Bearings – Rotary bearing – Plain bearing
Patent
1989-10-30
1991-10-01
Footland, Lenard A.
Bearings
Rotary bearing
Plain bearing
384441, F16C 2304
Patent
active
050528254
DESCRIPTION:
BRIEF SUMMARY
BACKGROUND OF THE INVENTION
The present invention relates to an axial mounting with skewing compensation, with a bearing housing for receiving a radial plain bearing and axial bearing segments and with a fastening flange for fastening the bearing housing in the shaft housing of a rotating machine.
FIELD OF THE INVENTION
On high-speed turbomachines with operating loads acting axially, these are absorbed by an axial bearing which is usually arranged in a common housing with one of the radial bearings. As a result of the operating loads, that is to say rotor unbalances and/or tilting movements attributable to a gyroscopic effect as a result of changes in the direction of vehicles or even because of production-related inaccuracies in the mountings, a skewing of the shaft and therefore of the bearing holder of the axial bearing can occur. As an example of this, mention may be made of large turbochargers of ship diesel engines, in which the high mass moments of inertia of the turbocharger rotors generate considerable gyroscopic moments in the event of changes in the direction of travel, and this leads to a one-sided loading and wearing of the axial bearing and, as a result of edge pressure, also of the radial bearing accommodated in a common bearing housing with the axial bearing, insofar as this radial bearing is a plain bearing.
DISCUSSION OF BACKGROUND
In a known bearing device with skewing compensation for a turbocharger engine, a bearing housing receiving the plain bearing and the stationary thrust ring of the axial bearing is equipped with a flange, the circumference of which is designed as a rigid ring connected to the hub part receiving the bearing elements by means of a disk which is thin-walled in relation to the said ring and which, under pronounced bearing loads, damps shocks on the axial and plain bearings as a result of its elastic flexibility and prevents a one-sided wearing of their sliding surfaces. However, as stated, the said disk is "thin-walled" only in relation to the circumference of the flange which is designed as a rigid thick-walled ring for fastening the bearing housing to the shaft housing of the turbocharger. But in absolute terms, the disk must nevertheless be rigid enough to ensure that its deformation does not exceed a specific permissible value.
Such dimensioning alone, without means for limiting the permissible deformations, does not offer any guarantee that these will be adhered to. In a further development of such a mounting for a turbocharger, therefore, the abovementioned disk connecting the rigid flange ring to the hub part of the bearing housing is made relatively thin and virtually in the form of a rigid diaphragm which is therefore more easily deformable by means of loads acting on the shaft, but the deformation of which is limited to a specific permissible value by a very rigid intermediate flange deformable virtually negligibly by the operating loads. This intermediate flange is clamped between the shaft housing and the diaphragm flange of the bearing housing, and its inner circumferential part serves as a stop for a ring part on the inner circumference of the diaphragm flange, there being, in the non-loaded state, between the annular end face of this ring part and the intermediate flange an axial play, for example 1 mm, which determines the maximum deformability of the diaphragm flange, for example as a result of the tilting of the bearing sliding surface of the axial bearing and of the plain bearing. When maximum deformation occurs, the end face of the abovementioned ring part on the inner circumference of the diaphragm flange comes to bear against the adjacent circumferential part of the intermediate flange, and this, under a load travelling over the bearing circumference, for example unbalances, leads to a sliding friction located at certain points and travelling over the entire circumference of the annular surfaces sliding on one another and, in the course of time, to an increase in the play between these. Under high loads, this then sooner or later leads t
REFERENCES:
patent: 2777739 (1957-01-01), Beerli
patent: 3049860 (1962-08-01), Beerli
patent: 3131003 (1964-04-01), Glaser
Asea Brown Boveri Ltd.
Footland Lenard A.
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