JP2001295889A - Elastic coupling device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To maintain durability while materializing a wide twisting angle in an elastic coupling device. SOLUTION: A damper mechanism 45 is a device to transmit torque and absorb twisting vibration, and is equipped with a driving member 52, plural torsion springs 54, a floating body 55 and a driven member 53. The driving member 52 has a ring-shaped part 52a and plural nails 52b extending inward from the ring-shaped part 52a in its radial direction. The plural torsion springs 54 are disposed between a pair of plural nails 52b. The floating body 55 is disposed between the rotational directions of the plural torsion springs 54. The driven member 53 has supporting members 56a, 57a to support the rotational direction end of the plural torsion springs 54.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to an elastic coupling device, and more particularly to an elastic coupling device for transmitting torque and absorbing torsional vibration.

[0002]

2. Description of the Related Art A lock-up device for a torque converter will be described as an example of an elastic connecting device.
The torque converter is a device that has a torus (impeller, turbine, and stator) composed of three types of impellers, and transmits power using fluid inside the torus. Such a torque converter is provided with a lock-up device in a space between the front cover and the torus. The lockup device is a device for mechanically transmitting the torque of the front cover to the transmission side. The lock-up device includes a clutch connecting portion and an elastic connecting mechanism. The clutch connecting portion is connected to or released from the front cover by a change in hydraulic pressure in the torque converter. The elastic connecting device is composed of, for example, a plurality of torsion springs. The torsion spring has a function of absorbing and attenuating torsional vibration when the lock-up device is connected.

[0003] In general, it is desired that the elastic coupling device realize a wider torsion angle and a lower rigidity in order to enhance the vibration absorbing performance. Therefore, a torsion spring which is long in the circumferential direction is used, or a plurality of springs are arranged so as to act in series in the circumferential direction. Here, in a structure in which a plurality of springs are arranged in series in the circumferential direction, an intermediate body (float member) is arranged between adjacent springs to support the ends of the springs.

[0004]

In the conventional elastic coupling device, the output member comprises a cylindrical boss, and has a plurality of claws extending radially outward therefrom. The plurality of claws support both circumferential ends of the springs arranged in series.
Further, the intermediate body has an annular portion disposed on the outer peripheral side of the spring, and a support portion extending radially inward therefrom and inserted between the springs.

In the structure described above, the pawl for supporting the load of the spring extends outward in the radial direction.
It is relatively difficult to maintain nail strength. That is, in order to sufficiently maintain the strength of the nail, it is necessary to ensure a sufficient width in the circumferential direction of the nail. This means that the free length of the spring to be arranged is shortened, and thus the torsion angle as the elastic coupling device is shortened. As described above, in the above-described structure, the problem of the strength of the nail and the favorable torsional characteristics are not compatible.

It is an object of the present invention to realize a wide torsion angle while maintaining durability in an elastic coupling device.

[0007]

According to a first aspect of the present invention, there is provided an elastic coupling device for transmitting a torque and absorbing a torsional vibration, comprising a first rotating member, a plurality of elastic members, and an intermediate member. And a second rotating member. The first rotating member has an annular portion and a plurality of claws extending radially inward from the annular portion. The plurality of elastic members are arranged between a pair of the plurality of claws. The intermediate member is disposed between the rotation directions of the plurality of elastic members. The second rotating member has a support for supporting the ends of the plurality of elastic members in the rotation direction.

[0008] In this elastic coupling device, the pawl of the first rotating member extends radially inward from the annular portion, so that sufficient strength can be maintained. Therefore, the circumferential length of the elastic member can be secured longer than before by reducing the circumferential width of the claw. In the elastic connecting device according to the second aspect, in the first aspect, the intermediate body is disposed at the same axial position as the first rotating member.

In this elastic coupling device, the axial dimension of the elastic coupling device can be sufficiently reduced. In the elastic connecting device according to the third aspect, in the first or second aspect, the intermediate body includes an annular connecting portion disposed on an inner peripheral side of the annular portion, and a plurality of elastic members extending radially outward from the annular connecting portion. And an elastic member supporting portion disposed between the rotation directions of the member. In this elastic connecting device, since the elastic member supporting portions are integrally connected by the annular connecting portion, each elastic member supporting portion does not move outward in the radial direction.

According to a fourth aspect of the present invention, in the first or second aspect, the intermediate member includes a plurality of intermediate members, each of the intermediate members having an arc-shaped portion disposed on the inner peripheral side of the annular portion. And an elastic member supporting portion extending radially outward from the arc portion and disposed between the plurality of elastic members in the rotation direction. In this elastic connection device, the intermediate body is composed of a plurality of members, so that the production is easy.

In the elastic connecting device according to the fifth aspect, in any one of the first to fourth aspects, the second rotating member comprises a pair of members arranged on both axial sides of the first rotating member and the intermediate member. .

[0012]

DESCRIPTION OF THE PREFERRED EMBODIMENTS First Embodiment Structure FIG. 1 is a schematic longitudinal sectional view of a torque converter 1 in which one embodiment of the present invention is adopted. The torque converter 1 is a device for transmitting torque from a crankshaft 2 of an engine to an input shaft (not shown) 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. The OO line shown in FIG.
The arrow R1 in FIG.
Is the direction of rotation.

The torque converter 1 mainly includes a flexible plate 4 and a torque converter body 5. The flexible plate 4 is a member made of a thin disk-shaped plate, and is a member that transmits torque and absorbs bending vibration input to the torque converter 1 from the crankshaft 2 side. The torque converter body 5 is
The torus 6 includes three types of impellers (the impeller 18, the turbine 19, and the stator 20), and a lockup device 7.

The front cover 14 is a disk-shaped member, and is disposed close to the flexible plate 4. A center boss 15 is provided on the inner periphery of the front cover 14.
Are fixed by welding. The center boss 15 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 crankshaft 2 by a plurality of bolts 10. On the outer peripheral side of the front cover 14 and on the engine side, a plurality of nuts 11 are arranged at equal intervals in the circumferential direction.
Has been fixed. A bolt 12 screwed into the nut 11 fixes the outer peripheral portion of the flexible plate 4 to the front cover 14. An annular ring gear member 13 is fixed to an outer peripheral portion of the flexible plate 4.

On the outer peripheral portion of the front cover 14, an outer peripheral cylindrical portion 16 extending toward the transmission in the axial direction is formed. An impeller 18 is attached to the tip of the outer cylindrical portion 16.
The outer peripheral edge of the impeller shell 22 is fixed by welding. As a result, the front cover 14 and the impeller 18
However, a fluid chamber filled with hydraulic oil (fluid) is formed therein. The impeller 18 mainly includes the impeller shell 2
2, a plurality of impeller blades 23 fixed inside the impeller shell 22, and an impeller hub 24 fixed to the inner periphery of the impeller shell 22.

The turbine 19 has an impeller 18 in a fluid chamber.
And are arranged to face each other in the axial direction. The turbine 19
Mainly, a turbine shell 25 and a plurality of turbine blades 2 fixed to a surface of the turbine shell 25 on the impeller side.
6 is comprised. The inner peripheral portion of the turbine shell 25 is fixed to a flange of the turbine hub 27 by a plurality of rivets 28.

The turbine hub 27 is non-rotatably connected to a transmission input shaft (not shown). The stator 20 is connected to the impeller 18 from the turbine 19.
This is a mechanism for rectifying the flow of the hydraulic oil returning to. The stator 20 is an integral member manufactured by casting a resin, an aluminum alloy, or the like. Stator 20 is arranged between the inner circumference of impeller 18 and the inner circumference of turbine 19. The stator 20 mainly includes an annular carrier 29 and a plurality of stator blades 30 provided on an outer peripheral surface of the carrier 29.
It is composed of The carrier 29 is supported on a fixed shaft (not shown) via a one-way clutch 35.

Next, the lock-up device 7 will be described. The lockup device 7 mainly includes a piston member 44 and a damper mechanism 45 (elastic coupling device). The piston member 44 is a disk-shaped member disposed close to the front cover 14 on the engine side in the axial direction. An inner peripheral cylindrical portion 48 extending toward the transmission in the axial direction is formed on an inner peripheral portion of the piston member 44. The inner peripheral cylindrical portion 48 is supported on the outer peripheral surface of the turbine hub 27 so as to be relatively rotatable and movable in the axial direction. In addition, the inner peripheral cylindrical portion 48
Of the transmission in the axial direction is a turbine hub 27.
The movement toward the transmission in the axial direction is restricted to a predetermined position by abutting the flange portion of the transmission. A seal ring 49 is disposed on the outer peripheral surface of the turbine hub 27, and the seal ring 49 seals an axial space at an inner peripheral portion of the piston member 44.

The outer peripheral portion of the piston member 44 functions as a clutch connecting portion. An annular friction facing 46 is fixed to the outer peripheral portion of the piston member 44 on the engine side. The friction facing 46 is attached to the front cover 14.
Opposes an annular and flat friction surface formed on the inner surface of the outer peripheral portion. A plurality of projections 47 extending toward the transmission in the axial direction are formed on the outer peripheral portion of the piston member 44.

The damper mechanism 45 includes a drive member 52
(First rotating member), driven member 53 (second rotating member), and a plurality of torsion springs 54 (elastic member)
It is composed of The drive member 52 is an annular plate member. The drive member 52 includes an annular portion 52a.
And a plurality of (four in this embodiment) claws 52b extending inward therefrom. A notch 60 is formed on the outer peripheral edge of the annular portion 52a so as to correspond to the protrusion 47. The protrusions 47 are in contact with both circumferential ends of the notch 60, and the engagement allows the piston member 44 to rotate integrally with the drive member 52 but to be movable in the axial direction. A plurality of elongated holes 61 extending in the circumferential direction are formed near the radial center of the annular portion 52a. The claw 52b has a planar shape in a wedge shape or a triangular shape in which the width in the circumferential direction becomes narrower from the outside in the radial direction to the inside.

The driven member 53 comprises a pair of plate members 56 and 57 arranged side by side in the axial direction. The plate member 56 is disposed on the engine side of the drive member 52, and the plate member 57 is disposed on the transmission side of the drive member 52. Plate members 56 and 57
Although the outer peripheral portions are separated in the axial direction with the drive member 52 and the float body 55 interposed therebetween, the inner peripheral portions are in contact with each other. The outer peripheral portions of the pair of plate members 56 and 57 are fixed by a plurality of rivets 59. The rivet 59 passes through the long hole 61 of the drive member 52 and is movable in the circumferential direction. When the rivet 59 comes into contact with the circumferential end of the elongated hole 61, the relative rotation between the drive member 52 and the driven member 53 is stopped. However, the stopper mechanism may be configured by another structure. In the plate member 56, a tubular portion 63 that connects the outer peripheral portion and the inner peripheral portion is formed at a radially intermediate portion. A gap is provided in the radial direction between the cylindrical portion 63 and the tip of the claw 52b. Each plate member 56, 57
A plurality of first and second support portions 56a and 57a arranged in the circumferential direction are formed on the inner peripheral portion. The first and second support portions 56a, 57a are provided with a torsion spring 5 described later.
4 is a structure for accommodating and supporting 4 and, more specifically, cut-and-raised portions on both sides in the radial direction cut and raised in the axial direction. The first and second support portions 56a, 57a
It corresponds to the space between b. The inner peripheral ends of the plate members 56 and 57 are connected to the turbine hub 27 by the rivets 28 described above.
Is fixed to the flange.

The plurality of torsion springs 54 include pawls 52.
b, and housed in the first and second support portions 56a and 57a. Space between each claw 52b and first and second
Two torsion springs 54 are arranged in the support portions 56a and 57a. Each torsion spring 5
Numeral 4 is a coil spring extending in the circumferential direction, and both ends on the outer side in the circumferential direction are each claw 52b and the first and second support portions 56.
a, 57a are supported at circumferential ends. Further, the torsion spring 54 is connected to the first and second support portions 56.
The movement in the axial direction is restricted by the cut-and-raised portions a and 57a.

The float body 55 is an annular plate member, which is on the inner peripheral side of the drive member 52 and the plate member 5.
It is arranged between 6, 57 axial directions. Float 55
Are arranged at the same axial position as the drive member 52, and have the same thickness as the drive section seat 52. Float 55
Is composed of an annular connecting portion 55a and a plurality of spring receiving portions 55b (elastic member supporting portions). Annular connecting portion 55
a is the cylindrical portion 63, the torsion spring 54 and the claw 52
and b. Annular connecting portion 55a
A radial gap is secured between the outer peripheral surface of the claw 52b and the inner peripheral surface of the claw 52b.

Further, the inner peripheral surface of the annular connecting portion 55a is rotatably supported by the outer peripheral surface of the cylindrical portion 63. In this way, the float body 55 is supported in the radial direction by the driven member 53, and the outward movement in the radial direction is restricted. Each spring receiving portion 55b is disposed between a pair of torsion springs 54 arranged in the circumferential direction,
The two torsion springs 54 are in contact with and support the circumferential ends. The spring receiving portion 55b has a fan shape or a triangular shape in which the planar shape increases in the circumferential direction as going from the inside to the outside in the radial direction. An outer peripheral edge of the spring receiving portion 55b secures a gap in a radial direction with an inner peripheral edge of the annular portion 52a of the drive member 52. For this reason, even if the float body 55 rotates relative to the drive member 52, no sliding resistance occurs between them. Further, locking claws 55c extending outward in the circumferential direction are formed at both circumferential ends of the outer peripheral portion of the spring receiving portion 55b. The locking claw 55c abuts on the outer peripheral portion at the circumferential end of each torsion spring 54 to prevent them from moving to the outer peripheral side.

Operation When torque is transmitted from the engine (not shown) to the crankshaft 2, the torque is transmitted to the front cover 14 and the impeller 18 via the flexible plate 4.
The hydraulic oil driven by the impeller blades 23 of the impeller 18 rotates the turbine 19. The torque of the turbine 19 is output to an input shaft (not shown) via the turbine hub 27. The hydraulic oil flowing from the turbine 19 to the impeller 18 flows through the stator 20 to the impeller 18 side.

When the hydraulic oil in the space between the front cover 14 and the piston member 44 is drained from the inner peripheral side, the piston member 44 moves to the front cover 14 due to a difference in hydraulic pressure, and the friction facings 46 of the front cover 14 Pressed against the friction surface. As a result, the front cover 14
, The torque is transmitted to the turbine hub 27 via the lock-up device 7.

In the damper mechanism 45 of the lock-up device 7, the torque from the drive member 52 is transmitted to the driven member 53 via the torsion spring 54. When the torque fluctuation from the engine is input, the torsion spring 54 is compressed in the rotation direction, and the drive member 52 and the driven member 53 rotate relatively. At this time, the pair of torsion springs 54 operate in series via the spring receiving portion 55b of the float body 55 therebetween.

Effect (1) Since the claws 52b of the drive member 52 extend radially inward from the annular portion 52a, sufficient strength can be maintained. Therefore, by shortening the circumferential width of the claw 52b, the circumferential length of the torsion spring 54 can be secured longer than before. (2) Since the float 55 and the drive member 52 are arranged at the same axial position, the axial dimension of the damper mechanism 45 can be sufficiently reduced. (3) Since the spring receiving portions 55b are integrally connected by the annular connecting portion 55a in the float body 55, the spring receiving portions 55b are not moved outward in the radial direction. Therefore, sliding with other members hardly occurs. Further, since the movement of the float body 55 in the radial direction is regulated by the driven member 53, the float body 55 does not easily slide on the drive member 52. Second Embodiment Structure The basic structure of the present embodiment is the same as that of the above-described embodiment, and only different points will be described here.

In this embodiment, the float is composed of a plurality of divided movable elements 72. In other words, each one
One armature 7 for a pair of torsion springs 54
2 are provided. Each mover 72 is, for example, a member formed by bending a sheet metal, and includes an arc portion 72a and a spring receiving portion 72b extending radially outward from the arc portion 72a. More specifically, the mover 72 is formed by bending a strip-shaped elongated plate having a predetermined width in one axial direction to form the arc-shaped portion 7.
2a and a spring receiving portion 72b, a portion 81 constituting a half of the arc-shaped portion 72a, a wall portion 82 on one side in the circumferential direction of the spring receiving portion 72b, and an outer periphery of the spring receiving portion 72b from one side in the circumferential direction. A wall portion 83 on the side, a wall portion 84 on the opposite side in the circumferential direction of the spring receiving portion 72b, and a portion 85 constituting the other half of the arc-shaped portion 72a are formed continuously. Arc 72
a secures a gap in the radial direction between the drive member 52 and the claw 52b even when the drive member 52 moves in the rotational direction. The inner peripheral surface of the arc-shaped portion 72a is the driven member 53
Is supported by the outer peripheral surface of the cylindrical portion 63. Also,
As described above, the spring receiving portion 72b is constituted by the wall portions 82 and 84 on both sides in the circumferential direction and the wall portion 83 on the outer peripheral side. Close. As a result, the spring receiving portion 72
b has a fan shape or a triangular shape in which the width in the circumferential direction increases from the inside to the outside in the radial direction. Further, locking claws 86 extending outward in the circumferential direction are formed at both circumferential ends of the outer peripheral portion of the spring receiving portion 72b. The locking claw 86 abuts on the outer peripheral portion at the circumferential end of each torsion spring 54 to prevent them from moving to the outer peripheral side.

An annular projection 74 is formed on the inner peripheral wall surface of the annular portion 52a at an intermediate position in the axial direction so as to extend annularly. As shown in FIG. 6, an annular groove 75 into which an annular projection 74 fits is formed on the outer peripheral wall of the spring receiving portion 72b. By this engagement, the float body 71 is guided by the drive member 52 and moves in the rotational direction. Therefore, the float body 71 is not easily moved in the axial direction, and the posture of the float body 71 is easily maintained normally.

Further, in this embodiment, the rivets 59 in the above embodiment are omitted. Instead, a protrusion 76 is formed on the plate member 56 and the plate member 5
A hole 77 is formed in 7. The protruding portion 76 extends from the outer peripheral edge of the plate member 56 by bending toward the transmission in the axial direction, extends within the long hole 61 of the drive member 52, and further extends into the hole 77 of the plate member 57. The distal end 76a of the protruding portion 76 is bent outward and abuts on the surface of the plate member 57 on the transmission side in the axial direction. The protrusion 76 is in contact with the hole 77 in the circumferential direction and cannot move in the circumferential direction, but can move in the circumferential direction in the long hole 61. When the protrusion 76 abuts on the circumferential end of the elongated hole 61, the relative rotation between the drive member 52 and the driven member 53 stops. To summarize the structure described above, instead of using another member such as a rivet, by extending a part of one plate member in the axial direction, the two plate members are engaged in the rotation direction and the axial direction, It constitutes a part of the stopper mechanism. In addition,
Since the long hole 61 only needs to have a width in the radial direction corresponding to the plate thickness of the protruding portion 76, it is a slit that is shorter in the radial direction than in the embodiment. Note that a structure in which the protruding portion extends from the plate 57 may be employed.

Effect (1) Since the claw 52b of the drive member 52 extends radially inward from the annular portion 52a, sufficient strength can be maintained. Therefore, by shortening the circumferential width of the claw 52b, the circumferential length of the torsion spring 54 can be secured longer than before. (2) Since the float 55 and the drive member 52 are arranged at the same axial position, the axial dimension of the damper mechanism 45 can be sufficiently reduced. (3) Since the float body 71 is composed of a plurality of members, manufacture is facilitated. In particular, in this embodiment, since each play 72 is manufactured by bending one sheet metal, the structure is simple and the cost is low. In addition, the weight has been significantly reduced. In particular, the circumferential width can be reduced,
Thereby, the circumferential free length of the torsion spring can be made longer than before. Other Embodiments The number of elastic members arranged in series may be three or more instead of two. Further, the type of the elastic member is not limited to the coil spring, and may be another type of spring or elastic body.

The damper mechanism according to the present invention can be applied not only to a lock-up device but also to a clutch disk assembly and a flywheel assembly.

[0034]

In the elastic connecting device according to the present invention, the pawl of the first rotating member extends radially inward from the annular portion, so that sufficient strength can be maintained. Therefore, the circumferential length of the elastic member can be secured longer than before by reducing the circumferential width of the claw.

[Brief description of the drawings]

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

FIG. 2 is a partial plan view of the elastic coupling device.

FIG. 3 is a sectional view taken along the line III-O in FIG. 2;

FIG. 4 is a partial plan view of an elastic connection device according to a second embodiment of the present invention.

FIG. 5 is a sectional view taken along line VO of FIG. 4;

FIG. 6 is a sectional view taken along the line VI-O in FIG. 4;

[Explanation of symbols]

 7 Lock-up device 45 Damper mechanism 52 Drive member 53 Driven member 54 Torsion spring 55 Float body 56 Plate member 57 Plate member

Claims (5)

[Claims] 1. An elastic coupling device for transmitting torque and absorbing torsional vibration, comprising: a first rotating member having an annular portion and a plurality of claws extending radially inward from the annular portion; A plurality of elastic members disposed between a pair of the plurality of claws; an intermediate member disposed between the plurality of elastic members in a rotational direction; and a support for supporting ends of the plurality of elastic members in the rotational direction. A second rotating member having a portion. 2. The elastic coupling device according to claim 1, wherein said intermediate body is arranged at the same axial position as said first rotating member. 3. The intermediate member is disposed between an annular connecting portion disposed on an inner peripheral side of the annular portion and a radially outward direction from the annular connecting portion, in a rotational direction of the plurality of elastic members. The elastic connecting device according to claim 1 or 2, comprising an elastic member supporting portion. 4. The intermediate body is composed of a plurality of intermediate members, each of the intermediate members being an arc-shaped portion disposed on an inner peripheral side of the annular portion, and extending from the arc-shaped portion radially outward. The elastic connecting device according to claim 1, further comprising: an elastic member supporting portion disposed between the elastic members in the rotation direction. 5. The elastic coupling device according to claim 1, wherein said second rotating member comprises a pair of members disposed on both sides of said first rotating member and said intermediate member in the axial direction.