RU2554033C1 - Rolling bearings with step rollers - Google Patents

Abstract

FIELD: machine building.SUBSTANCE: rolling bearing with step rollers contains an external ring (1) and an internal ring (2) with races, located between them rolling bodies made as two-step rollers installed in cage sockets, larger step (3) diameter contacts with race of the internal ring (2) of the bearing, and smaller step (4) diameter contacts with race of the external ring (1). Race diameters of the rings (1) and (2), and diameters of large and small steps (3) and (4) of the roller are in proportional relationship. Ratio d\d= k is equal to any number within permitted range, at that diameters of the roller steps are determined from equation: d= (D-D)\(k+1) and d=kd, where dis diameter of the large step (3) of the bearing roller; dis diameter of the small step (4) of the bearing roller; Dis diameter of race of external ring (1) of the bearing; Dis diameter of race of internal ring (2) of the bearing; k decreasing reduction factor c selected by the user.EFFECT: increasing by k times of speed of internal ring of the bearing relatively to its fixed external ring at same speed of rollers over the external ring relatively to the bearing axis or increased operation time of the bearing by k times at same speed of internal ring, reduced rollers slippage.2 cl, 2 dwg, 1 ex.

Description

The invention relates to the field of mechanical engineering and instrumentation and can be used in all industries.

A known rolling bearing, mainly of large dimensions, which contains rolling bodies — rollers made in two stages. A large stage is rolled in only along the raceway of the outer ring of the bearing, and a smaller stage of the roller, made with at least two sections, is rolled in only along the raceway of the inner ring of the bearing with a constant and identical speed. The large step of the roller is barrel-shaped and contacts the raceway of the outer ring of the bearing along the line, and the rolling elements — the rollers are made with a hole in which there is an axis with a clearance and two built-in angular contact rolling bearings. In this case, the assembly condition for the rolling bearing d _lm / D _wm1 = D _lm / D _wm2 = Const. Two disks act as separators and do not come into contact with either the rolling bodies or the rings of the main bearing (see RU No. 2291330 IPC F16C 19/54, F16C 33/34, published January 10, 2007).

The closest analogue is the radial roller gyro bearing, which contains the inner and outer rings with raceways, the rolling bodies placed between them, made in the form of rollers installed in the separator sockets. The rollers are made in two stages. The larger diameter of the step, having one section, is in contact only with the raceway of the outer ring of the bearing. 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. In this case, the assembly condition for the rolling bearing d _lm / D _wm1 = D _lm / D _wm2 = Const. The raceway of the inner ring of the bearing is made with a groove to form a gap with a diameter of a larger step of the roller, which is made spherical or barrel-shaped, and the raceway of the outer ring of the bearing is made spherical. The ratio of the diameter of the larger stage of the roller to the diameter of the lower stage of the roller is 2/1, and the number of rollers is a prime number, for example five (see RU No. 2385422 IPC F16C 19/22, published 03/27/2010).

A disadvantage of the known technical solution is the wrong model of rotation of the inner ring relative to the outer ring of the bearing, causing an increase in the frequency of rotation of the rollers relative to the axis of the bearing in the analog design compared to a standard bearing with the same model of rotation and the dimensions of the raceways of the outer and inner rings; in the analogue, simple fractions in which the variable diameters of the larger roller stage D _{wm2 are used} , made in a round or barrel-shaped form, and the raceways of the outer ring D _lm , corresponding in the form of the larger stage of the roller, have no answer at all and are not equal to const in particular, as fractions with variable components; There is no way to calculate the diameters of the steps of the rollers.

For a radial bearing with a model of rotation of the inner ring relative to the stationary outer ring, the task is set: to increase the frequency of rotation of the inner ring relative to the outer ring at the same speed of rotation of the rollers in comparison with a standard bearing and analogues; derive a mathematical formula for calculating the diameters of the steps of the rollers, which allows to reduce the frequency of rotation of the rollers.

является полным коэффициентом понижения частоты вращения роликов по наружному кольцу относительно оси подшипника, обусловленного геометрическими пропорциями диаметров дорожек колец между собой и диаметров ступеней ролика между собой, где:The problem is solved in that in the bearing containing the outer and inner rings with raceways (with tracks), the rolling bodies placed between them are made in the form of two-stage rollers installed in the separator sockets, steps of a larger diameter which run around the track of the inner bearing ring, and steps smaller diameter track run in its outer ring, the total coefficient lowering roller speed is proportional to the ratio of a diameter D ₁ \ D ₂ = n within dopa timogo and ₁ d \ d = k ₂ within the allowable, work relations $$\frac{D\mathrm{one}}{\mathrm{<figure-callout\; id="2"\; label="D"\; filenames="00000008.png"\; state="\{\{state\}\}">D</figure-callout>}2}\ast \frac{d\mathrm{one}}{\mathrm{<figure-callout\; id="2"\; label="d"\; filenames="00000008.png"\; state="\{\{state\}\}">d</figure-callout>}2}=nk$$

is the full coefficient of reduction of the frequency of rotation of the rollers along the outer ring relative to the axis of the bearing, due to the geometric proportions of the diameters of the tracks of the rings between themselves and the diameters of the steps of the roller between themselves, where:

d ₁ is the diameter of the larger stage of the bearing roller;

d ₂ is the diameter of the lower stage of the bearing roller;

D ₁ - the diameter of the track of the outer ring of the bearing;

D ₂ - the diameter of the track of the inner ring of the bearing;

n is the coefficient of the ratio of the diameter of the track of the outer ring D ₁ to the diameter of the track of the inner ring D ₂ , the value 1 \ n shows how much of the track of the outer ring rolls the roller at the same time as rolling around one revolution of the track of the inner ring relative to the stationary point of the track of the inner ring (1 \ n - frequency of rotation of the roller along the track of the outer ring relative to the axis of the bearing) in a standard bearing; the limits of permissible n are the size of the diameter of the track of the inner ring D ₂ , having the maximum and minimum acceptable sizes, suitable for the outer ring with an arbitrary diameter of the track D ₁ , when the sizes of the diameters of the rings allow you to place stepped functioning rollers between the rings;

k is an arbitrarily selected coefficient of lowering the frequency of rotation of the roller along the track of the outer ring, which is a proportionality coefficient of the ratio of the diameters of the steps of the roller d ₁ \ d ₂ , limited by the dimensions of the diameters of the steps of the rollers within the limits of the possibility of functioning of the bearing with step rollers, reducing the frequency of rotation of the rollers along the track of the outer ring relative to the axis of the bearing compared to a standard bearing, which is essentially a coefficient of reduction of the roller;

the stationary point of the track of the ring or track of the roller step is the surface point of the specified track, rigidly attached to the track and moving with the track;

the steps of the rollers and tracks of the bearing rings must be

cylindrical, that is, the diameters of the tracks of the rings and the steps of the rollers must be constant for each track or step.

полного коэффициента понижения частоты вращения роликов относительно оси подшипника во время обката роликом наружного кольца позволила выбрать и исчислить частоту вращения роликов относительно оси для подшипника с известными диаметрами дорожек наружного и внутреннего колец в пределах допустимого и подобрать (исчислить) диаметры ступеней ролика в соответствие с выбранным коэффициентом редукции k.Reduced dependence $$\frac{D\mathrm{one}}{\mathrm{<figure-callout\; id="2"\; label="D"\; filenames="00000008.png"\; state="\{\{state\}\}">D</figure-callout>}2}\ast \frac{d\mathrm{one}}{\mathrm{<figure-callout\; id="2"\; label="d"\; filenames="00000008.png"\; state="\{\{state\}\}">d</figure-callout>}2}=nk$$

the full coefficient of reduction of the frequency of rotation of the rollers relative to the axis of the bearing during rolling around the outer ring by the roller made it possible to select and calculate the frequency of rotation of the rollers relative to the axis for the bearing with known diameters of the tracks of the outer and inner rings within the acceptable range and select (calculate) the diameters of the steps of the roller in accordance with the selected coefficient reduction k.

Analysis of the known technical solutions, carried out according to scientific, technical and patent documentation, showed that the set of essential features of the claimed technical solution is not known from the prior art, therefore, it meets the conditions of patentability of the invention - “inventive step” and “novelty”.

The rolling bearing with stepped rollers is illustrated by drawings:

Figure 1 is a geometric diagram of a rolling bearing;

Figure 2 - sectional bearing.

The rolling bearing with stepped rollers consists of an outer ring 1, an inner ring 2, a stepped roller with a higher stage 3 and a lower stage 4.

Since a stepped roller rolls around the raceway of the inner ring with a larger step, and runs a raceway of the race of the outer ring and is designed to model the rotation of the inner ring relative to the outer ring of the bearing, which is opposite in comparison with the known models of rotation of the outer ring relative to the stationary inner ring of bearings with step rollers, then the real bearing will be called a bearing with stepped rollers of the second type; a bearing with a rotation model of the outer ring relative to the stationary inner ring will be called a bearing with stepped rollers of the first type.

The stepped roller may be a monolithic body or assembled from separate parts. Steps 3 and 4 of the roller are rigidly interconnected. The middle section of the roller with a large diameter (large step 3) runs around the track of the inner ring 2. At the same time, the side sections of the roller with a smaller diameter (smaller step 4) run around the track of the outer ring 2, divided by two tracks in width with a gap between them for more 3 roller steps.

To reduce the dimensions of a bearing with stepped rollers to the sizes of standard bearings, the outer and inner diameters of a standard ball or roller bearing and the width of the bearing are taken as the basis for the calculations. The diameters of the raceways of the outer and inner rings 1 and 2 of the bearing are determined by the selected diameters of the standard bearing, taking into account the presence of stepped rollers between them, and arbitrarily selected diameters of the stages 3 and 4 of the roller are matched by these diameters; the thickness of the inner ring of the bearing under consideration can be made smaller than that of a standard bearing, given the minimized wear of the raceway of the inner ring due to the lack of sliding friction inherent in standard bearings, to expand the range of sizes of the diameters of the rings and bring them closer to the diameters of the rings of a standard bearing. The absence of sliding friction between the rollers and the tracks of the rings makes it possible to make the track of the rings and the steps of the rollers of the bearing under consideration significantly narrower than the tracks of the rings and rolling elements of the standard bearing, narrowing the width of the tracks and the roller will not increase the sliding friction, but will bring the width of the bearing under consideration closer to the width of the standard bearing.

When rolling a larger step of the roller of one revolution of the track of the inner ring relative to the stationary point of the track of the inner ring, the roller makes D ₂ \ d ₁ = n ₁ revolutions along the track of the inner ring relative to the stationary point of the track of the inner ring.

When rolling a larger step of the roller n ₁ revolutions relative to the stationary point of the raceway of the inner ring, a smaller step of the roller will run the raceway of the outer ring by n ₁ revolutions. The length of the raceway of the outer ring, passed by the lower step of the roller from the starting point of contact to the final point of contact by the lower step of the roller of the track of the outer ring when passing n ₁ revolutions, is n ₁ πd ₂ , which is d ₁ \ d ₂ times less than during conventional rolling n ₁ revolutions along the raceway of the outer ring with a roller with a diameter of d ₁ (n ₁ πd ₁ ). The reduction coefficient of the roller k = d ₁ \ d ₂ k times reduced the length of the run-in of the raceway of the outer ring - k times reduced the frequency of rotation of the rollers along the track of the outer ring relative to the axis of the bearing

From figure 1 of the geometric diagram of the bearing we deduce the equality

r ₁ is the radius of the greater stage 3 of the roller;

r ₂ is the radius of the lower stage 4 of the roller.

For the convenience of deriving the formulas, we again write down the ratio of the diameters of the steps of the rollers found above:

Using formula (2), we express d _{1 in} terms of d ₂ :

We write formula (1) using formula (3)

From formula (4) we find d ₂ :

By the formula (3) we calculate the diameter d ₁ .

Arbitrarily chosen dimensions of the diameter D ₂ and the reduction coefficient k must be consistent with the diameter D ₁ and with each other to bring the bearing into a functioning structure. The agreed specified components satisfy the formula (1).

The above diameters d ₁ and d _{2 of} steps 3 and 4 of the roller satisfy the conditions of assembly of the bearing with the diameters of the ring tracks D ₁ and D ₂ , the reduction coefficient k of the roller, together with the absence of lubrication, provide good adhesion between the roller and the bearing rings, prevent the rollers from slipping and reduce the frequency of rotation of the rollers relative to the bearing axis is k times compared to a standard bearing (the coefficient n reduces the frequency of rotation of the rollers along the outer ring due to the difference in the lengths of the tracks of the outer and inner rings in the standard mercury and bearing with stepped rollers).

When rolling over a larger step 3 of a roller with a diameter d _{1 of the} track of the inner ring 2, the frequency of rotation of the roller along the outer ring 1 relative to the axis of the bearing will decrease by a factor of k compared with a standard bearing.

The use of a bearing with stepped rollers makes it possible to increase the frequency of rotation of the inner ring relative to the static outer ring of the bearing by a factor of k compared to a standard bearing with the same diameters D ₁ and D ₂ of the ring tracks, the speed of the stepped rollers along the track of the outer ring relative to the axis of the bearing will remain the same like a standard bearing.

If a bearing with stepped rollers is used not as a bearing with high-frequency rotation of one ring relative to another, but as a standard bearing with an average speed, its service life will increase up to k times compared to a standard bearing.

For an example of the calculation, we choose arbitrary sizes in any units of the diameters of the raceways of the outer and inner rings 1 and 2 of the bearing D ₁ = 116 and D ₂ = 68, the reduction coefficient k is three, and from them we calculate the diameters of the larger and smaller stages 3 and 4 of the roller .

We calculate the diameter of the lower step of the roller using the formula (5):

d ₂ = (D ₁ -D ₂ ) \ (k + 1) = (116-68) \ (3 + 1) = 12.

We calculate the diameter of the larger step of the roller using the formula (3):

d ₁ = kd ₂ = 3 * 12 = 36.

Calculation of diameters greater than 3 and less than 4 steps of the rollers using the calculation method, the selected coefficient k, formulas (5), (3) showed the simplicity of calculating a second type bearing with stepped rollers with an arbitrary diameter D _{1 of the} track of the outer ring 1 and the coefficient consistent with D ₁ k and the diameter D _{2 of the} track of the inner ring 2. You can select the size of the diameter D ₂ and coordinate with it the size of the diameter D ₁ and the coefficient k.

As a result of the operation of the bearing without sliding friction and excessive run of the rollers along the outer ring caused by a decrease in the frequency of rotation of the rollers, it will heat less. The properties of the metal and the mechanical properties of the bearing, depending on the heating temperature, will not change. Predictable savings in friction grease for the bearing can be excluded from service components. Without sliding friction, the wear of the rollers and ring tracks will decrease — design gaps will not increase. Without extra gaps, the rollers will not run out of the bearing rings, therefore, the noise level will fall. Noise will also be reduced due to the absence of sliding friction between the rings and the bearing rollers and a decrease in the length and speed of the roller along the outer ring. As the moment of sliding friction force of the bearing and the excess mileage of the rollers decrease, the energy consumption for overcoming the sliding friction forces and the excess mileage of the rollers will be reduced. On a plant-wide or multi-shift bearing mode, the energy savings will be significant. The service life of a bearing with stepped rollers will increase many times over compared to a standard bearing - there will be big savings in the purchase of spare bearings and replacement of bearings, they will need to be changed much less frequently. Downtime of equipment for repair or replacement of bearings will decrease many times - the volume of products and profit margins will increase. Replacing a high frequency rotation bearing made of expensive materials using expensive technology with a stepped roller bearing will also be profitable.

The claimed technical solution provides an increase in the frequency of rotation of the inner ring of the bearing relative to the static outer ring without increasing the frequency of rotation of the rollers relative to the axis of the bearing, or an increase in the life of the bearing compared to similar ring tracks and the frequency of rotation of the inner ring relative to the static outer ring with a standard bearing. The diameters of the roller steps of the presented bearing are calculated according to the derived formulas. Thus, the technical result is achieved.

The rolling bearing with stepped rollers can be manufactured using well-known equipment using modern materials and technologies.

Claims (2)

1. The rolling bearing with stepped rollers, containing the outer and inner rings with raceways, the rolling bodies installed between them, made in the form of two-stage rollers installed in the seats of the separator, the larger diameters of which are in contact with the raceway of the inner bearing ring, and the smaller diameters are in contact with the raceway of its outer ring, the diameters of the raceways of the outer and inner rings and the diameters of the larger and smaller steps of the roller are in proportion dence, characterized in that the ratio d ₁ \ d ₂ = k and is any number within permitted, the diameters of the bearing rollers steps determined from the relation: d ₂ = (D ₂ -D ₁₎ \ (k + 1) and d ₁ = kd ₂ , where
d ₁ is the diameter of the larger stage of the bearing roller;
d ₂ is the diameter of the lower stage of the bearing roller;
D ₁ - the diameter of the raceway of the outer ring of the bearing;
D ₂ - the diameter of the raceway of the inner ring of the bearing;
k is the coefficient of reduction of the roller, which reduces the speed of the stepped roller relative to the axis of the bearing during rolling by the roller of the raceway of the outer ring of the bearing in comparison with a standard bearing, equal from one to several units, independently selected according to needs. 2. The bearing according to claim 1, characterized in that the steps of the roller and the raceways rolled around by them should have a cylindrical shape, that is, constant diameters.

Images