JPH08303554A - Lockup damper device of fluid transmission device - Google Patents

Abstract

PURPOSE: To set a size in the axial direction and a size in the diameter direction at a minimum without weight increase of a lockup damper by forming a driven plate of one ring shape plate set to a specific position for a coil spring. CONSTITUTION: A driven plate 8 has the inside support surface 81, front side support surface 82 and rear side support surface 83 of a coil spring 9 and is formed of only one ring shape plate set to a position in which the tip positions of the front side support surface 82 and the rear side support surface 83 do not exceed the diameter direction outer peripheral tangent L1 and the axial direction tangent L2 of the coil spring 9 respectively. The inside support surface 81 and the front side support surface 82 of the coil spring 9 are formed on a coil spring holder 8b partially projected by the folding to a lockup piston 6 side and the coil spring holder 8b is set to about 1/3 of the entire length of the coil spring 9 at the nearly central part of the coil spring 9.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a lockup damper device for a fluid transmission device having a lockup function for directly connecting an input shaft and an output shaft.

[0002]

2. Description of the Related Art Conventionally, a drive plate provided on the lock-up piston side, a driven plate provided on the turbine runner side, and a coil spring interposed between the drive plate and the driven plate have been used for lock-up. As a lock-up damper device of a fluid transmission device having a lock-up damper that absorbs torsional vibration about an axis included in the transmitted driving force, Japanese Patent Publication No. 60-54546 and Japanese Utility Model Laid-Open No. 63-7 are known.
The one described in Japanese Patent No. 5656 is known.

[0003]

However, the former lock-up damper device of the fluid transmission device (Japanese Patent Publication No. 60).
No. 54,546), as shown in FIG. 14, a driven plate provided on the turbine runner side shares the function of supporting the coil spring, and the driven plate is an inward & forward supporting surface. 1st with outer & front support surface
And the second plate member having the inner and rear supporting surfaces and the outer and rear supporting surfaces, so that the two plate members are connected to each other. The increase in the number of parts including the pin causes an increase in the weight of the lock-up damper.

Further, a sufficient clearance is secured between the outer circumference of the coil spring and the inner surface of the lock-up piston in the axial direction and the radial direction so as to achieve the spring front support and the spring outer support by the driven plate. Since it is necessary, the axial dimension and the radial dimension of the lockup damper become large.

On the other hand, in the latter lock-up damper device for fluid transmission (Japanese Utility Model Laid-Open No. 63-75656), as shown in FIG. 15, one driven plate is provided on the turbine runner side. However, since the driven plate is not formed with any supporting surface for the coil spring, the supporting function of the coil spring is shared by the driving plate provided on the lock-up piston side.

Therefore, since the lock-up piston and the drive plate are doubly overlapped and fixed, the axial dimension and the radial dimension of the lock-up damper are increased by at least the thickness of the drive plate.

Further, since the drive plate has a rear support formed at the tip of the outer support, the drive plate is cracked by the centrifugal force acting on the rear support during rotation at high speed. It will be easier. For this reason, it is necessary to lengthen the outer peripheral flange of the lock-up piston and reinforce the drive plate, and the outer peripheral flange of the lock-up piston becomes long, resulting in an increase in the weight of the lock-up damper.

The present invention has been made in view of the above problems, and a first object of the present invention is to provide a lockup damper device for a fluid transmission having a lockup function for directly connecting an input shaft and an output shaft. SUMMARY OF THE INVENTION It is an object of the present invention to provide a driven plate that can set the axial dimension and the radial dimension of the lock-up damper to a minimum without increasing the weight of the lock-up damper.

In addition to the first purpose, the second purpose is to support the inside and the front of the coil spring with a high support function without disturbing the torsional vibration absorbing action about the axis. is there.

A third object is to achieve a high front supporting function of the coil spring in addition to the first or second object.

The fourth object is to provide the first to third objects.
In addition to the above purpose, it is to achieve the integration of the driven plate into the turbine shell simply and reliably.

[0012]

In order to achieve the first object, a lockup damper device for a hydraulic power transmission according to a first aspect of the present invention is a pump impeller connected to an input shaft through a transmission cover. And a fluid transmission device having a turbine runner connected to the pump impeller via a fluid and connected to an output shaft, and arranged between the turbine runner and the transmission device cover, and circulating when the lockup is released. Driving force is transmitted through the fluid, and at the time of lockup, a lockup piston that directly connects the input shaft and the output shaft, a drive plate provided on the lockup piston side, and a driven plate provided on the turbine runner side. And a coil spring interposed between the driving plate and the driven plate, the axial rotation included in the driving force transmitted at the time of lockup. In the lockup damper device of the fluid transmission device, which includes a lockup damper that absorbs the torsional vibration of, the driven plate has an inner supporting surface, a front supporting surface, and a rear supporting surface of the coil spring, It is characterized in that the front support surface and the rear support surface are formed by only one annular plate whose tip positions are set so as not to exceed the radial outer circumferential tangent line and the axial outer circumferential tangent line of the coil spring, respectively.

In order to achieve the above-mentioned second object, a lock-up damper device for a hydraulic power transmission device according to a second aspect of the present invention is the lock-up damper device for a hydraulic power transmission device according to the first aspect. The support surface and the front support surface are formed on a coil spring holding part that is partially projected by bending to the lock-up piston side, and the coil spring holding part is approximately at the center of the coil spring and the entire length of the coil spring. About 1/3
It is characterized by being set to a length of about a degree.

In order to achieve the third object, a lockup damper device for a hydraulic power transmission device according to a third aspect of the present invention is the lockup damper device for a hydraulic power transmission device according to the first or second aspect, wherein It is characterized in that a driven claw for supporting an end surface of the coil spring is formed on the drive plate, and a front support portion of the coil spring is provided at a tip end portion of the driven claw.

In order to achieve the fourth object, a lockup damper device for a hydraulic power transmission device according to a fourth aspect of the present invention is the lockup damper device for a hydraulic power transmission device according to any one of the first to third aspects, wherein The drive plate is arranged at an outer peripheral position of the turbine shell, and is integrated with the turbine shell at a fixing portion near the driven claw.

[0016]

The operation of the present invention will be described.

Taking the case of application to an automatic transmission of an automobile as an example, the operation of the transmission device will be described. The lockup piston arranged between the turbine runner and the transmission cover locks up according to the set running condition. Switching control between release and lockup (including slip lockup) is performed.

When the lockup is released, the driving force is transmitted via the fluid circulating through the pump impeller and the turbine runner, as in the fluid transmission device having no lockup function.

At the time of lockup in which the lockup piston is in pressure contact with the transmission cover, input shaft → transmission cover → lockup piston (lockup damper) → turbine runner → output shaft and driving force are transmitted to input shaft and output shaft. The lockup state is a direct lockup state or a slip lockup state in which the input shaft and the output shaft are coupled while allowing relative rotation.

When switching from release to lockup or from lockup to release, the driving force transmitted to the lockup piston fluctuates rapidly,
Also, lock-up state (slip lock-up state)
In this case, the transmitted driving force also fluctuates due to load fluctuations, but in such a case, the torsional vibration about the axis included in the transmitted driving force causes relative rotation between the drive plate and the driven plate of the lockup damper. It is absorbed by the expansion and contraction of the coil spring that accompanies the displacement.

At the time of assembling the lock-up damper, the coil spring is held by the driven plate provided on the turbine runner side, and in this state, the driving plate is moved while aligning the driven plate with the driving plate in the circumferential direction. It is assembled by inserting the provided lock-up piston in the axial direction.

At the time of this assembly, since the driven plate does not have the outer supporting surface of the coil spring, a portion corresponding to this outer supporting surface becomes a space for incorporating the coil spring, and the driven plate has a coil. Since the spring has the inner support surface excluding the outer support surface, the front support surface, and the rear support surface, these support surfaces achieve the coil spring holding function required during assembly.

Further, since the driven plate has only one part formed of only one annular plate and has no external supporting portion requiring a reinforcement due to a large centrifugal force, lockup occurs. It does not increase the weight of the damper.

Moreover, the tip positions of the front support surface and the rear support surface of the driven plate are set so as not to exceed the radial outer peripheral tangent line and the axial outer peripheral tangent line of the coil spring, respectively. Since the lock-up damper does not project from the above, the axial dimension and the radial dimension of the lock-up damper can be set to the minimum.

The operation of the invention according to claim 2 will be described.

In absorbing the torsional vibration about the axis,
The coil spring holding part that is partially projected by bending to the lock-up piston side is set at about the center of the coil spring and is set to about 1/3 of the total length of the coil spring. Since a spring shortening margin of about 1/3 of the total length of the coil spring is secured on both sides of the coil spring, the coil spring holding portion can absorb the torsional vibration by the coil spring even if torsional vibration due to a large amplitude occurs. It does not hurt.

Further, the coil spring holding portion is formed with an inner support surface and a front support surface of the coil spring,
Since the coil spring supports a portion having a length of about 1/3 of the total length, the inside and the front of the coil spring are supported by a high support function.

The operation of the invention according to claim 3 will be described.

Since the driven plate is formed with a driven claw for supporting the end surface of the coil spring, and the tip end of the driven claw is provided with a front support portion of the coil spring, the front side of the coil spring is prevented. Has a so-called three-point support state in which the center part thereof is supported by the front support surface of the coil spring holding part and both end parts thereof are supported by the front support part of the driven claw, and the high front support function of the coil spring is achieved. To be achieved.

The operation of the invention according to claim 4 will be described.

When the driven plate is provided on the turbine runner side, the driven plate is arranged at the outer peripheral position of the turbine shell,
In addition, a fixed part is formed by spot welding or the like at a position near the driven claw, that is, a flat position between the driven claw and the coil spring holding part, and the driven plate is integrated with the turbine shell at this fixed part. Be converted.

As described above, the driven plate can be integrated with the turbine shell by a simple fixing work such as spot welding, and by the reliable fixing by the plurality of fixing portions.

[0033]

Embodiments of the present invention will be described below with reference to the drawings.

(First Embodiment) First, the structure will be described.

FIG. 1 is a sectional view showing a torque converter to which a lockup damper device according to a first embodiment of the present invention is applied, and FIG. 2 is a front view showing a lockup piston having a flange / driving plate of the lockup damper. 3 is shown in FIG.
4 is a partially enlarged perspective view of the flange / driving plate, FIG. 5 is a partially enlarged perspective view showing a modified example of the flange / driving plate, and FIG. 6 is a driven plate of the lock-up damper. 7 is a partial perspective view of the driven plate, FIG. 8 is a partial perspective view of the driven plate to which a coil spring is attached, and FIG.
(A) is an end view of BB in FIG. 6, FIG. 9 (b) is an explanatory view of the operation at the BB position in FIG. 6, FIG. 10 (a) is an end view of CC in FIG. 6, and FIG. 6] is a DD end view of FIG. 6.

In FIG. 1, 1 is a converter cover (transmission device cover), 2 is a pump impeller, 3 is a turbine runner, 4 is a stator, 5 is a torque converter (fluid transmission device), 6 is a lock-up piston, and 7 is a flange. A dual drive plate, 8 is a driven plate, 9 is a coil spring, and 10 is a lock-up damper.

The pump impeller 2 is connected to an input shaft (engine crankshaft) (not shown) via a converter cover 1.

The turbine runner 3 is arranged to face the pump impeller 2 via a fluid, and is also connected to an output shaft (transmission input shaft) (not shown) via a turbine hub 11.

The torque converter 5 is arranged between the pump impeller 2, the turbine runner 3, and the pump impeller 2 and the turbine runner 3, and the one-way clutch 1
It is composed of three elements including a stator 4 fixed to a transmission case (not shown) via the element 2.

The lock-up piston 6 is arranged between the turbine runner 3 and the converter cover 1,
When the lockup is released, the driving force is transmitted through the circulating fluid, and when the lockup is performed, the input shaft and the output shaft are directly connected.

A facing 13 is attached to the lock-up piston 6, which is pressed against the inner surface of the converter cover 1 at the time of lock-up.

A lock-up oil pressure control device (not shown) is connected to the lock-up oil chamber 14 and the converter oil chamber 15 defined by the lock-up piston 6, and when the lock-up is released, the lock-up oil chamber 14 is converted from the converter. The hydraulic oil having the converter pressure is supplied to the oil chamber 15, and at the time of lockup, only the hydraulic oil on the lockup oil chamber 14 side is drained to create a differential pressure. The lock-up oil chamber 14
It is also possible to perform slip lock-up hydraulic control in which the clutch is not completely engaged by the drain adjustment, but is allowed to be slightly engaged and slipped between the input and output shafts.

The lock-up damper 10 is fixed to the outer peripheral position of the turbine shell 3a and the flange / driving plate 7 which also serves as the outer peripheral flange of the lock-up piston 6.
The driven plate 8 is formed by only one annular plate, and the coil spring 9 is interposed between the flange / driving plate 7 and the driven plate 8.

The structure of the flange / driving plate 7 will be described with reference to FIGS. 2 to 5. In the flange / driving plate 7, a U-shaped cut is made in the outer peripheral flange of the lock-up piston 6, and the outer peripheral flange is formed along the cut. Is bent inward to form drive claws 7a on the outer peripheral flange at eight positions at equal intervals, and an annular reinforcing portion 7b is integrally connected to the entire periphery of the end of the outer peripheral flange with the drive claws 7a formed. It consists of leaving.

The driving claw 7a of the driving plate 7 also serving as the flange.
As shown in FIG. 5, escape recesses 7c may be set on both sides of the bent base end portion of the above.

The structure of the driven plate 8 will be described with reference to FIGS. 6 to 10. The driven plate 8 has an inner support surface 81, a front support surface 82, and a rear support surface 83 of the coil spring 9. As shown in FIG. 10B, the front support surface 82 and the rear support surface 83 have tip positions that do not exceed the radial outer circumferential tangent line L1 and the axial outer circumferential tangent line L2 of the coil spring 9, respectively. It is formed only by an annular plate.

Inner support surface 81 of the coil spring 9
As shown in FIGS. 7 and 8, the front support surface 82 is formed on a coil spring holding portion 8b that is partially projected by bending toward the lockup piston 6 side, and the coil spring holding portion 8b is The length of the coil spring 9 is set at about the center of the coil spring 9 and about 1/3 of the total length of the coil spring.

As shown in FIG. 9B, the coil spring 9 is attached to the driven plate 8 via a spring seat 16.
Coil spring 9 by making contact with the end of
A U-shaped driven claw 8a for supporting the end surface of the coil spring 9 is formed, and a front support portion 8c of the coil spring 9 is provided at the tip of the driven claw 8a as shown in FIG.

The driven plate 8 is arranged at the outer peripheral position of the turbine shell 3a, and as shown in FIG. 7, it is integrated with the turbine shell 3a at a fixed portion 8d by spot welding near the driven claw 8a. Has been converted.

Explaining the coil spring 9, as shown in FIG. 10B, the coil spring 9 is supported by the driven plate 8 inward, forward and rearward, and the inner surface 71 of the flange / driving plate 7 is supported. The outside is supported by. Then, as shown in FIG. 8, the spring front support is supported at three points by the front support surface 82 and the front support portions 8c, 8c, and both ends are supported by the U-shaped driven claws 8a. .

As shown in FIG. 9B, the U-shaped driven claw 8a and the driving claw 7a maintain a predetermined clearance t, t regardless of the front-back movement position of the lock-up piston 6. The position is set. The drive claw 7a is shown in FIG.
As shown in, at the lock-up position (dotted line position) of the lock-up piston 6, the load point (position of +) is set substantially at the center position of the coil spring 9.

Next, the operation will be described.

[Lock-up control action] The lock-up control action will be described by taking the case of application to an automatic transmission of an automobile as an example.

The lock-up piston 6 arranged between the turbine runner 3 and the converter cover 1 has a hydraulic control for switching between lock-up release and lock-up (including slip lock-up) according to the set running conditions. Done.

When the lockup is released, the driving force is transmitted through the fluid circulating through the pump impeller 2, the turbine runner 3 and the stator 4 as in the torque converter having no lockup function.

When the lockup piston 6 is in pressure contact with the converter cover 1 during lockup, the engine crankshaft → converter cover 1 → lockup piston 6 (lockup damper 10) → turbine runner 3 →
Turbine hub 12 → The transmission input shaft and the driving force are transmitted, and the engine crankshaft and the transmission input shaft are directly connected to each other in a lockup state or a slip lockup state in which the engine crankshaft and the transmission input shaft are connected while allowing relative rotation. Becomes

[When assembling lock-up damper] To manufacture the flange / driving plate 7, a U-shaped cut is made in the outer peripheral flange of the lock-up piston 6, and a part of the outer peripheral flange is bent inward along the cut. Drive claw 7a
It is manufactured by forming.

In the case of the example shown in FIG. 5, the bending is performed from the escape concave portions 7c which are set on both sides of the bending base end portion of the portion which becomes the driving claw 7a, and the fine adjustment of the bending angle is eliminated. This is made possible by the recess 7c, and the drive pawl 7
The positional accuracy of a is secured.

The driven plate 8 is manufactured by making a predetermined cut in an annular plate material and bending it so as to obtain a set angle and roundness to form the driven claw 8a and the spring holding portion 8b. .

When the lockup damper 10 is assembled, the coil spring 9 is held by the driven plate 8 fixed at the outer peripheral position of the turbine shell 3a.

Then, while the driven claw 8a of the driven plate 8 and the drive claw 7a of the flange / driving plate 7 are aligned in the circumferential direction, the flange / driving plate 7 is attached to the turbine shell 3a.
It is assembled by inserting the lock-up piston 6 which integrally has the axial direction.

At the time of this assembly, since the driven plate 8 does not have the outer supporting portion of the coil spring 9, the portion corresponding to this outer supporting portion becomes a space for incorporating the coil spring 9, and the driven plate Since the coil spring 8 has inner, front, and rear supporting portions excluding the outer supporting portion of the coil spring 9, the coil spring holding function required at the time of assembly is achieved by these supporting portions.

[Coil Spring Supporting Operation] When the lock-up damper 10 is completely assembled or mounted on a vehicle, the coil spring 9 is supported by the outer surface of the coil spring 9 by the inner surface 71 of the flange / drive plate 7.
Are supported by the driven plate 8 for inward, forward, and rearward support and the flange / drive plate 7 for outward support. Both inside and outside and front and rear are supported. The function is achieved.

[Axial Torsional Vibration Absorption] In the above lockup control operation, the drive force transmitted to the lockup piston 6 suddenly fluctuates when switching from release to lockup or from lockup to release. Also, in the lockup state (slip lockup state), the driving force transmitted varies due to load variation and the like.

However, in such a case, the torsional vibration about the axis included in the transmitted driving force causes the coil spring 9 accompanying the relative rotational displacement between the flange / driving plate 7 and the driven plate 8 of the lockup damper 10. It is absorbed by the expansion and contraction of.

In this torsional vibration absorbing action about the axis,
The coil spring holding portion 8b partially protruding from the driven plate 8 is set at a substantially central portion of the coil spring 9 and has a length of about 1/3 of the entire length of the coil spring. Since a spring shortening margin of about 1/3 of the total length of the coil spring is secured on both sides of 8b, even if torsional vibration due to a large amplitude occurs, the coil spring holding portion 8b absorbs the torsional vibration by the coil spring 9. Does not hinder the action.

Further, in the torsional vibration absorbing action about the axis, the drive plate is integrally provided with the lock-up piston 6 as the flange-drive plate 7 which also serves as the outer peripheral flange of the lock-up piston 6, so that the flange-drive drive is also performed. There is no play between the plate 7 and the lockup piston 6,
Generation of rattling noise is prevented.

[Lock-up action] The lock-up piston 6 moves back and forth when the lock-up is started or released, but it is formed on the driven claw 8a formed on the driven plate 8 and the flange / driving plate 7. By setting the position with the driving claw 7a, as shown in FIG. 9B, the predetermined gaps t and t are maintained regardless of the front-rear movement position of the lock-up piston 6, so that the front-rear movement position of the lock-up piston 6 is maintained. Regardless of this, interference between the driving claw 7a and the driven claw 8a is prevented.

At the time of lockup, the load point of the drive claw 7a is set at the lockup position of the lockup piston 6 as shown in FIG. 9B by setting the drive claw 7a formed on the flange / drive plate 7. Since the coil spring 9 is arranged at a substantially central position, the coil spring 9 is prevented from being twisted or bent by the load applied from the drive claw 7a to the coil spring 9 in the action of absorbing the torsional vibration about the axis. Since the spring is expanded and contracted with the load substantially at the center position, the high torsional vibration absorbing action is secured during lockup.

The flange-driving plate 7 has a structure in which even if the driving claw 7a is formed, the annular reinforcing portion 7b to which the entire circumference of the end portion of the outer peripheral flange is integrally connected remains. Even if a large centrifugal force acts on the flange, the difference in bending strength between the portion where the drive pawl 7a is formed and the portion where the drive pawl 7a is not formed is small, and the fastening surface of the lock-up piston 6 where the facing 13 is provided. High flatness is maintained without waviness due to the difference in bending strength.

Therefore, it is possible to prevent the occurrence of judder due to the uneven surface pressure at the time of lock-up and the variation of the friction coefficient, and the facing 13 provided on the lock-up piston 6 is not partly greatly worn. Due to the uniform wear, the durability and reliability of the facing 13 can be improved.

[Light weight, compact size, and low cost of lock-up damper] The drive plate is an integral member as a flange / drive plate 7 formed also as the outer peripheral flange of the lock-up piston 6, and the driven plate 8 is The lock-up damper 10 is increased in weight because it has only one part formed by only one annular plate and does not have an outer support portion that requires a large centrifugal force and requires reinforcement. There is no invitation.

Moreover, the flange / driving plate 7 is provided on the outer peripheral flange of the lock-up piston 6 without increasing the axial and radial dimensions, and the driven plate 8 has an outer supporting portion for increasing the radial dimension. Since it is not provided and can be formed without protruding from the outer circumference of the coil spring 9, the axial dimension and the radial dimension of the lock-up damper 10 can be set to the minimum.

As a result, as shown in FIG. 1, the lockup damper 10 is made compact in a space portion slightly larger than the outer diameter of the coil spring 9 formed by the outer peripheral portion of the turbine shell 3a and the inner surface of the lockup piston 6. Can fit.

Since the drive plate is composed of the flange / drive plate 7 in which the independent parts as the drive plate are omitted, the lock-up damper 10 may be composed of two parts, the driven plate 8 and the coil spring. The lock-up damper 10 can be manufactured at low cost as the number of parts is reduced.

Next, the effect of focusing on the driven plate 8 will be described.

(1) In the lockup damper device of the torque converter, the driven plate 8 is connected to the inner support surface 81, the front support surface 82, and the rear support surface 83 of the coil spring 9.
And the front supporting surface 82 and the rear supporting surface 83 are formed by only one annular plate whose tip positions are set not to exceed the radial outer circumferential tangent line L1 and the axial outer circumferential tangent line L2 of the coil spring 9, respectively. Therefore, it is possible to provide the driven plate 8 in which the axial dimension and the radial dimension of the lock-up damper 10 can be set to the minimum without causing an increase in the weight of the lock-up damper 10.

(2) Inner support surface 8 of coil spring 9
1 and the front supporting surface 82 are formed on a coil spring holding portion 8b which is partially projected by bending toward the lockup piston 6 side, and the coil spring holding portion 8b is formed at a substantially central portion of the coil spring 9. Since the length is set to about 1/3 of the total length of the coil spring, the inside and the front of the coil spring 9 can be supported with a high supporting function without hindering the torsional vibration absorbing action around the axis.

(3) A driven claw 8a for supporting the end surface of the coil spring 9 is formed on the driven plate 8, and a front support portion 8c of the coil spring 9 is provided at the tip of the driven claw 8a. Since the coil spring 9 is provided, a high front supporting function of the coil spring 9 can be achieved.

(4) Mount the driven plate 8 on the turbine shell 3a.
Since it is arranged at the outer peripheral position of and is integrated with the turbine shell 3a at the fixed portion 8d near the driven claw 8a,
The driven plate can be easily and surely integrated with the turbine shell 3a.

(Second Embodiment) First, the structure will be described.

In FIG. 11, reference numeral 17 denotes a drive plate, which is constituted by a single annular plate having a plurality of drive claws 17a formed thereon. The drive plate 17 is fixed to the inner surface of the outer peripheral flange 6a of the lockup piston 6 (spot). This is an example in which the drive plate 17 is integrally provided with the lock-up piston 6 by forming the welded portion 17b). The other structure is the same as that of the first embodiment.

Next, the operation will be described.

When the drive plate 17 is provided integrally with the lock-up piston 6, a single elongated plate having a plurality of drive claws 17a is formed into an annular shape to form the drive plate 17, and the drive plate 17 is locked up. It is performed by fixing it to the inner surface of the outer peripheral flange 6a of the piston 6 by spot welding.

The effect of focusing on the driven plate is the same as that of the first embodiment.

Although the embodiments have been described above with reference to the drawings, the specific configuration is not limited to the embodiments, and modifications and additions within the scope of the present invention are included in the present invention. Be done.

For example, in the embodiment, the example of application to the torque converter is shown, but the invention can also be applied to other fluid transmission devices such as a fluid coupling.

[0088]

According to the first aspect of the invention, in a lockup damper device for a fluid transmission device having a lockup function for directly connecting an input shaft and an output shaft, a driven plate is provided inside a coil spring. A single sheet having a supporting surface, a front supporting surface, and a rear supporting surface, and the front end positions of the front supporting surface and the rear supporting surface are set at positions not exceeding the radial outer peripheral tangent line and the axial outer peripheral tangent line of the coil spring, respectively. (EN) Provided is a driven plate which does not increase the weight of the lock-up damper and can set the axial dimension and the radial dimension of the lock-up damper to the minimum because the device is formed by only the annular plate. The effect of being able to do is obtained.

According to the invention of claim 2, claim 1
In the lockup damper device of the fluid transmission device described above, the inward support surface and the front support surface of the coil spring are formed in a coil spring holding part that is partially projected by bending toward the lockup piston side, and
Since the coil spring holding portion is set to a length of about ⅓ of the total length of the coil spring in the substantially central portion of the coil spring, in addition to the above-mentioned effect, it does not hinder the torsional vibration absorbing action about the axis. An effect that the inside and the front of the coil spring can be supported with a high support function is obtained.

According to the invention of claim 3, claim 1
3. The lockup damper device for a hydraulic power transmission according to claim 2, wherein the driven plate is formed with a driven claw for supporting an end surface of the coil spring, and the tip of the driven claw is a coil spring. In addition to the above effects, the effect of being able to achieve a high front support function of the coil spring is obtained.

According to the invention of claim 4, claim 1
The lockup damper device for a fluid transmission according to claim 3, wherein the driven plate is arranged at an outer peripheral position of the turbine shell, and is integrated with the turbine shell at a fixing portion near a driven claw. In addition to the above effects,
The effect that the driven plate can be easily and reliably integrated with the turbine shell is obtained.

[Brief description of drawings]

FIG. 1 is a sectional view showing a torque converter to which a lockup damper device according to a first embodiment of the present invention is applied.

FIG. 2 is a front view showing a lock-up piston having a drive plate and a flange of the lock-up damper.

FIG. 3 is a sectional view taken along line AA of FIG. 2;

FIG. 4 is a partially enlarged perspective view of a flange / driving plate.

FIG. 5 is a partially enlarged perspective view showing a modified example of the flange / driving plate.

FIG. 6 is a front view showing a driven plate of the lock-up damper.

FIG. 7 is a partial perspective view of a driven plate.

FIG. 8 is a partial perspective view of a driven plate with a coil spring attached.

9A is an end view taken along the line BB of FIG. 6, and FIG.
FIG. 8 is an explanatory view of the action at the position BB of FIG.

10A is a C-C end view of FIG. 6, and FIG. 10C is a D-D end view of FIG.

FIG. 11 is a sectional view showing a torque converter to which a lockup damper device according to a second embodiment of the present invention is applied.

FIG. 12 is a front view showing a lock-up piston having a drive plate of a lock-up damper.

13A is a sectional view taken along line EE of FIG. 12, and FIG. 13B is a view taken in the direction of arrow F of FIG.

FIG. 14 is an explanatory diagram showing a first example of a conventional lock-up damper.

FIG. 15 is an explanatory diagram showing a second example of the conventional lock-up damper.

[Explanation of symbols]

 1 Converter cover (transmission device cover) 2 Pump impeller 3 Turbine runner 4 Stator 5 Torque converter (fluid transmission device) 6 Lock-up piston 7 Flange and drive plate (drive plate) 8 Driven plate 9 Coil spring 10 Lock-up damper

Claims (4)

[Claims] 1. A fluid transmission device having a pump impeller connected to an input shaft via a transmission cover, and a turbine runner arranged to face the pump impeller via a fluid and connected to an output shaft. A lock-up piston that is arranged between the turbine runner and the transmission cover, the driving force is transmitted through the circulating fluid when the lock-up is released, and the lock-up piston that directly connects the input shaft and the output shaft at the lock-up; A driving plate provided on the up-piston side, a driven plate provided on the turbine runner side, and a coil spring interposed between the driving plate and the driven plate,
A lock-up damper device for a fluid transmission, comprising: a lock-up damper that absorbs a torsional vibration about an axis included in a driving force transmitted at the time of lock-up, wherein the driven plate is an inner support surface of a coil spring. And an anterior support surface and a posterior support surface, and the front support surface and the posterior support surface are set at positions where the tip positions thereof do not exceed the radial outer circumferential tangent line and the axial outer circumferential tangent line of the coil spring, respectively. A lock-up damper device for a hydraulic power transmission device, which is characterized in that it is formed by only. 2. The lockup damper device for a fluid transmission device according to claim 1, wherein the inner support surface and the front support surface of the coil spring are
The coil spring holding portion is formed by partially bending the lock-up piston side, and the coil spring holding portion is approximately the center of the coil spring and has a length of about 1/3 of the total length of the coil spring. A lock-up damper device for a fluid transmission device characterized by being set to a height. 3. The lock-up damper device for a fluid transmission device according to claim 1, wherein the driven plate is formed with a driven pawl for supporting an end face of a coil spring, and the driven plate. A lock-up damper device for a fluid transmission device, wherein a front support portion of a coil spring is provided at a tip portion of a claw. 4. A lockup damper device for a fluid transmission according to claim 1, wherein the driven plate is arranged at an outer peripheral position of a turbine shell,
A lockup damper device for a hydraulic power transmission device, characterized in that the lockup damper device is integrated with a turbine shell at a fixing portion near a driven pawl.