SU1548543A1 - Spherical sliding-contact bearing - Google Patents

Abstract

The invention relates to mechanical engineering, in particular to a spherical slip bearing, and can be used in various industries of the national economy for self-alignment of the axes and shafts with their distortions in the hinged connections of machines and mechanisms. The purpose of the invention is to increase the carrying capacity, durability and maintainability of spherical slide bearings. In the spherical sliding support, the insert is made of two pairs of diametrically located elements, two of which are bearing and are located in the working areas of the support, and the other two are hollow on the side of the sleeve, filled with lubricant and located in non-working areas. Maintainability is increased due to the possibility of replacing one or two bearing elements of the liner when they are out of service, while retaining all other parts of the bearing for further work. 4 il.

Description

The invention relates to mechanical engineering and can be used for self-installation of axles and shafts at their distortions.

The aim of the invention is to increase the carrying capacity, durability and maintainability.

FIG. 1 shows a spherical bearing — in a plane perpendicular to the axis, section; in fig. 2 is a section A-A in FIG. one ; at aig. 3 - bearing element of the liner; in fig. 4 - liner element with a cavity for lubrication.

The bearing contains an outer ring 1 with an inner spherical surface, a sleeve 2 with an outer spherical surface and an insert made of two bearing elements 3 with bevels 4 on the torn surfaces connecting with other elements of the surfaces and two hollow elements 5 with edges bent on both sides 6 a lubricant 7. Bevels 4 are bounded on both sides by torques 8. In the outer ring 1 there are mounting grooves 9 and slots 10. In the corresponding cuts 10 places on the bearing elements 3 of the liner there are bend legs 1 1 with notches 12.

The bearing elements 3 of the liner can be made by stamping from an antifriction material, for example bronze, or from steel with a metallic coating on a rubbing surface, for example, electrolytic chromium, and non-metallic, for example FCM (solid lubricant) based on

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colloidal graphite, molybdenum disulfide with epoxy resin as a binder. The thickness of the bearing elements of the insert is chosen depending on the material chosen, the thickness of the coating, the size of the guaranteed clearance, the radii of the spheres of the outer ring and the sleeve.

The hollow elements 5 of the liner can be made by casting from an elastic antifriction material, such as nylon, polyamide, with an outer surface, according to the Shape of the corresponding sphere of the outer ring 1, and an assembly groove 9. The elastic and antifriction properties of the elements 5 ensure a tight fit of the edges 6 to the spherical surface of the sleeve 2, as well as their high wear resistance. The wall thickness of the elements of the liner 5 is selected to be less than the thickness of the supporting elements 3, and the space formed between the elements 5 and the spherical surface of the sleeve 2 is filled with lubricant 7, for example a grease. The thickness of the ends of the bearing elements 3 on the bevels 4 at the places of their contact with the elements 5 is assumed to be equal to the thickness of the walls of the elements 5 at these places.

The width of the elements 3 and 5 of the liner is limited by the width of the outer ring 1, their length along the arc of a circle in a plane perpendicular to the axis of rotation is limited to the planes BB and BB (Lig. 1) coinciding with the axis of rotation 00 and forming between So angles t and o.

The bearing is assembled as follows.

Bearing elements 3 are installed in the outer ring 1, then the sleeve 2 is inserted through the mounting grooves 9 until the centers of their spheres coincide and rotates so that its equatorial plane coincides with the YY axis and the axis of rotation 00 of Ofit. one). The position of the elements 3 is corrected and is fixed in the outer

ring 1 with the help of tabs L, which are folded back into the corresponding slots J 0 in the outer ring 1. Notches 12 limit the length of the bent legs 11 and prevent the material 3 of the elements from deforming in the friction zone. Thereafter, elements pre-filled with lubricant 7 are installed in the outer ring 1.

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5 of the liner so that the gaps for lubricant outflow between the sleeve 2 and the elements 5 are oriented to the sides of the bevels 4 on the elements 3, after which the sleeve 2 rotates into the working position (Fig. 2). A layer of the same lubricant, which is embedded in the cavity of the elements 5, is applied to the rubbing surfaces of the elements 3 and the sleeves 2 before their installation into the outer ring 1, because elements 5 do not require additional fastening, because their length along the arc of a circle in the equatorial plane is greater than torism in parallel planes and fixes is carried out by bearing elements 3. The elements 3 and 5 of the liner fit snugly against each other and are set relative to the direction of the external load so that its line of action passes through wasps bearing elements 3. In FIG. 1, the load is indicated by the index F, and the line of action of this load is indicated by an arrow.

In lifting machines, where spherical slide bearings are installed, for example, in the fastening heads of power cylinders, the vector of external load and the full response vector in the support are always directed along the axis of the cylinder rod at any position (tilt). At the same time, the smaller the coefficient of friction in the pipe joint, the smaller the radius of the circle of friction and the closer to the stem axis is the reaction vector. For hinges working with Sufficient lubrication in the boundary friction mode, it can be assumed that these vectors are directed along the axis of the stem and pass through the center of the hinge.

In connection with this, the loading zone of the support will be a constant position relative to the fixed parts of the hinge and the indicated vectors will pass through its pole. Thus, when external load is reversible, there can be two load zones

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nor, located in diametrically opposite sides of the support, with the unilateral action of an external load - one zone. The length of the loading zone in a spherical sliding bearing, depending on the size of the guaranteed clearance, can be limited by an angle of 90..J20, measured in a plane perpendicular to its rotation axis. In specified

the loaded zones in the support are installed bearing elements 3 of the liner, leaving free zones between them, the sleeve 2 and the outer ring 1. In these unloaded zones, the elements of the insert 5, made hollow on the side of the sleeve 2 and filled with lubricant 7, are installed.

The angle if is assumed to be 90 ... 120 °, Yu is the angle o (180 ° - c (Fig. 1).

The bearing works as follows.

At each relative turn

work in a more favorable boundary mode of friction. This made it possible to increase the total load, therefore, the bearing capacity of the bearing 1.5 ... 2 times and increase its durability 2 ... 3 times.

When the support works with reversible load, both bearing elements 3 of the liner are replaced during repair, while working with one-sided load, one loaded element 3 or the bearing rotates around the axis of rotation by 180 °, which causes

sleeve lubricant is transferred to 15 cht ° in the loaded area is

from the cavities of the liner elements 5 directly into the friction zone, constantly restoring the lubricating film. Bevels 4, made at the ends of the elements 3, contribute to a better penetration of the lubricant into the gap between the rubbing surfaces, and the shoulders 8 prevent the lubricant from leaving the friction zone on the ends of the sleeve 2.

The operation of the slit joint depends on the anti-seize properties of the antifriction and lubricants used. For example, the additional supply of Litol-24 grease to the friction zone of steel bushings using FCM based on fluoroplastic, colloidal graphite without and with the addition of 25% copper at a specific pressure of 30 ... 40 MPa allows reducing the coefficient of friction by an average of 2. ..4 times.

With a one-time lubrication of the lubricating surfaces of the grease and an increase in pressure to 100 ... 140 MPa during the wear of the lubricant film, the friction coefficient (force) approached its value when operating the same pair without using grease. If at this time the lubricating film was restored, the magnitude of the friction coefficient (force) decreased and the rubbing joint passed to the element of the liner not loaded to this point 3. The durability of the bearing in this case is doubled.

The ability to replace one or two bearing elements of the liner in the output

they are harder to preserve all other parts of the bearing for further work, increasing its maintainability and reducing the cost of repair and maintenance.

Claims (1)

Invention Formula A spherical slide bearing containing an outer shaft with an inner spherical surface, a sleeve with an outer spherical surface and a liner installed between them, about tl and h a, y u and u with with that In order to increase the carrying capacity, durability and maintainability, the liner is made in the form of conjugate pairs of diametrically located elements to absorb loads and a pair of diametrically arranged elements to accommodate the lubricant, and the elements for absorbing loads are made with spherical outer and inner surfaces, and the elements to accommodate the lubricant, they are equipped with cavities located on the side of said sleeve. 1 eleven 11 Fig.z Compiled by A. Dolinsky Editor A. Shandor. Tehred M. Khodanich. Order 130 Circulation 528 VNIIPI State Committee for Inventions and Discoveries at the State Committee on Science and Technology of the USSR 113035, Moscow, Zh-35, Raushsk nab. 4/5 Aa Shgg FIG 4 Proof. With. Shekmar Subscription