JP2002048217A - Lock-up device of torque convertor - Google Patents

Lock-up device of torque convertor

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Publication number
JP2002048217A
JP2002048217A JP2000262583A JP2000262583A JP2002048217A JP 2002048217 A JP2002048217 A JP 2002048217A JP 2000262583 A JP2000262583 A JP 2000262583A JP 2000262583 A JP2000262583 A JP 2000262583A JP 2002048217 A JP2002048217 A JP 2002048217A
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JP
Japan
Prior art keywords
portion
piston
lock
outer peripheral
member
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.)
Granted
Application number
JP2000262583A
Other languages
Japanese (ja)
Other versions
JP3717772B2 (en
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
Priority to JP2000-155613 priority Critical
Priority to JP2000155613 priority
Application filed by Exedy Corp, 株式会社エクセディ filed Critical Exedy Corp
Priority to JP2000262583A priority patent/JP3717772B2/en
Priority claimed from DE10123615.8A external-priority patent/DE10123615B4/en
Publication of JP2002048217A publication Critical patent/JP2002048217A/en
Publication of JP3717772B2 publication Critical patent/JP3717772B2/en
Application granted granted Critical
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Abstract

(57) Abstract: In a lock-up device for a torque converter having a disk-shaped piston, an outer peripheral cylindrical portion of a conventional piston can be omitted. A structure of a lock-up device (7) will be described. The piston 71 can be connected to and separated from the front cover. The torsion spring 74 is a member for connecting the piston 71 and the driven plate 73 in the rotation direction. The spring holder 75 is disposed so as to be able to rotate relative to the piston 71 and the driven plate 73. The spring holder 75 is provided on the outer peripheral side support portion 7 disposed on the outer peripheral side of the torsion spring 74.
5a. The radial movement of the spring holder 75 is restricted by the cylindrical portion 72f of the drive plate 72.

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 torque converter, and more particularly to a lock-up device having a disc-shaped piston which can be connected to and separated from a front cover.

[0002]

2. Description of the Related Art Generally, an elastic coupling mechanism absorbs and attenuates torsional vibration transmitted from an input rotary member to an output rotary member while transmitting torque from an input rotary member to an output rotary member. As a structure in which such an elastic connection mechanism is used, for example, a lock-up device disposed inside a torque converter is known.

[0003] A torque converter is a device that has three types of impellers (impeller, turbine, and stator) inside and transmits 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.

The lock-up device is arranged 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 clutch 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.

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.
Also, in the elastic coupling mechanism of the lock-up device, the torsion spring is compressed in the rotational direction between the retaining plate and the driven member to absorb torsional vibration.
Decay.

[0007]

In the lock-up device described above, an outer peripheral cylindrical portion is provided on the outer periphery of the piston,
The load of the torsion spring which tends to move to the outer peripheral side by the centrifugal force is supported by the cylindrical portion.
However, in such a structure, there arises a problem that the weight of the piston increases due to the outer cylindrical portion and a problem that the rigidity of the annular friction coupling portion increases.

An object of the present invention is to make it possible to omit the outer peripheral side cylindrical portion of a conventional piston in a lockup device for a torque converter having a disk-shaped piston.

[0009]

According to a first aspect of the present invention, there is provided a lock-up device for a torque converter which transmits torque and absorbs and attenuates torsional vibration. , An elastic member, a support member, and a restricting portion. The disk-shaped piston is a member for performing a clutch operation. The elastic member is a member for elastically connecting the piston and the output rotary member in the rotational direction. The support member has an outer peripheral side support portion arranged on the outer peripheral side of the elastic member. The support member is arranged to be rotatable relative to the piston and the output rotary member.
The restrictor restricts the radial movement of the support member.

In this lock-up device, the support member supports the outer peripheral side of the elastic member by the outer peripheral side support portion while the movement in the radial direction is restricted by the restricting portion. As described above, by restricting the movement of the elastic member to the outer peripheral side by the support member, the outer peripheral side cylindrical portion of the disc-shaped piston can be omitted.

According to a second aspect of the present invention, in the first aspect, the support member further includes an inner peripheral side support portion disposed on an inner peripheral side of the elastic member. The restricting portion is in contact with the inner peripheral side supporting portion to support the support member in the radial direction.

[0012] In the lockup device for a torque converter according to the third aspect, the restricting portion has an outer peripheral surface in contact with an inner peripheral surface of the inner peripheral side supporting portion. In the lock-up device for a torque converter according to claim 4, in claim 1, the support member further includes an axial support portion extending radially inward from the outer peripheral support portion and supporting one side of the elastic member in the axial direction. ing. The restricting portion is in contact with the axial supporting portion to radially support the support member.

According to a fifth aspect of the present invention, there is provided a lock-up device for a torque converter.
The elastic member comprises a pair of members arranged to act in series in the direction of rotation. The support member further has a torque transmitting portion disposed between the pair of elastic members in the rotation direction.

In this lock-up device, the support member functions as an intermediate float body for the pair of elastic members, and the outer cylindrical portion of the piston can be omitted with a simple structure.

[0015]

DETAILED DESCRIPTION OF THE INVENTION A. 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 to which an embodiment of the present invention is applied. 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. An arrow R1 indicates the driving side of the torque converter 1 in the rotation direction, and an arrow R2 indicates the opposite side.

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 comprising 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. A center boss 16 is provided on the inner peripheral end of the front cover 11.
Are fixed by welding. The center boss 16 is a cylindrical member extending in the axial direction, and is inserted into a center hole of the crankshaft 2.

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 peripheral 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 located in the fluid chamber in the impeller 21.
Are arranged to face each other in the axial direction. Turbine 2
2 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.
It is composed of The turbine shell 30 and the turbine hub 32 are 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 the annular stator shell 3.
5 and a plurality of stator blades 36 provided on the outer peripheral surface of the shell 35. Stator shell 3
5 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.

A 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.

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. A first thrust bearing 41 is arranged between the inner peripheral portion of the front cover 11 and the turbine hub 32 in the axial direction. In a portion where the first thrust bearing 41 is provided, a first port 17 through which hydraulic oil can be communicated in a radial direction is formed. The first port 17 includes an oil passage provided in the input shaft 3, a first hydraulic chamber A (described later), the turbine 22 and the front cover 11.
And in the space between them. A second thrust bearing 42 is provided between the turbine hub 32 and the inner peripheral portion of the stator 23 (specifically, the one-way clutch 37).
Is arranged. 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 is connected to the input shaft 3 and the fixed shaft 39.
And the fluid working chamber 6 are communicated with each other. Further, a third thrust bearing 43 is arranged between the stator 23 (specifically, the shell 35) and the impeller 21 (specifically, the impeller hub 28) in the axial direction. In the portion where the third thrust bearing 43 is disposed, the third port 19 through which hydraulic oil can communicate on both sides in the radial direction.
Are formed. That is, the third port 19 is connected to the oil passage between the fixed shaft 39 and the impeller hub 28,
The fluid working chamber 6 is communicated 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 is disposed in a space between the front cover 11 and the turbine 22 in the axial direction. The lock-up device 7 has a disk shape as a whole, and divides the space 9 substantially in the axial direction. Here, the space between the front cover 11 and the lockup device 7 is referred to as a first hydraulic chamber A, and the space between the lockup device 7 and the turbine 22 is referred to as a second hydraulic chamber B.

The lock-up device 7 has a function of a clutch and an elastic coupling mechanism, and mainly includes a piston 71, a drive plate 72, a driven plate 73, a plurality of torsion springs 74, and a spring holder 75. Have been.

The piston 71 is a member for connecting / disconnecting the clutch, and further functions as an input member in the lock-up device 7 as an elastic connection mechanism. The piston 71 has a disk shape with a center hole formed therein. The piston 71 extends over the entire radius in the space 9 so as to divide the space 9 substantially in the axial direction. On the inner peripheral edge of the piston 71, an inner peripheral side tubular portion 71b extending toward the transmission in the axial direction is formed. The inner peripheral side cylindrical portion 71b is supported by the outer peripheral surface of the turbine hub 32 so as to be movable in the rotation direction and the axial direction. The turbine hub 32
A flange 32a for restricting the movement of the piston 71 toward the transmission in the axial direction by being in contact with the inner peripheral cylindrical portion 71b is formed on the outer peripheral surface of the inner peripheral cylindrical portion 71b. Further, the inner peripheral side cylindrical portion 71b is formed on the outer peripheral surface of the turbine hub 32.
An annular seal ring 32b is provided in contact with the inner peripheral surface of the ring. Thus, the inner peripheral edge of the piston 71 is sealed in the axial direction. Further, a friction coupling portion 71c is formed on the outer peripheral side of the piston 71. The friction coupling portion 71c is an annular portion having a predetermined length in the radial direction, and has a planar shape in which both surfaces in the axial direction are surfaces perpendicular to the axial direction. An annular friction facing 76 is provided on the engine side of the friction connecting portion 71c in the axial direction.
Thus, the clutch of the lockup device 7 is constituted by the piston 71 and the flat friction surface of the front cover 11.

A cylindrical portion extending in the axial direction is not formed on the outer peripheral edge of the piston 71. The drive plate 72 is disposed on the outer peripheral portion of the piston 71 on the axial transmission side. The drive plate 72 is an annular member made of sheet metal. The drive plate 72 includes an annular portion 72a, a torque transmitting portion 72b extending outward from the annular portion 72a, and a connecting portion 72c. The annular portion 72a abuts on the axial transmission side surface of the piston 71,
It is fixed to the piston 71 by a plurality of caulks 71d. The torque transmitting portion 72b extends outward from the annular portion 72a. More specifically, the torque transmission unit 72b
From the inner side to the outer side in the radial direction, it smoothly curves so as to protrude toward the axial transmission side, and then smoothly curves so as to protrude toward the axial engine side, and further forms a cylindrical shape toward the axial transmission side. Extending. The distal ends (outer peripheral ends) of the torque transmitting portions 72b are connected to each other by an annular connecting portion 72c. A plurality of engaging portions 7 are provided on the outer peripheral portion axial direction transmission side of the annular portion 72a.
2e is formed. The engaging portion 72e is a portion that is cut so that both sides in the rotational direction are cut and protruded from the other portion toward the transmission in the axial direction.

Each of the plurality of torque transmitting portions 72b is a spring accommodating portion 72d between the rotation directions. In this embodiment, four spring accommodating portions 72d are formed. A torsion spring 74, which is a coil spring extending in the circumferential direction, is housed in the spring housing 72d. Each spring accommodating portion 72d has a pair of torsion springs 74.
a, 74b are arranged so as to act in series in the rotational direction. That is, a total of eight torsion springs are used. Here, one torsion spring means not only a single coil spring but also a combination of a coil spring and a small coil spring or an elastic body. Further, in each spring accommodating portion 72d, the torsion spring on the rotation direction R1 side is a torsion spring 74a, and the rotation direction R
Replace the torsion spring on the 2 side with the torsion spring 7
4b.

The driven plate 73 is a member for transmitting the torque from the torsion spring 74 to the turbine 22. The driven plate 73 is an annular member made of sheet metal provided on the outer peripheral side of the turbine shell 30 of the turbine 22. The driven plate 73 mainly includes an annular portion 73a.
And a plurality of claws 73b. Annular part 73a
Are fixed to the turbine shell 30 by, for example, welding. The plurality of claws 73b are bent from the outer peripheral edge of the annular portion 73a toward the engine in the axial direction. The pawl 73b corresponds to the torque transmitting portion 72b of the driven plate 72, and is inserted from the axial transmission side into a portion of the torque transmitting portion 72b that is curved so as to project toward the axial engine side. In this manner, the pawl 73b is in contact with both ends in the rotational direction of the pair of torsion springs 74a, 74b arranged in each spring accommodating portion 72d. Also,
A plurality of stopper claws 73c are formed on the driven plate 73. The stopper claw 73c extends from the inner peripheral edge of the annular portion 73a toward the engine in the axial direction. Each stopper claw 73c is arranged between the engaging portions 72e of the drive plate 72. As a result, the relative rotation between the drive plate 72 and the driven plate 73 increases, and when the stopper claw 73c comes into contact with the engaging portion 72e in one of the rotation directions, the compression of the torsion spring 74, that is, the damper operation is stopped.

The spring holder 75 is a member for supporting the torsion spring 74 in the radial direction.
The drive plate 72 and the driven plate 73 are disposed so as to be rotatable relative to each other. The spring holder 75 mainly includes an outer peripheral support 75 a and an inner support 7.
5b and a connecting portion 75c. Connection part 7
Reference numeral 5c denotes a substantially disk-shaped portion, which is disposed in contact with the frictional connection portion 71c of the piston 71 on the transmission side in the axial direction. That is, the connecting portion 75c is disposed between the frictional connecting portion 71c of the piston 71 and the torque transmitting portion 72b of the drive plate 72 in the axial direction. The outer peripheral side support portion 75a is a cylindrical portion extending from the outer peripheral edge of the connecting portion 75c to the transmission side in the axial direction. The outer peripheral side support portion 75a is arranged close to the outer peripheral side of the torsion spring 74. In addition, the outer peripheral side support portion 75a is disposed further outward than the cylindrical portion of the torque transmitting portion 72b. The inner peripheral side support portion 75b is a cylindrical portion extending from the inner peripheral edge of the connecting portion 75c to the transmission side in the axial direction. The inner peripheral side support portion 75b is inserted from the axial direction engine side into a smoothly curved portion of the torque transmitting portion 72b that protrudes toward the axial direction engine side. Further, the inner peripheral side support portion 75 b is close to the inner peripheral side of the torsion spring 74.

As described above, the spring holder 75 has a C-shape or a U-shape in which one side in the axial direction is open in the longitudinal section. The inner peripheral surface of the inner peripheral side support portion 75b is in contact with the outer peripheral surface of the cylindrical portion (slot) 72f formed in the annular portion 72a. As described above, the radial position of the spring holder 75 is determined by the cylindrical portion 72f. In other words, the spring holder 75 is supported by the drive plate 72 as a restricting portion so as to be relatively rotatable and restricted from moving outward in the radial direction. With such a structure, the spring holder 75 can support the load of the torsion spring 74 that moves radially outward due to centrifugal force.

As shown in FIGS. 6 and 7, the spring holder 75 includes first and second torque transmitting portions 75d, 7d.
5e are formed. The first torque transmitting portion 75d is a claw portion in which a part of the inner peripheral side supporting portion 75b is cut and raised outward in the radial direction, and is provided between the pair of torsion springs 74a and 74b in each of the spring receiving portions 72d. Are located in The second torque transmitting portion 75e is formed by being cut and raised so as to protrude toward the engine side in the axial direction formed on the connecting portion 75c corresponding to the first torque transmitting portion 75d. The second torque transmitting portion 75e is connected to each spring housing 7
A pair of torsion springs 74 arranged in 2d
a, 74b are arranged between the rotation directions. Since the spring holder 75 has the torque transmitting portions 75d and 75e for the pair of torsion springs 74a and 74b, the spring holder 75 functions as an intermediate float body. (3) Operation of Torque Converter Immediately after starting the engine, hydraulic oil is supplied into the torque converter 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 through the first hydraulic chamber A to the outer peripheral side, passes through the second hydraulic chamber B, and flows into the fluid operating chamber 6. For this reason, the piston 71 is moved to the engine side in the axial direction due to the hydraulic pressure difference between the first hydraulic chamber A and the second hydraulic chamber B. That is, the friction facing 76 is the front cover 1
1 and the lockup has been released.

When the lock-up is released in this manner, 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 hydraulic oil in the first hydraulic chamber A is discharged from the first port 17. As a result, the first hydraulic chamber A
The piston 71 is moved to the front cover 11 side by the hydraulic pressure difference between the front cover 11 and the second hydraulic chamber B, and the friction facing 76 is pressed against the flat friction surface of the front cover 11. As a result, the torque of the front cover 11 is transmitted from the piston 71 to the driven plate 73 via the drive plate 72 and the torsion spring 74. Further, the torque is transmitted from the driven plate 73 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.

In the lock-up connection state described above, the lock-up device 7 transmits torque and absorbs and attenuates torsional vibration input from the front cover 11. Specifically, when torsional vibration is input from the front cover 11 to the lock-up device 7, the torsion spring 74 is compressed between the drive plate 72 and the driven plate 73 in the rotation direction. More specifically, the torsion spring 74 is
Torque transmitting portion 72b and claw 73 of driven plate 73
b and is compressed in the rotational direction. At this time, the spring holder 75 is moved in the compression direction by the torsion spring 74, and relatively rotates with the drive plate 72 and the driven plate 73.

As described above, when the torsional vibration is input and the torsion spring 74 repeats compression, the torsion spring 74 moves radially outward due to centrifugal force and slides on the outer peripheral side support portion 75 a of the spring holder 75. . However, since the spring holder 75 is a member that moves in the rotational direction together with the torsion spring 74, the sliding resistance between the two members is significantly reduced. Therefore, the torsional vibration absorbing performance is sufficiently maintained. (5) Advantageous effects of the support member a) The spring holder 75 includes the drive plate 72
The outer peripheral side of the torsion spring 74 is supported by the outer peripheral side support portion 75a while the movement in the radial direction is restricted by the cylindrical portion 72f. As described above, by restricting the movement of the torsion spring 74 to the outer peripheral side by the spring holder 75, the outer peripheral side cylindrical portion of the disc-shaped piston 71 can be omitted.

B) The spring holder 75 functions as an intermediate float body for the pair of torsion springs 74a and 74b, and the outer cylindrical portion of the piston can be omitted with a simple structure.

C) The spring holder 75 has a smaller hysteresis than the conventional one because the inner peripheral side support portion 75b is positioned in the radial direction by the drive plate 72. In particular, hysteresis is small since the radial positioning portion is located on the inner peripheral side as compared with the related art. (6) Modification of First Embodiment a) The spring holder 75 in the above-described embodiment may have a structure in which the torque transmitting portions 75d and 75e are not provided. In that case, one torsion spring extending in the circumferential direction is arranged in each spring accommodating portion 72d.

B) By bending the radially intermediate portion of the spring holder 75 toward the transmission side in the axial direction as shown in FIG. 8, only the outer peripheral portion 75f and the inner peripheral portion 75g of the connecting portion 75c are subjected to friction of the piston 71. Connecting part 71
You may make it slide with respect to c. By changing the sliding between the piston 71 and the spring holder 75 from the surface contact to the line contact in this way, it is possible to reduce frictional sliding (hysteresis) between the two.

C) As shown in FIG. 9, the connecting portion 75c may be provided with an annular projecting portion 75h projecting toward the engine in the axial direction. In this case, only the projection 75h is the piston 71
Abuts against the frictional connection portion 71c. Also in this case, since the contact between the piston 71 and the spring holder 75 is changed from the surface contact to the line contact, friction sliding (hysteresis) between the two is reduced. Note that the annular convex portion may be provided on the piston side. B. Second Embodiment (FIGS. 10 to 13) In the second embodiment shown in FIGS. 10 to 13, the basic structure of the torque converter 1 is the same as that of the previous embodiment. The following mainly describes points different from the first embodiment.

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 a disk shape as a whole, and divides the space 9 substantially in the axial direction. Here, the space between the front cover 11 and the lockup device 7 is referred to as a first hydraulic chamber A, and the space between the lockup device 7 and the turbine 22 is referred to as a second hydraulic chamber B.

The lock-up device 7 has a function of a clutch and an elastic coupling mechanism, and is mainly composed of a piston 61, a driven member 63, a plurality of torsion springs 64, and a spring holder 65.

The piston 61 is a member for connecting / disconnecting the clutch, and further functions as an input member in the lock-up device 7 as an elastic connection mechanism. The piston 61 has a disk shape with a center hole formed. The piston 61 extends over the entire radius in the space 9 so as to divide the space 9 substantially in the axial direction. An inner peripheral side cylindrical portion 61b extending toward the transmission in the axial direction is formed on the inner peripheral edge of the piston 61. The inner peripheral side cylindrical portion 61b is supported by the outer peripheral surface of the turbine hub 32 so as to be movable in the rotation direction and the axial direction. The turbine hub 32
A flange 32a for restricting the movement of the piston 61 toward the transmission in the axial direction by contacting the inner cylindrical portion 61b is formed on the outer peripheral surface of the cylindrical member 61b. Further, the outer peripheral surface of the turbine hub 32 has an inner peripheral side cylindrical portion 61b.
An annular seal ring 32b is provided in contact with the inner peripheral surface of the ring. Thus, the inner peripheral edge of the piston 61 is sealed in the axial direction. Further, a friction coupling portion 61c is formed on the outer peripheral side of the piston 61. The friction coupling portion 61c is an annular portion having a predetermined length in the radial direction, and has a planar shape in which both surfaces in the axial direction are surfaces perpendicular to the axial direction. An annular friction facing 66 is stretched on the engine side of the friction connection portion 61c in the axial direction.
Thus, the clutch of the lockup device 7 is constituted by the piston 61 and the flat friction surface of the front cover 11.

The drive member 62 is fixed to the piston 61 and applies torque of the piston 61 to the torsion spring 6.
4 is a member for transmission. The drive member 62 is
As shown in FIG. 13, an annular fixing portion 62a and a fixing portion 6
A plurality of claw portions 62b extending radially outward from 2a, and a plurality of arc-shaped portions 62 extending radially outward from the fixed portion 62a
c. The fixing portion 62a is
1 and is fixed by a plurality of caulks 61f. Each claw portion 62b extends radially outward, curves so as to protrude toward the engine in the axial direction, and further extends toward the transmission in the axial direction. In this embodiment, a total of four claw portions 62b are formed. Note that the curved portion of the claw portion 62b is a frictional connection portion 61c of the piston 61.
Is in contact with

The arc-shaped portion 62c is formed between the claw portions 62b in the rotation direction, and extends long in an arc along the outer periphery of the fixed portion 62a. The arc-shaped portion 62c extends outward in the radial direction and is inclined as a whole toward the transmission in the axial direction. The arc-shaped portion 62c includes a first portion 62d, a second portion 62e, and a third portion 62f from the inside in the radial direction to the outside. The first portion 62d is entirely formed between the claws 62b in the rotation direction. The second portion 62e is a portion extending further outward from the first portion 62d. The second portion 62e is the first portion 62
The length of the first portion 62d in the rotation direction is shorter than that of the first portion 62d. Therefore, the second portion 62e is
It has an end face in the rotation direction separated from the claw portion 62b in the rotation direction. The third portion 62f is a portion extending further outward from the second portion 62e. The third portion 62f is the second portion 62
The length of the second portion 62e in the rotation direction is shorter than that of the second portion 62e in the rotation direction. The third portion 62f is a portion for supporting a spring holder 65 (described later) in a radial direction and an axial direction.

An arc-shaped spring accommodating portion is provided between the claws 62b of the drive member 62 in the rotation direction, that is, on the outer peripheral side of the arc-shaped portion 62c. In this embodiment, four spring housings are formed.

A pair of torsion springs 64a, 64 is provided between the respective spring accommodating portions, ie, between the claws 62b in the rotational direction.
b are arranged to act in series in the direction of rotation.
That is, a total of eight torsion springs 64 are provided.
Is used. Here, the torsion spring is a coil spring extending in the rotation direction, but may include not only a single coil spring but also a combination of a small coil spring and an elastic body in the coil spring. Also, in each spring housing,
The one in the rotation direction R1 is referred to as a torsion spring 64a, and the one in the rotation direction R2 is referred to as a torsion spring 64a.
b. The claw portion 62b is provided with a torsion spring 64a.
Abuts or approaches the R1 side end of the torsion spring 6
4b is in contact with or close to the R2 side end.

The spring holder 65 is assembled to the drive member 62, and the piston 61 and the drive member 62
And the driven member 63 can be relatively rotated. The spring holder 65 is an annular sheet metal member, and is disposed on the axial transmission side of the outer peripheral edge of the friction coupling portion 61c of the piston 61. The spring holder 65 is mainly composed of a cylindrical portion 65a and an annular portion 65 extending radially inward from the end of the transmission in the axial direction.
b. The cylindrical portion 65 a is arranged on the outer peripheral side of the torsion spring 64. Annular part 65b
Has an outer peripheral portion and an inner peripheral portion pressed down from the outer peripheral portion toward the engine side by press working. Annular part 65b
An inner peripheral surface 65g is formed at the boundary between the outer peripheral portion and the inner peripheral portion. The inner peripheral surface 65 g is provided on the third portion 62 of the drive member 62.
f is in contact with the outer peripheral surface. By this contact, the spring holder 65 moves the drive member 62 and the piston 61
Are positioned in the radial direction. Since the spigot portion of the radial support portion is formed by the press fracture surface, it is easy to form. Further, the inner peripheral portion of the annular portion 65b is located on the engine side in the axial direction of the third portion 62f of the drive member 62. With this structure, the spring holder 65 is prevented from coming off the drive member 62 and the piston 61 toward the transmission in the axial direction.

A plurality of claw portions 65c are formed on the inner peripheral edge of the annular portion 65b of the spring holder 65. Claw part 6
5c are formed in a row in the rotation direction, and extend toward the engine in the axial direction. The claw portion 65c is formed corresponding to the third portion 62f of the drive member 62, that is, at an intermediate position in the rotation direction between the claw portions 62b. The claw portion 65c extends between the pair of torsion springs 64a and 64b, and functions as a torque transmitting portion for connecting the two in the rotational direction. Note that the tip of the claw portion 65c is close to the curved portion of the claw portion 62b of the drive member 62, so that the spring holder 65 separates the drive member 62 and the piston 6
1 is restricted from moving toward the transmission in the axial direction.

As described above, the spring holder 65 is guided by the drive member 62 (in a state where it is immovably engaged in the radial and axial directions).
It can be moved in the rotation direction. In other words, the spring holder 65 holds the drive member 6
The support 2 is provided so as to be relatively rotatable and restricted from moving outward in the radial direction. With such a structure, the spring holder 65 can support the load of the torsion spring 64 that moves radially outward due to centrifugal force. Therefore, it is necessary to provide a cylindrical portion for receiving the spring on the outer peripheral edge of the piston 61. There is no.

The annular portion 6 of the spring holder 65
5b includes a claw portion 62b of the drive member 62 at the time of assembly.
Are formed with a plurality of notches 65d for penetrating through. A protruding portion 65e that protrudes in the axial direction from the other portion is formed at an axial end of the cylindrical portion 65a corresponding to the cutout 65d on the engine side in the axial direction. Projection 65
"e" is a structure for maintaining the balance in the rotational direction by compensating for the decrease in rigidity due to the notch 65d. A notch 6 is formed in the end of the cylindrical portion 65a in the axial direction corresponding to the claw portion 65c.
5f is formed. The notch 65f is a structure for maintaining the balance in the rotation direction by compensating for the increase in rigidity due to the claw portion 65c.

The driven member 63 is a member for transmitting the torque from the torsion spring 64 to the turbine 22. The driven member 63 is an annular member made of sheet metal provided on the outer peripheral side of the turbine shell 30 of the turbine 22. The driven member 63 has an annular fixing portion 63a fixed to the turbine shell 30 and a plurality of claws 63b extending from the outer peripheral edge toward the engine in the axial direction. The claw portion 63 b of the driven member 63 is
2b, and extends into the curved portion of the claw 62b. The claw portion 63b has a rotation direction width equivalent to that of the claw portion 62b of the drive member 62.
Similarly, the rotation direction R1 of the torsion spring 64a
It is in contact with or close to the side end and the end in the rotation direction R2 of the torsion spring 64b.

The claw portion 63b is movable in the axial direction with respect to the drive member 62. That is, the piston 61 can move in the axial direction by a change in hydraulic pressure while maintaining the state of being engaged with the torsion spring 64.

The claw portion 63b is located at an intermediate position in the rotation direction between the second portions 62e of the drive member 62, and
e is separated from the end face in the rotation direction by a predetermined angle in the rotation direction.
The driven member 63 can rotate relative to the drive member 62 until the claw portion 63b comes into contact with the end face in the rotation direction of the second portion 62e. In other words, the drive member 62
The second portion 62e and the claw portion 63b of the driven member 63 form a stopper mechanism for stopping the relative rotation between the two. As described above, the claw portion 63b has a function of a torque transmitting portion by engaging with the torsion spring 64, and also constitutes a part of a stopper mechanism of the elastic connecting portion. Therefore, it is not necessary to provide a special structure for the stopper mechanism. (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 hydraulic oil in the first hydraulic chamber A is discharged from the first port 17. As a result, the first hydraulic chamber A
The piston 61 is moved to the front cover 11 side by the hydraulic pressure difference between the front cover 11 and the second hydraulic chamber B, and the friction facing 66 is pressed against the flat friction surface of the front cover 11. As a result, the torque of the front cover 11 is transmitted from the piston 61 to the driven member 63 via the torsion spring 64. Further, the torque is transmitted from the driven member 63 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.

In the lock-up connection state described above, the lock-up device 7 transmits torque and absorbs and attenuates torsional vibration input from the front cover 11. Specifically, when torsional vibration is input from the front cover 11 to the lock-up device 7, the torsion spring 64 is compressed in the rotation direction between the piston 61 and the driven member 63. More specifically, the torsion spring 64 is compressed in the rotational direction between the claw 62b of the drive member 62 and the claw 63b of the driven member 63. At this time, the pair of torsion springs 64a, 6
Since 4b acts in series in the rotational direction, torsional characteristics with low rigidity and a wide torsion angle can be obtained.

As described above, when the torsional vibration is input and the torsion spring 64 repeats compression, the torsion spring 64 moves radially outward due to centrifugal force and slides on the spring holder 65. However, since the spring holder 65 is a member that moves in the rotation direction together with the torsion spring 64, the sliding resistance between the two members is extremely small. Therefore, the torsional vibration absorbing performance is sufficiently maintained. (5) Advantageous Effects of the Present Invention a) The spring holder 65 supports the outer peripheral side of the torsion spring 64 with the cylindrical portion 65a while being restricted from moving in the radial direction by the arc portion 62c of the drive member 62. Thus, the spring holder 65
By restricting the movement of the torsion spring 64 to the outer periphery, the outer cylindrical portion of the disc-shaped piston 61 can be omitted.

B) The spring holder 65 functions as an intermediate float body for the pair of torsion springs 64a and 64b, and the outer cylindrical portion of the piston can be omitted with a simple structure.

C) In the lock-up device 7, the structure is simplified, the number of parts is reduced, and the cost and weight can be reduced. In particular, the simplification of the structure of the spring holder 65 has reduced the weight and the number of equipment development steps.

In particular, since the drive member 62 has only the function of transmitting torque and does not have the function of holding the torsion spring, the structure is simplified and the weight and thickness can be reduced.

D) Since the spring holder 65 supports only the transmission side of the torsion spring 64 in the axial direction, the torsion spring 64 is in direct contact with the piston 61. As a result, the coil diameter of the torsion spring 64 can be made sufficiently large, and the design for realizing low rigidity becomes easy.

E) Further, since the spring holder 65, the torsion spring 64, and the driven member 63 can be arranged in an extra space between the outer periphery of the piston 61 and the outer periphery of the turbine 22, space efficiency is improved. That is, the axial dimension of the torque converter does not become extremely large due to these members. C. Other Embodiments The structure of the lockup device is not limited to the above embodiment. For example, the present invention can be applied to a lockup device for a double-plate clutch in which a plurality of plates are arranged between a piston and a front cover.

[0062]

In the lock-up device according to the present invention, the outer peripheral side cylindrical portion of the disc-shaped piston can be omitted by limiting the movement of the elastic member to the outer peripheral side by the support member.

[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, and is a sectional view taken along line II-II of FIG.

FIG. 3 is a partial plan view of an elastic coupling mechanism of the lockup device.

FIG. 4 is a perspective view of each member of the lock-up device.

FIG. 5 is a sectional view taken along line VV of FIG. 3;

FIG. 6 is a sectional view taken along line VI-VI of FIG. 3;

FIG. 7 is a partial perspective view of a spring holder.

FIG. 8 is a partial cross-sectional view of a lockup device according to another embodiment.

FIG. 9 is a partial cross-sectional view of a lockup device according to another embodiment.

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

FIG. 11 is a partially enlarged view of FIG. 10;

FIG. 12 is a view corresponding to FIG. 11, and a cross-sectional view at a different position from FIG. 11;

FIG. 13 is a partial perspective view of an elastic connecting portion of the lock-up device according to the second embodiment.

[Explanation of symbols]

 7 Lock-up device 11 Front cover 61 Piston 72 Drive plate 73 Driven plate (output rotating member) 74 Torsion spring (elastic member) 75 Spring holder (support member)

Claims (5)

[Claims]
1. A lock-up device for a torque converter for transmitting torque and absorbing / damping torsional vibration, comprising: a disk-shaped piston for performing a clutch operation; an output rotating member; An elastic member for elastically connecting the piston and the output rotating member in the rotational direction; and an outer peripheral side support portion disposed on the outer peripheral side of the elastic member. A support member disposed so as to be relatively rotatable, and a restricting portion that restricts radial movement of the support member;
Lockup device for torque converter with
2. The support member further includes an inner peripheral side support portion disposed on an inner peripheral side of the elastic member, and the restricting portion abuts on the inner peripheral side support portion to make the support member have a radius. The lock-up device for a torque converter according to claim 1, wherein the lock-up device is supported in a direction.
3. The torque converter lock-up device according to claim 2, wherein said limiting portion has an outer peripheral surface which abuts on an inner peripheral surface of said inner peripheral side supporting portion.
4. The support member further includes an axial support portion extending radially inward from the outer peripheral side support portion and supporting one side of the elastic member in the axial direction, wherein the restricting portion includes the axial support portion. The lock-up device for a torque converter according to claim 1, wherein the support member is supported in a radial direction by contacting the support member.
5. The elastic member comprises a pair of members arranged so as to act in series in the rotational direction, and the support member includes a torque transmitting portion disposed between the pair of members in the rotational direction. The torque converter lock-up device according to claim 1, further comprising:
JP2000262583A 2000-05-26 2000-08-31 Torque converter lockup device Active JP3717772B2 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2000-155613 2000-05-26
JP2000155613 2000-05-26
JP2000262583A JP3717772B2 (en) 2000-05-26 2000-08-31 Torque converter lockup device

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2000262583A JP3717772B2 (en) 2000-05-26 2000-08-31 Torque converter lockup device
DE10123615.8A DE10123615B4 (en) 2000-05-26 2001-05-15 Torque converter with lockup clutch
US09/855,537 US6571929B2 (en) 2000-05-26 2001-05-16 Torque converter with lockup device
KR1020010029010A KR20010107762A (en) 2000-05-26 2001-05-25 Torque converter with lockup device

Publications (2)

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JP2002048217A true JP2002048217A (en) 2002-02-15
JP3717772B2 JP3717772B2 (en) 2005-11-16

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Country Link
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JP2006037974A (en) * 2004-07-22 2006-02-09 Aisin Aw Industries Co Ltd Intermediate member for connecting damper spring of lockup damper in series
JP2007132522A (en) * 2006-12-28 2007-05-31 Exedy Corp Lockup device of fluid type torque transmission device
JP2009002358A (en) * 2007-06-19 2009-01-08 Valeo Unisia Transmission Kk Torsional vibration reducing device
JP2009068707A (en) * 2007-09-10 2009-04-02 Luk Lamellen & Kupplungsbau Beteiligungs Kg Torsional vibration damper
JP2009168226A (en) * 2008-01-18 2009-07-30 Exedy Corp Lock-up device
WO2011024640A1 (en) * 2009-08-26 2011-03-03 株式会社エクセディ Lockup device for torque converter
WO2011070852A1 (en) * 2009-12-09 2011-06-16 株式会社エクセディ Torque converter
WO2012147404A1 (en) * 2011-04-28 2012-11-01 株式会社エクセディ Lock-up apparatus for torque converter
KR20130040747A (en) * 2011-10-15 2013-04-24 유니프레스 가부시키가이샤 Vibration damping apparatus
WO2014126245A1 (en) * 2013-02-18 2014-08-21 株式会社エフ・シ-・シ- Torque damper device
JP2014219056A (en) * 2013-05-08 2014-11-20 株式会社エクセディ Lockup device for torque converter
WO2015079901A1 (en) * 2013-11-28 2015-06-04 株式会社エフ・シー・シー Lock-up device and torque converter
JP2016156416A (en) * 2015-02-24 2016-09-01 ヴァレオユニシアトランスミッション株式会社 Torsional vibration reduction device

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JP2006037974A (en) * 2004-07-22 2006-02-09 Aisin Aw Industries Co Ltd Intermediate member for connecting damper spring of lockup damper in series
JP4648664B2 (en) * 2004-07-22 2011-03-09 アイシン・エィ・ダブリュ工業株式会社 Intermediate member that connects the damper springs of the lockup damper in series
JP2007132522A (en) * 2006-12-28 2007-05-31 Exedy Corp Lockup device of fluid type torque transmission device
JP2009002358A (en) * 2007-06-19 2009-01-08 Valeo Unisia Transmission Kk Torsional vibration reducing device
JP2009068707A (en) * 2007-09-10 2009-04-02 Luk Lamellen & Kupplungsbau Beteiligungs Kg Torsional vibration damper
JP2009168226A (en) * 2008-01-18 2009-07-30 Exedy Corp Lock-up device
US8240442B2 (en) 2008-01-18 2012-08-14 Exedy Corporation Lock-up device
JP2011047442A (en) * 2009-08-26 2011-03-10 Exedy Corp Lockup device for torque converter
US8746425B2 (en) 2009-08-26 2014-06-10 Exedy Corporation Torque converter lock-up device
US9163677B2 (en) 2009-08-26 2015-10-20 Exedy Corporation Torque converter lock-up device
CN102472378A (en) * 2009-08-26 2012-05-23 株式会社艾科赛迪 Lockup device for torque converter
WO2011024640A1 (en) * 2009-08-26 2011-03-03 株式会社エクセディ Lockup device for torque converter
KR101348328B1 (en) 2009-08-26 2014-01-08 가부시키가이샤 에쿠세디 Lockup device for torque converter
JP2011122622A (en) * 2009-12-09 2011-06-23 Exedy Corp Lock-up device for torque converter
WO2011070852A1 (en) * 2009-12-09 2011-06-16 株式会社エクセディ Torque converter
US9702445B2 (en) 2009-12-09 2017-07-11 Exedy Corporation Torque converter
JP2012237441A (en) * 2011-04-28 2012-12-06 Exedy Corp Lock-up apparatus for torque converter
WO2012147404A1 (en) * 2011-04-28 2012-11-01 株式会社エクセディ Lock-up apparatus for torque converter
US9051977B2 (en) 2011-04-28 2015-06-09 Exedy Corporation Lock-up device for torque converter
KR101648240B1 (en) * 2011-10-15 2016-08-12 쟈트코 가부시키가이샤 Vibration damping apparatus
KR20130040747A (en) * 2011-10-15 2013-04-24 유니프레스 가부시키가이샤 Vibration damping apparatus
US9677642B2 (en) 2013-02-18 2017-06-13 Kabushiki Kaisha F.C.C. Torque damper apparatus
WO2014126245A1 (en) * 2013-02-18 2014-08-21 株式会社エフ・シ-・シ- Torque damper device
JP2014156923A (en) * 2013-02-18 2014-08-28 F C C:Kk Torque damper
JP2014219056A (en) * 2013-05-08 2014-11-20 株式会社エクセディ Lockup device for torque converter
WO2015079901A1 (en) * 2013-11-28 2015-06-04 株式会社エフ・シー・シー Lock-up device and torque converter
JP2015102231A (en) * 2013-11-28 2015-06-04 株式会社エフ・シー・シー Lock-up device and torque converter
JP2016156416A (en) * 2015-02-24 2016-09-01 ヴァレオユニシアトランスミッション株式会社 Torsional vibration reduction device

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