JPS6325225B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (a) Industrial Field of Use 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 and a 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, the transmission efficiency is inferior to mechanical couplings, but 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. ing.

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, U.S. Pat. No. 3,491,617 No. 3497043).

By the way, when a fluid coupling is used as a coupling for power transmission between an engine and a transmission, if the casing is mechanically directly connected to the output shaft of the fluid coupling via a turbine runner using a direct coupling clutch, the casing will not be connected to the output shaft. Torsional vibrations around the output shaft are directly transmitted from the engine to the transmission, which has an adverse effect on 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. A plate is fixed to the output shaft, and an annular clutch plate to which a clutch facing is fixed is supported on the outer periphery of the drive plate so as to be relatively movable in the circumferential direction. It is known that coil springs are housed in window holes drilled at intervals of (Refer to Publication No. 27488).

(c) Problems to be Solved by the Invention In a fluid coupling provided with a direct coupling clutch, a vibration damper device for absorbing torsional vibrations transmitted to an output shaft when mechanical power is transmitted by the 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, separate from the turbine runner, and the direct coupling clutch is Although a vibration absorbing damper device is provided between the piston of the direct coupling clutch and the drive plate inside the clutch facing, an increase in the axial dimension of the fluid coupling cannot be avoided.

In providing a direct coupling clutch equipped with a vibration absorbing damper device in a fluid coupling, the present invention devises the connection between the vibration absorbing damper device and the turbine runner of the fluid coupling, thereby making it possible to reduce the axial dimension of the direct coupling clutch equipped with the vibration absorbing damper device. The purpose is to make it as small as possible.

(d) Means for Solving the Problems The present invention forms a flange portion on the inner periphery of an annular piston that constitutes a direct coupling clutch together with the front cover of a casing of a fluid coupling, and the flange portion is integrally connected to a turbine runner. The vibration absorbing damper device is capable of sliding in the axial direction on a sliding bearing that rotates, and is in liquid-tight contact with a sealing material provided in a circumferential groove formed on the outer periphery of the sliding bearing. an annular driven plate connected to the driven plate; 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 the driven plate and the driving plate. and a vibration damper whose opposite ends are engaged with each other so that both plates vibrate in the circumferential direction, and the annular piston is movable in the axial direction with respect to the drive plate by spline engagement at its outer peripheral edge, and An annular driven plate is fixed to the turbine hub together with the outer shell of the turbine runner of the fluid coupling by rivets.

The fluid coupling may be a fluid coupling consisting of a pump impeller fixed to a casing and a turbine runner that rotates integrally with the output shaft, or a torque converter in which a stator and a one-way clutch are arranged.

(e) Effect According to the present invention, when used as a fluid coupling without activating the direct coupling clutch, the driving force of the prime mover, etc., transmitted to the casing is controlled by the flow of fluid by the pump impeller fixed to the casing. This fluid is converted into energy, which drives the turbine runner to rotate, and is reproduced as driving force at the output shaft that rotates integrally with the turbine runner, thereby performing power transmission having the characteristics of a fluid coupling.

When the direct coupling clutch is activated, the piston and the casing front cover facing the piston are mechanically connected via the clutch facing, so that the driving force of the driving crosspiece, etc., transmitted to the casing of the fluid coupling is reduced. Torsional vibrations transmitted from the prime mover etc. to the casing or from the output shaft are transmitted to the output shaft with high transmission efficiency and are interposed between the piston and the Kubin runner fixed to the output shaft. Absorbs torsional vibration caused by reverse driving force.

Moreover, since the driven plate of the vibration absorbing damper device is fixed to the turbine hub together with the outer shell of the turbine runner at its inner circumference by rivets, when the direct coupling clutch is activated, the driving force transmitted to the casing is transmitted to the piston. Via the spline engagement between the drive plate and the vibration damper of the vibration damper device, the vibration is transmitted to the turbine hub fixed to the output shaft over the shortest distance.

(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 peripheral edge of the piston 14.
4a has its cylindrical outer peripheral surface in sliding contact with a sealing material 21 disposed in a circumferential groove of a cylindrical surface formed on the outer periphery of the axial cylinder portion of the sliding bearing 20, thereby maintaining liquid tightness of the sliding contact portion.

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, and the rivet 11 is attached to the inner peripheral edge of the driven plate 17. Outer shell 34
It is also fixed to the turbine hub 10. An edge 17' is formed on the outer peripheral edge of the driven plate 17 and is substantially parallel to the power transmission surface 23 formed on the casing front cover 8.
A driven auxiliary plate 16 formed in a narrow annular shape by the same elastic member as the driven plate 17 is connected to the driven plate 17 by its inner peripheral edge.
The edge 16' is formed in two layers.
are arranged parallel to the edge 17' of the driven plate 17 with a required spacing therebetween. 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, for example, a coil spring 18, is inserted in a compressed state with 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 a first notch 1 formed in the flange 14b;
4c, and connects the piston 14 to the turbine runner 3 via a vibration damper device 40. Flange 14 of the piston 14
The axial length of the first notch 14c formed in b is determined by the amount of axial movement of the piston 14 for engaging and disengaging the direct coupling clutch 5 and the driven plate 1.
The length is such that engagement with the second notch 15a formed in the drive plate 15 is maintained even with an axial deflection amount of 7.

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 22
The power transmission surface 23 of the casing front cover 8
The direct coupling clutch 5 is released by separating it from the clutch to create a gap therebetween. 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 perform 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. 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,
Oil passages 31, 39, 38 are provided in the direct coupling clutch chamber 24.
Since pressure oil is supplied through the casing front cover 8 and the fluid circulation channel, the piston 14
The clutch facing 22 is brought into pressure contact with 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 engages with the notch 15a of the drive plate 15, and is transmitted to the drive plate 15, spring 18, driven plate 17, and turbine hub 10 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 33 of the piston 14 and the power transmission surface 23 of the casing front cover 8 frictionally engage with each other via the clutch facing 22, the piston 14 can easily pivot without being subjected to any restraining force. move in the direction.

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 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 circulating in 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 an annular piston that is movably disposed on the piston and a front cover of the casing that faces the piston, stepless torque conversion is achieved. It is possible to selectively exhibit the characteristics of fluid type joints such as vibration absorption characteristics, ease of operation, etc., and the characteristics of mechanical joints with high joint efficiency due to direct connection clutches. In the selected case, by providing the direct coupling clutch with a vibration absorbing damper device, 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. Alternatively, the adverse effect of the reverse driving force from the output side on the input side can be alleviated.

In the vibration absorbing damper device, an annular driven plate is fixed to the turbine hub together with the outer shell of the turbine runner at its inner periphery with rivets, and an annular drive plate is supported at the outer periphery of the driven plate so as to be relatively movable in the circumferential direction. and includes a vibration damper that is engaged with the driven plate and the drive plate at both ends and elasticizes both plates in the circumferential direction, and the annular piston is connected to the drive plate of the vibration absorbing damper device at the outer peripheral edge of the annular piston. Since the piston and the drive plate are engaged with each other through splines so as to be movable in the axial direction, when the direct coupling clutch is activated, the driving force transmitted to the casing is transmitted to the drive plate through the spline engagement between the piston and the drive plate. The driving force transmitted to the drive plate is transmitted to the driven plate via the vibration damper. Since the driven plate and the turbine hub are fixed with rivets, the driving force transmitted to the casing is transmitted to the output shaft of the fluid coupling through an extremely short path. Moreover, the driven plate of the vibration absorbing damper device is fixed to the turbine hub together with the outer shell of the turbine runner with rivets, the driving plate is supported on the driven plate so as to be movable relative to the driven plate in the circumferential direction, and the vibration damper is mounted between the two plates. Since both ends are engaged with each other so as to spring in the circumferential direction, the structure is simple and the axial dimension thereof can be made extremely short. Furthermore, since the annular piston is splined to the drive plate at its outer peripheral edge, 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. Although the annular piston is likely to become distorted due to uneven contact of the friction material or fluctuations in driving torque, the annular piston has a flange on its inner periphery that allows it to slide on a sliding bearing. Even when molded from a plate-shaped material of This makes it possible to increase the area of the spline engagement portion and ensure axial movement of the output shaft between the annular piston and the drive plate, thereby reducing the influence of the distortion on the annular piston. be able to. Furthermore, when the annular driven plate is fixed to the turbine hub with rivets together with the shell of the turbine runner, the driven plate is precisely centered with respect to the turbine hub together with the annular piston supported on a plain bearing that rotates integrally with the turbine hub. Even if there is a dimensional error due to the dimensional tolerance allowed during manufacturing for accuracy, the dimensional error can be absorbed by the spline engagement gap between the driven plate and the annular piston, so The concentricity can be made extremely good, and vibrations can be prevented from occurring. This eliminates the risk of the annular piston colliding with the plain bearing, thus preventing the occurrence of dents on the plain bearing surface or the sealing member. This prevents burrs from forming in the concave groove in which the annular piston is disposed, and prevents the seal member from protruding from the concave groove. There is no risk of mutual negotiation between the annular piston and the drive plate at the spline engagement portion where the annular piston and the drive plate engage. Therefore, the durability of the annular piston and the engagement portion between the piston and the drive plate is improved, and the flange portion formed on the annular piston and the seal member improve the fluid tightness between the slide bearing and the annular piston. This ensures smooth sliding of the annular piston.

Therefore, according to the present invention, it is possible to provide a fluid coupling equipped with a direct coupling clutch with a vibration absorbing damper device that is compact and has a short axial dimension.

[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, 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 front cover, an annular piston, and a friction material form a direct coupling clutch, and the annular piston slides in the axial direction on a sliding bearing that rotates integrally with the turbine hub of the turbine runner through a flange portion formed on its inner periphery. The annular piston is movably disposed in fluid-tight contact with a sealing material disposed in a circumferential groove formed on the outer periphery of the slide bearing. The vibration absorbing damper device is configured to be able to be freely engaged and detached from the casing and the front cover via a friction material, and the vibration absorbing damper device includes an annular driven plate fixed to the turbine hub by rivets together with the outer shell of the turbine runner at its inner peripheral portion, and the driven plate. A driving plate made of an annular plate-shaped member supported so as to be relatively movable in the circumferential direction on the outer periphery of the plate, and the driven plate and the driving plate are engaged with each other at both ends thereof, respectively. The vibration damper is configured to vibrate in a circumferential direction, and the annular piston is spline-engaged with the drive plate of the vibration absorbing damper device at its outer peripheral edge so as to be movable in the axial direction of the output shaft. A fluid coupling equipped with a direct clutch with a vibration absorption damper device.