RU2529931C2 - Radial-thrust rolling bearing - Google Patents

Abstract

FIELD: machine building.

SUBSTANCE: invention refers to production of all items and can be used in bearing industry at their manufacturing. A radial-thrust rolling bearing consists of external and internal races with two pairs of annular grooves and rolling elements. The rolling elements consist of cylindrical rollers and balls installed in the first pair of annular grooves. The number of balls set between two adjacent rollers is equal to the maximal number of balls set in the first pair of annular grooves in one row parallel to the bearing axis. Under the radial load on the bearing it is rotated with rolling of the rollers in the first pair of annular grooves provided in the internal and external races of the bearing. The roller diameter exceeds the ball diameter by at least the value of maximal contact deformations which provides for the transfer of radial load via the rollers. Under the radial load on the bearing the balls are an improved separator as they decrease the losses of energy for contacts with rollers. Under axial load on the bearing the movable ring is shifted in the direction of the bearing axis up to the contact of the balls with the second pair of annular grooves, and the balls become the rolling elements keeping the separation functions as well. Initial contact of the balls with the second pair of annular grooves is achieved due to the selection of roller length, width of the first pair of annular grooves, ball diameter and arrangement of the annular grooves.

EFFECT: longer service life of rolling bearings, reduced friction losses and lower labour inputs in bearing production.

2 cl, 1 dwg

Description

The invention relates to the production of all products in which the task is to increase the service life of angular contact bearings, and can be used in the bearing industry in the manufacture of angular contact bearings with a long resource. As an analogue, U.S. Patent No. 3,124,396 was adopted for a rolling bearing, in which instead of a cage, separators of the cylinder type are used, and holding rings are used to secure and hold the cylinders. A large number of contacted parts of the bearing inevitably leads to large friction losses, which reduces the service life of the bearing. The complexity of the assembly leads to unreasonably high cost of the bearing.

As a prototype, patent No. 002947 was adopted for a clean rolling bearing and its variants in terms of the shape and design of the locking elements. The locking elements are fixed by retaining rings, which together replace the separator with sliding friction between the balls and the separator. The point contacts stated in the prototype do not eliminate sliding friction, but lead to high contact pressures. Sliding friction always occurs when the speeds of different parts at a common point of contact differ in magnitude, in direction, or differ in magnitude and direction. The bearing does not provide a selection of gaps between the balls and bearing rings, which leads to an unstable position of the axis of rotation of the bearing. In a pure rolling bearing, the maximum diameters of the locking elements are smaller than the diameter of the balls, which at possible contacts leads to high rotation speeds of the locking elements and to an increase in sliding friction.

The proposed design of the angular contact rolling bearing is the outer and inner rings of the bearing, between which cylindrical rollers and balls are located in a certain way. In the drawing are indicated:

1 - outer ring of the bearing;

2 - an internal ring of the bearing;

3 - bearing rollers;

4 - balls of the bearing;

5 - annular grooves for rolling rollers;

6 - annular grooves for rolling balls;

7-beads.

The drawing shows a bearing in which one ball 4 is located between the two nearest rollers 3. In general, the number of balls 4 between the two nearest rollers 3 is equal to the maximum number of balls, which is located in the first pair of annular grooves 5, in one row parallel to the axis of the bearing and is determined by the width of the first pair of annular grooves 5. By increasing the number of balls 4 between the two nearest rollers 3, we increase the length of the rollers 3 and increase its load capacity with respect to the radial load. The carrying capacity with respect to the axial load does not change. With a radial load on the bearing, rotation in the bearing occurs when the cylindrical rollers 3 are run between the annular grooves 5. The diameter of the rollers 3 is greater than the diameter of the balls 4 by at least the maximum contact deformation, which ensures the transfer of radial load through the rollers 3. The location of the balls 4 in the annular grooves 5 between the nearest rollers 3 eliminates their contact with each other.

Balls 4 at a radial load represent an improved separator, since they minimize energy costs for contacts with balls 4. Each ball in case of contact with a roller can rotate around any of the axes passing through the center of the ball, and these axes may not coincide at the same contact balls. Existing separators do not have such capabilities, in which all the contacts of the rollers with the separator should be taken into account when determining friction losses. Replacing the separator with balls essentially means replacing sliding friction with the separator with rolling friction with balls or redistributing rolling friction and sliding friction with a decrease in total friction losses.

Under axial load on the bearing, the movable bearing ring moves in the direction of the bearing axis. The length of the rollers 3, the width of the annular grooves 5, the diameter of the balls 4 and the location of the grooves 5 and 6 are selected so that when the axial load on the bearing is initially selected, the gap between the balls 4 and the annular grooves 6 and the balls 4 become rolling elements. In this position with the selected axial clearances, the bearing is shown in the drawing. The freedom of movement of the balls 4 is thereby reduced, and the friction loss of sliding increases. This increase in losses must be taken into account at relatively large axial loads on the bearing compared to radial loads, since the radial load is perceived by one or two rollers 3, and the axial load is perceived by all balls 4 approximately equally. In the general case, that is, when both radial and axial loads are applied to the bearing, balls 4 and rollers 3 simultaneously perform the functions of rolling elements and a cage.

In the proposed bearing design, friction losses are reduced due to the use of balls 4 instead of the separator and the elimination of contacts between the ends of the cylindrical rollers 3 and the annular grooves 5. Balls 4 can be made hollow and from a material with a low specific gravity, which will further reduce friction losses slip.

Balls 4 and rollers 3 with a small size of the shoulders 7 and a sufficiently large size of the bearing can be pressed during assembly of the bearings, which will simplify the design of the bearings and reduce the cost of their manufacture.

Feasibility of the invention is to increase the service life of bearings, to reduce friction losses and reduce the complexity of manufacturing bearings.

It is not possible to calculate the economic effect due to the lack of statistically sound initial and comparative data.

Claims (2)

1. The angular contact rolling bearing, consisting of the inner and outer bearing rings and rolling bodies, characterized in that the rolling bodies are cylindrical rollers and balls located in the first pair of annular grooves designed to transmit radial load; the number of balls located between the two nearest rollers is equal to the maximum number of balls, which is located in the first pair of annular grooves, in one row, parallel to the axis of the bearing; the diameter of the rollers is greater than the diameter of the balls by at least an amount of maximum contact deformation; the length of the rollers, the width of the first pair of annular grooves, the diameter of the balls and the location of the two pairs of annular grooves are selected so that when the axial load on the bearing is initially selected, the gap between the balls and the second pair of annular grooves. 2. The angular contact rolling bearing according to claim 1, characterized in that the balls are hollow and with a minimum weight.

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