JPS6162616A - Hydrokinetic plane bearing device with member automatically fitted to state of operation at every time - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention provides that at least one 11!1 bearing segment is used for bearing journals or shaft journals, especially for bearing journals or shaft journals that rotate at high speed, especially for bearing time or 1'iB agent films. The present invention relates to a hydrodynamic plain bearing arrangement, in particular a radial bearing, designed for a turboset with automatic adaptation elements of the invention.

The main problem with hydrodynamic bearings next to turbosets is that the shaft tends to vibrate at high circumferential speeds.

This problem cannot necessarily be suppressed with known two-sided or multi-sided plain bearings.

The known hydrodynamic plain bearings for turbosets are relatively complex in their mechanical construction and are therefore very expensive. Despite its high technical costs, its fluid dynamics 17] ``I e'J''F
@ f<'t'i k fF 6 @ ”CLka1,
Yo We Q)'ft'Ah k cannot be brought completely under control.

The object of the invention is therefore to create a hydrodynamic plain bearing arrangement in which the above-mentioned vibrations can be brought under control in a simple manner.

To completely solve this problem, the present invention has an advantage in that the hydrodynamic pressure in the lubrication gap is guided into the pressure chamber on the back side by penetrating the segment flange surface of the F equilibrium segment in the arrangement of the supply passage. Then, all the balance pistons existing in that chamber should be activated.

The advantage of this arrangement is that the thickness of the lubricant film in the equilibrium segment remains almost constant, independent of e.g. the particular load, the magnitude of the circumferential speed, the viscosity of the lubricant, and the thermal expansion. 1-1 is advantageously achieved.

Furthermore, within the scope of the invention there is the advantage that the adjustment of the pressure of the balancing piston takes place completely automatically from the lubricating gap, so that no additional control unit is required.

Due to its structure, the film thickness of the pre-given equilibrium segment is created between the acting force governing the sliding gap and the reaction force of the equilibrium piston, which automatically adjusts the pressure maintenance value. In addition, C,!7, the consequences of the changes in the operating parameters described above can be effectively balanced in an ideally simple manner.

In order to avoid excitation of vibrations by the piston system, it is necessary to keep the reaction velocity of the piston small. This p
In order to maintain the desired inertia, it is proposed according to the invention to keep the cross section of the feed channel as small as possible, at most 5 stripes across the entire surface of the balancing segment.

The arrangement according to the invention - in a hydrodynamic plain bearing of simple construction, such as a multifaceted plain bearing, or - in a tilting segment -
Even in expensive structures such as plain bearings, it can be installed cost-effectively and without significant technical outlay.

Because narrow tolerances are no longer necessary.

Hereinafter, examples of the invention will be explained in detail with reference to the drawings.

FIG. 1 shows a complete tilting segment-plane bearing arrangement for supporting a rotary shaft 1 with three bearing segments, in which both supporting segments are each designated 2 and one counterbalancing segment is shown in its entirety. Shown in total in 3 parts. As Figure 1 shows, segments 2 and 5 are
They differ in their depiction and also in the way they work, which will be discussed later.

In the case of the support segment 2, we are dealing with a conventional bearing segment, which is machined into a locking pin 6 that is present in the retaining ring 4 and engages in a fixing hole 5. Its sliding surface is indicated by 7.

The balancing segment 5, as shown in particular in FIGS. 2 and 4, essentially consists of a segment body 8 with a sliding surface 7' and a balancing piston 9. The segment body 8 has a chamber 10
is formed, in which chamber a balance piston 9 is present.

Further, as the figure shows, the balance piston 9 is located in the free space 11
It also has a circular shoulder 12 on which a ring ring 13 is shown.

As is clear from Fig. 2, a rainbow pressure chamber 14 is formed in the equilibrium piston 9 and the segment body 8, and this pressure chamber passes through the sliding surface 7' and is arranged offset from the center 21. The supply passage 15 is terminated. Balance piston 9
and the segment body 8 are connected to the fixing pin 16 and the fixing hole 17.
The mutually corresponding elements are held in position relative to each other by means of means. Retaining the counterbalancing piston 9 in the retaining ring is achieved here as well by the hole 5 in the case of the support segment 2.
The fixing pin 6 that engages with the The direction of rotation of the shaft 1 is indicated by an arrow 18, and is indicated by a total clearance 20.

How does equilibrium segment 3 work? I will explain next. @
1 is placed in rotational motion, a hydrodynamic lubricant film 22 is automatically configured in the lubrication gap 20. In this case, the lubricant flows into the pressure chamber 14 through the supply channel 15 until the pressure chamber is filled and the forces, ie the acting and reaction forces, on the segment body 8 are the same on both sides. To the well-known Eri and to the work shown in Figure 5,
The hydrodynamic pressure in the lubricating gap 20 is even smaller at the center 21 of the base surface 7' over the beginning and end of its length L. It has therefore been found to be advantageous to provide the supply channel 15' in the region of the total pressure rise or in the region of the pressure drop in the lubrication gap 20 in relation to the direction of rotation 18. In this way, the influence of machining operating parameters is largely avoided. It has been found advantageous if the spacing 23 of the feed passages 15,15' from the center 21 of the segment body 80 and the veneer surface 7' amounts to at least 10% and at most 40% of the length of the veneer surface. On the left side of FIG. 3, the supply passage 15 is drawn at 82% of the lubricating gap length L, which corresponds to an offset of 82-50, or 32% with respect to the center 21.

In this case, the supply channel 15 is therefore arranged in a particularly significantly depressed pressure range. Alternatively, on the right side of FIG. 3, the position of the feed passage 15' is shown at 16% of the length O of the feed gap 20. This corresponds to a shift of 50-16, or 34 inches.

Ultimately, the optimum length of the supply channel 15,15' depends in particular on the respective lubrication gap size, the length of the balancing piston and the desired lubrication gap thickness.

FIG. 4 shows the design of the balance segment 3 according to FIGS. 1 and 2. FIG. In this case, the surface 24 of the balance piston 90 is designed to be spherical, but it is also satisfactory if the surface 25 of the segment body 8 is made cylindrical as shown.

The present invention is not limited to liquid lubricants, and can also be applied to gaseous lubricants, such as air-based lubricants. half,
Bearings comprising a plurality of balancing segments 3, which can be arranged both radially and axially, can also be applied. Similarly, in an embodiment not shown, the balance segment 3
A large number of balanced pistons 9 can be formed in total.

[Brief explanation of drawings]

FIG. 1 is a sectional view of the tilting segment-plain bearing arrangement; FIG. 2 is a partially enlarged view of FIG. 1 in the range VC of the equilibrium segment; FIG. FIG. 4 shows an exploded arrangement perspective view of the balance segment, showing two exemplary possible positions of the passageway: 1. Axis of rotation, 2. Support segment, 3. Balance segment), 7.7.・Small surface, 8...Segment body,
9. Balance piston, 14. Pressure chamber, 15.15'.
・Supply passage, 20...Bearing clearance

Claims (6)

[Claims] (1) Hydrodynamics, in which at least one bearing segment is designed as a counterbalancing segment for bearing journals or shaft journals, in particular for fast-rotating bearing journals or shaft journals, with automatic adaptation of the bearing gap or lubricant film. In the flat bearing device, the pressure in the lubricating gap (20) penetrates the sliding surface (7') of the segment body (8) of the balance segment (3) due to the arrangement of the supply passages (15, 15'), and the pressure on the back side is increased. Plain bearing device, characterized in that it is guided into a chamber (14) and acts on a counterbalancing piston (9) located in the chamber (10) (FIG. 2). (2) The supply passages (15, 15') are connected to the segment main body (8
) (FIG. 2), in particular outside the center (21) of the sliding surface (7). (3) Distance (23
, 23') is at least 10% of the slip surface length, maximum 4
0% (FIG. 2), the plain bearing device according to claim 1 or 2. (4) The cross section of the supply passage (15) is the balance segment (3)
Plain bearing arrangement according to any one of claims 1 to 3, wherein the sliding surface (7') is at most 5%. (5) The bearing segments (2, 3) are cylindrical or spherical tilting segments, in particular the balanced piston (9
), the support ring (26) is spherical (24) (second,
4), a plain bearing device according to any one of claims 1 to 4. (6) the balancing piston (9) has a circular shoulder (12) for installing the sealing ring (13) (FIG. 2) any one of claims 1 to 5; Plain bearing device described in one.