JP2000161385A - Bearing for hydraulic multiple disc clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a bearing for a hydraulic multiple disc clutch, simple in structure, and excellent in durability and operation reliability. SOLUTION: An inner race 71 and outer race 73 of a bearing 70 are formed up by means of sheet metal working. Plural notches are provided at every specified intervals at the tip end part of the outer race 73, cut-out pieces formed by the aforesaid notches are bent outward every one piece so as to be formed into projected parts 73c, and concurrently, intermittent cut-out pieces which are left as they are not bent outward, are thereby formed into clutch pressurizing parts 73b.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing for a hydraulic multi-plate clutch having a simple structure and excellent in durability and operation reliability.

[0002]

2. Description of the Related Art A hydraulic multi-disc clutch has a hydraulic chamber for operating a piston, and an operating oil pressure applied to the hydraulic chamber is transmitted to a clutch plate via a piston, thereby engaging and disengaging the clutch. Release, slip control, and the like are performed.

When the above-mentioned hydraulic multi-plate clutch is used, for example, as a differential limiting device for a center differential device, a hydraulic chamber is provided on the housing side of the center differential device in order to prevent centrifugal hydraulic pressure from being generated by rotation. On the other hand, it is desirable that a clutch drum accommodating a clutch plate therein is provided rotatably relative to the housing. . In such a case, for example, JP-A-2-29073 by the present applicant
As disclosed in Japanese Patent Application Publication No. 1 (1993) -111, generally, a ball bearing (bearing) and a pressure plate are interposed between a piston and a clutch plate, and the piston is connected to the clutch via the ball bearing and the pressure plate. While rotating relative to the plate, the clutch plate is pressed according to the operating oil pressure.

[0004]

However, indirectly pressing the clutch plate via the pressure plate as described above causes a complicated structure and a large-sized device. Further, since the piston and the clutch plate are connected via a plurality of members, the processing tolerances of the respective components are accumulated, and it is difficult to arrange the respective members concentrically during assembly, which causes an If the hydraulic multi-plate clutch is operated in the state of being centered, there is a possibility that the durability and operation reliability of the bearing may be reduced particularly at high speed continuous rotation.

The present invention has been made in view of the above circumstances, and has as its object to provide a hydraulic multi-plate clutch bearing having a simple structure and excellent durability and operation reliability.

[0006]

According to a first aspect of the present invention, there is provided a bearing for a hydraulic multi-plate clutch, comprising: a clutch portion provided in a rotatable clutch drum; A hydraulic multi-plate clutch bearing, which is interposed between the pistons disposed in such a manner as to be rotatable relative to each other and is capable of transmitting the hydraulic pressure applied to the pistons to the clutch portion. An inner race to be fitted, and an outer race fitted to the inner race so as to be relatively rotatable via a plurality of balls,
The outer race is integrally formed with a clutch pressing portion having an intermittent pressing surface capable of pressing the clutch portion, and a projection that engages with the clutch drum and regulates relative rotation between the outer race and the clutch drum. It is characterized by having been formed.

In a second aspect of the present invention, the outer race and the inner race are formed by sheet metal processing of a steel plate member in the first invention.

In the third aspect of the present invention, in the hydraulic multi-plate clutch bearing according to the second aspect of the present invention, a plurality of cuts are provided at predetermined intervals at a tip end of the outer race, and the cuts formed by the cuts are formed. The present invention is characterized in that the projections are formed by bending outwardly for each of the pieces, and a piece that is not bent outwardly is formed as the clutch pressing portion.

[0009]

Embodiments of the present invention will be described below with reference to the drawings. 1 is an enlarged sectional view of a main part of a center differential device, FIG. 2 is a skeleton diagram schematically showing a drive system of a four-wheel drive vehicle including the center differential device, and FIG. It is a perspective view showing an outer race.

Referring to FIG. 2, a vertical transaxle type drive system to which the present invention is applied will be described. A transmission case 3 is joined to a rear portion of a torque converter case 1 and a differential case 2, and a rear portion of the transmission case 3 is provided. An extension case 4 is joined to the transmission case 3, and an oil pan 5 is attached to a lower portion of the transmission case 3.

Reference numeral 10 denotes an engine, and the crankshaft 11 of the engine 10 is connected to the torque converter case 1.
It is connected to a torque converter 13 having an internal lock-up clutch 12, and an input shaft 14 from the torque converter 13 is input to an automatic transmission 30 inside the transmission case 3.

An output shaft (transmission output shaft) 15 from the automatic transmission 30 outputs coaxially with the input shaft 14, and the output shaft 15 is coaxially connected to a center differential device 50 inside the extension case 4. Have been.

Inside the transmission case 3, a front drive shaft 16 is disposed parallel to an input shaft 14 from the torque converter 13 and the transmission output shaft 15, and a rear end of the front drive shaft 16 is connected to the center differential device. 5
0 through a pair of reduction gears 17, 18 (transfer drive gear 17, transfer driven gear 18), and the front end of the front drive shaft 16 is driven by front wheels via a front differential device 19 inside the differential case 2. Is configured to be transmitted.

On the other hand, the output from the center differential device 50 is transmitted to a rear drive shaft 20, and the rear drive shaft 20 is configured to transmit a driving force to rear wheels via a propeller shaft 21, a rear differential device 22, and the like. ing.

The automatic transmission 30 has a front planetary gear 31, a rear planetary gear 32, and the front planetary gear 31 and the rear planetary gear 32.
On the other hand, the high clutch 33, the reverse clutch 34, the brake band 35, the forward clutch 36, the overrunning clutch 37, the low and reverse brake 3
8, one-way clutches 39 and 40 are provided, and by selectively engaging these one-way clutches, four forward speeds and one reverse speed are obtained.

An oil pump 41 is provided in front of the automatic transmission 30 so as to connect the impeller sleeve 13a of the torque converter 13 and the drive shaft 42 so as to be always driven. The control valve body 43 is housed. The control valve body 43 supplies and discharges oil to and from each friction engagement element of the clutch or brake and selectively engages.

Next, the center differential device 50 will be described with reference to FIG.

The transmission output shaft 15 and the rear drive shaft 20 are rotatably fitted coaxially via a radial bearing 23, and the transfer drive gear 17 is connected to the transmission output shaft via a radial bearing 24 and a thrust bearing 26. It is rotatably fitted to the shaft 15.

The transfer drive gear 17 and the transmission output shaft 15 are supported by the transmission case 3 via ball bearings 25.

The rear drive shaft 20 is supported via a ball bearing 27 on the inner periphery of a cylindrical projection 4a projecting rearward in the extension case 4.

A composite planetary gear type center differential device 50 is coaxially provided between the transmission output shaft 15, the rear drive shaft 20, and the transfer drive gear 17.

That is, a large-diameter first sun gear 51 is formed on the transmission output shaft 15 on the input side of the center differential device 50.
Sun gear meshes with the small diameter first pinion 52 to
Gear train is formed.

A second sun gear 53 having a small diameter is formed adjacent to the first sun gear on the rear drive shaft 20 for outputting power to the rear wheels, and the second sun gear 53 is large. The second gear train is formed by meshing with the second pinion 54 having a diameter.

The first pinion 52 and the second pinion 54 are formed integrally with a pinion member 55, and a plurality (for example, three) of the pinion members 55 are respectively fixed to a carrier 56 described later. It is rotatably supported on a shaft 58.

The transfer drive gear 17 is connected to the front end of the carrier 56.
From the front to the front wheels.

The transmission output shaft 15 is rotatably inserted into the carrier 56 from the front, while the rear drive shaft 20 is rotatably inserted from the rear, and the first sun gear 51 is inserted in the center of the space. And the second sun gear 53 are stored. Each of the first pinions 52 of the plurality of pinion members 55 corresponds to the first sun gear 51, and each of the second pinions 54 corresponds to the second pinion 54.
Each of the pinion shafts 58 is mounted on the sun gear 53 so as to mesh with each other.

Behind the carrier 56, a hydraulic multiple disc clutch 60 for limiting the differential of the center differential device 50 is provided.

More specifically, a cylindrical clutch drum 61 having a rear end opened is connected to the rear of the carrier 56, and the clutch drum 61 rotates around the rear drive shaft 20 via a ball bearing 62. It is movably supported.

A clutch hub 63 is spline-coupled to the rear drive shaft 20. The outer periphery of the clutch hub 63 is opposed to the inner periphery of the clutch drum 61, and a clutch portion 64 is provided between them.

The clutch portion 64 includes a clutch hub 63
A plurality of drive plates 65 spline-coupled to the outer periphery of the clutch drum 61 and a plurality of driven plates 66 spline-coupled to the inner periphery of the clutch drum 61 are alternately arranged to form a main part, and these are engaged. Thereby, torque transmission between the rear drive shaft 20 and the carrier 56 is possible.

On the other hand, near the inner rear end of the extension case 4, a piston 67 slidable on the inner periphery of the extension case 4 and the outer periphery of the projection 4a is provided so as to face the clutch portion 64. A hydraulic chamber 68 is formed between the piston 67 and the extension case 4.

A hydraulic oil supply passage 69 communicates with the hydraulic chamber 68, and the piston 67 is operated by a hydraulic pressure supplied by a hydraulic control device (not shown).

A bearing 70 is connected between the clutch portion 64 and the piston 67 so as to be relatively rotatable. The piston 67 can press the clutch portion 64 via the bearing 70. ing.

Hereinafter, the configuration of the bearing 70, which is the gist of the present invention, will be described in detail. The bearing 70 includes an inner race 71 slidably supported by the protrusion 4a of the extension case 4 and an outer race 7 rotatably supported by the inner race 71 via a plurality of balls 72.
3 is provided.

The inner race 71 is formed of an annular steel plate member formed by sheet metal working.

At the end of the inner race 71, a cylindrical portion 71a which can be fitted to the projection 4a of the extension case 4 is provided.
This cylindrical portion 71a is slidably fitted to the protrusion 4a. Further, a step portion 71b is formed behind the cylindrical portion 71a, and an outwardly curved portion 71c is formed behind the step portion 71b.

Here, a key groove 4b is formed in the projection 4a in the axial direction, and a cylindrical portion 71 is formed in the key groove 4b.
By fitting a key 71d provided inwardly at a, the rotation of the inner race 71 is restricted, and the inner race 71 is supported by the projection 4a in a state in which only movement in the axial direction is permitted.

A spring receiver 74 is provided near the tip of the projection 4a.
The inner race 71 is urged rearward by a return spring 75 interposed between the inner race 71 and the piston 67 at the rear end of the inner race 71.

The outer race 73 is formed of an annular steel plate member formed by sheet metal working. The outer race 73 is formed to have a larger diameter than the inner race 71 and is disposed on the outer periphery of the inner race 71.

A curved portion 73a is formed on the rear side of the outer race 73 at a position facing the curved portion 71c of the inner race 71.

Here, the curved portion 71c of the inner race 71
And the curved portion 73a of the outer race 73 are formed in a shape capable of holding a plurality of balls 72 in these gaps.
The outer race 73 is rotatably supported by the inner race 71 via a plurality of balls 72 held between the curved portion 71c and the curved portion 73a.

As shown in FIG. 3, a plurality of cuts are provided at predetermined intervals at the end of the outer race 73, and the cuts formed by the cuts are bent outward for each of the cuts. The projection 73c is formed.

The rear end of the clutch drum 61 is provided with a groove 61a at a position corresponding to the projection 73c. The projection 73c is fitted into the groove 61a, so that the outer race 73 is formed. Is engaged with the clutch drum 61 in a state where relative rotation is restricted and only axial movement is permitted. That is,
The outer race 73 is configured to rotate integrally with the clutch drum 61 by a projection 73c.

On the other hand, at the end of the outer race 73, the piece that is not bent is abutted on the driven plate 66 located at the rearmost position in the clutch drum 61 as the clutch pressing portion 73b.

That is, the outer race 73 of the bearing 70 has a clutch pressing portion 73b capable of pressing the clutch portion 64.
And a projection 73c that can be fitted into the concave groove 61a of the clutch drum 61 are integrally formed.

Next, in the above-described configuration, first, the power of the engine 10 is input to the automatic transmission 30 via the torque converter 13 and the input shaft 14, and the transmission power automatically shifted by the automatic transmission 30 is transmitted. From the output shaft to the first sun gear 51 of the center differential device 50. The shifting power input to the first sun gear 51 is
According to the torque distribution ratio set by the specifications of each gear element, the reduction gear 17 integrated with the carrier 55 is used.
And output to the second sun gear 53. Here, the torque distribution to the reduction gear 17 and the second sun gear 53 is differentially limited by the hydraulic multi-plate clutch 60.

When the shifting power of the first sun gear 51 is distributed to the carrier 56, the clutch drum 6
1 is rotated integrally with the carrier 56. Accordingly, the driven plate 66 and the outer race 73 are rotated integrally with the clutch drum 61. At this time, the outer race 73 is coaxially aligned with the transmission output shaft 15 and the rear drive shaft 20 by the centering function by its own rotation.

That is, since the clutch pressing portion 73b is formed so as to intermittently contact the driven plate 66, the frictional resistance between the driven plate 66 and the clutch pressing portion 73b is small. It can slide easily with respect to the driven plate 66. For this reason, the outer race 73 is centered at an appropriate position by the centrifugal force at the time of its rotation.

Therefore, when the center differential device 50 is driven, the outer race 73 and the inner race 7
1 can always be positioned concentrically, and without excessive force being applied to the bearing 70, the durability of the bearing 70 can be improved and the operation reliability can be improved.

Further, since the clutch pressing portion 73b for pressing the driven plate 66 is formed intermittently, the lubricating oil for lubricating the clutch portion 64 can be easily discharged outward from between the clutch pressing portions 73b. In addition, the circulation of the lubricating oil becomes smooth.

Further, since the inner race 71 and the outer race 73 of the bearing 70 are formed by sheet metal working, the manufacturing process can be simplified and the production cost can be reduced.

Also, by forming the outer race 73 by sheet metal working, the clutch pressing portion 73b can be easily formed integrally with the outer race 73. Therefore, there is no need to interpose an intermediate member such as a pressure plate between the outer race 73 and the clutch part 64, and the number of parts can be reduced, the manufacturing process can be simplified, the production cost can be reduced, and the like.

Further, by forming the stepped portion 71b on the inner race 71 and bringing the return spring 75 into direct contact with the stepped portion 71b, the bearing 70 can be made compact.

Since the outer race 73 is externally fitted on the outer periphery of the inner race 71 via the ball 72,
The axial dimension of the bearing 70 can be reduced.

[0055]

As described above, according to the present invention, it is possible to provide a bearing for a hydraulic multi-plate clutch having a simple structure and excellent in durability and operation reliability.

[Brief description of the drawings]

FIG. 1 is an enlarged sectional view of a main part of a center differential device.

FIG. 2 is a skeleton diagram schematically showing a power distribution control device of a four-wheel drive vehicle.

FIG. 3 is a perspective view showing an outer race.

[Explanation of symbols]

 Reference numeral 60: hydraulic multi-plate clutch 61: clutch drum 64: clutch part 67: piston 70: bearing (bearing for hydraulic multi-plate clutch) 71: inner race 72: ball 73: outer race 73b: clutch pressing part 73c: projection

Claims (3)

[Claims] 1. A clutch unit disposed in a rotatable clutch drum and a piston disposed opposite to the clutch unit, which are connected to each other so as to be relatively rotatable. In a bearing for a hydraulic multi-plate clutch capable of transmitting operating hydraulic pressure applied to the piston to the clutch portion, an inner race which is pressed against the piston, the outer race is rotatably rotatable relative to the inner race via a plurality of balls. An outer race to be fitted, a clutch pressing portion having an intermittent pressing surface capable of pressing the clutch portion, and a relative rotation between the outer race and the clutch drum engaged with the clutch drum. A bearing for a hydraulic multi-plate clutch, wherein a restricting projection is integrally formed. 2. The hydraulic multi-plate clutch bearing according to claim 1, wherein the outer race and the inner race are formed by sheet metal processing of a steel plate member. 3. A plurality of cuts are provided at predetermined intervals at a tip end of the outer race, and the cuts formed by the cuts are bent outwardly for each interval to form the protrusions. 3. A piece which is not bent to a predetermined angle is formed as the clutch pressing portion.
4. The bearing for a hydraulic multi-plate clutch according to item 1.