SU1432292A1 - Sliding-contact thrust bearing with aligning device - Google Patents

Abstract

The invention relates to mechanical engineering and m. used, for example, as the thrust bearing of a steam or gas turbine or the main thrust bearing of a vessel. The goal is to increase the carrying capacity and reliability. The thrust sliding bearing includes a yoke with a backing ring, inner and outer rings. Six fixed stops are pressed into the backing ring evenly around the circumference, on which the lower row balancers rest, the balancers are made with shanks. The shoulders of the balance bar of the lower row serve as supports for the balancers of the upper row with thrust pads mounted on them. The balancers have along the entire length of the outer or inner cylindrical surface of the radial groove in which the spring ring is installed. The spring ring engages all twelve balancers of the upper and lower rows and presses them against the inner or outer ring of the holder, lined with oil-resistant rubber. Elastic elements are also installed between the walls of the grooves of the cage and the shanks. During operation, with unequal loads acting on the pillows, the balancers of the upper and lower rows set in motion and move until the loads are equalized, as well as the moments that unfold the balancers. 2 hp f-ly, 8 ill. (L 4 CO to IN9 50 th

Description

The invention relates to mechanical engineering, in particular to thrust sliding bearings with a leveling device, and can be applied, for example, as a thrust bearing of a steam or gas turbine or a main thrust bearing of a vessel.

The purpose of the invention is to increase the carrying capacity, increase reliability and reduce bearing dimensions by reducing the magnitude of the residual load non-uniformity.

FIG. 1 shows a thrust bearing with an external arrangement of a spring ring, a plan view; figure 2 - the same, with the internal position of the spring ring; in fig. 3 - section A-A in FIG. 1; in fig. 4 is a section BB in FIG. one; in fig. 5 is a view of B in FIG. four; in fig. 6 is a schematic illustration of a scan of a cylindrical cross section of a bearing along an average radius; in fig. 7 - the position of the balancer in the holder of the thrust bearing; in fig. 8 - diagram of the forces acting on the balancer.

The device (Figs. 1-5) contains a holder, which is a lining ring 1 with an inner 2 and outer 3 annular protrusions with grooves 4. The grooves can be located both on one of the annular protrusions (Fig. 2.1) and on o6opfx immediately . In the backing ring 1 uniformly around the circumference are pressed stationary stops 5, the number of which is equal to the number of balances 6, 7, respectively, the lower and upper rows, as well as the number of pillows 8.

The stops 5 are supported by balance weights 6 of the lower row, the shoulders of which serve as supports for the balancers 7 of the upper row (Fig. 3) with thrust pads 8 mounted on them. The weights 6, 7 have the entire outer length (Fig. 1) or the inner ( 2) the cylindrical surface of the radial groove 9 (Fig. 4), in which the spring ring 10 is installed. The latter covers the balance weights 6, 7 and presses them against the inner 2 (Fig. 1) or outer 3 (Fig. 2) annular ledge of the yoke lined with, for example, oil resistant rubber 11.

The spring ring is made so that its diameter before installation - in the groove was smaller with the outer arrangement of the ring 10 (Fig. O or more with the inner (Fig. 2) arrangement

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ring 10 diameter radial groove

9 (Fig. 1 and 2, denoted TENS) in the balancers 6, 7. Thus, after installing the ring 10 in the grooves 9 of the balancers 6, 7, placed in the holder, due to the elastic deformation of the ring

10 arises a force pressing the balancers 6, 7 to the rubber facing II. The distance between the inner 2 and outer 3 annular protrusions of the cage is large with a radial size of 6, 7 by the value of G (Fig. 4), which ensures that when the balance bar 6, 7 is pressed to the rubber facing 11, the gap between the outer cylindrical surface of the latter

and the outer annular protrusion 3 of the cage (Fig. 1) or the gap between the inner cylindrical surface of the balancers 6, 7 and the inner annular protrusion 2 of the cage (Fig. 2). The size of the gap cP is chosen so as to ensure free (without contact with the cage ring , not lined with rubber 11) reversal of balancers 6, 7 at permissible angles during load typing. On the inner (Fig. 1) or outer (Fig. 2) cylindrical surfaces of the balancers 6, 7, there are cylindrical shanks that fit into the groove 4 of the corresponding annular ledge of the cage and fix the balancers 6, 7 in the circumferential direction. The cylindrical surface of the shank or the surface of the groove as well as one of the caliper protrusions of the holder are lined with oil-resistant rubber.

The cushion 8 is fixed in the circumferential direction by a rectangular protrusion entering the groove on the outer annular protrusion 3 of the casing 1 (Fig. 5), and in the radial direction an inner annular protrusion 2 on which it is supported by a cylindrical section, as well as a split ring 12, located in the radial slots on the outer cylindrical surface of the cushions and the annular protrusion 3 of the clip (Fig. 4). The assembly of the cushions from the cage during assembly is prevented by a cylindrical collar on the inner cylindrical surface of the cushion, which enters the groove on the annular protrusion 2, and the split ring 12. 11l preventing the contact surfaces of the cushion 8 from preventing, the balancers of the upper row 7 have

inserts 13 and 14 with solid work surfaces (Fig. 4).

When the subgipnik is in operation, the axial stop from the rotating ridge (not shown) is perceived by the cushions 8, through which they are transmitted to the balancers 7, supported on the balancers 6, and then through them to the holder. With equal loads acting on the cushions 8, the balancers 6, 7, respectively, of the upper and lower rows are fixed. With unequal loads, the balancers 6, 7, respectively, of the upper and lower rows, entering the leveling device, start to move.

Consider the process of leveling the load on a two-pillow bearing. A schematic illustration of a cylindrical section along the middle radius of such a bearing is shown in FIG. 6. Pillows N1 and N2 at points A and B, respectively, rest on the balance weights N and N2 of the upper row, which in turn rest on the Shoulders of the lower row balancers at the points AJ, A, B, Bj. Lower row balancers can rotate on a swing edge.

If the loads acting on the pillows are not equal to P, i P, then h, where h is the thickness of the oil caps between the working surfaces of the ridge and the underlays. At Р t Рg the balancer operates the moment, which is different from zero (Fig. 6). If P, P2, then M is 0.51 (,) 0, and Mg is 0.51 (P, - PJ) 0, from which it follows that the balancer N1 of the lower p is turned counterclockwise, and N2 - clockwise. As a result, points A, AJ and, consequently, A move away from the ridge surface (h, increases), and B,, B and, therefore, B approach the ridge surface (h decreases), Balance turn and movement of A and B points the absence of friction forces is carried out until the equality M M O is satisfied, i.e. P PI The research and conclusions obtained are also valid for a bearing with an arbitrary number of pillows.

The presence of friction forces significantly affects the leveling ability of the device and leads to the appearance of a residual non-uniformity which is determined by the magnitude of the moment that prevents the balance from turning.

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sir. The latter depends on the magnitudes of the reactions at the points of contact of the balancers with the rings of the holder and with each other, the first of which are decisive.

The proposed device makes it possible to reduce the magnitude of the reactions, and consequently, the magnitude of the moment preventing the rotation of the balancers, and to reduce the magnitude of the residual non-observability, as the balance weights 6, 7, when rotated, overcome the forces of elastic resistance arising when the rubber facing P strength training on their shoulders. The magnitude of the moment of resistance from the elastic compression forces of rubber compared with the unwinding moments acting on the balancers can be neglected, which suggests that the residual unevenness in the proposed technical solution is determined by the forces of friction on the shoulders of the balancers and is 4-10%.

Claims (3)

1. A thrust sliding bearing with a leveling device, containing a holder with outer inner rings with grooves, a lever-mechanical leveling device, formed in the form of circumferentially balanced balancers of the upper and lower rows with shanks on one of their cylindrical surfaces, and pillows, characterized in that, in order to increase the carrying capacity and reliability by reducing the residual uneven loading, it is provided with elastic elements placed between the walls of the yoke and the inner and the outer cylindrical surfaces of the balancers, as well as between the walls of the grooves of the yoke and the shanks. 2. A bearing according to Claim 1, characterized in that the resilient element located between the outer ring of the cage and the outer cylindrical surfaces of the balancers is made in the form of a spring ring mounted in the grooves which are worn on the outer cylindrical surfaces. 3. Bearing according to claim 1, characterized in that the resilient member interposed between the inner 10 A-A Y / / // z :::: L / / j: 7 // /// z / yi //// z / /   - - y yyy - - - - y, 5 Bud 6 // z / yi ///  yy - 5, 5 Fi.Z g "w, in at "6 I / one( f7 // f / f / / t / f / Fi.C FIG. five 0.9 PI O.SPf 0.5Pi 0.5P 0.5P 0.5 Pj 6 FIG. 7 irpeSfH /