RU29352U1 - Sliding support - Google Patents

Description

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Sliding support

The utility model relates to the field of engineering, in particular, to sliding bearings with wear compensation and can be used in the oil, gas and other industries.

A sliding bearing with auto-compensation of wear is known, comprising a sleeve covering the shaft pin, between which a layer of lubricant is located, while the shaft pin and the sleeve are mated to fit with a guaranteed tightness that does not exceed the volumetric elastic deformations of the sleeve (see auth. SU No. 964287, F16 C 17/02, 1979).

A disadvantage of the known technical solution is the increased friction loss due to the massiveness of the sleeve, which in turn leads to increased contact pressure on the friction surface.

 F16 C 17/02

Closest to the proposed utility model is a sliding bearing containing a sleeve that encompasses a shaft pin through a lubricant layer with a lubricant cavity for landing with guaranteed interference fit, while on both sides of the sleeve portion of the sleeve it has bells in the form of elastic dish-type elements that interact with the movable lips of the axial compression mechanism of the sleeve (see ed. certificate No. SU 964287, F16 C 17/02, 1979).

A disadvantage of the known design of the sliding support is the impossibility of providing a hydrodynamic lubrication regime that provides, in comparison with other modes (boundary, semi-fluid) lubrication, the most rational functioning of the friction unit. This is due to the flatness in the circumferential direction of the cylindrical contact of the central tubular part of the sleeve with the shaft pin and the difficulty of access from the lubricating cavity of the oil to the friction zone to ensure the minimum (critical) thickness of the lubricant layer necessary for the implementation of the liquid lubrication regime. In the known support, disk-shaped bell sockets have increased rigidity, which requires considerable effort on the part of the axial compression mechanism of the sleeve to maintain interference fit while periodically compensating for wear. The latter reduces the amount of automatically compensated (auto compensation) wear, determined by the amount of interference in the coupling of the shaft journal and the sleeve, leads to the need to increase the number of periodic pery.iiHrovok to maintain the functionality of the sliding support in the wear compensation mode, which provides, as you know, the most favorable dynamics of wear and the longest service life of the support (see Tenenbaum MM in the book: Handbook of tribotechnics. TZ M: Mashinostroenie, 1976. 271 p.). In addition, with the increase in the number of adjustments, maintaining the operability of the sliding support during its operation becomes more complicated. For these reasons, the known technical solution practically does not allow the compensation of angular distortions of the shaft journal during deformation of the shaft bending from the working load. Thus, the principle of self-alignment of the support parts is violated, compliance with which is one of the rational ways to ensure the operability of the structure, in particular due to a decrease in stress concentration (Orlov P.I. Design fundamentals. M. Engineering, 1988. The principle of self-alignment p.323-328 Reshetov D.N. Efficiency and reliability of machine parts.M.: Mechanical Engineering, 1974. 208p.).

It is based on the present; it is a useful model for increasing the operability and simplification of operation of the sliding support by improving the lubrication regime, ensuring self-stability, increasing the limit of auto-compensation of wear by elastic deformations of the sleeve elements, as well as reducing axial forces and the number of adjustments during periodic compensation of wear during operation .

material for planting with a guaranteed interference fit of a sleeve with a lubricating cavity and with elastic bells located on both sides of its central part interacting with the movable lips of the axial compression mechanism of the sleeve, according to the utility model, the sockets are made in the form of an annular rim with petal inclined relative to the axis of the sleeve knitting needles, and in the central part of the sleeve axial slots are made evenly along its perimeter in the spaces between the lobe spokes, while an annular mbrana. In preferred embodiments of the method:

- the friction bearing surface of the central part of the sleeve is made with a radius smaller or larger than the radius of the shaft journal;

-bubbles of the sleeve are made in the form of individual elements, the petal spokes of which are fixed in the nests of the elements of the central part of the sleeve;

- the central part of the sleeve is equipped with a tubular insert;

- in the central part of the sleeve in the areas between its axial slots placed arcuate sector inserts;

- the support is equipped with a limiter installed in the middle part of the sleeve between the sockets, having a gap 5 relative to the inner wall of the case of the axial compression mechanism of the sleeve, where bpr is the gap corresponding to the maximum permissible radial draft of the shaft journal.

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in FIG. 1 shows a cross-sectional sliding support;

figure 2 is a cross-sectional view of the support along the broken section AA;

in Fig.Z-sliding support with sockets in the form of separate (built-in) elements in the sleeve;

figure 4 - bearing sleeve which is equipped with a tubular liner;

in FIG. 5-support sleeve, in the Central part of the sleeve which is installed arcuate sector inserts;

in FIG. 6 - support with a radial displacement limiter.

A sleeve 3 with a lubricating cavity 4 is installed on the pin 1 of the shaft 2 with a guaranteed interference fit. There is always a layer of lubricant between the pin 2 and the central part 5 of the sleeve 3 (not shown in the drawing). In the simplest case, the lubricant layer is the thinnest (multimolecular) boundary film of the lubricant. The presence of such a film is due to the microscopic gap between the rough friction surfaces of the trunnion and the sleeve even with plastic deformations in the actual contact spots of microroughnesses (Kragelsky I.V., Dobychin M.N., Kombalov BC Fundamentals of friction and wear calculations. M .: Machine-building, 1977 , 526s.). To facilitate the access of the lubricant from the cavity 4 to the friction zone in the central part 5 of the sleeve 3 there may be small diameter radial holes. In addition to the central part 5, the sleeve 3 has elastic sockets 7. Each socket 7 interacts with the movable jaws 8 of the axial compression mechanism 9 of the sleeve 3. The axial compression mechanism 9 is a housing 10 connected to a screw

(Fig. 1) or screw-on (Fig. 2) cover 11. Between the housing 10 and the flange of the covers 11, a compensation gasket 12 is placed. The smaller the thickness of the gasket 12, the greater the axial compression of the sleeve 3 and the greater the interference between the shaft journal 1 and with sleeve 3, and hence a large amount of wear compensation due to elastic deformations of sleeve 3 (shaft pin 1 is assumed to be absolutely rigid). The sleeve 3 is kept from joint rotations; together with the shaft pin 1, the forces of friction against the housing 10 and the sponge 8 of the axial compression mechanism 9 of the sleeve. In the event that, for example, due to vibration of the friction forces it may not be enough to exclude the angle of rotation of the sleeve 3 in the housing 10, the support may be provided with a stopper in the form of a pin, screw, key, etc. (not shown in the drawing).

The sleeve 3 consists of a central part 5, directly interacting with it, with the pin 1 of the shaft 2 and two elastic sockets 7, which interact, in turn, with the axial compression mechanism 9 of the sleeve 3. The sockets 7 are made in the form of an annular rim 13 with an inclined angle and to the axis of the sleeve with the petal spokes 14, which are more technologically disposed evenly around the circumference. The number of petal knitting needles in each bell should be at least two) w, but better than three or more pieces. In the spaces between the tabs of the spokes 14 in the socket 7, windows 15 are formed, which is easier; deformation of the sleeve 3 under the action of the axial compression mechanism 9. Correspondingly, of the windows 15 in the central part 5 of the sleeve there are axial slots 16. Distribution of the working load on compliant angle a petal knitting needles 14 provides

self-alignment of the sliding support during angular misalignment of the journal 1 due to deformation of the bending of the shaft 2. For the formation of a closed lubricating cavity 4 in the sleeve 3, an elastic or metal (which increases the circumferential stiffness of the sleeve when the moment of friction is sensed) is introduced, the annular membrane 17, the cavity of which becomes in this lubricant cavity. To facilitate the access of lubricant to the friction zone in the membrane, radial holes 6 of small diameter are made. A porous material such as cotton wool, impregnated with lubricant, can also be placed inside the membrane, which will ensure a metered consumption of lubricant. If the support on the shaft side is sealed, for example using an elastic sleeve, then partially or completely the internal cavity of the housing 10 can be filled with lubricant, especially when implementing the hydrodynamic lubrication mode.

The design of the sliding support assumes the implementation of the supporting surface of the friction of the Central part of the sleeve 3 with a radius smaller or larger radius of the journal 1 of the shaft. In the first case, the difference in radii should preferably be no greater than the guaranteed guaranteed radial interference provided by the axial compression mechanism 9 of the sleeve 3. Then the surfaces of the sleeve 3 of the journal 1 will completely coincide, which reduces the pressure in the actual contact spots of the rubbing surfaces. However, in this case, a boundary or semi-fluid lubrication regime is implemented. When the radius of the surface of the central part of the sleeve is slightly larger than the radius

Valado trunnions in contact in the presence of interference are wedge-shaped micro or macro-pin gaps that provide liquid lubrication, which eliminates wear in the steady state operation of the support.

In one embodiment of the sliding support (Fig. 3), the elastic sockets 7 are made in the form of separate elements 18, the petal spokes 19 of which are fixed in the nests of the central part 5 of the sleeve 3. This allows the sockets to be made of material with the required elastic properties, which are not always appropriate; required antifriction properties, and the central part should be made of antifriction and / or wear-resistant material, which positively affects the operability of the sliding support.

In another embodiment, the sliding bearings (figure 4), the Central part of the sleeve 3 is supplemented by a tubular liner 20 of an antifriction, for example, a composite or a polymeric material. Due to the pressing of the Central part of the sleeve 3 to the pin 1, the tubular liner 20 is bulging in the slots 16, resulting in the formation of wedge-shaped gaps 21, which provide a hydrodynamic lubrication mode. At the same time, “vyp.” D1 sections of the insert 20 prevent it from turning relative to the sleeve 3.

Instead of a tubular antifriction insert in the central part 5 of the sleeve 3, individual inserts 22 of antifriction and / or wear-resistant material can be fixed (Fig. 5). In the latter case, the shaft journal is also faced with wear-resistant material. As

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wear resistant materials can be used hard alloys and cermets, such as silicon carbite.

Under the influence of radial overloads or significant vibrations on the support, the support can be protected (Fig. 5) by a stop 23, which partially unloads the sockets and acts as a damper due to the viscous friction of the stop in the lubricant and the difficulty of oil flow in an extremely small gap 5. The value 5 should be , where 5pr is the gap corresponding to the maximum permissible radial draft of axle 1.

The sliding support works as follows. When the jaws 8 act on the axial compression mechanism 9 of the sleeve 3, the axial forces (shown by arrows in Fig. 1) act on the annular rims 13 of the sockets 7, and from them, through the spokes 14, the forces are transformed into radial ones, which deform the central part 5 of the sleeve 3 in the radial direction , thereby creating the required guaranteed interference in the coupling of the shaft pin 1 with the sleeve 3 through a layer of lubricant. This layer is initially formed during the assembly of the support and then is constantly regenerated during rotation of the shaft journal due to the viscous properties of the lubricant and the hydrodynamic effect of the working sliding support, especially when there are micro and micro wedge gaps in the friction pair. In the case of an angular skew of the axis of the pin 1 when the shaft 2 is bent relative to the axis of the support, the friction surface of the sleeve 3, due to the flexibility of the petal spokes, is self-installing relative to the surface of the pin 1

shaft, which eliminates the concentration of contact pressure. When the shaft vibrates due to the small gap 5 between the limiter 23 and the housing 10, the vibrations are damped and damped. In cases of radial overloads of the sleeve 1 from the journal 1, the gap 5 is completely selected by moving the cutter 23, which ensures the unloading of the elastic sockets with a further increase in the radial load.

The technical result of the utility model consists in increasing the operability of the sliding support in the aggregate of a number of its criteria: friction loss, wear resistance, vibration resistance, accuracy, as well as ergonomic indicators (reduced effort, increased service periods, etc.).

Claims (6)

1. The sliding bearing containing the shaft pin, coupled to the shaft pin through the lubricant layer to fit with a guaranteed interference fit the sleeve with the lubricant cavity and with elastic sockets located on both sides of its central part interacting with the movable lips of the sleeve axial compression mechanism, characterized in that the sockets are made in the form of an annular rim with petal spokes inclined with respect to the axis of the sleeve, and axial slots are made evenly in the central part of the sleeve along its perimeter in spaces ezhdu spade spoke while in the lubricant space of the sleeve is placed an annular membrane. 2. The support according to claim 1, characterized in that the abutment surface of the central part of the sleeve is made with a radius smaller or larger than the radius of the shaft journal. 3. The support according to claims 1 and 2, characterized in that the bells of the sleeve are made in the form of separate elements, the petal spokes of which are fixed in the nests of the elements of the central part of the sleeve. 4. The support according to claim 1, characterized in that the Central part of the sleeve is equipped with a tubular liner. 5. The support according to claim 1, characterized in that in the Central part of the sleeve in the areas between its axial slots placed arcuate sector inserts. 6. The support according to claim 1, characterized in that it is equipped with a limiter installed in the middle part of the sleeve between the sockets, having a gap δ in the range of 0 ≤ δ ≥ δ _pr relative to the inner wall of the case of the axial compression mechanism of the sleeve, where δ _pr is the gap corresponding to the maximum permissible radial draft of the shaft journal.