RU2402700C2 - Rolling bearing and procedure for its fabrication - Google Patents

Abstract

FIELD: machine building.

SUBSTANCE: rolling bearing consists of external and internal rings with rolling elements (balls or rollers) installed between them and retained with separator at distance one from another along circumference between rings. The rolling elements contact spring elements of the rings or the separator and perform reciprocal motions in the direction of radial forces. Also the rolling elements can be installed in seats, made in the rings or in the case of the separator along their external or internal diametre in the direction parallel to their central axis; the rolling elements thrust against springs positioned in orifices connected with the seats and arranged in the direction of radial forces. Maximal diametre of tops of the rolling elements projecting from the separator can differ from diametres of recesses of grooves of the rings at value of amplitude of possible fluctuations of the bearing; a gap of the same value can be made between the rings and the separator. The rings can be made in form of springs of open box-like shape with a cavity on a side or with a slit along the groove to retain rolling elements, or with a cavity on a base side. The orifices for the springs can be made in the direction of equal radial and axial forces at radial-thrust design of the bearing. The procedure for fabrication of bearings with rings of a box-like shape consists in cogging or in rolling a sheet work-piece around fusible insertion; further, the insertion is removed when rings are heated for quenching; also heating and quenching of rings can be performed at a process premises. According to another version of the fabrication procedure the cavities in the rings are ground; at grinding the ring can be imparted with a counter motion at a cutting speed.

EFFECT: raised smoothness of operation of "shaft-bearing-case" systems; improved conditions of operation and increased service life of items.

24 cl, 12 dwg

Description

The invention relates to the field of mechanical engineering and machine parts, in particular to radial and angular contact ball bearings with ball and roller rolling bodies.

A known rolling bearing, which is a support for shafts or axles, perceiving from them radial, axial and radial-axial loads and ensuring their free rotation due to the placement between the support and the surface of rotation of the rolling bodies (balls or rollers), consisting of outer and inner rings, between which rolling bodies are placed, held along the perimeter of the circle between the rings at a certain distance from one another by a separator (see book: Polytechnical Dictionary / Ed. Col .: Ishlinsky A.Yu. (Ch. ed.), etc. - 3rd ed., re slave and add. - M .: Sov. Encyclopedia, 1989. - p. 395).

The disadvantage of this bearing is the inability to compensate for variable static and dynamic peak loads that occur when starting or braking shafts and axles, which increase sharply when the resonance mode of the system consisting of shafts, bearings and their bearings in the housings, or with other types of additional dynamic and static peak loads.

The elimination of these disadvantages is the main task solved in the proposed application for an invention. Its solution is provided by:

1) installation of rolling bodies (balls or rollers) with emphasis on springs or elastic rings with the possibility of travel in the seats or in the grooves of the rings in the direction of action of the forces created by the resonant and other peak dynamic and static additional loads arising in the shaft-bearing-housing system , with the limitation of the magnitude of this stroke due to the stiffness of the elastic elements, which compensates for the effect of resonant and other additional dynamic or static peak loads;

2) the placement of sockets, rolling elements and springs in the outer and inner rings, or in the separator, or in the elastic elements between them, in various combinations and variants of their designs;

3) the execution of the outer and inner rings hollow and elastic.

This increases the smoothness of the shaft-bearing-housing system, especially at the time of its launch and braking, or with other additional dynamic and static loads of a peak nature, which improves the operating conditions of the products and increases their durability.

The designs of the proposed bearings, rolling elements and springs placed in them, mounted in sockets and holes, made in the outer and inner rings or in the cage, or between cages, in various designs, are shown in the drawings.

1 shows a bearing consisting of an outer-ring housing 1 and the inner ring 2. In the housing, also performs the function of the separator parallel to its longitudinal axis formed socket diameter d _{of holes} 3 with flats l, cut separator opening in which the rolling elements are installed 4 with a diameter d _since , (D _otv> d _as> l), with emphasis on imposed radial openings 5 which are perpendicular to the seat 3, the spring 6, which due to their rigidity provide compensation for load bearing during normal operation and the possibility of displacement under the action of rolling bodies bearing resonance and other additional dynamic and static peak loads. On the outer surface of the inner ring, a double-breasted 7 or a single-breasted 8 groove can be made to hold and guide the rolling bodies. In this case, the maximum diameter of the circle formed by the peaks of the rolling bodies protruding from the separator must be less than the diameter of the circumference of the groove cavity by the amplitude A _{1 of the} possible oscillations of the system, and a gap of ₁ ≥A ₁ must be made between the ring and the separator. For angular contact bearings, the direction of the holes for the springs can be made coincident or close to the direction of the resultant radial and axial forces, for example, at a standard angle of 15 °, 25 °, etc. to the end plane of the bearing, and the direction of the nests is made at the same angles to the longitudinal axis of the bearing.

Figure 2 shows the options for holding the springs around the periphery of the separator ring. It can be made by the supporting surface of the hole into which the bearing is inserted (version 1), or by plugs 9, 10, which can either be pressed (version 2), or screwed (version 3) into the housing, or pressed, screwed around this housing, soldered or welded, for example by contact, diffusion or other welding, bandage 11 (version 4). The contact of the rolling elements 4 with the springs 6 can be made directly along the rim (version 1), which is suitable for rolling bodies in the form of balls, or through intermediate supporting elements 12, 13, 14 with a flat (version 5), convex (version 6) or concave (version 7) head shape, which allows their use for both balls and rollers.

Other versions of the springs for holding the rolling elements in the sockets are shown in the table.

Unlike the prototype, in the proposed bearing, the rolling bodies are installed with the possibility of their rotation in the separator seats on the springs, which provide the possibility of displacement of the rolling bodies together with the inner ring of the bearing in the direction of action of additional forces exceeding normal working forces, which eliminates the transmission of transverse vibrations from shaft to the outer ring and bearing support, and break them, as a general system of oscillations, especially dangerous when the resonance mode is reached. The implementation of the proposed nests and the installation of spring-loaded rolling elements in them makes it possible to compensate for other static or dynamic additional (peak) loads arising during the start-up, operation and braking of the bearing. The number of rolling elements placed in the cage may be equal to the number of standard bearings, including in radial and radial thrust versions.

The installation and operation of the proposed bearings does not differ from the operation and installation of the base. Differences exist only in the dimensions of the outer ring and in its design, which has longitudinal sockets with flats for rolling bodies and spring holes perpendicular to the nests, and, if necessary, in the use of plugs and bandages to hold the springs in the holes and in the use of intermediate supports in contact with the bodies rolling.

The combination of these features is a new technical solution, not obvious from the basic level of technology, their implementation is possible in real production, because the proposed bearings differ from the basic ones only in the presence of longitudinal sockets for rolling elements, radial holes for the springs and the introduction of the springs themselves. This provides a new positive effect, which consists in breaking the oscillation system, including resonant, due to compensation of additional (peak) static or dynamic loads that occur during operation of the bearing.

Further development of the proposed bearing design is associated with a variation in the arrangement of rings, seats for the rolling elements, holes for the springs and the springs themselves.

Figure 3 shows a bearing, consisting of an inner ring-housing 15 and an outer ring 16 with double-breasted 7 or single-breasted 8 groove on its inner side, for holding and guiding rolling elements in it. In this case, also perform the function of the separator in the slot 3 with the diameter d _{of holes,} truncated dihedron l of an outer diameter of the separator, the rolling bodies 4 are provided having a diameter d _as , (D _otv> d _as> l), with emphasis on the entered into the holes 5 of the spring 6, which due to the stiffness compensation workloads provide during normal operation of the bearing, and also possible to mix the rolling bodies in the nest under the influence of them resonance and other dynamic or static additional peak loads. In this case, the maximum diameter of the circle covering the peaks of the rolling bodies protruding from the housing should be greater than the diameter of the circumference of the groove cavity by the amplitude A _{2 of the} possible oscillations of the system, and a gap of ₂ ≥A ₂ must be made between the outer ring and the separator. The holding of the springs 6 along the periphery of the inner ring can be performed by the bearing surface of the shaft on which the bearing is mounted, or the holes for the springs can be made blind or plugged with plugs, or with a bandage inserted inside the holes of the cage-separator like the previous versions of the bearing (Fig. 2, execution 1 ... 4). The contact of the rolling elements 4 with the springs 6 can be made directly along the rim or through the intermediate supporting elements similar to the previous embodiment of the bearing (figure 2, version 1, 5 ... 7). At the same time, all spring versions listed in the table are also possible. For angular contact bearings, the direction of the holes for the springs can be made coincident or close to the direction of the resultant radial and axial forces, for example, at a standard angle of 15 °, 25 °, etc. to the end plane of the bearing, and the direction of the nests is made at the same angles to the longitudinal axis of the bearing.

In contrast to the prototype, in the new proposed bearing, the rolling bodies are mounted on an inner ring-casing, which is also a separator, with the possibility of their rotation in the seats of the cage-separator on springs, allowing them to be displaced together with the casing in the direction of the forces acting on the bearing that exceed normal labor forces, which allows you to compensate for vibrations of the inner ring with the shaft and break them as a system of oscillations relative to the outer ring and bearing bearings, especially dangerous when the resonant- mode. The implementation of the proposed nests and spring-loaded rolling elements allows you to compensate for other static or dynamic additional (peak) loads that occur during operation of the bearing. The number of rolling bodies installed in the cage-separator may be equal to their number in standard bearings.

The installation and operation of the proposed bearings does not differ from the operation and installation of the base. Differences exist only in the size of the inner ring and in its design, which has longitudinal nests with flats for rolling bodies and normal spring holes for the nests, as well as, if necessary, the use of plugs or bandages to hold in the spring holes and in the use of intermediate support elements for bodies rolling.

The combination of these features is a new technical solution, not obvious from the basic level of technology, their implementation is possible in real production, because the proposed bearings differ from the basic ones only in the presence of longitudinal sockets for rolling elements, radial holes for the springs and the introduction of the springs themselves. This provides a new positive effect, which consists in breaking the oscillation system, including resonant, due to compensation of additional (peak) static or dynamic loads that occur during operation of the bearing, which are especially dangerous when starting or braking the entire system.

However, the above bearing designs exclude the possibility of circular movement of the rolling bodies in the grooves of the rings, which does not meet the principles of operation of rolling bearings and worsens the performance to reduce their friction.

To eliminate this drawback, new bearing designs with a rotating cage are proposed, the designs of which are shown in the drawings.

4 shows a bearing consisting of inner ring 2, outer ring 16 and the separator body 17 in which the longitudinal axial slot diameter d _{of holes} 3, cut along the dihedron l, performed pairwise on both outer and inner diameters of the separator, in which rolling elements 4 are installed in pairs with a diameter of d _. , where d _resp > d _since > l, with an emphasis on the springs 6 introduced into the radial holes 5 between the seats, the stiffness of which provides the ability to compensate for loads during normal operation of the bearing and the possibility of displacements of the rolling body pairs in the seats under the influence of resonant or other peak additional dynamic or static loads on the bearing. On the outer and inner rings, double-breasted 7 or single-breasted 8 grooves can be made, which serve to guide and hold the rolling bodies in them. To improve the layout and operating conditions of the bearing, the diameters and flats of the seats and the diameters of the rolling elements on the outer and inner surfaces of the cage can be made of different sizes, respectively: d ' _holes and d'' _holes , d' _because and d '' _since , l 'and l''. In this case, the maximum circle diameters created by the peaks of the rolling bodies protruding outward and into the separator must be greater than the diameters of the troughs of the ring grooves by the amplitude A ₁ and A _{2 of the} possible oscillations of the system, and gaps with ₁ ≥A ₁ must be made between the support rings and the separator and with ₂ ≥A ₂ . For angular contact bearings, the direction of the holes for the springs can be made coincident or close to the direction of the resultant radial and axial forces, for example, at an angle of 15 °, 25 °, etc. to the end plane of the bearing, and the direction of the nests is made at the same angles to the longitudinal axis of the bearing.

Unlike previous versions of bearings, the new version provides the possibility of rotation of the cage with rolling bodies, which fully meets the working conditions of this class of bearings. The number of rolling bodies installed in the cage may be equal to their number for standard radial and angular contact bearings.

The installation and operation of the proposed bearings does not differ from the operation and installation of the base. Differences exist only in the dimensions of the outer ring and in the design of the separator, which has longitudinal nests for rolling elements on its inner and outer diameters and openings perpendicular to the nests for springs, as well as paired rolling bodies.

The combination of these features is a new technical solution, not obvious from the basic level of technology, their implementation is possible in real production, because the proposed bearings differ from the basic ones only in the presence of a cage-separator with longitudinal sockets for rolling elements, radial holes for the springs and the introduction of the springs themselves. This provides a new positive effect, which consists in rolling the separator with rolling bodies along the bearing rings, which reduces friction.

Figure 5 shows the further development of the previous design, in which to reduce the dimensions of the separator 18 of the socket 3 with rolling elements 4 and the holes 5 with springs 6 are made in a checkerboard pattern. All other structural elements and gaps are adequate to the previous options. For angular contact bearings, the direction of the holes for the springs can be made coincident or close to the direction of the resultant radial and axial forces, for example, at an angle of 15 °, 25 °, etc. to the end plane of the bearing, and the direction of the nests is made at the same angles to the longitudinal axis of the bearing.

The installation and operation of the proposed bearings does not differ from the operation and installation of the base. Differences exist only in the dimensions of the outer ring and in the design of the separator, which has longitudinal nests for rolling elements and radial holes for springs on its inner and outer diameters, as well as rolling bodies made in a checkerboard pattern.

The combination of these features is a new technical solution, not obvious from the basic level of technology, their implementation is possible in real production, because the proposed bearings differ from the basic ones only in the presence of a cage with staggered sockets for rolling elements and holes for the springs and rolling elements and springs placed in them. This provides a new positive effect, which consists in reducing the size of the bearing.

Figure 6 shows the development of the previous design, consisting of an inner ring 2, an outer ring 16 and a separator 19, to reduce the dimensions of which the sockets 3, arranged in a checkerboard pattern, are made elongated or enlarged to diameters d ″ ’ _holes that overlap the average diameter of the separator , and along it between the sockets there is made an annular groove 20 passing through the hollows of the sockets at a distance d _since -c-t _to from the outer and inner cylindrical surfaces of the separator (where d _since - the diameter of the rolling elements 4, c - the gaps between the rings and the separator, t _to - the depth of double-breasted 7 or single-breasted grooves 8 for holding and directing bodies rolling), into which an annular spring 21 is inserted, which is flat or flat with recesses, 21, which contacts the rear vertices of the rolling bodies 4. In this case, the remaining design parameters and bearing clearances are adequate to the previous versions, including with different sizes of diameters of nests d ''' _holes and d'''' _holes , diameters of rolling elements d' _since and d '' _since and groove depths t ' _k and t'' _k . For angular contact bearings, the grooves for the spring can be made at an angle close to the resultant radial and axial forces, for example, 15 °, 25 °, etc. to the end face of the bearing, and the spring itself can be made with the same cone angle.

The installation and operation of the proposed bearings does not differ from the operation and installation of the base. Differences exist only in the dimensions of the outer ring and in the design of the separator, having on its inner and outer diameter enlarged sockets for rolling elements located in a checkerboard pattern, as well as rolling bodies inserted into them, while an annular groove is made between the nests passing through the cavities of the nests , and a ring spring of a different shape or another shape is introduced into it, which contacts the rear vertices of the rolling elements.

The combination of these features is a new technical solution, not obvious from the basic level of technology, their implementation is possible in real production, because the proposed bearings differ from the basic ones only by the presence of a cage with staggered sockets for rolling elements and rolling bodies inserted into them, as well as by making an annular groove between the sockets passing through the troughs of these sockets, into which a flat ring spring is inserted that contacts the rear vertices of the bodies rolling. This provides a new positive effect, which consists in reducing the size of the bearing.

Figure 7 shows the further development of previous designs, while to improve the operating conditions of the bearing between the outer ring-cage 1 and the inner ring-cage 15, with sockets 3, rolling elements 4 and springs 6 introduced an intermediate working ring 22 with double-breasted 7 or single-breasted 8 grooves used to hold and guide the rolling elements. All other structural elements and clearances For angular contact bearings, the direction of the holes for the springs can be made close to the total vector of radial and axial forces, for example, at an angle of 15 °, 25 °, etc. to the end plane of the bearing, and the seats are made at the same angles to the longitudinal axis of the bearing, adequate to the previous options, including with different diameters of the rolling elements.

The installation and operation of the proposed bearings does not differ from the operation and installation of the base. Differences exist only in the design of the outer ring of the separator with sockets, rolling elements and springs and the inner ring of the separator with sockets, rolling elements and springs in combination with a working ring placed between these rolling elements.

The combination of these features is a new technical solution, not obvious from the basic level of technology, their implementation is possible in real production, because the proposed bearings differ from the basic ones only in the design of the outer ring of the separator with sockets, rolling elements and springs and the inner ring of the separator with sockets, rolling elements and springs in combination with an intermediate working ring located between the rolling bodies of the inner and outer ring-separators. This provides a new positive effect, consisting in the ability to quickly replace the intermediate ring after its wear.

On Fig shows the development of two previous designs, forming a bearing, consisting of an inner ring 2, an outer ring 16, two cages 23 and 24, for example, of the standard type, holding rolling elements 4, between which is introduced a flat thin-walled flexible ring spring 25, covering protruding surfaces of both rows of rolling elements. To keep the annular spring from the side of the ends of the bearing, thrust rings 26 or 27 can be installed, placed respectively inside (version 1) and outside the bearing (version 2). The remaining design parameters are adequate to the previous versions of the bearings, including with different diameters of the rolling elements. For angular contact bearings, end thrust rings can be placed inside the outer and inner rings and contact with the sides of the rolling elements, and their rigidity is selected based on the need to compensate for the axial force.

The installation and operation of the proposed bearings does not differ from the operation and installation of the base. The only differences are in the execution of two rows of separators with rolling bodies, separated by a flat thin-walled ring spring, covering the protruding surfaces of both rows of rolling bodies, which is located between the thrust rings installed at the ends of the bearing.

The combination of these features is a new technical solution, not obvious from the basic level of technology, their implementation is possible in real production, because The proposed bearings differ from the basic ones only by installing two rows of separators with rolling bodies on top of each other, separated by a flat thin-walled flexible ring spring, covering the protruding surfaces of both rows of rolling bodies, which is located between the thrust rings installed at the ends of the bearing. This provides a new positive effect, which consists in reducing the size and simplifying the design of the bearing.

Figure 9 shows the further development of the previous design, in which a flat thin-walled flexible annular spring 28 inserted between the upper and lower rows of rolling elements 4 is at the same time a separator in which holes 29 are made that hold the tops of the rolling bodies in a checkerboard pattern. All other structural elements of the bearing are adequate to the previous versions, including with different diameters of the rolling elements. For angular contact bearings, mechanical end rings can be placed inside between the outer and inner rings and contact with the sides of the rolling elements, and their stiffness should compensate for the magnitude of the axial force that occurs in the work.

The installation and operation of the proposed bearings does not differ from the operation and installation of the base. Differences exist only in the execution between the rings of two rows of rolling bodies installed one above the other in a staggered manner, separated by each other and held by a flat thin-walled ring spring with holes covering the tops of both rows of rolling bodies, which is placed between the thrust rings installed at the ends of the bearing.

The combination of these features is a new technical solution, not obvious from the basic level of technology, their implementation is possible in real production, because the proposed bearings differ from the basic ones only in the execution between the rings of staggered one above the other two rows of rolling bodies, separated by a flat thin-walled ring spring with holes covering the tops of both rows of rolling bodies, and serving as a separator located between the bearings installed at the ends thrust rings, which at angular contact bearings can be placed inside the outer and inner rings and in contact with the sides of the rolling elements , and their rigidity should compensate for the magnitude of axial forces arising during operation. This provides a new positive effect, which consists in reducing the size and simplifying the design of the bearing.

Further improvement of the bearing is associated with a reduction in its dimensions and in minimizing differences from standard designs.

Figure 10 shows a new bearing design, in which the outer ring is made in the form of a hollow box spring 30 with a support base of a cylindrical, conical, spherical or other shape, double-breasted 7 or single-breasted 8 grooves to hold the rolling elements 4 and a side cavity formed by grinding grooves (version 1), or by squeezing (rolling) a sheet blank of a ring around a fusible insert (version 2), which is removed by heating the ring for quenching. In this case, to reduce ring warping during heating and quenching, it can be installed in the annular technological case, and a spacer ring can be introduced into the cavity obtained after the fusible insert is removed before quenching, which is then removed. The final formation of the surfaces of the ring after hardening is provided by grinding, by analogy with the processing of the rings of the base bearings.

A similar design is possible for the inner ring of the bearing 31 (design 3) or for both of them together (design 4). In this case, the external shape and dimensions of the rings 30, 31, as well as the rolling elements 4 and the separator 32 can be standard, including for angular contact design.

The installation and operation of the proposed bearings does not differ from the operation and installation of the base. The differences are only in the lateral recesses in the body of the rings to provide them with rigidity, compensating for the magnitude of forces under normal bearing load and providing elastic deformations when additional peak dynamic or static loads appear, or in compressing (rolling) a sheet blank of a ring around a low-melting insert, removed when heating the ring for hardening, which is performed to reduce warpage when installing the ring in the technological case, which allows classifying this technical re solution as a device and method of its manufacture.

The combination of these features is a new technical solution, not obvious from the basic level of technology, their implementation is possible in real production, because the proposed bearings differ from the basic ones only in the lateral recesses in the body of the rings, formed by grinding or rolling a sheet of the ring ring on the low-melting insert and hardening in the technological case. This provides a new positive effect, which consists in reducing the size and simplifying the design of the bearing.

11 shows a new bearing design, in which the outer ring is made in the form of a hollow box spring 33 having a support base, sides and double-breasted 7 or single-breasted 8 grooves for holding rolling elements 4, divided by a groove in the groove cavity, which provides access to cavities. Such a ring can be formed by compressing (rolling) a sheet blank, for example, around a low-melting insert (version 1), removed by heating the ring for quenching, for example, through a technological hole 34 made in the base or on the side surface of the ring. In this case, to reduce ring warpage during heating and quenching, it can be installed in an annular process housing. The final formation of the ring after hardening is provided by grinding, by analogy with the processing of the rings of the base bearings.

A similar design is possible for the inner ring of the bearing 35 (design 2) or for both of them together (design 3). In this case, the external shape and dimensions of the rings 33, 35, as well as the rolling elements 4 and the separator 32 can be standard, including for bearings of angular contact design, and the technological plummet 34 at the base of the inner ring can be made from the side of the groove slot.

The installation and operation of the proposed bearings does not differ from the operation and installation of the base. Differences exist only in the execution and in the hardening of the hollow box-shaped spring rings with a support base, two lateral sides and a groove for accommodating and guiding rolling elements, which is divided along the groove cavity with a slot providing access to the cavity, which makes it possible to classify this technical solution as a device and method of its manufacture. At the same time, the box-shaped ring shape, opened by the slot, provides rigidity that compensates for the forces acting on the bearing under normal load, and provides the possibility of elastic deformation when additional (peak) dynamic or static loads appear.

The combination of these features is a new technical solution, not obvious from the basic level of technology, their implementation is possible in real production, because the proposed bearings differ from the basic ones only in the execution of elastic hollow box-shaped outer and inner rings with a slot in the groove cavity, providing it with elastic properties and access to the cavity, as well as by making a technological hole to remove the low-melting insert. In this case, a new positive effect arises, consisting in a decrease in dimensions and an increase in the elasticity of the bearing.

On Fig shows a new bearing design, in which the outer ring is made in the form of a box-shaped spring 36, hollow on the base side and having two sides with double-breasted 7 or single-breasted 8 grooves for holding and guiding the rolling elements 4 (version 1). In this case, the cavity of the ring can be obtained by grinding in a hardened whole ring or by squeezing (rolling) a sheet billet around a detachable insert removed after quenching, followed by grinding.

A similar design is possible for the inner ring of the bearing 37 (design 2) or for both of them together (design 3). In this case, the external shape and dimensions of the rings 36, 37, as well as the rolling elements 4 and the separator 32 can be standard, including for angular contact design.

The development of previous designs of the bearing is version 4. To increase the bearing surface of the rings, it is also possible to perform on the outer 38 or inner 39 rings, or on both rings, protrusions 40 obtained by undercutting the rings by grinding through a slot separating their bases. Moreover, the parameters of the grinding wheel 41, its diameter D _cr , the radius of rounding of the apex r and the installation angle α are selected from the conditions of placement inside the bearing ring, in the following limits:

D _cr - 0.5 ... 2.5 of the width of the bearing ring,

r - 0.25 ... 0.5 of the thickness of the ring,

α - 25 ... 50 °.

The basic is the inner diameter of the cavity D _ext , selected from the conditions of strength and durability of the bearing.

To reduce the complexity of this treatment on the supporting surfaces of the outer and inner rings, an annular groove-slot can be pre-grinded, into which then a grinding wheel 41, which is rotated about its central axis, is introduced. In this case, the ring makes circular motions, and the grinding wheel is provided with a feed. Undercut processing on the other side of the ring is carried out similarly when reinstalling the ring around its longitudinal axis.

It is also possible to design the outer 42 and / or inner 43 rings in the form of a hollow box spring, separated by a slot at the base of the rings. Such rings can be formed by compressing (rolling) a sheet stock, for example, around a low-melting detachable insert, which is then removed by heating the ring under quenching and flowing out through the slot. At the same time, to reduce ring warping during heating and quenching, it can be installed in a detachable ring technological case. The final formation of the ring after hardening is provided by grinding, by analogy with the processing of the rings of the base bearings.

A further development of the proposed method of processing the bearing is grinding the grooves on the outer and inner rings of the bearing assembly. At the same time, it is installed by an inner (or outer) ring that is not machined in this operation, onto a mandrel, for example, a collet, and then a rotating grinding wheel is brought to the machined surface of the outer (or inner) ring, and on the other, a rotating roller is pressed, which ensures this ring circular feed, which can be oncoming or passing. In order to increase the relative cutting speed between the grinding wheel rotating towards each other and the machined ring, the latter can be rotated by the pressure roller at a speed close to the speed of rotation of the grinding wheel.

The installation and operation of the proposed bearings does not differ from the operation and installation of the base. Differences exist only in the design of spring rings hollow on the base side, having double-breasted or single-breasted cavities for accommodating rolling bodies, the parameters of which provide them with rigidity, compensating for the forces acting on the bearing under normal load, and provide the possibility of elastic deformation when additional (peak ) dynamic or static loads, which makes it possible to classify this technical solution as a device and method of its manufacture.

The combination of these features is a new technical solution, not obvious from the basic level of technology, their implementation is possible in real production, because the proposed bearings differ from the basic ones only in the execution of spring-loaded outer and inner rings hollow from the base side. This provides a new positive effect, which consists in reducing the size, as well as in simplifying the design and manufacturing technology of the bearing.

All of the above bearing designs can be double-row.

Actual versions of the proposed bearings are possible in the entire range of standard external or internal diameters and depend on the nature of their work. At the same time, linking the design parameters of the rings and rolling elements to standard values facilitates their selection, design and manufacture, however, the final wall thickness of the box-shaped rings can be selected according to the test results.

A fairly simple of the above bearing designs is a design with rolling bodies placed between its outer and inner rings, installed in two rows one above the other in a checkerboard pattern, separated by each other and held by a flat thin-walled ring spring with holes that span the upper sections facing each other rolling elements, which makes the spring a separator, and thrust rings can be placed at the ends of the bearing to exclude axial movements of this spring.

This design is most easily obtained by remaking two standard-sized bearings of different series with a multiple of balls with the same width, using the rings with the largest outer and smallest inner diameters from the pairs of rings, and removing the intermediate rings. For example, for deep groove ball bearings 117 of the light series and 409 of the heavy series, in which the ring widths are 22 and 29 mm, respectively, the inner diameters are 85 and 45 mm, the outer diameters are 130 and 120 mm, the number of balls 14 and 7 with diameters 13.5 and 23.02 mm, they can be joined when removing the intermediate rings and cages, and from the upper bearing - and the balls through one, with subsequent placement of the remaining balls in a checkerboard pattern between the balls of the lower bearing, which leads to the formation of circles spanning the vertices of each other between each other of the upper and lower rows of balls, in the diameter range from D ₁ = 130- (130-85) / 2-13.5 = 94.0 mm, to D ₂ = 45 + (120-45) / 2 + 23, 02 = 105.52 mm, between which it is possible to install a spring ring separator.

Such a separator can be made of an elastic ring with a thickness of 0.5 mm with an average diameter of 100 mm, making it possible to obtain holes in it, for example, by grinding, electro-erosion or other processing, when the ring is covered by a separator from the upper bearing with tools installed in it having diameters of 11 , 54 mm, adequate to the deepening of the upper balls by 3.25 mm from the outer diameter of the ring, and accordingly a diameter of 15.50 mm, adequate to the deepening of the lower balls by 3 mm from the inner diameter of the ring.

More simplified is the conversion of two bearings of standard designs of different series using a larger outer and smaller inner rings, close in width, and two cages with rolling elements, multiple in number, between which the ring is placed, in the form of a flexible thin-walled spring. For example, radial ball bearings 112 of the light series and 405 of the heavy series can meet these requirements, with ring widths of 18 and 21 mm, inner diameters of 60 and 25 mm, outer diameters of 95 and 80 mm, and the number of balls 12 and 6 with a diameter of 11.11 and 16.67 mm. This allows the bearings to join when removing the pairs of inner and outer rings overlapping each other, and from the upper cage - and the balls through one, with subsequent placement of the remaining balls in a checkerboard pattern between the balls of the lower cage, which leads to the formation of a wave surface covering the vertices of the placed between each other the balls of the upper and lower rows, in the diameter range from D ₁ = 95- (95-60) / 2-11,11 = 66.39 mm, to D ₂ = 25 + (80-25) / 2 + 16 , 67 = 69.17 mm. To prevent axial movement of the spring at the ends of the bearing can be placed thrust rings.

At the same time, the costs of reworking the bearings consist of the sum of the costs of acquiring two pairs of standard bearings, removing one of the upper and the other of the lower ring, removing the balls from the upper cage through one, manufacturing a spring ring, two side support rings and subsequent assembly the whole design, which can be estimated at 300% of the cost of the basic bearings, which for the examples given is about 50 cu

In the manufacture of special bearings of the proposed designs, it is possible to precisely match the shape and size of the balls and rings in the entire range due to specific designs of shafts and bearings, and the cost of their manufacture decreases with an increase in the batch of bearings up to 150 ... 200% compared with the basic version.

The most simple to manufacture are bearings with rings hollow from the base side, as they can be obtained from standard bearings of any size when grinding the required cavities, the shape of which follows the shape of the cavity of the ring, and the cavity depth can be from 1/3 to 2/3 of the ring thickness, which does not increase the cost by more than 50% of the initial cost of the bearings. Moreover, the technological modes for the proposed methods of manufacturing these bearings do not differ from the typical grinding modes of the original rings, and the cost of their implementation does not exceed 0.1 ... 0.25 of the cost of the base bearing.

The effectiveness of the proposed bearings is to improve the working conditions of the shaft-bearing-bearing system due to the exclusion of resonant modes during start-up and braking, which increases the reliability, durability and other quality indicators of their work. At the same time, the costs of reworking bearings are paid for by the achieved quality indicators from all of the above, among which the most important is to reduce the likelihood of breakage when passing through resonant modes, but their accounting in monetary terms is difficult. Moreover, they can be estimated conditionally as 0.1 ... 0.2 system prices. For example, for turbines priced from 100 thousand to 1 million cu they will make up from 10 to 200 thousand cu, which significantly covers the costs of manufacturing bearings and provides the same economic effect from 10 to 200 thousand cu

Considering the annual demand for such bearings is about 1 thousand pieces, the total economic effect can reach over 10 million cu In addition, it provides a social effect by reducing system breakdowns, simplifying its maintenance, reducing production and disposal needs, which in turn reduces pressure on the environment.

The totality of all the data presented confirms the feasibility of widespread use of the proposed bearing designs and methods for their manufacture.

At present, an experimental batch of these bearings is being tested at Kherson combines and AO Zarya.

Claims (24)

1. A rolling bearing, consisting of outer and inner rings, between which rolling bodies (balls or rollers) are placed, held along the circumference between the rings at a certain distance from one another by a separator, characterized in that the rolling bodies are brought into contact with the spring elements of the rings or separator with the possibility of oscillatory or reciprocating movements within the elasticity of the spring elements in the direction of the forces from the radial loads of the bearing, or in the direction of the resultant forces from rad cial and axial loads. 2. Bearing according to claim 1, characterized in that in its outer ring performs the function of the separator housing, the inner diameter of the housing, parallel to its longitudinal axis, the socket is cylindrical with a diameter d _{of holes} cut by the inner diameter of the housing Lysko, size 1 , and rolling elements of diameter d are installed in the sockets, _as , (D _otv> d _tk> l), with emphasis on their springs introduced into openings arranged radially to the back side slots, and to avoid loss of the springs of the holes from the outer surface of the housing can be fitted or pressed into the screwing hole plugs, or an additional ring enclosing the housing is installed, while the contact of the rolling elements with the springs can be made directly at the end of the springs or through intermediate support elements with a flat, convex or concave head shape, and the maximum diameter is around spine, formed by projecting from the separator vertices rolling bodies, may be smaller than the diameter of the circle formed by the trough of the groove of the inner ring on the amplitude value A _1, the possible oscillations of the bearing, wherein between the inner ring and the separator may be formed of the same size with a gap _{1 1} ≥A. 3. Bearing according to claim 1, characterized in that its inner ring, performs the function of the separator housing, the outside diameter of the housing, parallel to its longitudinal axis, the socket is cylindrical with a diameter d _{of holes} cut by the outer diameter of the housing Lysko, size 1 , and rolling elements of diameter d are installed in the sockets, _as , (D _otv> d _tk> l), with emphasis on their springs introduced into openings arranged radially to the back side slots, and to avoid loss of the last spring holes may be formed blind or the inner surface of the housing can be mounted screwing either pressed into the plug holes, or an additional ring is installed inside the housing, while the contact of the rolling elements with the springs can be made directly at the end of the springs, or through intermediate support elements with a flat, convex or concave shape of the heads And the maximum diameter of the circle formed by projecting from the separator vertices rolling bodies may be greater than the diameter of the circle formed by the trough of the groove of the outer ring, the magnitude of the amplitude A ₂ of possible bearing oscillations, wherein between the inner ring and the separator may be formed of the same magnitude clearance C ₂ ≥A ₂ . 4. The rolling bearing according to claim 1, characterized in that between its outer and inner rings there is a cage-separator, in which cylindrical nests are made in pairs on the outer and inner diameters of the housing, parallel to its longitudinal axis, respectively, with diameters d ' _holes and d _"holes cut by the outer and inner diameter of the housing dihedron, respectively the value l 'and l", and a slot arranged in pairs rolling elements, respectively, the diameter (d' _because, (d _'otv> d'_tk> l '), and d ” _because , (d” _off > d _{unnecessarily} > l ”), with emphasis on the springs inserted into the through holes Holes made on the same radial axis to the rear sides of the pair of sockets, while the contact of the rolling elements with the springs can be made directly along the rim of the springs or through intermediate support elements with a flat, convex or concave head shape, and accordingly the maximum and minimum diameters of the circles formed the peaks of the rolling bodies protruding from the separator can be respectively larger or smaller than the diameter of the circumference of the troughs of the grooves of the outer and inner rings by the amplitude A of possible vibrations The bearings, wherein between the rings and the separator may be made of the same magnitude with gaps ₁ and ₂ ≥A ≥A. 5. The rolling bearing according to claim 1, characterized in that between its outer and inner rings there is a cage-separator, in which cylindrical nests, respectively, with a diameter of d ', are made in a checkerboard pattern along the outer and inner diameters of the housing, parallel to its longitudinal axis _holes and d ” _holes , cut off by the outer and inner diameters of the housing according to the flats, respectively, with a value of l 'and l”, and rolling elements, respectively, with a diameter of d', are installed in the nests _since , (d ' _open >(d' _since > d _{unnecessarily} > l '), and d' _since , (d ” _open > d” _since , d ” _{unnecessarily} > l ”), With emphasis on the springs inserted into the holes located on the radial axis to the rear sides of the sockets, and to hold the springs in these holes, screw-in or pressed-in plugs can be introduced, while the contact of the rolling elements with the springs can be made directly at the end of the springs or through intermediate support elements with a flat, convex or concave head shape, and the maximum and minimum diameters of circles formed by the vertices protruding from the separator t ate rolling, respectively, there may be more or less than the diameter of the circumference of the trough of the grooves of the outer and inner rings by the magnitude of the amplitude A of the possible oscillations of the bearing, while the gaps with ₁ > A and c ₂ ≥A can be made between the outer and inner rings and the cage . 6. The rolling bearing according to claim 1, characterized in that between its outer and inner rings there is a cage-separator, in which cylindrical nests are made in a checkerboard pattern according to the outer and inner diameters, parallel to the longitudinal axis of the housing, with diameters d ″ ' _holes and d ”” _holes , enlarged to overlap the average diameter of the housing, cut off by the outer and inner diameters of the housing according to the flats, respectively, with a value of l' and l ”, and rolling elements, respectively, with diameters d 'are installed in the nests, _because , (d ''' _off >d' _because > l '), and d ” _because , (d ”” _from > d ” _because > l”), and between them, according to the average diameter of the separator, an annular groove is made, passing through the troughs of these nests, respectively, at a distance d ' _since -s ₁ -t ' _to and d ” _since -c ₂ -t ” _k from the outer and inner diameters of the separator, where c ₁ , c ₂ are the gaps between the separator and the outer and inner rings, t 'and t” _k are the depth of the grooves in these rings, which serve to hold and guide them rolling elements, and a flat ring spring is introduced into the annular groove of the separator in contact with the rear vertices of the rolling elements. 7. The rolling bearing according to claim 1, characterized in that in its outer and inner rings, which are separator housings, respectively, according to their inner and outer diameters, parallel to their longitudinal axes, are made cylindrical nests, respectively, with a diameter of d ' _holes and d ” _holes , cut respectively by the inner and outer diameters of the housings according to the flats, respectively, with a value of l 'and l ”, and rolling elements are installed in the nests, respectively, with diameters d _since , (d ' _hole >d' _because > l ') and d ” _because , (D _"holes> d"_tk> l "), with emphasis on their springs introduced into openings arranged radially to the back side of the socket, and between the upper and lower rings of the rolling element operating introduced intermediate ring with grooves serving to hold and guide rolling bodies. 8. The rolling bearing according to claim 1, characterized in that between its outer and inner support rings are placed one above the other two cages with rolling bodies, between which a flat thin-walled ring spring is inserted, covering the protruding surfaces of both rows of rolling bodies, and to hold the ring springs from the end faces of the bearing, thrust rings are installed, located inside or outside the bearing support rings. 9. The rolling bearing according to claim 1, characterized in that between its outer and inner support rings are arranged in staggered rows one above the other in the staggered order of the rolling body, between which a flat thin-walled annular spring serving as a separator is introduced with holes that sequentially cover protruding surfaces rolling elements from both rows. 10. The rolling bearing according to any one of claims 1 to 9, characterized in that, for an angular contact bearing design, the openings for the springs are made in the direction of the resultant forces from the action of radial and axial loads on the bearing, or at an angle close to this direction, and sockets for rolling elements are made at the same angle to the longitudinal axis of the bearing. 11. The rolling bearing according to claim 1, characterized in that its outer ring is made in the form of a hollow open box-shaped spring having a support base, sides and a groove for holding and guiding the rolling bodies along it, which is divided along the axis of the groove cavity by an opening slot, creating access to the cavity and providing the ring with rigidity sufficient to compensate for forces under normal bearing load and providing elastic deformation to the ring when additional dynamic or static peak loads occur. 12. The rolling bearing according to claim 1, characterized in that its inner ring is made in the form of a hollow open box spring having a bearing base, sides and a groove for holding and guiding the rolling bodies along it, which is divided along the axis of the groove cavity by an opening slot, creating access to the cavity and providing the ring with rigidity sufficient to compensate for forces under normal bearing load and providing elastic deformation to the ring when additional dynamic or static peak loads occur. 13. The rolling bearing according to claim 1, characterized in that its inner and outer rings are made in the form of hollow open box springs having a bearing base, sides and a groove for holding and guiding the rolling bodies, each of which is divided along the axis of the depression of the opening groove a slot that creates access to the cavity and provides the rings with rigidity sufficient to compensate for forces under normal bearing load and provide elastic deformation of the rings when additional dynamic or static peaks appear new loads. 14. The rolling bearing according to claim 1, characterized in that its outer ring is made in the form of a hollow box spring with a support base and a groove for holding rolling elements, and a cavity is provided on its lateral side, providing the ring with rigidity sufficient to compensate for the force normal bearing load and providing elastic deformation when additional dynamic or static peak loads occur. 15. The rolling bearing according to claim 1, characterized in that its inner ring is made in the form of a hollow box spring with a support base and a groove for holding rolling elements, and a cavity is provided on its lateral side, providing the ring with rigidity sufficient to compensate for the forces at normal bearing load and providing elastic deformation when additional dynamic or static peak loads occur. 16. The rolling bearing according to claim 1, characterized in that its outer and inner rings are made in the form of hollow box springs with a support base and a groove to hold the rolling bodies, and on the side of the rings is made along the cavity, providing them with rigidity sufficient for compensation of the magnitude of forces under normal bearing load and providing elastic deformation when additional peak dynamic or static loads occur. 17. The rolling bearing according to claim 1, characterized in that its outer ring is made in the form of a box-shaped hollow spring, open on the base side and having two sides connected by a transverse side with a groove for holding and guiding the rolling bodies, which provide ring stiffness sufficient to compensate for the magnitude of forces at normal bearing load and provide elastic deformation when additional dynamic or static peak loads occur. 18. The rolling bearing according to claim 1, characterized in that its inner ring is made in the form of a hollow box-shaped spring open on the base side and having two lateral sides connected by a transverse side with a groove for holding and guiding the rolling bodies, which provide ring stiffness sufficient to compensate for the magnitude of forces at normal bearing load and provide elastic deformation when additional dynamic or static peak loads occur. 19. The rolling bearing according to claim 1, characterized in that its outer and inner rings are made in the form of hollow U-shaped springs open from the base side and having two sides connected by a transverse side with a groove for holding and guiding the rolling bodies, which provide the ring rigidity sufficient to compensate for the magnitude of the forces under normal bearing load and provide elastic deformation when additional dynamic or static peak loads occur. 20. The rolling bearing according to claim 1, characterized in that its outer and inner rings, made in the form of hollow U-shaped springs open from the base side, have protrusions that increase the bearing surface of the rings by performing undercut lateral sides inside the ring through Central groove-slot at the base of the rings. 21. The rolling bearing according to claim 1, characterized in that its outer and inner rings are made in the form of box-shaped hollow springs, with an annular dividing slot on the base. 22. The rolling bearing according to any one of claims 1 to 9 and 11-21, characterized in that it is double-row. 23. A method of manufacturing a rolling bearing according to any one of paragraphs.11-21, characterized in that the support rings of the hollow box-shaped form are obtained by compressing or rolling a sheet blank of the ring around the fusible insert, which is then removed by heating the rings for quenching, while heating and quenching the rings can perform in the technological building. 24. A method of manufacturing a rolling bearing according to any one of paragraphs.14-21, characterized in that the cavities in the rings are made by grinding, and the ring can be imparted in the opposite direction with the cutting speed during grinding.

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