JPS6325224B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (A) Field of Industrial Application The present invention relates to a fluid coupling, particularly to a fluid coupling used in a vehicle transmission. In the present invention, the fluid coupling includes a fluid torque converter fluid coupling.

(B) Prior art A fluid coupling transmits the driving force transmitted to the casing from the pump impeller fixed to the casing to the turbine runner via fluid, and then transmits the driving force from the turbine runner to the fixed output shaft. Therefore, although the transmission efficiency is inferior to mechanical couplings, it has characteristics such as stepless torque conversion characteristics, vibration absorption characteristics, and ease of operation, so it is widely used as a coupling for transmissions, especially vehicle transmissions. There is.

In order to combine the above-mentioned good properties of the fluid coupling with the high coupling efficiency of the mechanical coupling, it is known to provide a direct coupling clutch between the turbine runner and the casing of the fluid coupling (for example, US Pat.
(See specification No. 3491617 and specification No. 3497043).

By the way, when a fluid coupling is used as a coupling between an engine and a transmission, when the casing is mechanically connected to the output shaft of the fluid coupling via a turbine runner using a direct coupling clutch, the engine is connected to the transmission connected to the output shaft. The torsional vibrations around the output shaft are directly transmitted from the torsion, which adversely affects the power transmission mechanism of the transmission.

On the other hand, in order to absorb torsional vibrations around the output shaft in a mechanical joint, the clutch plate to which the clutch facing is fixed is not fixed to the output shaft of the joint, and the drive plate has an outer diameter smaller than the inner diameter of the clutch facing. An annular clutch plate having a plate fixed to the output shaft is supported on the outer periphery of the drive plate so as to be movable relative to the drive plate, and holes are formed in the drive plate and the clutch plate at appropriate intervals in the circumferential direction. It is known to form a vibration absorbing damper device in which a coil spring is housed in a window hole so that the drive plate and the clutch plate are elasticized in the circumferential direction (for example, see Patent Application Publication No. 27488 of 1972).

(c) Problems to be solved by the invention A vibration absorbing damper device for absorbing torsional vibrations transmitted to an output shaft when mechanical power is transmitted by the direct coupling clutch in a fluid coupling provided with a direct coupling clutch. It is particularly preferable to provide this in a vehicle transmission.

However, when attempting to apply the known mechanism of the mechanical coupling to a direct coupling clutch provided between the turbine runner and the casing of the fluid coupling, a drive plate is provided on the output shaft of the fluid coupling separately from the turbine runner, and the drive plate is connected to the piston of the direct coupling clutch, but it is difficult to make the piston slidable in the axial direction of the fluid coupling and to connect the piston and the drive plate so that they rotate integrally. . In particular, the piston of the direct coupling clutch of a fluid coupling is formed into a ring shape with a large outer diameter from a thin plate-like material, and its inner circumferential edge serves as the output shaft of the fluid coupling or the base of the turbine runner (turbine hub).
Since the annular piston is slidably supported by the drive plate, the annular piston is easily twisted when the annular piston is brought into pressure contact with the inner surface of the casing of the fluid coupling via a friction material, or when the pressure contact with the inner surface of the casing is released. If there is a dimensional error in the piston and the means for connecting them, a dragging phenomenon occurs in which only a portion of the friction material comes into contact when the annular piston engages or disengages from the inner surface of the casing, and the axial direction of the annular piston This may impair movement and impair the mechanical power transmission or release function of the direct coupling clutch.

The present invention fixes a driven plate made of a flexible elastic member in the axial direction of the fluid coupling to the turbine runner of the fluid coupling, and supports a drive plate so as to be movable relative to the driven plate in the circumferential direction. Spline engagement with the annular piston of the direct coupling clutch through multiple notches eliminates the occurrence of strain when the annular piston engages or disengages from the inner surface of the casing of the fluid coupling, and is particularly effective in releasing the direct coupling clutch. The purpose of this is to improve the disengagement of the clutch without causing a dragging phenomenon when the clutch is moved.

(d) Means for Solving the Problems The present invention provides a turbine runner that rotates integrally with the output shaft of a fluid coupling, and an annular piston that is disposed so as to be movable in the axial direction of the output shaft. The piston and the front cover of the casing of the fluid coupling facing the piston constitute a direct coupling clutch by being connected through a vibration damper device equipped with a vibration damper for absorbing torsional vibrations around the shaft. , the piston is slidable in a liquid-tight manner on the base of the turbine runner, and can be freely engaged and disengaged from the front cover via a friction material by fluid pressure supplied to chambers formed on both sides of the piston in the axial direction, thereby absorbing vibration. The damper device includes a driven plate made of an annular elastic member connected to the turbine runner at its inner circumferential portion to flexibly support it in the axial direction of the output shaft, and a An annular driving plate made of a plate-shaped material is movably supported, and the elastic force of a vibration damper whose both ends are engaged with the driven plate and the driving plate is applied between the driven plate and the driving plate in the circumferential direction. Further, a flange portion having a plurality of first notches formed in the outer circumference of the annular piston is provided, and a plurality of second notches are formed in the outer circumference of the vibration absorbing damper device. spline engagement.

In a preferred embodiment of the present invention,
The driven plate of the vibration absorbing damper device has a driven auxiliary plate fixed to its outer periphery so that the driven plate is formed in two layers along the rotating surface of the driven plate, and the driving plate is formed in two layers. A window is formed in this two-layer driven plate while being supported between the plates. In addition, either or both of the first notch of the flange formed on the outer periphery of the annular piston and the second notch formed on the outer periphery of the drive plate of the vibration absorbing damper device. A surface hardening treatment is applied, and further a surface hardening treatment is applied to the peripheral edges of the windows formed on the driven plate and the driving plate, or a member having a hardened surface is interposed therebetween.

(E) Effect According to the present invention, when the direct coupling clutch is engaged, the outer periphery of the annular piston is not affected until the annular piston of the direct coupling clutch engages with the front cover of the casing via the friction material. The spline engagement between the first notch formed in the flange of the vibration absorbing damper device and the second notch formed in the outer periphery of the drive plate of the vibration absorbing damper device is in a loose state where no power is transmitted. Until the annular piston engages with the front cover and the friction material, even if there are dimensional irregularities inside the fluid coupling, such as dimensional errors in the drive plate, the annular piston, or the notch, these dimensional irregularities can move the annular piston independently. Power is transmitted by engagement of the direct coupling clutch through the front cover, friction material, annular piston, first and second notches, drive plate, vibration damper, driven plate, and turbine runner, and is transmitted to the output shaft. be exposed. In addition, when the direct coupling clutch is disengaged and operated as a fluid joint, when a force is applied to the annular piston to separate from the front cover due to fluid pressure, the contact pressure of the spline notch causes friction to cause the elastic member to The driven plate of the vibration absorbing damper device is bent in the axial direction, and a slight gap is formed between the annular piston and the front cover via the friction material, and at this moment, power is transmitted between the notches. Since the condition is removed,
The contact pressure and friction between the notches is released, and the annular piston smoothly returns to the released position.

(f) Embodiment FIG. 1 is a sectional view of an embodiment in which the present invention is applied to a hydraulic torque converter, taken along a plane including the rotation center axis of the output shaft of the torque converter, and showing the main parts thereof. It is.

As is well known, the hydraulic torque converter 1 includes:
It is composed of a pump impeller 2, a turbine runner 3, and a stator 4. In the figure, an outer shell 32 of the pump impeller 2 is fixed by welding to a dish-shaped casing front cover 8 to constitute a casing of the torque converter 1, and is rotatably supported on a fixed shaft 13. Further, the outer shell 34 of the turbine runner 3 is spline-fitted to the front end of the output shaft 9 rotatably supported in the shaft hole of the fixed shaft 13, and the rivet 11 is attached to the turbine hub 10 which rotates integrally with the output shaft 9. are connected by. Furthermore, the stator 4 is connected to the fixed shaft 13 via a one-way clutch 12.

The casing front cover 8 has a pilot 6 at its center of rotation and a connecting nut 7 welded to its peripheral edge, and is connected concentrically to the output shaft (not shown) of the engine via the pilot 6 and connecting nut 7. connected.

A direct coupling clutch 5 is provided for mechanically connecting the pump impeller 2 and the turbine runner 3. The direct coupling clutch 5 is connected to the turbine hub 1.
a slide bearing 20 that is spline-fitted to the shaft cylinder portion of the slide bearing 20 and is prevented from moving in the axial direction by the inner surface of the casing front cover 8 so as to be substantially integrated with the turbine hub 10; An annular piston 14 supported so as to be relatively movable in the axial direction on a cylindrical surface formed on the outer periphery, fixed to a flat annular power transmission surface 33 formed on the outer periphery of the piston 14, and fixed by a friction material. Clutch facing 2 formed in an annular sheet shape
2. Power transmission surface 3 formed on the piston 14
a flat annular power transmission surface 2 formed on the casing front cover 8 at a position opposite to 3;
3. A direct coupling clutch release chamber 25 formed between the casing front cover 8 and the piston 14 when the clutch facing 22 fixed to the piston 14 is pressed against the casing front cover 8; A direct coupling clutch engagement chamber 24 is formed between the outer shell 34 of the turbine runner 3 and the outer shell 34 of the turbine runner 3. The direct coupling clutch release chamber 25 includes a radial direction groove 35 formed in a surface inscribed in the casing front cover 8 of the sliding bearing 20, an oil passage 30 formed at the tip of the output shaft 9, and an oil passage 30 formed in the front end of the output shaft 9. The output shaft 9 is connected to a switching valve (not shown) through an oil passage 36 formed between the fixed shaft 13 and a through hole 37 that is radially bored in the output shaft 9 and communicates the oil passages 30 and 36. ing. Further, the direct coupling clutch engagement chamber 24 is connected to the fluid circulation passage surrounded by the outer shell 32 of the pump impeller 2 of the torque converter 1 and the outer shell 34 of the turbine runner 3 through a gap between the opposing surfaces of the outer shells 32 and 34. The fluid circulation flow path communicates with oil passages 38 and 39 formed at the base of the stator 4 and the fixed shaft 1.
3 and the outer shell 32 of the pump impeller 2 through an oil passage 31 that is connected to the switching valve (not shown). A cylindrical flange 14a is formed on the inner circumferential edge of the piston 14, and the flange 14a has a seal disposed in a circumferential groove of a cylindrical surface formed on the outer periphery of the shaft cylinder portion of the sliding bearing 20 on the cylindrical outer circumferential surface of the flange 14a. It makes sliding contact with the material 21 to keep the sliding contact portion liquid-tight.

The piston 14 of the direct coupling clutch 5 is directly coupled to the turbine runner 3 of the torque converter 1 via a vibration damper device 40. The vibration damper device 4
0 consists of a driven plate 17, a driving plate 15, and a coil spring 18 as a vibration damper. The driven plate 17 is made of an elastic member, and its main part is formed into an annular shape that follows the shape of the outer shell 34 of the turbine runner 3. The driven plate 17 is formed into an annular shape that follows the shape of the outer shell 34 of the turbine runner 3. It is fixed to the turbine hub 10 together with the shell 34 . An edge 17' is formed on the outer peripheral edge of the driven plate 17 and is approximately parallel to the power transmission surface 23 formed on the casing front cover 8. A driven auxiliary plate 16 is fixed to the driven plate 17 by its inner peripheral edge to form a two-layered structure, and its edge 16' is parallel to the edge 17' of the driven plate 17 at a required distance. will be placed in Edge 1 of this driven plate 17
7' and the edge 16' of the driven auxiliary plate 16, a driving plate 15 formed in an annular shape from a thick plate is loosely fitted.

FIG. 2 is a front view of the main parts of the vibration absorbing damper device 40 as seen from the direction of arrow A in FIG. 1, with some parts omitted, and FIG. 2 is a side view showing the drive plate 15, in which a plurality of windows 15b are formed in the inner circumferential edge of the drive plate 15 at appropriate intervals in the circumferential direction, and each of the driven plate 17 and the driven auxiliary plate 16 is A window 17 having the same circumferential dimension as the window 15b formed in the drive plate 15 is provided at the edges 17' and 16'.
a, 16a are respectively formed, and the window 17
Tabs 17b and 16b bent in a direction away from the drive plate 15 are formed on the outer or inner periphery of each of the drive plates 17a and 16a in the diametrical direction.

Window 15b of the driving plate 15, window 1 of the driven plate 17
7a and the window 16a of the driven auxiliary plate 16, a spring serving as a vibration damper, such as a coil spring 18, is inserted in a compressed state with the direction of its elastic force acting in the circumferential direction of the drive plate 15. Therefore, when the driven plate 17 and the driven auxiliary plate 16 move relative to the driving plate 15 in the circumferential direction, the spring 18 moves the driven plate 17 and the driven auxiliary plate 16.
The side edges of the windows 17a, 16a and the window 15 of the drive plate 15
b is compressed by the side edges of b, producing a spring force in the direction of restoring the relative movement. A protrusion 15c is formed on the side edge of the window 15b of the drive plate 15 to support the end of the spring 18. Tabs 17b and 16b formed on the driven plate 17 and the driven auxiliary plate 16
ensures that the spring 18 operates only in the plane in which it lies, and that the windows 15b, 17
a, 16a to prevent it from falling off.

The outer peripheral edge of the piston 14 of the direct coupling clutch 5 has a free end connected to the drive plate 15 of the vibration damper device 40.
A flange 14b that engages with the flange 14b is integrally arranged in a cylindrical shape, and a first notch 14 formed in the axial direction and consisting of a plurality of notches each having a predetermined length is formed in the free end of the flange 14b.
c is formed. On the other hand, the outer circumferential surface of the drive plate 15 has a plurality of notches formed in the diametrical direction.
A notch 15a is formed, and the second notch 15a is formed.
a is spline-engaged with a first notch 14c formed in the flange 14b, and the piston 14
to the turbine runner 3 via the vibration damper device 40
is connected to. Flange 1 of the piston 14
The axial length of the first notch 14c formed in the first notch 4b depends on the amount of axial movement of the piston 14 and the amount of axial deflection of the driven plate 17 for engaging and releasing the direct coupling clutch 5. Also, the length is such that engagement with the second notch 15a formed in the drive plate 15 is maintained.

Note that the circumferential portion of the driven plate 17 and the driven auxiliary plate 16 between the windows 17a and 16a is compressed by the spring 1 when moving relative to the driving plate 15 in the circumferential direction.
8, and a resistance member 19 is sandwiched between the bulged portion and the driving plate 15 to provide appropriate drag resistance during the relative movement. possible.

The operation of the embodiment described above will be explained.

When the function of the hydraulic joint is performed without engaging the direct coupling clutch 5, the direct coupling clutch release chamber 25 of the torque converter 1 is communicated with a hydraulic power source (not shown) via a switching valve, and the fluid circulation passage is connected to the above-mentioned hydraulic pressure source. It is communicated with a reservoir (not shown) via a switching valve. Pressure oil from the hydraulic source is sent to the direct coupling clutch release chamber 25 through the oil passage 36, through hole 37, oil passage 30, and groove 35, and is surrounded by the outer shell 32 of the pump impeller 2 and the outer shell 34 of the turbine runner 3. Since the fluid circulation passage and the pressure oil in the direct coupling clutch engagement chamber 24 are communicated with the reservoir, the pressure difference acting on both sides of the piston 14 causes the piston 14 to slide to the right in FIG. Thing 2
2 to the power transmission surface 2 of the casing front cover 8
3 to create a gap therebetween, and release the direct coupling clutch 5. The pressure oil circulates in the fluid circulation channel through the gap and is returned to the reservoir through the oil channels 38, 39, and 31. The joint thus acts as a torque converter.

When the direct coupling clutch 5 is engaged to exhibit the function of the mechanical joint, the direct coupling clutch release chamber 25 of the torque converter 1 is communicated with the reservoir via the switching valve, and the fluid circulation flow path of the torque converter 1 is connected to the switching valve. It communicates with the pressure oil source through. The pressure oil in the direct coupling clutch release chamber 25 flows through the groove 35 and the oil passage 3.
0, drained through the through hole 37 and oil passage 36,
The direct coupling clutch engagement chamber 24 has oil passages 31, 39, 3.
8 and the fluid circulation channel, the piston 14 is moved towards the casing front cover 8 and the clutch facing 22
is the power transmission surface 23 of the casing front cover 8
, and the direct coupling clutch 5 is engaged. At this time, the power transmitted to the casing of the torque converter 1 is transmitted from the power transmission surface 23 of the casing front cover 8 to the clutch facing 22, the power transmission surface 33 of the piston 14, the piston 14, the notch 14c of the piston 14, and the vibration absorbing damper device. 40 engagement with the notch 15a of the drive plate 15, the drive plate 15,
Spring 18, driven plate 17, turbine hub 10
is transmitted in this order, and is mechanically transmitted to the output shaft 9. Before the direct coupling clutch 5 is engaged, the engagement between the notch 14c of the piston 14 and the notch 15a of the drive plate 15 is in a loose state in which no power is transmitted. Until the power transmission surface 23 of the front cover 8 is frictionally engaged with the clutch facing 22, the piston 14 easily moves in the axial direction without being subjected to any restraining force.

When the direct coupling clutch 5 is engaged or when torsional vibration from the engine as the drive source is transmitted to the casing of the torque converter 1, the piston 14
When a difference in rotational speed occurs between the drive plate 15 and the turbine runner 3, this speed difference is converted into a relative movement in the rotational direction between the drive plate 15 and the driven plate 17, and due to the elasticity of the spring 18 inserted between them. Absorbed.
When the resistance member 19 is interposed between the driving plate 15, the driven plate 17, and the driven auxiliary plate 16,
The drag resistance of the resistance member 19 increases vibration absorption.

When releasing the direct coupling clutch 5 from the engaged state, the piston 14 is moved into the direct coupling clutch release chamber 25.
Although it is necessary to slide the clutch to the right in FIG. 1 by means of pressure oil introduced into the piston, the drive that was transmitted from the notch 14c of the piston 14 to the notch 15a of the drive plate 15 while the direct coupling clutch 5 was engaged. Power and both notches 14
Due to the frictional resistance between c and 15a, the piston 14
The sliding movement to the right may be obstructed. In this case, if the driven plate 17 and the driven auxiliary plate 16 are made of an elastic member so that they can be bent in the axial direction, the driven plate 17 is slightly bent in the axial direction, and the power transmission surface of the casing front cover 8 is 23 and the clutch facing 22, and at that moment the power transmission state between the two notches 14c and 15a is released, so that the piston 14
can be smoothly slid. Also, when such an action is performed, the tabs 17 of the driven plate 17 and the driven auxiliary plate 16 guiding the spring 18
b, 16b are likely to come into mechanical contact with the spring 18, so the driven plate 17 and the driven auxiliary plate 1
It is preferable that the contact surface of 6 with the spring 18 be subjected to surface treatment to prevent friction and increase hardness, or that a thin plate of hard material be fixed.

FIG. 4 is a cross-sectional view of the main parts of another embodiment in which the present invention is applied to a hydraulic torque converter, similar to FIG. 1.

In this embodiment, the turbine runner 3 of the torque converter 1 is configured to be a flat type in which the degree of bulge of the outer shell 34 is reduced as much as possible. The cross-sectional shape of is flatter than that of the embodiment shown in FIG.
This is effective in shortening the axial dimension of fluid couplings.

(G) Effects of the Invention The present invention includes at least a pump impeller fixed to a casing and a turbine runner that rotates integrally with an output shaft, and the driving force transmitted to the casing is caused to flow from the pump impeller to the turbine runner. At least the fluid coupling transmits the fluid to the output shaft by the circulating flow of the fluid that flows back to the pump impeller, the fluid coupling is connected to the turbine runner via a vibration damper device that absorbs torsional vibration around the output shaft, and is connected to the turbine runner in the direction of the output shaft. By configuring a direct coupling clutch that mechanically connects the casing and the output shaft by a movably provided annular piston and a front cover of the casing that faces the piston, stepless torque conversion characteristics are achieved. It is possible to selectively exhibit the characteristics of a hydraulic joint, such as vibration absorption characteristics and ease of operation, and the characteristics of a mechanical joint, which has high joint efficiency due to a direct coupling clutch, and also select the characteristics of a mechanical joint with a direct coupling clutch. In such cases, by providing a vibration absorbing damper device on the direct coupling clutch, torsional vibrations, torque fluctuations, etc. transmitted to the casing are effectively absorbed or blocked by the vibration absorbing damper device and are not transmitted to the output side, or It is possible to alleviate the adverse effects of the reverse driving force from the output side on the input side.

In the present invention, the vibration absorbing damper device includes a driven plate that is formed of an annular elastic member connected to the turbine runner of the fluid coupling at its inner peripheral portion and is flexible in the axial direction of the output shaft of the fluid coupling. , a driving plate made of an annular plate-shaped member supported so as to be movable relative to the driven plate in the circumferential direction on the outer periphery of the driven plate; and a driven plate that is engaged with the driven plate and the driving plate at both ends, respectively. The ring-shaped piston includes a flange portion in which a plurality of first notches are formed in the outer circumferential portion of the annular piston. The drive plate is spline-engaged with a plurality of second notches formed in the outer circumference of the drive plate.

Therefore, when the direct coupling clutch is disengaged and the fluid coupling is exhibiting its characteristics, the annular piston of the direct coupling clutch is moved by the first piston provided on its flange.
The notch and the second part provided on the drive plate of the vibration absorbing damper device
The annular piston is rotated at the same rotational speed as the turbine runner of the fluid coupling in an idle state with no power transmission between it and the notch, and even when the direct coupling clutch is engaged, the annular piston is free from friction. The loose state is maintained until the annular piston contacts the front cover of the casing of the fluid coupling through the material, and until the annular piston frictionally engages with the front cover.
The annular piston is easily moved in the axial direction by fluid pressure without being subjected to any external restraining force in the rotational and axial directions.

When the annular piston engages the front cover with fluid pressure via the friction material, the power transmitted to the casing of the fluid coupling is transferred from the front cover of the casing to the friction material, the annular piston, and the flange portion of the annular piston. The engagement between the first notch and the second notch formed on the outer periphery of the drive plate of the vibration absorbing damper device, and the output shaft of the fluid coupling via the drive plate, vibration damper, driven plate, and turbine runner of the fluid coupling. The fluid coupling no longer has the property of transmitting torque through the fluid and operates only as a mechanical coupling with a direct coupling clutch. At this time, when torsional vibrations and torque fluctuations from the drive source are transmitted to the casing of the fluid coupling, these vibrations and fluctuations are absorbed by the vibration damper.

In the engaged state of the direct coupling clutch, torque is transmitted by the spline engagement between the first notch formed in the annular piston flange and the second notch formed in the outer periphery of the drive plate, as described above. There is. Since the first and second notches are a plurality of notches that spline engage with each other, the contact pressure of the abutment surfaces of the notches is large due to torque transmission due to the engagement of the notches. Therefore, when fluid pressure is applied in a direction to separate the annular piston from the front cover of the casing of the fluid coupling in order to release the direct coupling clutch from the engaged state, the contact pressure on the contact surface of the notch is large. The frictional resistance of the contact surface is large. Therefore, if the driven plate of the vibration absorbing damper device has high rigidity in the axial direction, the annular piston will not separate from the front cover even with a slight fluid pressure due to the frictional resistance. However, in the present invention, the driven plate is made of an elastic member and is formed to be easily bent in the axial direction of the output shaft of the fluid coupling. When fluid pressure is applied in the direction of separating from the front cover, like when torque is transmitted from the annular piston to the drive plate,
When the contact pressure between the contact surfaces of the first notch formed on the outer periphery of the annular piston and the second notch formed on the outer periphery of the drive plate is large, the annular piston and the drive plate are in contact with each other. While the notch remains engaged due to pressure, that is, the driven plate is locked to the annular piston in the rotational direction, the driven plate is deflected in the axial direction of the output shaft due to the fluid pressure, so that the annular piston and the front Even a slight gap is formed between the engagement surface with the cover via the friction material. Due to the formation of this slight gap, power transmission from the front cover to the annular piston is eliminated, so the annular piston can be detached from the front cover of the fluid coupling casing without causing any drag between it and the front cover with a slight fluid pressure. ,
The fluid coupling restores the state of transmitting torque via fluid. If drag occurs between the annular piston and the front cover in the converter state, sufficient torque is not transmitted, and as a result, sufficient fluid circulation flow cannot be ensured, causing heat generation in the fluid coupling.
When the torque to be transmitted between the annular piston and the driving plate becomes zero, the contact pressure on the abutment surface between the first and second notches disappears, and the bent driven plate moves between the notches. Restores without frictional resistance. Furthermore, when fluid pressure is applied to the annular piston in a direction that presses it against the front cover in order to engage the direct coupling clutch, the annular piston contacts the front cover and torque is transmitted between the annular piston and the front cover. Until now, the notches slid against the drive plate without any frictional resistance, but when torque was transmitted to the front cover via the friction material, the contact pressure on the abutment surface between the notches increased. As a result, the driven plate is then bent in the axial direction of the output shaft, and the frictional engagement between the annular piston and the front cover is completed. Therefore, even when the annular piston is molded from a thin plate-like material, there is no risk of the annular piston being distorted, and this allows the annular piston to slide fluid-tightly onto the base of the turbine runner. Since there is no need to take measures against piston twisting, the structure can be simplified.

As described above, according to the present invention, when the direct coupling clutch is engaged or disengaged, the annular piston is not strained, and the clutch is easily disengaged, and when the direct coupling clutch is engaged, torsional vibrations and torque fluctuations are absorbed by the vibration absorbing damper device. It was designed to do so.

[Brief explanation of the drawing]

FIG. 1 is a sectional view showing a main part of an embodiment of the present invention, FIG. 2 is a front view of a part of the vibration damper device seen from the direction of arrow A in FIG. 1, and FIG. A side view of a part of the vibration damper device seen from direction B,
FIG. 4 is a sectional view showing the main parts of another embodiment of the present invention. In the figure, 1 is the torque converter, 2 is the pump impeller, 32 is the outer shell of the pump impeller, 3 is the turbine runner, 34 is the outer shell of the turbine runner, 8 is the casing front cover, and 5 is the direct coupling clutch. , 14 is the piston,
14a and 14b are flanges of the piston, 14
c is the first notch, 22 is the clutch facing, 23 and 33 are the power transmission surfaces, 40 is the vibration absorbing damper device, 18 is the spring as the vibration damper, 17 is the driven plate, and 16 is the driven support. plate, 15 is its driving plate, 15a is the second notch,
15b, 16a, and 17a indicate windows, respectively.

Claims (1)

[Scope of Claims] 1. A pump comprising at least a casing, a pump impeller fixed to the casing, and a turbine runner that rotates integrally with an output shaft rotatable with respect to the casing; In the fluid coupling, the driving force transmitted to the output shaft is transmitted to the output shaft by a circulating flow of fluid circulating in a circulating flow path formed between the pump impeller and the turbine runner. An annular piston is disposed between the turbine runner and the annular piston is connected to the turbine runner via a vibration damper device including a vibration damper that absorbs torsional vibration around the output shaft. A direct coupling clutch is formed of a front cover, an annular piston, and a friction material, and the annular piston is slidable in a liquid-tight manner on the base of the turbine runner and is inserted into chambers formed on both sides of the piston in the axial direction. The vibration absorbing damper device is configured such that it can be freely engaged and detached from the front cover of the casing via a friction material by the supplied fluid pressure, and the vibration absorbing damper device has an annular shape connected to the turbine runner at an inner peripheral portion and movable in the axial direction of the output shaft. a driven plate made of a flexible elastic member; a drive plate made of an annular plate-shaped member supported so as to be movable relative to the driven plate in the circumferential direction at the outer periphery of the driven plate;
The annular piston has a plurality of first notches on its outer periphery. With a vibration absorbing damper device, the cutout is spline engaged with a plurality of second notches formed in an outer peripheral portion of the drive plate of the vibration absorbing damper device. Fluid coupling with direct coupling clutch. 2. The driven plate of the vibration absorbing damper device has an outer periphery formed in two layers along the rotating surface of the driven plate, and the driving plate is supported between the two layered driven plates, and has a structure formed on the driven plate. 2. A fluid coupling equipped with a direct coupling clutch with a vibration absorbing damper device according to claim 1, wherein the window is formed in the two-layered portion of the driven plate. 3. The surface of either or both of the first notch formed in the annular piston and the second notch formed in the drive plate of the vibration absorbing damper device is hardened. A fluid coupling comprising a direct coupling clutch with a vibration absorbing damper device according to claim 1 or 2. 4. The vibration absorbing damper device according to claim 1 or 2, wherein a contact portion of the driven plate and the driving plate of the vibration absorbing damper device with the vibration damper is surface hardened. Fluid coupling with direct coupling clutch. 5. Claim 1, wherein the annular piston is slidable in a liquid-tight manner onto a bearing portion integrally formed at the base of the turbine runner by means of a flange formed on the inner peripheral edge of the annular piston. A fluid coupling comprising a direct coupling clutch with a vibration absorbing damper device according to item 1 or 2.