RU232837U1 - ROLLING BEARING - Google Patents

Abstract

The utility model relates to the field of mechanical engineering, in particular to radial-thrust roller bearings, as well as to axial (thrust) rolling bearings. The technical result is achieved by using a rolling bearing comprising outer and inner rings with rolling raceways, a separator located between them and rolling elements installed in it, wherein the rolling elements are made in the form of spherical rollers, conical recesses are made on the ends of the rollers, the separator is made in the form of two side rings connected to each other with sockets for the spherical rollers, coordinating centers are installed in the side rings of the separator in the area of the sockets, on the conical ends of which rollers are installed in conical recesses, wherein in one side ring of the separator the coordinating centers are fixedly installed, in the second the coordinating centers are spring-loaded, the axial dimensions of the conical recesses on the ends of the rollers are larger than the axial dimensions of the conical ends of the coordinating centers, and friction plates are installed between the separator and the rollers on the side of the spring-loaded coordinating centers. The technical result is an increase in the reliability of the rolling bearing due to an increase in the time of occurrence of catastrophic wear of friction pairs.

Description

The utility model relates to the field of mechanical engineering, in particular to radial-thrust roller bearings, as well as to axial (thrust) rolling bearings.

Bearing units assembled from rolling bearings are known (GOST 520-2011 Rolling bearings. General specifications).

The disadvantage of the bearing unit is that the critical path of friction-sliding of the surfaces of the balls of the proposed contact form along the mating surface coordinating them depends on the constancy of the contact area, which is constant in the known designs of the bearings of the unit. The disadvantage is due to the fact that during operation, the contact of the rolling elements with the surface of the separators does not provide the minimum possible distance between the rolling elements, as a result of which the separator, occupying a significant place between the tracks, deprives the possibility of using a larger number of rolling elements, which leads to an increase in the load on an individual rolling element and, ultimately, to a decrease in the performance characteristics of the bearing unit as a whole during the operation of the roller bearing. In addition, the bearing cannot operate as a bearing unit that simultaneously perceives both radial and axial loads, for example, when it simultaneously contains both an axial bearing of type 8102 and a cylindrical radial bearing of type 1002932.

A sliding bearing unit is known, comprising a shaft, a sleeve with through channels, a part placed between them in the form of a floating ring with through radial holes in its body and grooves on the inner surface, with sensors installed in them for measuring radioactivity, and a lubricant filling the gaps with radioactive isotopes introduced into it (patent RU No. 186493, IPC F16C17/18, F16C33/10, 2019).

The disadvantage of the bearing unit is its design, which excludes the possibility of using it as both a radial bearing unit and an axial one.

A rolling radial roller bearing without a separator is known, comprising outer and inner rings with rolling raceways and rolling elements arranged between them, made in the form of two-stage rollers, two sections of large stages of the rollers of the upper tier enter with a clearance into the grooves of the smaller stages of the rollers of the lower tier, wherein the diameters of the three sections of the large stages of the lower tier, contacting with the three sections of the smaller stages of the rollers of the upper tier, are equal, and all the rollers of both the upper and lower tiers contact each other and the rolling raceways along three lines, forming a single closed annular power set of rollers of the upper and lower tiers (patent RU No. 2334137, IPC F16C19/22, F16C19/28, F16C33/34, F16C33/36, 2008).

The disadvantage of the bearing is that the critical path of friction-sliding of the surfaces of the balls of the proposed contact form along the mating coordinating surface depends on the constancy of the contact area, which in known designs of roller bearings is constant, since it cannot move from one friction pair to another and be distributed between them in comparison with the proposed design, and this reduces the wear time. In addition, the bearing cannot operate as an axial one, for example, type 8103.

A bearing is known, on the outer ring of which two triangular-type bores are made for rolling tracks of two spherical sections made on the outer side of large steps of the rollers of the upper tier, which contact the contact spot in the zone of the triangular-type bores - along rolling tracks equal in diameter to the rolling track of the outer ring, while along the axis of the rollers of the lower tier two thrust bearings are installed, made, for example, in the form of a ball, which are located in cups made, for example, from carbon fiber, and contact the surfaces of the high flanges of the inner ring and the thrust ring (patent RU No. 2384765, IPC F16C19/22, F16C19/28, F16C33/34, F16C33/36, 2010).

The disadvantage of bearings is their complex design, as well as uneven deformation of the rolling elements due to abrasion during use, resulting in the formation of "cavities" filled with excess lubricant, which creates viscous resistance, worsening the performance properties of the bearing. In addition, the bearing cannot operate as an axial one, for example, type 8103.

A rolling bearing with tapered rollers without a separator is known, containing a free and tight ring, rolling elements located between them, made in the form of tapered rollers arranged in two rows, forming a single closed annular set of rollers, wherein the plane of linear contacts of the rollers of one row with the second passes, for example, along the longitudinal axis of symmetry of the thrust bearing (patent RU No. 2349803, IPC F16C19/22, F16C19/32, 2009). A bearing, all of whose tapered rollers contain a coaxial through hole, in which a grease nipple is installed on the side of the smaller diameter of the roller, and a rigid rod made, for example, of metal ceramics is installed behind the thrust bearing, and the spherical head of the thrust bearing is made with eccentricity (patent RU No. 2384764, IPC F16C19/22, F16C19/32, F16C33/34, 2010).

The disadvantage of bearings is the complexity of the design, as well as the uneven deformation of the rolling elements due to their abrasion during use, resulting in the formation of "cavities" filled with excess lubricant, which creates viscous resistance, worsening the performance properties of the bearing.

A known rolling bearing comprises an outer and an inner ring, one of which is split along the vertical axis of symmetry of the bearing, equipped with cylindrical rolling raceways with flanges on both sides of the rolling raceways, rolling elements in the form of cylindrical rollers having a spherical shape at the ends, a separator for separating the rolling elements, connecting the rolling raceways with flanges, made in the form of sections of curved surfaces, with the same radii equal to the radius of the sphere of the ends of the rollers (patent RU No. 2582630, IPC F16C19/22, F16C19/26, F16C33/34, F16C33/58, 2016).

The disadvantage of the bearing is the uneven deformation of the rolling elements due to abrasion during use, resulting in the formation of “cavities” filled with excess lubricant, which creates viscous resistance, deteriorating the performance properties of the bearing.

A rolling support is known, made in the form of radial-thrust rolling bearings installed in a housing, containing a retaining ring, outer and inner rings, solid metal bearing balls (or rollers) and separating balls (or rollers) having a solid lubricating material on the surface, arranged alternately with the bearing rolling elements (application for invention RU No. 96101411, IPC F16C19/14, 1998).

The disadvantage of the support is the smaller number of supporting rolling elements, compared to a non-separating rolling bearing, and additional friction forces between the supporting rolling elements and the separating rolling elements.

A rolling roller bearing is known, comprising an inner ring and an outer ring with rolling raceways and rolling elements in the form of cylindrical rollers, wherein the rolling raceway of the inner ring is made in the form of the surface of a single-sheet hyperboloid, the surface of the rolling raceway of the outer ring oppositely repeats the surface of the rolling raceway of the inner ring and has a curvature of the same magnitude but different in sign (patent RU No. 2588176, IPC F16C19/22, F16C19/34, F16C33/34, F16C33/58, 2016). A bearing in which the rolling path of the inner and outer rings is equidistant over the entire width of the rings, and the center of the bearing is located on a plane dividing the width of the bearing in half (RU patent No. 2585437, IPC F16C19/22, F16C19/34, F16C33/34, F16C33/58, 2016).

The disadvantage of bearings is the uneven deformation of the rolling elements due to abrasion during use, resulting in the formation of “cavities” filled with excess lubricant, which creates viscous resistance, deteriorating the performance properties of the bearing.

A radial thrust rolling bearing is known, consisting of inner and outer bearing rings and rolling elements, which are cylindrical rollers and balls located in the first pair of annular grooves, designed to transmit radial load (patent RU No. 2529931, IPC F16C19/20, F16C19/49, 2014).

The disadvantage of the bearing is the uneven deformation of the rolling elements due to abrasion during use, resulting in the formation of “cavities” filled with excess lubricant, which creates viscous resistance, deteriorating the performance properties of the bearing.

A rolling bearing with stepped rollers is known, comprising outer and inner rings with rolling raceways, rolling elements installed between them, made in the form of two-stage rollers installed in separator seats, the larger diameter steps of which contact the rolling raceway of the outer ring of the bearing, and the smaller diameter steps contact the rolling raceway of its inner ring (patent RU No. 2553489, IPC F16C19/22, F16C33/36, 2015).

The disadvantage of the bearing is that the critical path of friction-sliding of the surfaces of the balls of the proposed contact form along the mating coordinating surface depends on the constancy of the contact area, which in known designs of roller bearings cannot move from one friction pair to another in comparison with the proposed design, and this reduces the wear time.

The closest is a rolling bearing containing outer and inner rings with rolling raceways, separators located between them and cylindrical rollers installed with end contact surfaces in the recesses of the separators, the shapes of which correspond to the shape of the end contact surfaces of the rollers, and the axial dimensions are larger than the axial dimensions of the end contact surfaces of the rollers (patent RU No. 194002, IPC F16C19/22, F16C33/34, F16C33/46, 2019).

The disadvantage of the bearing is that there is an occurrence of uneven deformation of the rolling elements and their wear due to abrasion during use. This leads to an increase in the gaps between the contact surfaces, which are filled with excess lubricant, which creates viscous resistance, worsening the performance properties of the bearing.

The objective of the proposed technical solution is to develop a rolling bearing design that allows the load to be distributed during wear of the contact surfaces of rolling elements and their coordinating elements from one friction pair to another.

The technical result is an increase in the reliability of the rolling bearing due to an increase in the time of occurrence of catastrophic wear of friction pairs.

The technical result is achieved by using a rolling bearing comprising outer and inner rings with rolling raceways, a separator located between them and rolling elements installed in it, wherein the rolling elements are made in the form of spherical rollers, conical recesses are made on the ends of the rollers, the separator is made in the form of two side rings connected to each other with sockets for the spherical rollers, coordinating centers are installed in the side rings of the separator in the area of the sockets, on the conical ends of which rollers are installed in conical recesses, wherein in one side ring of the separator the coordinating centers are fixedly installed, in the second the coordinating centers are spring-loaded, the axial dimensions of the conical recesses on the ends of the rollers are larger than the axial dimensions of the conical ends of the coordinating centers, and friction plates are installed between the separator and the rollers on the side of the spring-loaded coordinating centers.

The total resistance to bearing rotation is the result of rolling friction and sliding friction in the contact zones between the rolling bodies and raceways, and the end contact surfaces of the rollers (rolling bodies) and their coordinating elements. The design provides the possibility of increasing the time of onset of critical wear of the contacting roller-separator friction pairs while maintaining the possibility of a fixed spacing of the rolling bodies from each other along the pitch circle and provides a reduction in contact deformation zones on the raceways, significantly reducing the forces of rolling and sliding friction, slowing down wear and increasing the service life of the bearing.

The implementation of rolling elements in the form of spherical rollers (barrel-shaped rollers) ensures the rotation of rolling elements with a low coefficient of friction. The implementation of the separator with coordinating centers, on the cone-shaped ends of which rollers are installed with cone-shaped recesses, the use of friction plates ensures a minimum contact area between the contacting surfaces and eliminates friction of the rollers on the end surfaces of the separator during operation of the bearing unit.

The drawing shows a longitudinal section of the rolling bearing of the spindle front support in section.

The rolling bearing consists of an outer ring 1 and an inner ring 2, a separator 3 and rolling elements - spherical rollers 4 located between them. Rollers 4 are installed in seats of separator 3. In side rings 5 and 6 of separator 3, at the location of rollers 4, coordinating rollers 4 centers 7 are installed. Moreover, in one side ring of separator 3, ring 5, coordinating centers 7 are installed with spring loading by spring 8 - "floating centers", and in the second ring of separator 3, ring 6, coordinating centers 7 are installed motionless - "rigid centers". The coordinating centers 7 of the rings 5 and 6 are installed coaxially and protrude into the seats of the separator 3 with their conical ends 9, on which the rollers 4 are installed. On the ends of the rollers 4, coaxially with the coordinating centers 7, conical recesses 10 are made, by means of which the rollers 4 are installed on the conical ends 9. The axial dimensions of the conical recesses 10 on the ends of the rollers 4 are greater than the axial dimensions of the conical ends 9 of the coordinating centers 7. Between the separator 3 and the rollers 4, on the side of the “floating centers”, friction plates 11 (made of a multicomponent polymer material, fluoroplastic) are installed. Rollers 4 are installed in the separator seats, ensuring a minimum initial gap between the outer working surfaces within 5-10 µm, which is necessary and sufficient for lubricating the rolling elements 4 and the rolling raceways of the outer 1 and inner 2 rings.

A rolling bearing works as follows.

During the use of the rolling bearing, the rollers 4 rotate and move along the raceways of the outer 1 and inner 2 rings, maintaining their position relative to each other within the calculated values, thus eliminating the possibility of contact between the rollers 4 and friction between them. In combination with the minimized friction along the contact surface of the rolling elements 4 and the separator 3, since the contact is reduced to a point contact by the tops of the conical surfaces (the same conical shape of the recesses 10 and the ends 9 in combination with the difference in their axial dimensions - the axial dimensions of the recesses are larger than the axial dimensions of the end contact surfaces of the rollers, provide not only a fixed location of the rolling elements, but also the shape of the point contact along the roller axis), a decrease in the wear of the base elements of the rigid and floating centers 1 and the rolling element 5 is ensured and, on this basis, the reliability and service life of the rolling bearing are increased.

During operation, the bearing experiences various loads: radial, axial and combined. The coordinating centers 7 installed in rings 5 and 6 of the separator 3, on the conical ends 9 of which the rollers 4 are installed, in addition to reducing the friction coefficient in the places where the rolling bearing parts are adjacent, allow for the absorption of axial loads. Spring-loaded "floating centers" serve to perceive radial loads and compensate for the gaps of the rubbing surfaces of the rolling elements under combined loads on the bearing. Friction plates 11 allow for the reduction of gaps between the contacting surfaces and the degree of heating, as well as the reduction of wear on the end part of the separator 3 and rollers 4. Thus, the bearing design allows for an increase in its durability and reliability.

The design of the coordinating centers 7 – the execution of the working surface in the form of conical ends 9 – allows to reduce the area of contact with the end of the roller, thereby ensuring a reduction in the value of the friction coefficient and a reduction in the heating of the rubbing surfaces of the bearing parts.

Thus, a rolling bearing containing outer and inner rings with raceways, spherical rollers with conical recesses made on the ends of the rollers, a separator made in the form of two side rings connected to each other with sockets for spherical rollers, in the side rings of which, in the area of the sockets, coordinating centers are installed, on the conical ends of which rollers are installed with conical recesses of a larger axial size, spring-loaded in one of the rings, and friction plates between the separator and the rollers on the side of the spring-loaded coordinating centers, ensures an increase in the reliability of the rolling bearing due to an increase in the time of the onset of catastrophic wear of the friction pairs between the end contact surfaces of the rollers (rolling elements) and the elements coordinating them by increasing the service life of the friction pairs.

Claims (1)

A rolling bearing comprising outer and inner rings with rolling raceways, a separator located between them and rolling elements installed therein, characterized in that the rolling elements are made in the form of spherical rollers, conical recesses are made on the ends of the rollers, the separator is made in the form of two side rings connected to each other with sockets for the spherical rollers, coordinating centers are installed in the side rings of the separator in the area of the sockets, on the conical ends of which rollers are installed in conical recesses, wherein in one side ring of the separator the coordinating centers are fixedly installed, in the second the coordinating centers are spring-loaded, the axial dimensions of the conical recesses on the ends of the rollers are larger than the axial dimensions of the conical ends of the coordinating centers, and friction plates are installed between the separator and the rollers on the side of the spring-loaded coordinating centers.