RU2276749C2 - Anti-friction bearing - Google Patents

Abstract

FIELD: mechanical engineering and other industries.

SUBSTANCE: proposed anti-friction bearing is just radial-thrust single-row bearing with inner and detachable outer races and single-stage rollers located between them and mounted in cage. Larger diameter of larger stage of roller is engageable only with two raceways of detachable outer race at two points at angle α. Lesser diameter of cylindrical roller stage is engageable through intermediate member only with two raceways of inner race at two points at constant and similar speed of rotation. Raceway of inner race is provided with circular bore forming clearances under larger diameter of larger stage of roller. Intermediate member is made in form of rigid torus ring exceeding lesser diameter of roller stages. Raceways for rigid torus ring are made on outer side of inner race of bearing; grooves for torus ring are made on cylindrical surfaces of lesser diameters of roller.

EFFECT: enhanced durability of bearing due to avoidance of slippage of rollers; reduced elastic hysteresis in zone of engagement of lesser diameter of roller stages.

1 dwg

Description

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

Known rolling bearings containing inner and outer rings with raceways, the rolling bodies located between them, made in the form of balls or rollers installed in the nests of the separator.

The main disadvantage of the known rolling bearings is, along with rolling friction, the presence of rolling friction with slipping of the rolling elements relative to the raceways:

- slippage of the rolling elements relative to the raceways caused by shear deformation of the material at the point of contact;

- sliding of the rolling elements relative to the raceways in case of violation of rolling as a result of shifts and distortions of the bearing rings under load (see PI Orlov, book 2 "Fundamentals of Design" M .: Mashinostroenie, 1977, p. 453 ... 460).

For example, take a single-row angular contact ball bearing with a split outer ring with a four-point contact No. 116220 according to GOST 8995-75, for which d100 × D180 × B34; DW25.4; Z = 14; α = 26; Nk = 4000 min ^-1 ; Nzh = 5000 min ^-1 . Ball ⌀25.4 rolls in cord with ⌀23 mm along bearing raceways. On the outer raceways with ⌀163 mm, the ball is rolled in in one revolution of the shaft:

N revolutions = π163 / π23 = 7.086.

And on the raceways of the inner ring with ⌀117 mm, the ball makes in one revolution of the shaft:

Revolutions = π117 / π23 = 5.086

That is, along the raceways of the outer ring of the bearing, the ball makes two turns more than along the raceways of the inner ring of the bearing. This value is equal to the value of the ball slipping in the bearing for only one revolution of the shaft. And the balls in the bearing 14 and each in one revolution of the shaft makes two extra turns or this path slides.

However, the bearing can do 5000 min ^-1 . Then the number of "extra" revolutions will be done in just one minute with all the balls (Z = 14):

N = 14 × (5000 × 2) = 140,000 min ^-1 .

This contradiction has been working in rolling bearings, both radial and angular contact, for 120 years since the manufacture of bearings at a factory in Germany, when industrial production was mastered.

Analogues for this proposed invention are applications No. 2001119832 and No. 2002107654.

The purpose of the invention:

- ensuring a clean rolling of the rolling bodies when rolling them along the raceways of both the inner and outer rings of the bearing;

- in general, to increase the durability of the bearing, only by eliminating the slip of rolling elements, as well as by reducing the value of the elastic hysteresis in the contact zone of a smaller diameter of the steps of the roller;

- increase the frequency of rotation of the rolling bearings, for example, two times in relation to the known bearings.

The goals and technical effect of the present invention is achieved due to the fact that the intermediate link is a rigid torus ring, which is made larger in relation to the calculated smaller diameter of the roller steps, and raceways for a rigid torus ring are made both on the inner bearing ring and cylindrical sections of smaller diameters of the steps of the roller.

The drawing shows a rolling bearing angular contact single row with a detachable outer ring with four point contact of the rolling elements with raceways. The direction of perceived loads is radial and axial in both directions.

The rolling bearing consists of a detachable outer ring 1, rolling elements 2, cage 3, inner ring 4 and intermediate 5. Rolling bodies 2 are made in the form of a single-stage roller, the larger diameter of the larger side of the roller is made spherical in shape and contacts only with raceways with a diameter D _{1m of the} outer ring 1 at two points along the diameter of the roller D _wm2 with a contact angle α (α is from 12 ° to 36 °, as an example). A smaller diameter of the steps of the roller 2 is made cylindrical with radial ring grooves along which the intermediate link 5 is run. The latter is made in the form of a hard torus with an increased diameter relative to the calculated one. An annular groove is made on the inner ring 4 with the formation of gaps for a larger diameter of the larger step of the roller 2. Additionally, the radial annular grooves are made on the inner ring 4 — raceways with a diameter of d _1m , along which the design diameter D _{wm1 contacts} — the smaller diameter of the roller step 2 .

The separator 3 is centered on the outer diameter with the ring 1, contains center inserts for fixing the rollers 2, as well as connecting step rivets (see drawing).

The rolling bearing shown in the drawing works as follows: when the shaft rotates, the inner ring 4 is rotated, the step roller 2 with its smaller diameter D _{wm1 is run} through the intermediate link 5 along the raceways with the diameter d _{1m of the} inner ring 4. The larger diameter of the larger step D _{wm1 is} rolled in raceways D _{1m of the} outer ring 1. In this case, it is necessary that the assembly condition is met:

D _1m / D _wm2 = d _1m / D _wm1 = const.

It should be noted here that this condition allows the rolling bodies 2 to run on the outer and inner raceways with a constant and the same speed without slipping.

The intermediate link 5, the hard torus ring, is in contact simultaneously with the raceways of the inner ring 4 and the annular grooves of the smaller diameter of the steps of the roller 2. Moreover, this link 5 is involved in the transmission of both radial load and axial load. Intermediate 5 — a rigid annular torus, made larger than the calculated diameter of the smaller diameter of the roller step D _wm1 , works with its radius from the center of the roller 2. The larger radius of the hard torus 5 when running reduces the elastic hysteresis at the contact with the raceway diameter d _1m . Since in contact with the raceways d _1m passes and rolls in the increased radius of the torus hard ring 5. And in contact with the raceways D _{1m of the} outer ring 1 there are two sections with a diameter D _wm2 - a larger diameter of the stage of the roller 2.

It should be noted that these diameters of the rigid annular torus can also be different in outer diameter, and in cross section the torus must be ideal and the same. This fact will not affect the operation of the bearing during its rotation, it will only affect the speed of running the intermediate link 5 in its average diameter of the torus ring. However, this circumstance will affect the natural vibrations of the bearing.

It would be better if the outer diameters of the torus are the same for each roller (for example, for the first roller, the torus dH will be 65 mm, and for the next, dH will be 63 mm). That is, it will be nice to alternate the dH of the torus with values that are multiples of 2; 3; four; 5 .... This will affect the smoothness of rotation during rotation of the bearing, thereby increasing its reliability.

The absence of slipping of the rolling elements will significantly increase the speed of the bearing, for example, two or more times and at the same time increase the durability and reduce noise during operation.

The absence of slipping of the rolling elements also contributes to a reduction in oil consumption. Oil mist can be used as an example. Large excess lubricant consumption in the high-speed bearing reduces the speed of the bearing and acts as a brake.

Claims (1)

The rolling bearing is angular contact single row, containing an inner and detachable outer ring, the rolling elements placed between them, made in the form of single-stage rollers installed in a cage, the larger diameter of the larger roller stage, made spherical, contacts only two raceways of the split outer bearing ring in at two points at the contact angle α, a smaller diameter of the roller steps made cylindrical through the intermediate link only contacts the raceways of the inner ring ca bearing at two points, with a constant and uniform speed, while the condition of the bearing assembly: D _1m / D _wm2 = d _1m / D _wm1 = Const, where D _1m is the diameter of the raceways of the outer ring of the bearing; D _wm2 is the larger diameter of the greater step of the roller; d _1m is the diameter of the raceways of the inner ring of the bearing; D _wm1 - smaller diameter of the steps of the roller, and the raceway of the inner ring of the bearing is made with an annular groove and forms gaps under the larger diameter of the larger step of the roller, characterized in that the intermediate link is a rigid torus ring, which is made larger in relation to the calculated smaller diameter of the steps of the roller, and the raceway under the hard torus the ring is made on the outer side of the inner ring of the bearing, the grooves for the torus ring are made on the cylindrical sections of smaller diameters of the steps of the roller.