JPS5855362B2 - Bidirectional load type ball bearing - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a ball bearing that can support loads in two directions, radial and axial, with a single bearing. outer ring and
This invention relates to a ball bearing composed of three rows of steel balls arranged between them.

Conventionally, it was necessary to use two types of rolling bearings, a radial type and a thrust type, in combination for parts that are subject to action in two directions, radial and axial, such as the shaft acting force of pumps, etc., but with the present invention. The two-way ball bearing can be used alone in such cases, eliminating the need to use two types in combination as in the past.

The present invention will be explained below with reference to FIG. 1 showing an example of implementation.

The outer ring A is the stationary side, and the inner ring B is the rotating side, and the outer circumference of the outer ring 4.2 of the inner ring B, whose upper half vertical cross section is U-shaped as shown in the drawing, is the raceway surface. The inner and outer raceway rings 3 of the outer ring A are formed on these raceway surfaces to have an inverted U-shaped cross section.
. Furthermore, a row of steel balls 6 is inserted between the inner circumference of the outer raceway 2 of the inner ring B and the outer circumference of the inner raceway 3 of the outer race A. Ball group rows 5, 6.
7 are arranged on concentric circles.

Each of these inner and outer circumferential raceway surfaces is provided with a structure composed of curved surfaces 9 to 20 into which steel balls can be inserted and transferred.

Since the ball bearing of the present invention has the above-described structure, when an axial load G and a radial load F are both applied to the shaft 8, the support mechanism for the radial load is similar to the conventional general one. Although it is essentially the same as the radial type bearing, the acting force of the axial load G is due to the fact that the outer ring A is fixed, and the inner curved surfaces 10, 15, 18 curved surface and inner ring B
It is supported by the curved surface of 12.13.20.

In addition, for the axial load H opposite to G, curved surfaces 9, 16, 17 of outer ring A and curved surfaces 11, 14 of inner ring B
, 19.

For example, in the conventional example shown in FIG. 2, there is a gap between the bearing rings 22 and 23, and in the case of FIG. 3, there is a gap between the bearing rings 31 and 32.

In contrast, the object of the present application is a sphere (Fig. 1 5 or 6).
are in close contact in the radial direction.

In the bearing of the present invention, when a load is applied in the axial direction, each of the bearing rings 1 to 4 and the spheres 5, 6, and 7 are in close contact with each other in the radial direction, and there is a gap between the bearing rings 2 and 3 that produces elasticity. Moreover, since bearing rings 1 and 3 or bearing rings 2 and 4 are integrally molded, the axial direction at the mutual contact area between each bearing ring 1 to 4 and each sphere 5 to 7 is There is no distortion of the entire bearing due to misalignment, and the curved surfaces 9 to 20 have the advantage that any load in any axial direction is firmly absorbed.

On the other hand, in a bearing as shown in FIG. 2, in which the outer raceway ring 22 and the inner raceway shaft 23 are not in close contact with each other through a sphere, the raceway rings 22 and 23 have elasticity in the direction of the gap between them. For example, when an axial G-direction load is applied, the force causes damage between the bearing rings 21, 22 and the sphere 25, and between the bearing rings 23,
24 and the sphere 27 open and misalignment occurs, causing distortion in the entire bearing and making it more likely to be damaged during rotation.

In the case as shown in FIG. 3 as well, since there is no sphere between the bearing rings 31 and 32, the amount of deformation due to the load in the axial direction or the load in the radial direction causes a large amount of distortion as in the case of FIG. 2.

In Fig. 4 of the modification of Fig. 3, the normal pressure angle (direction in which pressure is received) at the contact surface between the sphere and the drive wheel is different from β and α for spheres 46 and 47, respectively, and the load is shared on the round sphere. It seems possible to change the ratio, but the radial direction load transmission line N
There is still a gap between the drive wheel and the sphere, which causes displacement in the radial or axial direction due to the load, causing vibration damage.

On the other hand, as mentioned above, the bearing of the present invention has one driving wheel 1 to
4 are closely assembled with spheres 5 to 7, the spheres are supported by curved surfaces 9 to 20 provided on the drive wheels, and there is no displacement between the spheres and the drive wheels or between the drive wheels in both the axial and radial directions. Therefore, it is provided as a ball bearing that can simultaneously withstand loads in all directions without the risk of damage due to distortion, etc., and without relying on a combination of multiple bearings.

As described above, the ball bearing of the present invention has a structure that can support loads in two directions, radial and axial. On the other hand, it is no longer necessary to use two types of rolling bearings, radial type and thrust type, as in the past, and support can be achieved by using only the two-way type ball bearing of the present invention, reducing the number of bearings used and making the bearing box smaller.・It has many advantages not found in conventional rolling bearings, such as reduction in disassembly, maintenance, and assembly man-hours due to transposition and simplified structure, and reduction in machining processing time.

[Brief explanation of the drawing]

FIG. 1 is an axial longitudinal cross-sectional view showing an example of an embodiment of the present invention, and the bearing portion shows the upper half portion. FIGS. 2 to 4 are explanatory diagrams showing conventional examples. In the figure, A is the outer ring, B is the inner ring, 1.2, 21.22°31.
32 is the outer raceway ring, 3, 4, 23, 24° 33.34 is the inner raceway axis, 5, 6, 7, 25, 27° 36.37, 46,
47 is a row of steel balls, 8 is a rotating shaft, 9 to 20 are curved surfaces, F, G
, G', H, and N are load directions, and α and β are pressure angles.

Claims (1)

[Claims] 1 As stated in the text and shown in the drawings, the outer circumferences of the inner and outer raceways of the inner ring formed in a U-shape in cross section are the raceway surfaces, and the inner and outer races of the outer ring with an inverted U-shape in cross section are fitted onto these raceway surfaces. A sphere is inserted between the inner circumferential raceway surface of the outer raceway of the inner ring and the outer circumferential raceway surface of the outer raceway ring of the outer ring. , a two-way load type ball bearing consisting of these spheres arranged on a concentric circumference.