RU116584U1 - BEARING BALL-ROLLER RADIALLY THRESHOLD THREE ROW COMBINED WITH SEALS - Google Patents

Abstract

 A three-row angular contact ball-roller bearing combined with seals, comprising an outer ring, an inner ring for two roller rows and two ball-ring half-rings, rolling elements located between the raceways in the cages, and seals, characterized in that the outer ring is made two raceways: one for two roller rows, the other for one ball row, seals are fixedly mounted in the outer ring, the inner working edges are in contact with the inner rings, m radial clearance in roller rows must always be less than the radial clearance in the ball-row, and the axial clearance in the roller rows must be greater than the axial clearance in the ball-row.

Description

The invention relates to mechanical engineering and can be used in technical fields where rolling bearings are used, in particular, in bearing units of railway transport.

Known rolling bearings of the following designs:

1 Double-row radial roller bearing with two protective washers, double type 882000 * (Figure 1), consisting of two outer rings (2), two inner rings (1), two rows of cylindrical rollers (3), two cages (4) and two protective washers (5).

The outer rings of the bearing have two sides, the inner rings have one side.

2 Double-row tapered roller bearing of the cassette type - type TBU *, (Figure 2), having one outer ring (4), two inner rings (1), two rows of tapered rollers (2) with cages (3) and two seals (in the figure 2 not shown).

The indicated bearing designs are currently used in axle boxes of railway transport.

A design flaw of a double-row radial roller bearing with cylindrical rollers (Figure 1) is the perception of the axial forces acting in the assembly by means of sliding friction of the ends of the rollers against the beads of the rings and the uneven effect of the radial load on each raceway due to different radial clearance values in the two rows of bearings.

As a result of sliding friction of the ends of the rollers against the sides, additional heating of the bearing occurs, and wear products enter the lubricant, which ultimately leads to a decrease in the service life of the bearing.

The design drawback of TBU double-row tapered bearings (Figure 2) is the uneven effect of the radial load on the raceways of the inner and outer rings, while the bearing is subjected to radial and axial loads. This leads to increased specific pressures at the contact points of the rings and rollers in the same row of the bearing, which leads to a decrease in the service life of the bearing. In addition, the use of tapered rollers in the same dimensions of the bearing, instead of cylindrical, reduces the radial bearing capacity of the bearing.

The closest in design to the proposed bearing design on request is a radial roller bearing, shown in Figure 1. It is taken as a prototype.

All of these drawbacks noted in the existing bearing designs are excluded in the proposed new design of a ball-roller angular contact 3-row ball bearing combined with seals proposed in the application (Figure 3).

The bearing consists of an inner ring (1), an outer ring (2), rollers (3), roller row cages (4), balls (5), a ball row cage (6), seals (7), inner rings of a ball row (8 ), intermediate rings (9).

The inner ring of the bearing (1) has one rim.

The outer ring of the bearing (2) without rims, has one groove.

The bearing has two roller rows and one ball row.

Each row of rollers is guided by a separator (4).

Adjustable intermediate rings (9) are installed between the rows of rollers.

The inner ring of the ball row of the bearing consists of two half rings (8).

In the ball row, a separator (6) is used.

The ball row is a design of an angular contact bearing.

The internal cavity of the bearing at the manufacturer must be filled with lubricant.

To hold the lubricant and prevent foreign particles from entering the bearing, seals are installed in the outer race of the bearing.

The proposed bearing design allows the radial load to be perceived only by the roller rows, and the axial load only by the ball row.

Thus, in this bearing design, in contrast to the bearing design shown in Figure 1, sliding friction is completely excluded, i.e. both radial and axial loads are perceived by rolling bodies.

This circumstance contributes to the exclusion of additional heating of the surfaces of the sides and ends of the rollers when the axial load is applied to the bearing.

Bearing perception of axial load by rolling elements (ball row), instead of friction of sliding of the ends of the rollers on the side of the ring, can significantly reduce the moment of friction of the bearing.

In addition, it eliminates the ingress of abrasive into the lubricant, which is formed from the wear of the surfaces of the sides and ends of the rollers during sliding friction.

In order to ensure that the radial load acting in the assembly is perceived only by the roller rows, and the axial load by the ball row only, certain ratios of the radial and axial clearances must be provided in the bearing.

The use of uniform sizes of raceways in the bearing design on the outer and inner rings makes it possible to ensure the same radial clearance value in each roller row, which contributes to an even load distribution between the roller rows and, accordingly, to reduce the specific pressure at the contact points of the rollers with the raceways. This, in turn, allows to increase the service life of the bearing.

Using the proposed invention will allow for more reliable operation of bearings in railway nodes.

Claims (1)

A three-row angular contact ball-roller bearing combined with seals, comprising an outer ring, an inner ring for two roller rows and two half-rings of a ball row, rolling elements located between the raceways in the cages, and seals, characterized in that the outer ring is made two raceways: one for two roller rows, the other for one ball row, seals are fixedly mounted in the outer ring, the inner working edges are in contact with the inner rings, m radial clearance in roller rows must always be less than the radial clearance in the ball-row, and the axial clearance in the roller rows must be greater than the axial clearance in the ball-row.