DE663649C - Segment block track bearings - Google Patents

Description

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L 4

ISSUED ON OCTOBER 17, 1938

L 4:, W. 1938

Segment block track bearings (Michell bearings) are able to absorb extremely high pressures. Nevertheless, there is often a need to reduce the surface loading of such bearings as much as possible, in particular when lubricants of only low viscosity have to be used. In such Cases, the thickness of the lubricating film is much less, so that to achieve the wing loading is kept correspondingly smaller in order to ensure sufficient operational reliability must become.

To track bearings even when using low viscosity lubricants To be able to load higher, it has already been proposed, the track pin, which is slightly tapered and guided in a corresponding sleeve, during the To relieve the operation on its end face, that in the between the lug end face and bearing bush remaining chamber, the lubricant is introduced under pressure so that a complete or partial relief of the track bearing surfaces is achieved. This arrangement has however, the disadvantage that the distance between the two track bearing surfaces due to the tapered Guide the thrust bearing pin must be measured very precisely and adhered to on the one hand a jamming of the track pin in its socket, on the other hand an excessive to avoid excessive escape of the pressure lubricant. It is also at the known arrangement does not involve a segment block track bearing.

Finally, it is not possible with the known arrangement to increase the lubricant overpressure to produce in the bearing housing itself, so that a special multi-part and expensive lubricant pressure pump must be arranged outside the warehouse.

In order to avoid these disadvantages, the thrust bearing plates are used in the case of Scgmentklotzspurlagem and surround the segment blocks with a pressure-tight chamber closed on all sides, which is completely filled with lubricant under increased pressure and with one each Annular gap above and below the thrust bearing plate between the rotating and stationary part is equipped, the radius of the lower gap is smaller than that of the upper one. According to the invention, these annular gaps and the pressure are designed to be pressure-tight of the lubricant by a single centrifugal pump impeller or several counter-connected Generated impellers, which are arranged so that their inlet sides through a bypass channel with each other in Are connected while their outlet sides pour into the pressure-tight chamber, the running wheels, if there are several, on different sides of the thrust bearing plate are arranged.

Although it is known to surround the thrust bearing with a lubricant chamber, which each have an annular gap above and below

*) The patent holder has indicated as the inventor:

Dr.-Ing. Wilhelm Scluilz in Oscherslebcn, Bode.

the thrust bearing plate is sealed against the rotating parts. With this well-known However, it is not a question of execution in the lubricant chamber to generate an overpressure by which the thrust bearing is to be relieved. The lubricant chamber only serves to hold one take up oil supply, which the sliding surfaces of the segment block track bearing flows in.

ίο The purpose of an existing circulation pump is to create an oil circuit around the Always supply fresh oil to stores. The. As a result, the chamber is not designed to be pressure-resistant.

In the drawing, an exemplary embodiment is shown, namely A denotes the axial thrust acting on the bearing from above, T the lower end of the rotating parts designed as a thrust bearing, 5 the tiltable segment blocks, / C an annular chamber closed on all sides in which an increased pressure can be generated (this chamber is particularly marked in the drawing by strong lines), L ₁ , L ₂ two interconnected auxiliary impellers which generate an increased pressure of the lubricant completely filling the chamber in chamber / C ', b the width of an annular surface on which the lubricant pressure generated by the auxiliary impellers L _L and L ₂ is effective and generates a force opposing the axial thrust, U a bypass channel bypassing the chamber / C, which connects the suction sides of the auxiliary impellers L ₁ and L ₂ and in which a pressure equalization between the inlet of the two auxiliary impellers and a fluid circulation take place n can.

The whole arrangement is made so that the underside of the thrust bearing plate directly to generate a thrust counteracting the axle thrust Relief force is harnessed. The thrust bearing plate thus becomes a relief disc, similar to

■ 15 this is used in centrifugal pumps, but the fluid pressure is generated by special auxiliary impellers. These are connected to one another in such a way that they generate an increased lubricant pressure in a chamber which completely encloses the thrust bearing plate and the blocks. The radius of the sealing gaps of these auxiliary impellers are, however, different by the dimension b , namely that of the impeller L _{1 is} the larger, the

55 of the wheel L _{2 is} the smaller one, so that an annular surface of width b arises, on which the lubricant pressure prevailing in the chamber / C creates a counter to the axial thrust ^ 4.

acting force. It is thus of the segment blocks S only the difference g ₀ these two forces to record his that can be kept as small by proper design of the auxiliary wheels that even with lubricants lowest toughness proper Ausbildungdes lubricating film and DA ₆ _ complete with an operating safety is achieved.

In order to prevent the contents of the lubricant in the chamber K from heating up, the auxiliary impellers are dimensioned so that their delivery heights are different, so that a water flow through chamber K and bypass channel U is created. This also contains a larger amount of lubricant, so that a permanent exchange of the working lubricant can take place.

It is also possible to do without one of the running wheels entirely if only the sealing gaps between the rotating part and the stationary housing remain unchanged and have a difference b of the radius.

The encapsulation of the thrust bearing plate and segment blocks in conjunction with an or several auxiliary impellers and sealing gaps between rotating and stationary the parts of different radius thus enables hydraulic relief of segment block bearings, so that they can also be used with lubricants of low viscosity for large axle thrusts can be designed to be operationally reliable.

Claims (1)

Claim: ■ Segment block track bearing with the thrust bearing plate and the segment block surrounding, pressure-resistant chamber closed on all sides, which is completely filled with lubricant under increased pressure, and with an annular gap each above and below the thrust bearing plate, _two rotating and stationary parts, with the radius of the lower gap is less than that of the upper, characterized in that the annular gaps pressure-tight are formed and that the pressure of the lubricant by a single centrifugal pump impeller or more against cascaded wheels is produced, which are disposed so that their inlet sides by an L ^T mfüh- u ₀ rungskanal are in communication with each other, while their outlet sides pour into the pressure-tight chamber, the impellers, if there are several, are arranged on different sides of the thrust bearing plate. For this-1 sheet of drawings