are frictional surfaces, the torque transmission capacity is larger than that of a lockup device having a single frictional surface.

The front cover 11 and the piston 7
4 is transmitted to the wiring 80, more specifically, the first connecting portion 80 a and the second connecting portion 80 of the wiring 80.
b. Second Embodiment (FIGS. 10 to 15) In the second embodiment shown in FIG. 10 and thereafter, the basic structure of the torque converter 1 is the same as that of the above-described embodiment. Less than,
Only the points different from the first embodiment will be mainly described.

In this embodiment, unlike the previous embodiment, no boss member is provided. Instead, the center boss 11c supports the turbine hub 32 in the axial direction with the first thrust bearing 86 interposed therebetween. Therefore, the turbine hub 32 has a cylindrical portion 32a that extends toward the transmission in the axial direction as compared with the above-described embodiment. An annular groove is formed on the outer peripheral surface of the cylindrical portion 32a, and a seal ring 87 is disposed in the groove.
The seal ring 87 abuts the inner cylindrical portion 94b of the piston 94 to seal both sides in the axial direction. Further, the inner peripheral edge portion of the piston 94 is a flange 32b of the turbine hub 32.
And the movement to the axial transmission side is restricted.

The piston coupling mechanism 75 will be described.
The piston connection mechanism 75 mainly includes one wiring 8
8. The wiring 88 is, for example, a thin wire made of steel and having a diameter of about 2 to 3 mm. The wiring 88 extends annularly and has an endless shape. As shown in FIG. 11, the wiring 88
The first connecting portions 88a and the second connecting portions 88b are formed alternately in the rotation direction. Each of the first connecting portion 88a and the second connecting portion 88b is a one-turn loop-shaped portion. The first connecting portion 88a and the second connecting portion 88b are wound in the same direction, and have the same axial height.

The first connecting portion 88a is a portion connected to the front cover 11. As shown in FIG. 13, a projecting portion 89 is formed at each portion of the front cover 11 corresponding to the first connecting portion 88a of the wiring 88.
The protruding portion 89 is a portion formed so that a part of the main body of the front cover 11 protrudes in the axial direction by press working. The protruding portion 89 has a substantially cylindrical shape, and the first connecting portion 88
a. In addition, a flange portion 89a is formed at the tip of each protruding portion 89 so as to extend outward from the cylindrical portion. The flange 89a is formed by caulking,
The first connecting portion 88 a of the wiring 88 is prevented from coming off in the axial direction from the projecting portion 89.

The second connecting portion 88b is a portion connected to the piston 94. Each second connecting portion 8 in the piston 94
A driven pin 94c is provided in a portion corresponding to 8b. The driven pin 94c is a member fixed to the piston 94 to engage with the second connecting portion 88b of the wiring 88. The driven pin 94c has an engagement portion 94d. The engagement portion 94d is a cylindrical portion extending in the axial direction, and is inserted into the second connection portion 88b of the wiring 88. The engaging portion 94d is movable relative to the second connecting portion 88b in the axial direction.

The driven pin 94c further includes a contact portion 94
e, a neck 94f and a head 94g. Contact part 94
e is provided on the axial transmission side of the engagement portion 94d. The contact portion 94e has a larger diameter than the engagement portion 94d, and is in contact with the piston 94 in the axial side surface of the engine. Further, the contact portion 94e is provided with the second
The connecting portion 88b is in contact with the transmission in the axial direction. The neck 94f is provided on the axial transmission side of the engagement portion 94d. The neck 94f has a smaller diameter than the engagement portion 94d, and is inserted into a hole formed in the piston 94. The head 94g is provided on the axial transmission side of the neck 94f. 94g head
Is larger in diameter than the neck 94f and abuts against the axial transmission side surface around the hole of the piston 94.

The assembly of each member in the piston connection mechanism 75 will be described. First, the protrusion 89 is formed on the front cover 11. Next, the wiring 88 is set on the protrusion 89. Specifically, wiring 8
8, each of the protrusions 89 is inserted into the first connecting portion 88a. In this state, the tip of the protruding portion 89 is caulked next to form the flange portion 89a. Finally, the piston 94 is moved closer to the wiring 88, and each driven pin 94c is inserted into the second connecting portion 88b of the wiring 88.

In the assembling process described above, the piston 94 can be assembled simply by moving the piston 94 in the axial direction with respect to the wiring 88. Therefore, the working process is simplified and the manufacturing cost is reduced.

When the piston 94 moves toward the front cover 11 from the clutch disengaged state, the driven pin 94
c pushes the second connecting portion 88 b of the wiring 88 toward the front cover 11. At this time, since the contact portion 94e of the driven pin 94c partially contacts the second connecting portion 88b, the loop root portions of the second connecting portion 88b are deformed so as to be separated from each other in the axial direction. As a result, the first connecting portion 88a is also deformed such that the root portions of the loop are separated from each other in the axial direction. By the above operation, the first connecting portion 88a and the second connecting portion 88b are deformed so that the loop is small and tightened, and the protrusion 89 and the driven pin 94 are respectively formed.
It is strongly wrapped around c.

In this state, the torque of the front cover 11 is reduced by the protrusion 89, the wiring 88, and the driven pin 94.
Power is transmitted to the piston 94 in the order of c. In the clutch connected state, the elastic force is applied to the driven pin 9 by the deformation of the first and second connecting portions 88a and 88b of the wiring 88.
4c and the piston 94 act on the side away from the front cover 11.

The front cover 11 and the piston 9
4 is transmitted to the wiring 88, more specifically, the first connecting portion 88 a and the second connecting portion 88 of the wiring 88.
b. [Other Embodiments] The lock-up device according to the present invention can be applied to not only a torque converter but also other fluid type torque transmission devices such as a fluid coupling.

In the lock-up device according to the present invention, the pins and the protrusions are used for engagement with the wiring, but the present invention is not limited to these. In addition, although the axially movable engagement of the ring-shaped portion of the wiring with the pin or the like is provided on the piston side in any of the embodiments, they may be used for engagement of the front cover with the wiring.

The means for fixing the wiring and the means for engaging with the wiring are not limited to the above-described embodiment. The ring-shaped portion of the wiring includes not only the ring and the loop having the ring-opening shape shown in the embodiment but also other shapes such as a ring in which a root portion abuts.

[0068]

In the lock-up device according to the present invention, the torque is transmitted from the front cover to the piston using the ring member, so that the structure is simplified.

[Brief description of the drawings]

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

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

FIG. 3 is a partially enlarged view of FIG. 1, showing a piston stopper.

FIG. 4 is a perspective view of a drive plate and a driven plate of the lockup device.

FIG. 5 is an exploded perspective view of each part of a piston coupling mechanism of the lockup device.

FIG. 6 is a perspective view showing an engagement state between a wiring and a drive pin.

FIG. 7 is a partial cross-sectional view showing an engagement state between a wiring and a driven pin.

FIG. 8 is a partial perspective view of a stopper.

FIG. 9 is a partially enlarged view of FIG. 3 and is a cross-sectional view of a stopper.

FIG. 10 is a schematic longitudinal sectional view of a torque converter according to a second embodiment.

FIG. 11 is a plan view of a piston connection mechanism.

FIG. 12 is a diagram showing an engagement state between a wiring and a driven pin.

FIG. 13 is a diagram showing an engagement state between a wiring and a protrusion.

[Explanation of symbols]

 7 Lock-up device 74 Piston 74c Driven pin 75 Piston coupling mechanism 80 Wiring 81 Drive pin

Claims (4)

[Claims]
1. A hydraulic torque transmission device comprising: a front cover having a friction surface; an impeller fixed to the front cover to form a fluid chamber; and a turbine disposed in the fluid chamber so as to face the impeller. In Claim 1, It is a device arrange | positioned between the said turbine and the said front cover, The some elastic members arrange | positioned along with the rotating direction, It is fixed to the said turbine, The torque is input from the said several elastic members. A driven plate having a frictional connection portion proximate to the friction surface of the front cover, and a drive plate for outputting torque to the plurality of elastic members; And a piston for pressing the piston against the friction surface. The piston is relatively non-rotatable with respect to the front cover and axially movable. A mechanism for binding, the piston lock-up device of hydraulic torque transmitting device and a piston coupling mechanism having a transmission capable of ring member a torque between said front cover.
2. The ring member includes a plurality of first portions capable of transmitting torque with the front cover, and the ring members are alternately arranged in the rotation direction with the first portions so as to transmit torque with the piston. The lock-up device for a hydraulic torque transmitting device according to claim 1, comprising a plurality of second portions.
3. At least one of the first portion and the second portion is a ring-shaped portion, and at least one of the piston and the front cover extends in the axial direction and is inserted into the ring-shaped portion. 3. The lock-up device for a hydraulic torque transmitting device according to claim 2, wherein the lock-up device has an axial extension.
4. The hydraulic torque transmission according to claim 1, wherein the ring member applies an elastic force to the piston at a side away from the frictional connection portion at least when the clutch is engaged. Equipment lock-up device.
JP2001011173A 2001-01-19 2001-01-19 Lockup device for fluid torque transmission device Pending JP2002213567A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2001011173A JP2002213567A (en) 2001-01-19 2001-01-19 Lockup device for fluid torque transmission device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2001011173A JP2002213567A (en) 2001-01-19 2001-01-19 Lockup device for fluid torque transmission device

Publications (1)

Publication Number Publication Date
JP2002213567A true JP2002213567A (en) 2002-07-31

Family

ID=18878337

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2001011173A Pending JP2002213567A (en) 2001-01-19 2001-01-19 Lockup device for fluid torque transmission device

Country Status (1)

Country Link
JP (1) JP2002213567A (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015005379A1 (en) * 2013-07-11 2015-01-15 株式会社エクセディ Lockup device for torque converter
US9784352B2 (en) 2013-06-04 2017-10-10 Exedy Corporation Lock-up device for torque converter
US10030740B2 (en) 2013-06-04 2018-07-24 Exedy Corporation Lock-up device for torque converter

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10030740B2 (en) 2013-06-04 2018-07-24 Exedy Corporation Lock-up device for torque converter
US9784352B2 (en) 2013-06-04 2017-10-10 Exedy Corporation Lock-up device for torque converter
JP2015017671A (en) * 2013-07-11 2015-01-29 株式会社エクセディ Lock-up device of torque converter
CN105339706A (en) * 2013-07-11 2016-02-17 株式会社艾科赛迪 Lockup device for torque converter
KR20160032091A (en) * 2013-07-11 2016-03-23 가부시키가이샤 에쿠세디 Lockup device for torque converter
US9732835B2 (en) 2013-07-11 2017-08-15 Exedy Corporation Lockup device for torque converter
WO2015005379A1 (en) * 2013-07-11 2015-01-15 株式会社エクセディ Lockup device for torque converter
KR102114792B1 (en) 2013-07-11 2020-05-25 가부시키가이샤 에쿠세디 Lockup device for torque converter

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