DE650544C

DE650544C - bearings

Info

Publication number: DE650544C
Application number: DEA73361D
Authority: DE
Inventors: Dr Nils Arvid Palmgren
Original assignee: Svenska Kullagerfabriken AB
Current assignee: SKF AB
Priority date: 1934-01-29
Filing date: 1934-06-08
Publication date: 1937-09-24

Description

Die Erfindung bezieht sich auf den Fall, daß ein in ein Lagergehäuse eingebautes Kugellager durch ein Gleitlager ersetzt werden soll. Die Breite des ortsfesten Ringes S des Gleitlagers in axialer Richtung muß dann ebenso groß wie die des auszuwechselnden äußeren Laufringes des Kugellagers sein, damit der Gleitlagerring in das Lagergehäuse paßt. Die Breite der Gleitfläche des Gleitlagers kann also höchstens so breit wie der Lagerring sein. Diese Breite ist nur gering und wird in vielen Fällen keine ausreichende Betriebssicherheit des Gleitlagers ergeben, auch wenn das Lager im Ölbade läuft; denn wenn an Stelle der Kugellagerringe nur die beiden Gleitlagerringe in das Lagergehäuse eingesetzt werden würden, so würde das Öl bei hohen Drehzahlen durch den Innenring nach außen geschleudert werden, so daß sich ein der Schmierung schädlicher Ölschaum bilden könnte. Um diese Ölschaumbilduhg zu verhindern und dadurch ein möglichst tragfähiges Gleitlager innerhalb der Kugellagerabmessungen zu erhalten, wird gemäß der Erfindung vorgeschlagen, auf einen Teil der schon geringen Lagerbreite zu verzichten und den hierdurch gewonnenen Platz zur Unterbringung von an sich bekannten ringförmigen Seitenscheiben zu benutzen, die folgendeThe invention relates to the case that a built into a bearing housing Ball bearing is to be replaced by a plain bearing. The width of the stationary ring S of the plain bearing in the axial direction must then be as large as that of the one to be replaced Be the outer race of the ball bearing so that the plain bearing ring into the bearing housing fits. The width of the sliding surface of the plain bearing can therefore be at most as wide as the Be bearing ring. This width is only small and in many cases will not be sufficient Reliability of the plain bearing results, even if the bearing runs in the oil bath; because if instead of the ball bearing rings only the two plain bearing rings in the bearing housing were used, the oil would flow through the inner ring at high speeds be thrown outwards, so that an oil foam harmful to the lubrication could form. In order to prevent this oil foam formation and thereby a stable as possible Obtaining plain bearings within the ball bearing dimensions is proposed according to the invention, on part of the To do without even a small storage width and the space gained as a result for accommodation to use of per se known annular side windows, the following

O₀ technischen Merkmale aufweisen:O _{0 have} technical characteristics:

a) Ihr Innendurchmesser soll wesentlich kleiner sein als der Durchmesser der Gleitfläche des inneren Lagerringes.a) Your inside diameter should be significantly smaller than the diameter of the sliding surface of the inner bearing ring.

b) Der Innenumfang der Seitenscheiben soll über das Niveau des Ölsumpfes hinausragen. b) The inner circumference of the side windows should protrude above the level of the oil sump.

c) Die Seitenscheiben sollen innerhalb der Breite -des Lageraußen- und -innenringes angeordnet sein.c) The side windows should be arranged within the width of the bearing outer and inner ring be.

d) Die Seitenscheiben sollen an dem äußeren Lagerring angebracht sein.d) The side windows should be attached to the outer bearing ring.

e) Die Seitenscheiben sollen die Schmiermittelzufuhr zu den rotierenden Teilen des Lagers in an sich bekannter Weise drosseln,e) The side windows are designed to supply lubricant to the rotating parts of the Throttle the bearing in a manner known per se,

d. h. sie müssen mit Ausnehmungen versehen sein, die einerseits genügend öl in das Lager eintreten lassen, andererseits darf aber die ölmenge nicht so groß sein, daß eine Ölschaumbildung eintritt.d. H. they must be provided with recesses, on the one hand, enough oil in the camp let enter, on the other hand, however, the amount of oil must not be so large that an oil foam formation entry.

Durch die mittels der Seitenscheiben erzielte Verhinderung der Ölschaumbildung wird die durch die Anordnung der Seitenscheiben erlittene Einbuße an Lagerbreite aufgehoben und darüber hinaus eine größere . Tragfähigkeit des Gleitlagers erhalten, als wenn keine Seitenscheiben aufweisende Gleitlagerringe mit einer Breite, wie sie die zu ersetzenden Kugellagerringe haben, verwendet werden würden. Bisher ist nirgendwo die Lehre gegeben worden, wie ein in einemDue to the prevention of oil foam formation achieved by means of the side windows becomes the loss of bearing width suffered by the arrangement of the side windows repealed and, moreover, a larger one. Carrying capacity of the plain bearing than if there are no sliding bearing rings with side plates with a width as they are too replacing ball bearing rings would be used. So far is nowhere the teaching has been given as one in one

*) Von dem Patentsucher ist als der Erfinder angegeben worden:*) The patent seeker stated as the inventor:

Dr. Nils Arvid Palmgren in Göteborg, Schweden.Dr. Nils Arvid Palmgren in Gothenburg, Sweden.

Claims

A plain bearing running in the oil bath must be designed in order to be able to be used in a bearing housing instead of a ball bearing if the formation of oil foam is to be avoided at high uni-speed. -; '';"£ it is already known to ensure good lubrication in plain bearings ^ with a circumferential inner ring by preventing the oil from foaming by side rings, ίο With these plain bearings, however, the lubricant supply to the rotating parts of the Bearing throttling side discs arranged outside the width of the sliding bearing outer and inner ring and arched to a large extent to the bearing outer ring, so that the known sliding bearing could not be used to replace a ball bearing built into a bearing housing.

In the drawing, two embodiments of the invention are shown, for example, and in the following description there are still other features of the invention explained.

Fig. Ι is a cross section in an axial plane through the new warehouse.

Fig. 2 is a side view of this bearing. Fig. 3 is a cross section in an axial plane through a further embodiment. Fig. 4 is a side view of this bearing. In Fig. 1, the inner ring 1 is at its Provided the outside with a spherical sliding surface 3. The cross section of the ring is executed high, so that the sliding surface on a relatively large radius lies. The outer ring 2, which fits the sliding surface of the inner ring, supports the two side plates 4 and 5. Because these disks have a much smaller inner diameter than that of the sliding surface of the inner ring, one can use the oil bath Let go up to level 8 in Fig. 1 without the oil bath swirling from the inner rings will. If the disks were not there, the level of the oil bath would not be possible to avoid foaming let rise higher than up to level 9 according to FIG. The side windows are through Pierced holes 10 through which the oil flows to the bearing. Because of the small However, the size of the holes can be determined by the movement of the inner ring or that rotating with the same Oil does not transmit the movement to the oil bath located outside the side windows.

The side disks 4 and 5 are provided with flat bearing surfaces 6 and 7, which are turned towards the inner ring and lie in radial planes. As a result, the bearing is able to take up axial loads. the Side disks 4 and 5 are supported by the axial pressure exerted on them by the inner ring, As FIG. 1 shows, against those parts of the outer ring 2 which are the immediate Make continuations of the spherical sliding ■■ surfaces of this ring. Through this '\ f the .side windows allow the possibility of '; adjust to the inner ring when it is inclined to the outer ring should come. The axial pressure is therefore even with such a position of the inner ring transferred to the bearing surfaces 6 and 7 of the side panels, and the axial The load-bearing capacity of the bearing is retained undiminished even if it is misaligned.

At the edges of the outer ring a number of recesses 11 are provided so that the side windows are only supported in places by the outer ring. This will the main advantage achieved that the flat from the beginning of the storage surfaces 6, 7 of When loaded, panes experience local deflections that lead to the formation of wedge-shaped Contribute oil spaces, which is a prerequisite for achieving complete fluid friction are. The recesses also serve to drain the oil from the bearing. Be through the side windows the centers of the spherical sliding surfaces of the inner and outer rings prevent to be displaced axially to one another when there is an axial load on the bearing, which is the radial Would affect the bearing capacity. Because the side windows are arranged within the width determined by the two bearing rings, the bearing can be designed with the external dimensions standardized for ball bearings will.

In the embodiment according to FIGS. 3 and 4, the inner ring 1 is on the outside provided with a cylindrical sliding surface, which is a corresponding surface of the outer ring 2 touched. Thin sheet metal disks 4, S are attached to the sides of the outer ring, in which recesses 10 for a connection between the oil bath and the interior of the Storage are provided. Between the inner ring 1 and the disks 4, 5 is a relative Large clearance available, so that the inner and outer rings are axially in the Relation to each other can move freely by a certain amount. The Fortune the side windows to prevent foaming is in this embodiment the same as in the embodiment according to FIGS.

Pa ϊ en τ λ ν s i> r ΐ: c η ε:

ι. Plain bearings with inner and outer bearing ring and oil bath lubrication, marked through within the width of the

C50544

Bearing outer and inner ring arranged, attached to the outer bearing ring, the supply of lubricant to the rotating parts of the bearing is known per se Way throttling, ring-shaped side discs, the inner diameter of which is much smaller than the diameter of the Sliding surface of the inner bearing ring and its entire inner circumference over the level of the Ülsumpfes protrudes.

2 .. plain bearing according to claim i, characterized characterized in that the side plates with essentially flat, turned against the inner bearing ring, in one Radial plane lying bearing surfaces ..... are provided.

3. Plain bearing according to claim 1 or 2, characterized in that the sliding surfaces of the two bearing rings are spherical and that the side washers are supported against parts of the outer bearing ring, which is a direct continuation of the spherical sliding surface of this ring form.

1 sheet of drawings