JPS609466Y2 - Combination unit of single row ball bearing and cam roller clutch with foot - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to a combination with a roller type one-way clutched bearing, and particularly to a combination of a legged cam roller clutch and a single row ball bearing for use in places with large radial loads.

Conventionally, since one-way clutches generally cannot bear radial and thrust loads, it has been necessary to provide bearings on both sides of the one-way clutch to support it when it is used in places where these loads are large.

In addition, for legged cam roller clutches that have an inner ring and an outer ring, when used in places with extremely light radial loads such as torque converter stators, they are used alone without being combined with a bearing, but the belt This type of one-way clutch is not used in places where there is a large radial load due to gears, sprags, etc., and sprag type or roller type one-way clutches without legs are used, and in most cases, two-way clutches are used.
Row support bearings are used.

However, when two rows of bearings are used, the mounting width inevitably increases, making it unsuitable for use in devices that require a compact one-way clutch.

The present invention overcomes the above-mentioned difficulties by providing a combination unit with a special configuration of a single row ball bearing and a footed cam roller clutch using one ball bearing and a footed cam as the other bearing. The purpose is to overcome it.

That is, the present invention makes the gap between the circumferential surface of the inner ring or outer ring and the circumferential surface of the leg cam larger than the radial clearance of a single row ball bearing and smaller than the amount of inclination of the outer ring, which will be described later, to reduce radial and thrust loads. Most of the load is carried by the ball bearing, and only the load that falls due to the angular gap, that is, the load that this contact part receives when the inner ring and outer ring are tilted relative to each other and the curved surface of the inner ring or outer ring contacts the circumferential surface of the leg cam. By supporting the bearing with a cam with legs, it is possible to use a single row of bearings even under large radial loads, thereby overcoming the above-mentioned difficulties.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below based on embodiments of the present invention with reference to the accompanying drawings.

FIG. 1 shows a sectional view of a combination unit according to the present invention.

Reference numeral 1 denotes an outer ring, which in FIG. 1 has an approximately cylindrical outer peripheral surface and a two-stage approximately cylindrical inner peripheral surface.
The outer peripheral surface is processed in various ways depending on various external environments, and lubricating plugs, pulleys, etc. (not shown) are attached.

The two-stage inner circumferential surface of the outer ring 1 is divided into a portion 2 of the inner ring 5 that faces the outer circumferential surface of the legged cam 6 and a portion 3 that faces the cylindrical outer circumferential surface of the inner ring.

A groove 4 for fitting a retaining ring 18, which will be described later, is formed in the portion 3.

Reference numeral 5 denotes an inner ring which extends from the legged cam 6 forming a plurality of cam surfaces 8 and a plurality of protrusions 7 and the cylindrical outer peripheral surface (see FIG. 2).

When the inner ring 5 and outer ring 1 are aligned with their end surfaces aligned,
A space (see FIG. 2) is formed by the cam surface 8 and protrusion 7 of the inner ring 5 and the inner circumferential surface 2 of the outer ring 1, and the cylindrical part 3 of the outer ring 1 faces the part 3 of the inner ring 5. An annular space is formed by the cylindrical outer peripheral surface.

At this time, a roller 10 is placed in this space by a spring 11.
is biased toward the narrower gap between the cam surface 8 and the inner circumferential surface 2 of the outer ring 1.

The pattern is illustrated in FIG.

Further, a ball bearing having a plurality of balls 15 is positioned in the orbit of the inner ring 11 and the outer ring 16 in the annular space described above, and the groove 4
The ball bearing is fixed in the axial direction by a retaining ring 18 fitted therein.

Although the above description has been made based on the inner cam type roller clutch shown in FIG. 2, the roller clutch may also be of the outer cam type shown in FIG.

Regarding the structure, the only difference is that the cam surface 8, the protrusion 7, etc. are formed on the outer ring 1, so a description thereof will be omitted.

Further, explanations of the following effects and the like will also be omitted.

When all the parts are assembled as described above, the inner ring 5 and the outer ring 1 are arranged so that a gap β of the following size is provided between the inner circumferential surface of the outer ring 1 and the opposing surface of the protrusion 7. is shaped (see Figures 2, 3 and 4).

That is, the clearance β between the legged cam 6 and the outer ring 1 is larger than the predetermined radial clearance α of the ball bearing (see FIG. 4), and the amount of inclination of the outer ring 1 due to the ball bearing when the inner ring 5 does not have the protrusion 7, i.e. It is set smaller than the amount of inclination γ determined purely by the internal structure (see Figure 5), which is determined by calculations based on the radial clearance α, the radius of the ball 15, etc. When a directional load is applied to the combination unit according to the present invention, the outer ring 1 does not tilt excessively, and no abnormal wear occurs between the inner circumferential surface 2 of the outer ring 1 and the facing surface of the protrusion 7 of the inner ring 5. I am trying to handle this load.

Next, the operation of the present invention will be explained based on the above configuration.

When the inner ring 5 rotates clockwise relative to the outer ring 1 in FIG.
The gap between the cam surface 8 and the cam surface 8 is wedged in the direction of the narrower portion, and due to the wedge action of the roller 10, a large frictional force is generated between the roller, the cam surface 8, and the inner circumferential surface 2 of the outer ring 1, and the inner ring 5 and the outer ring 1 It rotates integrally with.

When the inner ring 5 rotates counterclockwise relative to the outer ring 1, the roller 10 moves between the inner circumferential surface 2 of the outer ring 1 in the above-mentioned space and the cam surface, even though the roller 10 is biased in the above-mentioned direction by the spring 11. 8
The inner ring 5 and the outer ring 1 are moved in the direction of the wider space, and the above-mentioned frictional force is not large enough to cause the inner ring 5 and the outer ring 1 to rotate together.

Drifting occurs.

When the combination unit according to the present invention receives a large load in the radial direction shown by arrow A in FIG. and the legged cam 6.

As is clear from the above explanation of the structure and operation, according to the combination unit of a single row ball bearing and a legged cam roller clutch according to the present invention, most of the load in the radial and thrust directions is carried by the ball bearing, and the bearing is disposed in the gap β. By having the leg cam support only the load of the fall due to the corner gap, this compact combination unit of the present invention can be used in areas with large radial loads without excessive wear between the leg cam and the outer ring. It becomes possible to install with a smaller installation width.

In addition, since the load is supported separately at this time, the life of the ball bearing can be extended.

[Brief explanation of the drawing]

FIG. 1 is a sectional view of the combination unit according to the present invention, taken along the line II in FIG. 2. FIG. FIG. 2 is a plan view of a portion of an inner cam type legged cam roller clutch, and FIG. 3 is a view similar to FIG. 2 of an outer cam type legged cam roller clutch. Fig. 4 is an enlarged sectional view of the combination unit according to the present invention showing the radial clearance of the ball bearing and the gap between the leg of the leg cam and the outer ring, and Fig. 5 is an enlarged sectional view of the combination unit according to the present invention, showing the radial clearance of the ball bearing and the gap between the leg of the leg cam and the outer ring. It is a figure similar to FIG. 4 showing the amount of inclination of the outer ring. Explanation of symbols of main parts, inner ring...5, outer ring...
...1, Cam with legs ...6, Roller ...
・10, Spring...11, Ball bearing...1
5, 16, 17, protrusion...7°

Claims (1)

[Scope of utility model registration request] A roller-type one-way clutch having a cam with legs, a roller, and a spring, and a single-row ball bearing are provided adjacent to each other in the axial direction between an inner ring that moves integrally and an outer ring that moves integrally. In the combination unit of cam roller clutch with
α is the radial clearance of the ball bearing, β is the clearance between the outer ring or inner ring and the protruding part of the leg cam, and γ is calculated based on the radial clearance and the radius of the ball of the ball bearing, and is purely internal. If the amount of inclination of the outer ring or inner ring due to the ball bearing when there is no protruding part of the cam with legs is determined by the structure, then the gap between the outer ring or inner ring and the protruding part of the cam with legs is γ〉 A combination unit characterized by setting β>α.