SU1467262A1 - Shaft combined bearing - Google Patents

Abstract

The invention relates to mechanical engineering and can be used as supports for high-speed shafts of mechanisms and machines for various purposes. The purpose of the invention is to increase the economy of the support when working at high speeds of rotation. The support contains a tapered hydrostatic bearing 1, a ball bearing 2 and an intermediate element 3 with a conical} S3 KIM butt, equivalent to the adolescent bearing 1. In the annular groove of the hydrostatic bearing 1 there is a subdivided W1 5, in the groove of which is concentrated the spring is on the additional sleeve 9. The bearing pockets of the JO of the additional sleeve 9 are smaller with respect to the carrying pockets — 1 8 main; sleeves 5; As the speed of the shaft 14 is increased, the successive shaft upayut the work carrying the pockets 8, 13, 10 ,, n smaller. At the same time, the working pressure drops and the hydrostatic weighing is again carried out by bearing pockets of a larger size, but with a reduced flow rate of the working fluid. The design of the device allows the support to operate at elevated shaft rotational speeds. from 1 SKsa fenvcCTra

Description

The invention retreats to machine-building and can be used as a support for high-speed shafts of mechanisms and machines of various purposes. Cheney ,,

The purpose of the invention is to increase the eco-mism of the support when working with high rotational speeds.

FIG. Figure 1 shows the longitudinal support, longitudinal section; on

four

ig, 2 - hydrostatic case: bearing, longitudinal section; on

Figo 3 - the same, side view; figure 4 - the EXTERNAL sleeve, a longitudinal section; 4a of FIG. 5 - the same, side view; on ig. 6 - internal additional sleeve, after-cut; 7 - jo same side view; .on FIG. 8 - graphical dependences showing the change in the flow rate of the working fluid t | epe3 hydrostatic water lift depending on the peripheral speed of rotation of the shaft

The combined support (fig. I) contains a conical hydrostatic 15 BEARING 1, a radial-resistant ball-bearing heel 2 and an intermediate one: a lement 3 with a conical end face and a hydrostatic bearing. In a conical hydrostatic yodoshshshka (Fig. 2) there is an annular groove 4, in which a sleeve 5 is installed ifta, in the latter there is an annular groove 6 (Fig. 3). The sleeve-ia 5 is held in the extreme left position by the spring 7 (Fig. 1) and forms 3 bearing pockets 8 with the intermediate element. An additional sleeve 9 is installed in the annular flow 6 of the sleeve 5. The working pockets of the sleeve 9 are made bearing pockets 10, the volume of which is less than the volume of the carrying pockets 8 of the sleeve 5 o Under the action of the spring 1: th split retaining ring 1 2, the additional sleeve 9 is held in the extreme left position, forming the bearing pocket 13. The conical hydrostatic bearing is centered with the shaft G4 and From the axial movement of the nut 15.

A ball bearing 2 is placed in the case of the support 16, centered on the intermediate element 3 and held against axial movement by a nut 17 and a lid 18,

The pockets 8, 10 and 13 through the openings 19 of the additional sleeve 9 are connected to the cavity 1 of high pressure,

which is connected through the radial channels 20 to the cavity II of the working fluid supply to the hydrostatic bearing. The cavity of the annular groove 21, made in the grip 22, is sealed with seals 23 and 24, the bearing housing is closed with the clamps 18 and 25, which have seals 26 and 27. The stiffness of the spring 11 is chosen to exceed the stiffness of the spring 7,

The support works as follows.

At low speeds of rotation of the shaft 14, the hydrostatic bearing 1 is tightly pressed against the intermediate element 3 and they rotate as one piece.

Increasing the frequency of rotation of the shaft 14 to the calculated value creates a fluid pressure in the pockets 8, which provide the bearing capacity of the hydrostatic bearing 1, between

The conical surfaces of parts I and 3 produce a liquid film C1 which facilitates the slippage of the intermediate element 3 and the inner ring of the ball bearing with respect to the hydrostatic, h) bearing. The circumferential speed of rotation of the inner ring of the wide-support in this case is a fraction of the circumferential speed of rotation.

shaft 14.

As the speed of rotation of shaft 1 increases, the pressure of the working fluid in cavity I increases. Sleeve 5, together with an additional sleeve

9 due to the pressure difference in the cavity I and in the pockets 8, 10 and 13, overcoming the force of the more compliant spring 7, moves to the intermediate element 3 until the stroke h is selected. In this

If the bearing capacity of the hydrostatic bearing instead of the pockets 8 is provided by the bearing pockets of 13 smaller sizes. Reducing pocket sizes leads to lower carrier

the ability of the hydrostatic bearing and the restoration of the gap S to the calculated value, and therefore, to ensure a constant flow of fluid through the hydrostatic bearing, to a predetermined value. I

With a further increase in the speed of rotation of the shaft 14 and the pressure of the working fluid in the cavity I, the sleeve 9, overcoming the force of the spring 11, moves to the intermediate element 3 until the choice of stroke h. Bearing capacity of hydrostatic bearing 1,, maintaining the gap Sf. and the constancy of the flow of working fluid through it. are provided with carrying pockets 10 When the speed of rotation of shaft 4 decreases, the process of regulation ff. and fluid flow occurs as a result of the sequential connection of pockets of different sizes in reverse order. First, due to the more rigid spring 11, the additional sleeve 9 returns to the initial position and pockets 13 come into operation. Then the sleeve 5 moves and adjusts, and the flow rate of working fluid is carried out by means of pockets 8.

The nature of the change in fluid flow through a hydrostatic bearing Fc. Gs, depending on the circumferential speed of rotation of the shaft n for a support in which only the carrier pockets 8 work, shows curve A (Fig. 8). The nature of the change in the flow rate q from the circumferential speed of rotation

shaft P | for the support, in which the carrying pockets 8, 13 and 10 come into operation, shows curve B.

As follows from the above dependencies, the proposed support allows the support to operate at high values of the circumferential speed of rotation of the shaft. At the same time, the efficiency of the support increases, and thus, the energy consumption of its maintenance decreases.

Claims (1)

Invention Formula A combined shaft bearing containing ball angular contact and tapered hydrostatic bearings, an intermediate element installed between them with a tapered face facing the hydrostatic bearing, as well as a spring-loaded sleeve in the axial direction of the hydrostatic bearing, characterized in that with a chain cost-effective when working with high rotational speeds of the shaft, it is provided with an axially spring-loaded additional 1 sleeve with a tapered end, facing to the intermediate element, and executed on the specified torda. carrying pockets connected. with a source of pressure lubricant, and in the sleeve there is a groove in which an additional sleeve is concentrically mounted. X: v.Vvogcs oo vS.v h xxxvw x.w.x OCCSXSNSX4SX 4vSi FIG. 2 Phie. J // t u ///// SHSM Fiel Fi.V .five Fie.7 M.GSPr NG / C in n lO Jof-MiiH -one