JP2003322239A - Fluid coupling with baffle plate - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fluid coupling with a thin and light baffle plate. <P>SOLUTION: A pump impeller 3 comprises a pump hub 3h, which is mounted on the turbine hub 4h of the turbine impeller 4 pivotally coupled to an output shaft 2 in relative relation through a bearing 9, and a pump shell 3s, which is welded to the external end of the pump hub 3h. The baffle plate 15, which is fitted on the external peripheral face of the pump hub 3h in to a ring like form and thicker than the pump hub 3h is held between a small flange 30 which is formed in the pump hub 3h, and the pump shell 3s. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention has a pump impeller connected to an input shaft and a turbine impeller connected to an output shaft, which are opposed to each other to form a working oil circulation circuit between them. The present invention relates to an improvement of a fluid coupling with a baffle plate in which a baffle plate protruding into the circulation circuit is attached to one of the impellers.

[0002]

2. Description of the Related Art Such a fluid coupling with a baffle plate is already known as disclosed in, for example, Japanese Patent Laid-Open No. 2002-21970.

[0003]

In the conventional fluid coupling with a baffle plate, the baffle plate was formed integrally with the hub of the pump impeller or the turbine impeller at the time of casting of the hub of the pump impeller or the turbine impeller. In order to avoid deformation due to shrinkage, the plates are formed to have approximately the same wall thickness, so it has been difficult to make the baffle plate thin and thus lightweight.

Therefore, it is conceivable to manufacture the baffle plate thinly separately from the hub and weld it to the hub. Even in that case, considering the thermal strain at the time of welding, it is necessary to reduce the thickness of the baffle plate. There is a limit, and it is not enough to satisfy the weight reduction.

The present invention has been made in view of such circumstances, and an object thereof is to provide the fluid coupling having a thin and lightweight baffle plate.

[0006]

In order to achieve the above object, the present invention provides a pump impeller connected to an input shaft and a turbine impeller connected to an output shaft so as to face each other, and between them. Turbine of a turbine impeller in which a pump impeller is connected to an output shaft in a fluid coupling with a baffle plate in which a circulation circuit for working oil is formed and a baffle plate protruding to the circulation circuit is attached to one of both impellers. A pump hub, which is rotatably supported by the hub via bearings, and a pump shell, which is welded to the outer end of the pump hub, are fitted with an annular baffle plate that is fitted to the outer peripheral surface of the pump hub and is thinner than the pump hub. The first feature is that it is sandwiched between a small flange formed on the pump hub and the pump shell.

According to this first feature, the annular baffle plate is independent of the pump hub and other members,
The baffle plate can be formed thinner than the pump hub by itself, and the inner diameter of the annular baffle plate is set to be relatively large corresponding to the outer diameter of the pump hub surrounding the turbine hub. It is also possible to reduce the radial width of the baffle plate, which can greatly reduce the weight of the baffle plate.

Further, since the support of the baffle plate is completed at the same time as the welding of the pump shell to the pump hub, it is easy to manufacture.

Further, according to the present invention, the pump impeller connected to the input shaft and the turbine impeller connected to the output shaft are opposed to each other, and a circulation circuit of working oil is formed therebetween to form a circulation circuit for both impellers. On the other hand, in a fluid coupling with a baffle plate in which a baffle plate protruding to the circulation circuit is attached, the pump impeller is rotatably supported by a turbine hub of a turbine impeller connected to the output shaft via a bearing. A pump hub and a pump shell welded to the outer end of the pump hub, and an annular baffle plate fitted to the outer peripheral surface of the pump hub and thinner than the pump hub, a small flange formed on the pump hub, and the pump hub. The second characteristic is that the outer peripheral surface is clamped by a protrusion formed by caulking.

Also according to this second feature, the annular baffle plate can be formed thinner than the pump hub independently of the pump hub and other members, and the inner diameter of the annular baffle plate is the turbine. Since it is set to be relatively large corresponding to the outer diameter of the pump hub surrounding the hub, it is possible to reduce the radial width of the baffle plate, which can contribute to the weight reduction of the baffle plate.

In the first and second features, the input shaft and the output shaft correspond to the crankshaft 1 and the speed change spindle 2 in the embodiments of the present invention described later, respectively.

[0012]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below based on the embodiments of the present invention shown in the accompanying drawings.

FIG. 1 is a vertical cross-sectional view showing a fluid coupling with a baffle plate according to a first embodiment of the present invention in a non-connected state of a lockup clutch, and FIG. 2 is a function showing a connected state of a lockup clutch of the same fluid coupling. Explanatory drawing, FIG. 3 is 3 of FIG.
3 is a sectional view taken along line -3 and FIG. 4 is a longitudinal sectional view of the baffle plate portion showing the second embodiment of the present invention.

First, a description will be given of the first embodiment of the present invention shown in FIGS.

In FIG. 1, a crankshaft 1 of an automobile engine and a transmission main shaft 2 of a multi-stage transmission are coaxially arranged, and these are connected via a fluid coupling F.

The fluid coupling F includes a pump impeller 3 and a turbine impeller 4 that faces the pump impeller 3 and defines a circulation circuit 5 for the working oil therebetween.

The pump impeller 3 is a bowl-shaped and annular pump shell 3s, and a large number of pump blades 3b, 3b ..., Pump shell 3s which are brazed to the inner surface of the pump shell 3s and arranged in the circulation circuit 5. A retainer plate 3r which is brazed to the inner surface of the pump blades 3b, 3b, 3b, 3b, ...
And a pump hub 3h welded to the inner peripheral edge of the pump shell 3s.

A positioning projection 36 is formed on each blade 3b at an edge facing the core 3c, and a positioning hole 37 with which the positioning projection 36 engages is formed in the core 3c. Further, the retainer plate 3r is provided with positioning notches 35, 35 ... For engagement with the blades 3b.

An annular baffle plate 15 projecting into the circulation circuit 5 is provided on the outer periphery of the pump hub 3h as follows.

The annular baffle plate 15 is formed to be sufficiently thinner than the pump hub 3h, is fitted on the outer peripheral surface of the pump hub 3h, and is integrally formed on the outer periphery of the pump hub 3h. 3h
It is clamped together with the retainer plate 3r by the pump shell 3s welded to.

That is, the pump hub 3h of the pump shell 3s
When welding to, the baffle plate 15 is first fitted to the outer peripheral surface of the pump hub 3h and brought into contact with the small flange 30. Then, the pump shell 3s to which the retainer plate 3r has already been brazed is fitted to the outer peripheral surface of the pump hub 3h, and the baffle plate 15 is pressed toward the small flange 30 side. In this state, the inner peripheral edge of the pump shell 3s is welded to the pump hub 3h. To do.

The turbine impeller 4 is also a bowl-shaped and annular turbine shell 4s, and a large number of turbine blades 4b, 4b ..., Turbine shell which are brazed to the inner surface of the turbine shell 4s and arranged in the circulation circuit 5. These turbine blades 4b, 4b are brazed to the inner surface of 4s.
Retainer plate 4r for pressing the radially inner end of
The turbine core 4c connects the intermediate portions of all the turbine blades 4b, 4b ..., And the turbine shell 4s and the turbine hub 4h welded to the inner peripheral edge of the retainer plate 4r.

A turbine impeller 4 is provided on the pump shell 3s.
A side cover 6 that covers the rear surface of the crankshaft 1 is continuously provided, and a flywheel 7 fixed to the end of the crankshaft 1 is connected to the side cover 6.

A hub 6h is provided at the center of the side cover 6.
Is formed, the end of the transmission main shaft 2 spline-coupled to the turbine hub 4h is rotatably supported by the hub 6h via a bush 8.

The pump hub 3h is arranged so as to surround the turbine hub 4h on the inner peripheral side of the circulation circuit 5, and a ball bearing 9 is interposed between these hubs 3h and 4h. At this time, the inner race 9a of the ball bearing 9 is fitted to the outer peripheral surface of the turbine hub 4h, and the annular shoulder 10 of the turbine hub 4h and the retaining ring 11 locked to the turbine hub 4h are axially moved. It is pinched. The outer race 9b of the ball bearing 9 is fitted to the inner peripheral surface of the pump hub 3h, and the annular shoulder portion 12 of the pump hub 3h,
It is axially sandwiched by the retaining ring 13 that is locked to the pump hub 3h. Thus, the pump impeller 3 and the turbine impeller 4
The two hubs 3h and 4h are axially connected to each other via a ball bearing 9, and the pump hub 3h is rotatably supported on the turbine hub 4h via the ball bearing 9. The ball bearing 9 does not have a seal that allows working oil to flow between the inner and outer races 9a and 9b.

A lock-up clutch L is provided between the turbine impeller 4 and the side cover 6 so as to directly connect them. The lock-up clutch L is defined between the back surface of the turbine impeller 4 and the inner side wall of the side cover 6, and also serves as a clutch chamber 17 as an oil chamber that communicates with the circulation circuit 5, and this clutch chamber 17. The clutch piston 18 is arranged in the clutch chamber 17 so as to be divided into an inner chamber 17a on the turbine impeller 4 side and an outer chamber 17b on the side cover 6 side.
A friction lining 18a is provided on the end surface of the side cover 6 facing the inner wall.

The clutch piston 18 is connected via a torque damper 20 to a plurality of transmission pawls 21 projecting from the rear surface of the turbine impeller 4, and the friction lining 18a.
The seal member 22 is attached to the outer peripheral surface of the turbine hub 4h so as to be movable in the axial direction between a connection position where the side wall is pressed against the inner wall of the side cover 6 and a non-connection position where the side cover 6 is separated from the inner wall.
It is slidably supported via.

The transmission main shaft 2 is provided with a first oil passage 24 which communicates with the outer chamber 17b of the lockup clutch L. The pump hub 3h is integrally formed with a cylindrical oil pump drive shaft 26 which is arranged so as to surround the transmission main shaft 2 and drives the oil pump 27. The oil pump drive shaft 26 and the transmission main shaft 2 are provided between the oil pump drive shaft 26 and the transmission main shaft 2. A second oil passage 25 communicating with the other end surface of the ball bearing 9 is defined therein. Thus,
A ball bearing 9 is provided between the second oil passage 25 and the circulation circuit 5.
Are communicated with each other via.

The first oil passage 24 and the second oil passage 25 are connected to the discharge side of the oil pump 27 and the oil sump 2 by a switching valve 29.
8 and 8 are alternately connected.

Next, the operation of the first embodiment will be described.

When the engine is idling or operating at a low speed, the switching valve 29 is connected to the first oil passage 24 as shown in FIG.
Is connected to the discharge side of the oil pump 27, while the second oil passage 25 is connected to the oil sump 28, which is controlled by an electronic control unit (not shown). Therefore, the rotational torque of the crankshaft 1 of the engine is
When the oil is transmitted to the side cover 6 and the pump impeller 3 to rotate and drive the oil pump 27, the operating oil discharged from the oil pump 27 is transferred to the switching valve 29.
Flow through the first oil passage 24, the outer chamber 17b of the clutch chamber 17 and the inner chamber 17a into the circulation circuit 5 and, after filling the circuit 5, move to the second oil passage 25 via the ball bearing 9 and switch valve Reflux from 29 to the oil sump 28.

In the clutch chamber 17, the outer chamber 17b is the inner chamber 1 due to the flow of the working oil as described above.
Since the pressure becomes higher than that of 7a and the pressure difference causes the clutch piston 18 to be pushed in the direction of being separated from the inner wall of the side cover 6, the lockup clutch L is in the disengaged state, and the pump impeller 3 and the turbine impeller are Four
Allows relative rotation between.

Therefore, when the pump impeller 3 is rotationally driven from the crankshaft 1, the rotation of the pump impeller 3 causes a centrifugal force to act on the working oil in the circulation circuit 5. As described above, in the outer peripheral part of the circulation circuit 5, the torque is transmitted from the pump impeller 3 to the turbine impeller 4 and the working oil is transferred from the turbine impeller 4 to the pump impeller 3 in the inner peripheral part of the circulation circuit 5. Then, such a circulation is repeated.

By the way, in the vicinity of the stall point where the circulation flow rate of the working oil is high, the baffle plate 15 protruding into the circulation circuit 5 obstructs the circulation of the working oil, so that the drag torque can be reduced.

Since the baffle plate 15 has a relatively small resistance to the circulation of the working oil in the normal rotation range where the circulation flow rate of the working oil is small, the working oil circulates in the circulation circuit 5 relatively smoothly, so Efficiency is improved.

When the speed ratio between the pump impeller 3 and the turbine impeller 4 approaches 1, an electronic control unit (not shown)
By switching the switching valve 29 by, as shown in FIG.
The second oil passage 25 is connected to the discharge side of the oil pump 27, and the first oil passage 24 is connected to the oil sump 28. As a result, the discharge working oil of the oil pump 27 passes through the second oil passage 25 from the switching valve 29, flows into the circulation circuit 5 through the ball bearing 9 and fills the circuit 5 contrary to the previous time. After that, move to the inner chamber 17a of the clutch chamber 17,
It also fills the chamber 17a. On the other hand, since the outer chamber 17b of the clutch chamber 17 is opened to the oil sump 28 via the first oil passage 24 and the switching valve 29, in the clutch chamber 17, the inner chamber 17a has a higher pressure than the outer chamber 17b. The clutch piston 18 is pressed toward the side cover 6 side by the pressure difference, the friction lining 18a is brought into pressure contact with the inner wall of the side cover 6, and the lockup clutch L is brought into the connected state.

By connecting the lock-up clutch L as described above, the pump impeller 3 and the turbine impeller 4 are directly connected to each other, so that the rotation of the crankshaft 1 can be performed regardless of the reduction in the fluid transmission efficiency of the baffle plate 15. Torque can be efficiently transmitted to the speed-change main shaft 2, that is, high transmission efficiency can be achieved, and fuel consumption can be reduced.

Thus, it is possible to satisfy both the reduction of the drag torque and the improvement of the transmission efficiency between the two impellers 3 and 4 during the normal operation of the engine.

In such a fluid coupling F with a baffle plate, the annular baffle plate 15 fitted to the outer peripheral surface of the pump hub 3h has a small flange 30 on the outer periphery of the pump hub 3h and the pump shell 3 welded to the pump hub 3h.
Since it is held together with the retainer plate 3r by s, it is possible to independently form the pump hub 3h to be thinner than the pump hub 3h regardless of the pump hub 3h and other members. Further, the inner diameter of the annular baffle plate 15 is the turbine hub. Since the baffle plate 15 is set to have a relatively large size in accordance with the outer diameter of the pump hub 3h surrounding the 4h, it is possible to reduce the radial width of the baffle plate 15 and, as a result, reduce the weight of the baffle plate 15. This greatly contributes to the weight reduction of the fluid coupling F.

Further, since the support of the baffle plate 15 is completed at the same time when the pump shell 3s is welded to the pump hub 3h, it is easy to manufacture.

Further, the retainer plate 3r, the baffle plate 15, the small flange 30 and the pump shell 3 are also provided.
Since it is sandwiched between s, the brazed portion of the retainer plate 3r with the pump shell 3s is reinforced.

Next, a second embodiment of the present invention will be described with reference to FIG.

In the second embodiment of the present invention, the pump hub 3h
The annular baffle plate 15 fitted to the outer peripheral surface of the pump hub 3h and the small flange 30 on the outer periphery of the pump hub 3h.
It is clamped by the projection 31 formed by caulking on the outer peripheral surface of the. After the clamping, the pump shell 3s becomes the pump hub 3h.
Be welded to. The protrusion 31 may be an annular protrusion or a plurality of protrusions arranged in an annular shape.

The other structure is the same as that of the previous embodiment, and in FIG. 4, the same parts as those of the previous embodiment are designated by the same reference numerals and the description thereof will be omitted.

Also according to the second embodiment, the baffle plate 15 can be formed thinner than the pump hub 3h by itself, and the annular baffle plate 1 can be formed.
The inner diameter of 5 is the pump hub 3 surrounding the turbine hub 4h.
Since the baffle plate 15 is set to have a relatively large size corresponding to the outer diameter of h, it is possible to reduce the radial width of the baffle plate 15, which greatly reduces the weight of the baffle plate 15 and the weight of the fluid coupling F. Can be contributed to.

The present invention is not limited to the above embodiment, and various design changes can be made without departing from the scope of the invention. For example, the present invention can be applied to a fluid coupling that does not have a lockup clutch.

[0047]

As described above, according to the first aspect of the present invention, the pump impeller connected to the input shaft and the turbine impeller connected to the output shaft are opposed to each other and actuated therebetween. Turbine hub of a turbine impeller in which a pump impeller is connected to an output shaft in a fluid coupling with a baffle plate in which an oil circulation circuit is formed and a baffle plate protruding to the circulation circuit is attached to one of both impellers. A pump hub that is rotatably supported relative to each other by a bearing, and a pump shell that is welded to the outer end of the pump hub, and an annular baffle plate that is fitted to the outer peripheral surface of the pump hub and that is thinner than the pump hub. Since the small flange formed on the pump hub and the pump shell are sandwiched, the annular baffle plate is independent of the pump hub and other members. Alone it is possible to form thinner than the pump hub, yet the inner diameter of the annular baffle plate, corresponding to the outer diameter of the pump hub surrounding the turbine hub, from would be set relatively large,
It is also possible to reduce the width of the baffle plate in the radial direction, greatly reducing the weight of the baffle plate and contributing to the weight reduction of the fluid coupling. Moreover, the support of the baffle plate is completed at the same time as the welding of the pump shell to the pump hub, so that it is easy to manufacture.

Further, according to the second feature of the present invention, the pump impeller connected to the input shaft and the turbine impeller connected to the output shaft are opposed to each other, and a circulation circuit of the working oil is provided therebetween. In a fluid coupling with a baffle plate, in which a baffle plate protruding to the circulation circuit is attached to one of both impellers, the pump impeller is connected to the turbine hub of the turbine impeller connected to the output shaft via a bearing. An annular baffle plate, which is composed of a pump hub rotatably supported relative to one another and a pump shell welded to the outer end of the pump hub and is fitted to the outer peripheral surface of the pump hub and is thinner than the pump hub, is formed on the pump hub. Since the small flange and the protrusion formed by caulking on the outer peripheral surface of the pump hub are sandwiched, the annular baffle plate is also It can be made thinner than the pump hub independently of the pump hub and other members, and the inner diameter of the annular baffle plate is set to be relatively large, corresponding to the outer diameter of the pump hub surrounding the turbine hub. Therefore, the width of the baffle plate in the radial direction can be reduced, which can greatly reduce the weight of the baffle plate and contribute to the weight reduction of the fluid coupling.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view showing a fluid coupling with a baffle plate according to a first embodiment of the present invention in a non-connection state of a lockup clutch.

FIG. 2 is an operation explanatory view showing a connection state of a lockup clutch of the fluid coupling.

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

FIG. 4 is a vertical sectional view of a baffle plate portion showing a second embodiment of the present invention.

[Explanation of symbols]

F ... Fluid coupling 1. Input shaft (engine crankshaft) 2 output shaft (shift main shaft) 3 ... Pump impeller 3h ... pump hub 3s ・ ・ ・ ・ Pump shell 4 ... Turbine impeller 4h ... Turbine hub 5 ... Circulation circuit 9 ... Bearing (ball bearing) 15 ... Baffle plate 30 ... Small flange 31 ... Protrusion

Claims (2)

[Claims] 1. A pump impeller (3) connected to an input shaft (1) and a turbine impeller (4) connected to an output shaft (2) are opposed to each other, and working oil circulates between them. A baffle plate (1) that forms a circuit (5) and projects into the circulation circuit (5) on one of both impellers (3, 4).
In a fluid coupling with a baffle plate attached with 5), a pump impeller (3) is connected to a turbine hub (4h) of a turbine impeller (4) connected to an output shaft (2) via a bearing (9). A pump hub (3h) that is rotatably supported relative to one another, and a pump shell (3s) welded to the outer end of the pump hub (3h), and is an annular pump hub that is fitted to the outer peripheral surface of the pump hub (3h). (3h)
A fluid coupling with a baffle plate, wherein a thinner baffle plate (15) is sandwiched between a small flange (30) formed on the pump hub (3h) and the pump shell (3s). 2. A pump impeller (3) connected to the input shaft (1) and a turbine impeller (4) connected to the output shaft (2) are opposed to each other, and a working oil circulation is provided therebetween. A baffle plate (1) that forms a circuit (5) and projects into the circulation circuit (5) on one of both impellers (3, 4).
In a fluid coupling with a baffle plate attached with 5), a pump impeller (3) is connected to a turbine hub (4h) of a turbine impeller (4) connected to an output shaft (2) via a bearing (9). A pump hub (3h) that is rotatably supported relative to one another, and a pump shell (3s) welded to the outer end of the pump hub (3h), and is an annular pump hub that is fitted to the outer peripheral surface of the pump hub (3h). (3h)
A thinner baffle plate (15) is provided with a small flange (30) formed on the pump hub (3h) and a protrusion (3) formed by caulking on the outer peripheral surface of the pump hub (3h).
1) A fluid coupling with a baffle plate, which is sandwiched between and.