RU2232926C2 - Antifriction bearing - Google Patents

Abstract

FIELD: mechanical engineering, instrument engineering.

SUBSTANCE: invention can be used in all industries. Proposed antifriction bearing contains solids of revolution-rollers which are made two-step. Larger diameter of step rolls only over path of bearing outer race, and smaller diameter of roller step, made at least with two sections, rolls only along path of bearing inner race at constant and equal velocity of rotation. Solids of revolution-rollers can be made two-step beveled. Solids of revolution can be provided with rings interacting with paths of bearing races and rolling over diameters of stepped roller. Rings can be made flexible, three-support type.

EFFECT: increased velocity of rotation, reduced value of elastic hysteresis in zone of contact of solids of revolution and bearing races, provision of damping of load fluctuations.

7 cl, 16 dwg

Description

The invention relates to the field of mechanical engineering and instrumentation and can be used in all industries. The invention relates to the most important structural elements of machines and devices and makes up the bulk of the friction units.

Known rolling bearings containing inner and outer rings with raceways placed between them rolling elements made in the form of rollers installed in the seats of the separator.

One of the disadvantages of the known standard rolling bearings during their operation is the presence of rolling friction with slipping of the rolling elements.

For example, take a single row radial roller bearing according to GOST 8328-75 (d65 × D100 × B18; d _p = 9 mm, Z = 20, d _1m = 73.5 mm, D _1m = 91.5 mm). For one revolution of the shaft, the roller d _p makes along the raceway of the inner ring d _1m

N turns = π 73.5 / π 9 = 8.166,

and along the raceway of the outer ring D _1m

N turns = π 91.5 / π 9 = 10.166.

Thus, the roller makes two turns more than along the track of the inner ring - this is the amount of slippage of the roller. Thus, we have rolling friction with slippage.

Known rolling bearing - prototype - according to the patent FR 2699238, And C. F 16 C 19/22, containing inner and outer rings with raceways, rolling bodies located between them, made in the form of rollers installed in the seats of the separator, in which the rolling bodies - rollers - are made of two stages, a larger diameter of the stage, having one contact section only with the raceway of the outer ring of the bearing, and a smaller step diameter made with two sections interacting only with the raceway of its inner ring with a constant and equal speed, nyatsya condition of the bearing assembly:

d _1m / Dwm ₁ = D _1m / Dwm ₂ ,

where d _1m is the diameter of the raceway of the inner ring of the bearing;

Dwm ₁ is the diameter of the lower step of the roller;

D _1m is the diameter of the raceway of the outer ring of the bearing;

Dwm ₂ - the diameter of the greater step of the roller,

and the raceway of the inner ring of the bearing is made with one groove for the formation of a gap with a large diameter step of the roller.

According to the new version, the roller should be two-stage and the assembly condition for bearing No. 2113 should be met:

d _1m / Dwm ₁ = D _1m / Dwm ₂ = Const, 75.112 / 7.388 = 10.166 (turns)

91.5 / 9 = 10.166 (turnover).

The assembly condition is fulfilled, and as a result, we have a clean rolling of the rolling elements along both the outer and inner raceways of the bearing rings.

The purpose of the invention:

- providing a higher bearing speed;

- reduce the effect of elastic hysteresis in the contact zone of the rolling elements with the raceways of the bearing;

- provide damping of load fluctuations;

- ensure clean rolling without slipping and angular contact bearing.

The goals and technical effect of the invention is achieved due to the fact

that the step of the rolling body - the roller - with a large diameter is made spherical or barrel-shaped, and the raceway of the outer bearing ring is made spherical;

that the step of the rolling body - the roller - with a smaller diameter is made conical;

that the larger diameter of the step of the roller and its two sections with a smaller diameter of the step are conical;

that the rolling bodies - rollers - are equipped with intermediate rings that are made with an increased outer diameter relative to the calculated one according to the condition of the assembly of the bearing, the latter are in contact and rolled around with their outer diameters to the raceways of the outer and inner rings of the bearing, and the inner diameters of the rings are contacted and rolled around the outer the diameters of the steps of the roller;

that the rolling bodies - rollers - are equipped with rings made of elastic tricycle, for example, with point contact with the raceways of the bearing;

that rings mounted on a twisted roller on the inside contain a spherical surface;

that the rolling body — the roller — consists of a single-stage cylindrical roller made according to the diameter of the smaller stage of the roller, and the larger diameter of the stage of the roller is made in the form of a ring.

Figure 1 shows the rolling bearing radial single row roller with an annular groove on the raceway of the inner ring. The direction of perceived loads is radial.

The rolling bearing consists of an outer ring 1, rolling elements 2, cage 3 of the inner ring 4. This rolling bearing is distinguished by the design of rolling elements 2. A large rolling stage in diameter Dwm _{2 is} made with a spherical surface or barrel-shaped. This design provides the point contact of a larger stage of the roller with the race of the outer ring 1.

The rolling elements 2 are made with a Central hole.

The condition of the Assembly of the rolling bearing in figure 1:

d _1m / Dwm ₁ = D _1m / Dwm ₂ = Const,

Const, for example, is 7.

As an example, 210/30 = 280/40 = 7, where Const is a constant number that can be either integer or fractional.

This assembly condition allows the rolling elements 2 to run along the bearing raceways at the same peripheral speed, which results in a clean rolling of the rolling elements 2 without slipping.

Figure 2 shows the rolling bearing radial roller spherical single row with a protruding inner ring and two protective washers. The direction of perceived loads is radial.

The rolling bearing consists of the same parts as in figure 1, the cage is not shown. This bearing is distinguished by the design of the ring 1, in which the raceway is made spherical.

The inner ring 4 is made with an annular groove and contains two sections - raceways, which are contacted by the cylindrical surfaces of the rolling elements 2 with a smaller step diameter Dwm ₁ . The protruding sections of the inner ring 4 are made spherical.

The radii of the sphere of the ring 1 and 4 pass through the axis of the bearing at the point of the axis of symmetry of the bearing (vertical axis of symmetry). Spherical sections of the ring 4 are in contact with the protective washers 6, the latter are pinched in the grooves of the outer ring 1.

A larger diameter of the step of the roller Dwm ₂ on the outer surface can be made with a spherical or barrel-shaped surface. In the first case, the roller will have point contact with the raceway, and in the second case it will be linear, when the radius of the sphere of the ring 1 coincides with the radius of the barrel-shaped surface of the roller 2.

On the external surfaces (diameters Dwm ₁ Dwm ₂ ), 7 types of bee honeycombs were knurled (the depth and width of the knurled contour is selected in the range from 0.05 to 0.15 mm or more, depending on the dimensions of the rolling bodies and operating conditions). The condition of the Assembly of the rolling bearing in figure 2 is similar to figure 1.

Figure 3 shows the rolling bearing radial roller single row closed type with two protective washers and locking thrust rings. The direction of perceived loads is radial.

This type of rolling bearing is designed to operate in extreme conditions (in space, in the extreme north, at temperatures up to -80 ° C).

The rolling bearing of FIG. 3 consists of the same parts as in FIG. This bearing is distinguished by the design of the rolling bodies 2. They contain an internal cavity 8 made, for example, of porous cermet, as well as annular grooves 9 grooved on the cylindrical sections of the stepped roller 2 and communicating with the internal cavity 8. The annular groove 9 and the channels are also made from porous cermet, which contains a lubricant, for example, VNIIP-274N.

On the outer surface of the rolling bodies along Dwm ₁ and Dwm ₂ , knurling is performed (as shown in FIG. 2, item 7). The bearing contains two protective washers 6 and two locking rings 10 located in the annular grooves of the ring 4. The condition for assembling the rolling bearing is similar to the bearing in figure 1.

Figure 4 shows the radial roller bearing with needle rollers single-row complete with a cage. The direction of perceived loads is radial.

A rolling bearing of this type consists of an outer ring 1, rolling elements 2, a cage 3, an inner ring 4.

It differs in that the rolling bodies are made with three steps of a larger diameter Dwm ₁ and four steps of a smaller diameter Dwm ₁ . The raceway with a diameter d _{1m of the} ring 4 is made with three annular grooves to form a gap for the steps of a larger diameter of the roller 2. The condition for assembling the bearing is similar to FIG. 1.

Figure 5 shows the rolling bearing radial roller spherical double row with a separator and a cylindrical bore. The direction of perceived loads is radial and axial in both directions.

The rolling bearing consists of an outer ring 1 with a raceway of a spherical type, rolling elements 2, an inner ring 4, a cage is not shown.

This bearing is distinguished by the design of the inner ring 4, in which two annular grooves are made at an angle for arrangement with a gap of a larger diameter of the roller step Dwm ₃ . On the inner ring 4 there are two inclined raceways in contact with the conical sections of the lower stage of the roller 2 with diameters Dwm ₁ and Dwm ₂ . Contact of these surfaces is carried out along a line with inclined raceways (as in tapered bearings). The diameter of the larger roller stage Dwm _{3 is} in contact with the raceway of the outer ring 1 of a spherical type.

Figure 6 shows the rolling bearing angular contact roller single row with tapered rollers, for example, with a contact angle (α up to 30 °). The direction of perceived loads is radial and axial only in one direction.

The rolling bearing consists of an outer ring 1 containing a spherical type raceway, rolling elements 2, a cage 3, an inner ring 4 with an annular groove (as in FIG. 5) and containing a wide end (like a tapered bearing). The inclined raceway of the ring 4 is in contact with the conical surface, the diameters of the lower roller stages Dwm ₁ and Dwm ₂ .

The diameter of the larger roller step Dwm ₃ contacts in point only with the raceway of the spherical type of the outer ring 1. The wide end of the ring 4 carries out a radial tension and receives axial force.

Figure 7 shows the rolling bearing angular contact roller single row with tapered rollers of the stepped type. The rolling bearing of this type consists of the same parts as the bearing in FIG. 6.

It differs by the execution of the raceway of the outer ring 1 - inclined (conical), and the rolling bodies 2 are made of conical step type. The diameters of the lower roller stage Dwm ₁ and Dwm _{2 are} in line contact only with the raceway of the inner ring 4. The diameters of the larger roller stage (conical type) Dwm ₃ and Dwm _{4 are} in line contact only with the raceway of the outer ring 1. A wide end in the rolling bearing radial interference and perceives axial force.

On Fig shows the rolling bearing angular contact roller double row with tapered rollers of the stepped type and two inner rings. The direction of perceived loads is radial and axial in both directions.

The bearing allows adjustment of the radial and axial clearance due to the expansion ring 11, the cage is not shown.

Figure 9 shows the rolling bearing radial roller single row with single-sided inner ring and a flat thrust ring. The direction of perceived loads is radial.

A rolling bearing of this type consists of an outer ring 1 made with two flanges, rolling elements 2, a cage 3, a single-flange inner ring 4 made with an annular groove, a flat thrust ring 12.

Figure 10 shows a section bB of Fig.9. Figure 10 shows the direction of rotation of the rolling elements 2 with arrows (two sections of a stepped roller with a diameter of Dwm ₂ and Dwm _{1 are} conventionally shown) when two of its sections (rollers) are run along the raceways with an outer ring 1 and an inner ring 4. The separator in FIG. .10 conditionally not shown.

The rolling body 2 consists of a stepped roller and contains on the outside a ring 13 with a diameter Dwm ₂ (diameter of a larger stage of the roller) and two rings 14 with a diameter of Dwm ₁ (diameter of a smaller stage of a roller). The outer diameters of the rings 13 and 14 are increased by the value of the optimal relative clearance (as in plain bearings). The assembly condition of this bearing is similar to FIG. 1:

d _1m / Dwm ₁ = D _1m / Dwm ₁ = Const (Const, for example, is 7).

A hard roller is calculated according to this formula, as in FIG. After that, the thickness of the rings 13 and 14 is outlined (for example, equal to 5 mm) and the middle stepped roller is installed.

The diameters Dwm ₁ and Dwm ₂ are calculated, and the true sizes of the rings are increased by the value of the optimal relative clearance. A clearance is necessary to ensure the passage of lubricant and to replace the rings with rings of another profile.

Figure 11 shows a view In figure 9, where the rings 13 and 14 are made of elastic tricycle with contact at the point with the raceways of rings 1 and 4 and a stepped roller. This design of rings 13 and 14 allows the rolling bearing to dampen and absorb shock loads, the possibility of damping load oscillations (the presence of an intermediate element also made it possible to ensure damping of load oscillations in the bearing).

The middle roller in Fig. 9 can be stepped, but it can also be cylindrical, only the thickness of the rings 13 and 14 will change, and in the contact zone of the ring and the middle roller they run without sliding, with a constant and identical speed.

12 shows a rolling bearing similar to the rolling bearing of FIG. 9. This embodiment is characterized in that the middle step roller 2 is knurled (as in FIG. 2 for better grease retention on the outer surface of the rollers in the knurling grooves). For better circulation of the lubricant, for example, annular grooves are made on the inner surface of the rings 13 and 14. The outer diameter of the rings 13 and 14 is increased compared with the rings in Fig.9. Knurling of the type of bee honeycomb is made on the outer surface of the rings 13 and 14. At the ends of the rollers 2 there are bumpers for holding the lubricant, and the rings 14 freely pass through the outer diameter of the bobbin.

The assembly condition is similar to the rolling bearing in Fig.9.

In Fig.13 shows a rolling bearing angular contact roller single row with tapered rollers. A rolling bearing of this type consists of the same parts as in FIG. 7.

It differs from FIG. 7 by the presence of a ring 13, which is freely worn with a gap through the diameter Dwm ₁ . Ring 13 is installed in the middle of the roller 2 in its groove with a gap.

On Fig shows a view G of Fig.13, where the ring 13 is made of elastic tricycle with contact at the point with the raceway of the outer ring 1. This design of the ring 13 allows damping of load oscillations in the rolling bearing.

On Fig depicts a single row radial bearing with twisted cylindrical rollers. The direction of perceived loads is radial.

A rolling bearing of this type consists of an outer ring 1, rolling elements 2, a cage 3, an inner ring 4 made with an annular groove and additionally bearing two locking thrust rings 10 located in the annular grooves of the ring 4.

It differs in that the rolling bodies 2 comprise a middle twisted cylindrical roller 15, on which two rings 16 and an enlarged middle ring 17 are mounted on the outside with a gap, as in FIGS. 9 and 12.

The inner surfaces of the rings 16 and 17 are made with a spherical or barrel-shaped surface and are in contact with the twisted roller 15 at a point. The condition of the assembly is similar to Fig.9.

It should be noted that the ring 17 is mounted on a twisted roller 15 with the possibility of significant damping of load fluctuations in the rolling bearing.

The rolling bearings in Figs. 1-4 work as follows: when the shaft rotates, the bearing ring 4 receives rotation, the roller 2 with its smaller diameter Dwm of the _1st stage is rolled in only along the raceway with the diameter d _{1m of the} inner ring 4. The larger diameter Dwm _{2 of the} stage of the roller 2 is rolled only along the raceway D _{1m of the} outer ring 1. Rotation of the rolling elements 2 occurs under rolling conditions without slipping relative to the raceways of the bearing rings.

The bearing in figure 2 is characterized by the presence of knurling on the outer surfaces of the rolling elements 2, which allows you to save the oil film during operation of the bearing in the contact zone of the rollers with the raceways of the rings. This condition allows you to use the bearing with its performance in extreme conditions. For example, when landing heavy liners and hitting the wheels with concrete covering the landing strip (known bearings are so heated that the rolling bodies are welded to the raceways), however, the chassis wheels should already rotate before touching the “concrete” with the drive, for example, from compressed air, since rest friction is undesirable here.

The rolling bearing in figure 3 is distinguished by the ability to allocate lubricant to the outer surface of the rollers and transfer it to the raceways. Part of the lubricant also contains the labyrinths of the grooves of the knurled pattern of the hexagon (such as bee honeycombs).

The lubricant is released from the heating of the roller during its operation from the internal cavity 8. When the bearing is cooled (when it is not working), the lubricant collects in the cavity 8. Pre-heating of the bearing can be carried out, for example, by heating diodes located in the bearing area.

The bearing in figure 4 differs from the known bearings with needle rollers with the possibility of rolling elements 2 run in the raceways with a constant and the same speed without slipping. The assembly of the bearing is provided, for example, with a radial clearance equal to the working temperature of the outer ring (for example, from +90 to + 120 ° C) based on the nominal size of the raceway of the outer ring. The condition of the assembly of the bearing is similar to figure 1.

The rolling bearing in Fig. 5 differs in the condition of assembly from the condition of assembly of the bearings in Figs. 1-4, in the presence of tapered rollers with diameters Dwm ₁ and Dwm ₂ (tapered sections of the roller).

Assembly condition for this bearing:

d _1m / Dwm ₁ = d _2m / Dwm ₂ = D _1m / Dwm ₃ = Const.

It should be noted that pure rolling of a larger stage of rollers with a diameter of Dwm ₃ (diameter in the "Pole") can be carried out only in the "Pole" of these rollers, and on the consoles of this section of the roller (to the right and to the left of the "Pole") the rolling takes place with sliding.

To eliminate this drawback, it would be better if Dwm ₃ touches a point with a raceway of a spherical type of outer ring 1.

It is necessary that the radius of the sphere of the roller 2 on the diameter Dwm ₃ be smaller than the radius of the sphere of the raceway of the ring 1. This will achieve a clean rolling of the rollers 2 along the raceway of the ring 1. The generatrix of the conical section of the roller with diameters Dwm ₁ and Dwm ₂ also rolls without sliding along raceways (inclined track) of the inner ring 4.

The bearing of FIG. 6 has an assembly condition similar to that of FIG. 5, and works just like the previous bearing (see FIG. 5). The difference is that the bearing this single-row and wide end of the inner ring 4 provides a radial tension and perceives axial load during operation of the bearing.

The assembly condition ensures that this rolling bearing (angular contact single row with tapered rollers) and its rolling bodies 2 run along the raceways of rings 1 and 4 with a constant and equal rotation speed (with a constant peripheral speed) without slipping, which ensures pure rolling. The condition of pure rolling at a wide end is absent.

The rolling bearing in FIG. 7 works similarly to FIGS. 5 and 6.

It differs by the condition of assembly and the presence of a linear contact of the stepped conical roller 2 with the raceways of rings 1 and 4.

Build Condition:

d _1m / Dwm ₁ = d _2m / Dwm ₂ = D _1m / Dwm ₃ = D _2m / Dwm ₄ = Const,

where d _1m is the diameter of the raceway (min) of the inner ring of the bearing;

Dwm ₁ - (min) the diameter of the smaller step of the conical roller;

d _2m is the diameter of the raceway (max) of the inner ring of the bearing;

D _1m is the diameter of the raceway (min) of the outer ring of the bearing;

Dwm ₃ is the diameter of the larger step (min) of the conical roller;

D _2m is the diameter of the raceway (max) of the outer ring of the bearing;

Dwm ₄ - (max) diameter of the larger step of the conical roller.

The values of max and min refer to the places of mating (touching) the diameters of the conical roller and raceways of the bearing rings.

This rolling bearing, compared with FIGS. 5 and 6, is capable of transmitting large radial and axial loads, since it has linear contact with the raceways.

The rolling bearing in Fig. 8 works like the bearing in Fig. 7. Its difference is that it is capable of allowing adjustment of the radial and axial clearance due to the expansion ring 11. The assembly condition of Fig. 8 is similar to Fig. 7.

The rolling bearing in Fig. 9 works somewhat differently with respect to the bearings in Figs. 1-4, when the bearing of this design is used, the outer diameters of the stepped roller 2 are run without sliding along the inner diameters of the rings 13 and 14 with a constant and identical rotation speed. The outer surfaces of the rings 13 and 14 in contact with the raceways of the rings 1 and 4 are also run in non-slip at a constant and equal speed (see figure 10).

The presence of radial channels for lubrication in the ring 1 and the roller 2 (shown in Fig. 9 by a dashed line) and the presence of a relative clearance between the roller 2 and the rings 13 and 14 contributes to the stable operation of the bearing. Under certain conditions and high speeds of rotation in the bearing, it is possible to create conditions for hydrodynamic lubrication (in the gap between the rings and roller 2, as well as in the gap of the annular groove of the ring 4, if this gap is sufficiently small). The increased diameter of the rings 13 and 14 in contact with the raceways of rings 1 and 4 somewhat reduces the amount of elastic hysteresis.

The presence of an intermediate element (see Fig. 11), and this is the design of the rings 13 and 14, which are made elastic, can provide damping of load fluctuations in the bearing and even absorb shock loads, for example, when landing heavy liners or participating in car races. However, the rings 13 and 14 must be made of appropriate material.

The rolling bearing in Fig. 12 works similarly to the bearing in Fig. 9. It differs from the bearing of Fig. 9 in the increased radial clearance between the rings 13 and 14 and the outer surface of the stepped roller 2. This design reduces the elastic hysteresis in the contact zone of the rings 13 and 14 with the raceways of the rings 1 and 4. the outer surface of the stepped roller 2 and on the outer surface of the rings 13 and 14 serves the purpose of retaining the lubricant in the knurling grooves and transferring it to the contact surface during operation of the bearing.

This bearing is also capable of operating in conditions of limited lubrication (for example, when the lubricant supply pipe or helicopter gearbox is broken). In this case, the criterion will be the duration of the gearing, and not the performance of the bearing.

The rolling bearing in Fig.13 works similarly to the bearing of Fig.7. The assembly condition of the bearing (its calculation) is divided into two stages.

Define the dimensions of the conical roller - the lower step of the roller 2:

d _1m / Dwm ₁ = d _2m / Dwm ₂ = Const (for example, equal to 9).

Then we calculate the assembly condition for a larger stage of the conical roller (diameter of the ring 13 - hard gapless ring):

D _1m / Dwm ₃ = D _2m / Dwm ₄ = Const (and also equal to 9).

In practice, the ring 13 is a rigid step of the conical roller (as in FIG. 7).

Artificially increase the outer diameter of the ring 13 to the dimensions of the ring assembly from the side of the diameter Dwm ₁ . A smaller step of the tapered roller 2 makes, for example, nine revolutions per revolution of the shaft. The large stage of the roller 13 is run without sliding in the annular groove of the lower stage of the roller 2.

In order to ensure damping of load oscillations, the ring 13 is made flexible with three bearings (see Fig. 14), with point contact along the raceway of the ring 1.

It is known that rolling bearings with tapered rollers are prone to hauling, which leads to excessive heating of the bearing rings, jamming of the assembly, failure of the whole machine unit, device, machine. The proposed bearings of this type are also prone to hauling. These bearings can be operated, for example, at the optimum heating temperature (for example, t = 90 ° C - stable, operation is possible, since the temperature does not increase). However, the service life will be reduced if the operating temperature (t = + 150 ° C).

The rolling bearing in Fig. 15 is similar in terms of the assembly condition to Figs. 1, 9, 12. The rings 16 and 17 are mounted on the twisted roller 15 with a clearance.

This bearing is capable of transmitting significant shock loads due to the presence of a twisted roller 15, this allows both the outer 1 and the inner ring 4 to damp. A bearing of this type works without slipping; under normal conditions, its rings 16 and 17 run along the raceways of rings 1 and 4 with a constant and identical speed. And only in extreme cases, at the time of impact, a sharp increase in load, the ring 17 is run in with sliding, as the twisted roller 15 sags and the position of the roller axis relative to the bearing axis is violated.

The proposed bearing can find application, for example, in the rollers of tracked vehicles, the operation of which takes place on rough terrain.

In Fig.16 shows a radial single row roller bearing with an annular groove on the raceway of the inner ring.

The direction of perceived loads is radial.

The rolling bearing consists of an outer ring 1, a rolling element 2, a cage 3, an inner ring 4. A roller 2 is made with a diameter Dwm ₁ - a diameter of a smaller step of a roller, on which a ring 13 with a design diameter of Dwm ₂ - a diameter of a larger step of a roller is mounted. The true diameter of the larger stage of the roller 13 is increased by the value of the optimal relative clearance.

On Fig given an example of a more technologically advanced bearing execution for mass production in the factories of the bearing industry. However, it should be noted some feature of these radial roller bearings.

With a radial clearance Gr in the rolling elements, when they are run along the raceways of rings 1 and 4, there is rolling with slipping. With a significant radial clearance in the bearing, the amount of slip increases in the range from 0.2 to 1% for all rollers, however, the bearing remains operational.

In the known bearing No. 2113, the slip value of one roller is from 13 to 20%. The proposed rolling bearing has the following advantages compared to standard bearings:

- the ability to work at high speeds;

- stability of gaps and increased alignment of the shaft;

- the ability to work in a wide range of temperatures, in extreme operating conditions;

- reduction of elastic hysteresis in the contact zone of the rolling elements;

- the possibility of damping load fluctuations;

- increased bearing life.

- to ensure clean rolling without sliding and angular contact rolling bearings with tapered rollers of step type.

Claims (7)

1. A rolling bearing containing inner and outer rings with raceways, rolling bodies placed between them, made in the form of rollers installed in the seats of the separator, rolling elements — rollers are made in two stages, a larger step diameter having one section contacts only with the raceway the outer ring of the bearing, and the smaller diameter of the step, made with two sections, is in contact only with the raceways of its inner ring with a constant and the same speed of rotation, while assembly condition of the bearing d _1m / Dwm ₁ = D _1m / Dwm ₂ = Const, where d _1m is the diameter of the raceway of the inner ring of the bearing; Dwm ₁ is the diameter of the lower step of the roller; D _1m is the diameter of the raceway of the outer ring of the bearing; Dwm ₂ - the diameter of the greater step of the roller, and at least one raceway of the inner ring of the bearing is made with at least one groove to form a gap with a large diameter of the roller step, characterized in that the step of the rolling body - roller with a large diameter is made spherical or barrel-shaped, and the raceway of the outer ring of the bearing is made spherical. 2. The rolling bearing according to claim 1, characterized in that the stage of the rolling body - the roller with a smaller diameter is made conical. 3. The rolling bearing according to claims 1 and 2, characterized in that it is made of an angular contact type, and the larger diameter of the roller step and its two sections with a smaller step diameter are made conical. 4. The rolling bearing, in which the rolling bodies - rollers are made in two stages, characterized in that the rolling bodies - rollers are equipped with intermediate rings, which are made with an increased outer diameter in relation to the calculated one according to the condition of the bearing assembly, the latter are contacted and run in their outer diameters with the tracks rolling of the outer and inner rings of the bearing, and the inner diameters of the rings are in contact and run on the outer diameters of the steps of the roller. 5. The rolling bearing according to claim 4, characterized in that the rolling bodies - rollers are provided with rings made of elastic tricycle, for example, with point contact with the raceways of the bearing. 6. The rolling bearing according to claim 4, containing twisted cylindrical rollers, characterized in that the rings mounted on the twisted roller, on the inside, contain a spherical surface. 7. The rolling bearing, according to claims 4 and 5, characterized in that the rolling body - the roller consists of a single-stage cylindrical roller made according to the diameter of the smaller stage of the roller, and the larger diameter of the stage of the roller is made in the form of a ring.

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