DE6900931U - RADIAL PISTON MACHINE. - Google Patents

Description

ap / A 2912 Voith Getriebe KG

Keyword: "Sxzenterring" Heidenheia (Brenz)

The invention relates to a Kä machine wiheit sit svisi radially one within the other and eccentrically to one another, in each case separately in rotors supported by roller bearings and rotatable independently of one another with constant eccentricity, especially a radial piston machine (Pump or motor).

In machines in which two are mutually exclusive rotatable parts are present, one of which is arranged eccentrically offset around the other part - like this E.g. in radial piston machines with a revolving eccentric ring of the The case is - each of these rotatable parts must be stored twice in the common housing. Because of the eccentric displacement namely, it is not possible, the outer rotating part directly on the shaft of the passing through it to support internal rotor in stock, such as this for example is common in so-called loose wheel bearings of gears on a shaft passing through the gear.

It is well known that the two pairs of bearings are axially adjacent to one another to be arranged, with the bearings for the outer rotor for fundamental considerations axially within the bearings of the a = ideren Rotors must lie. The non-rotating bearing ring can be arranged inside or outside (see e.g. German patent specification 848,888 or U.S. Patent 3,280,757). Both options are practically carried out; these known solutions, however have the disadvantage of a very large axial length (four bearing widths).

If you order to reduce the axial space requirement the two bearings on each side one above the other, i.e. one eccentric ring

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bearing vtnd one rotor bearing each in a plane normal to the axis, then the dimensions of the outer bearing become very large (see e.g. Russian patent specification 182 463). The very detrimental consequences are; Increase in the peripheral speed in the outer bearing and at Rolling bearings Restriction of the maximum permissible speed. This disadvantage is particularly serious because it is considered that positive displacement pumps Only develop their full power at high speeds =

Another disadvantage of these solutions is that many, within narrow tolerance limits, aligned circular cylinders and flat, radially extending surfaces on the right and left of a housing and the housing cover or end shields are turned sweetness and the processing of the mutually eccentric positions Large in the two housing parts or in the housing and cover Manufacturing difficulties and complicated devices required and is therefore time-consuming and costly

The object of the invention is to avoid the disadvantages listed above by means of suitable structural shaping of the individual parts of the machine unit mentioned at the beginning, ie to reduce the production costs and the production time. This object is achieved in that the two bearings on each side of the machine ^{are arranged one inside the other in at least approximately 1 of the} same inclined plane, and that the outer ring of the inner bearing and. the inner ring of the outer bearing are designed as a common, uniform eccentric ring carried by the housing. This saves the full strength of the inner naad outer rolling bearing ring with approximately the same _r smallest wall thickness at the narrowest point between the two exzen triscfcen Kreiszylindrtflächen. The running length of the outer roller bearing can thus be kept significantly, smaller and a restriction of the permissible η ^ τ '***''*'? »Τ» bearing speed can thereby be avoided.

The disc-shaped, eccentric one formed in this way Double bearing bing kit hardened and ground running surfaces for

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Both rolling bearings can be easily and precisely manufactured and in simple titmouse either by means of screws and pins on the side attach to the two end shields; the housing parts have then just sine simple the bearing ring inside or outside receiving Centering and a machined, flat, lateral clamping surface on. Or the entire bearing plate forms with the eccentric from the start terring a uniform part. In this case, even warped on the centering surface between the end shield and the eccentric ring * The end shield must then be made of a hardenable,

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However, the number of Zetrierflächen to be machined very precisely is then reduced to a hininiua.

The roller track diameter of the roller bearings can be reduced even further if, as provided according to a further concept of the invention, the roller bearings are designed as needle roller bearings and an axial guide bearing is provided for each rotor part. Expediently, the rotor part with the outwardly leading input and output shaft journals is given an axial guide bearing mounted directly in the housing to accommodate the axial forces acting on this rotor part from the outside via the input or output shaft, and the other rotor part is attached to the first Have it supported loosely in the same direction?

The invention is illustrated by means of one in the drawings Embodiment ia explained in more detail below. Show it:

Fig. 1 is a longitudinal section through the axis of a hydrostatic Unit with floating control pin and double set of displacement bodies and training the bearing of the rotors according to the invention :,

;. 2 t * jT »» n individual eccentric ring for the rotor bearing in the hydrostatic unit according to? Ig ~ 1 in an axial view.

5 one other type of "attachment ^1" of the eccentric to the bearing plate, nSmücn such. That he kit i? Gn forms a single part.

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The hydrostatic unit ls & six shown in Figure 1,

Can be used as a pump or as a motor, depending on whether its Input or output shaft 1 connected to a power source and

driven or whether the inlet connection 2 of the unit is connected to * 1η JH

Pressure source is connected. With the shaft 1 is the radially standing cylinder 3, which is arranged in two heaters and which receives the Yerdrängerkölbchen 4 and guides these in the direction of the otofang and in the axial direction, the rotor 5, carried by the Elisen 8 unä S ₁ ία asn oeiorä χϊ 6 and f is stored. The center of rotation of the rotor and the bearings mentioned above is marked with no 12 «Uta das

Fixed dimension e eccentric to the axis 12 is the radial guide rotor 13 , which also revolves with the rotor 5, for radial guidance of the X-lobes 4 by means of the bearings 14 and 15.

to axis 2;> The rotor 13 is z «mtrisch / mounted in the housing ring 30.

The essential part of the present invention is the eccentric ring 10 shown individually in FIG screwed to the end shields 11 and 17 and centered via the centering shoulders 16. It can also, as shown in FIG. 3 (ring IQ ¹ ), be combined with the end shield 11 ^f to form a "piece 110" 1. The centering shoulders 16 then do not need to be manufactured. The connection housing 41 can then be centered in the bearing plate II "" via a centering that is relatively easy to manufacture and screwed onto it.

Because the roller bearings are designed as needle roller bearings, their radial overall height can be changed without impairing the resistance to wear ^. <7 eir> are held. Although these bearings cannot guide the Bofcor axially; However, an axial guide can be achieved, while the Botor 5 connected to the shaft 1 is axially fixed, for example by the ball bearing arranged in the laser shield 17, while the more classical rotor 5 is positioned on the slide bearing.

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Pairs of surfaces 51/52 *> ■ * "! Al supported-any from the outside on the shaft Acting thrust forces are absorbed by the bearing 50.

Sins further simplification of manufacturing and a reduction the radial space requirement and thus the weight is thereby achieved that the outer ring 54 of the bearing 14 or I5 with the Fixing flange 55 is combined, which is about the centering is centered on the rotor I3 and screwed to it. (Saving a special bearing outer ring). Thanks to this arrangement, viz aes running ring combined in the outer rotor can without danger an unreasonable exceeding of the decisive for rolling bearings

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be pushed into each other * Through this and through dit daä each tine running surface of two eccentrically lying belts on tine » tiafctitliehen part are attached, the following advantages result

&) Yerainöerune of the bearing distance at Hotor 5 and thus Vermin Modification of the axial length of the Kotors and the Seeamttn AgS ^ t-Ifttes. With the same axial architectural structure, instead of just one »Rti legs can be accommodated by displacement pistons and dlt Conveyor ropes can be doubled for the same construction volume.

b) The reduction in the distance between the bearings results in a reduction in the deflection of the rotor, which is very important in view of the extremely small gap between rotor 5 and control pin 28.

c) No, or at most "sine tmweaentliche enlargement of Wllzkreisdurchaessers for eccentrically to Welleö * CHSE liegesdtn WXlzlager of the rotor V $ against herk ^ ssallcheB axially staggered bearings of the rotors 5 and 1>"&&& therefore no reduction of the maximum allowable Betrlebsdrehz & hl "

d) Easily manufacturability of the geiselnsanen disk-shaped body (double center ring 10) for the inner and outer bearings. This Exzenterrin "10 kaim for da * right," tffid the left bearing couple used t be.

e) Easier processing of the housing parts.

f) Saving toq Two outer and two roller bearing races.

g) This leads to a reduction in the number of non-identical passages seat surfaces to be produced; daait is a closer sweetness of tolerance achievable.

Heid * nheiiB; (Brenz), January 9th, 1969 Pö / HKh

Claims (1)

ap / A 2912 Voith gearbox JCennsrorti "eccentric ring * Heideniseiis (Brenz) 1) Machine unit with two radially one inside the other and eccentrically to one another, each for se In roller bearings, independently rotatable rotor with constant eccentricity, ins ^ tondlir * ftadlilkolbettlaichlne (fcjflfce cder This means that both bearings (7 15 to * «· 6 and 14) each side of the shark in an extremely intense Achettnkrtchten tbtnt * ind, and dtA each »eil · der AuÄenrlnt dft Camp and the Iotitnrln * de "iuieren Lattr" as jMHirnaatr more uniform, from the housing (bearing plate 11) fttrlgetier liienterrihC (IP tor. 10 *) tueeehilden «ind. 2} Unit according to claim 1, characterized in that the ttlzlager as ltadel ~ ftolle & bearings are designed for each Rotor part is provided with an axial guide bearing. 3) Unit according to claim Z, characterized in that the rotor (5) with the outwardly leading an * or Afetrleb * ~ shaft journal (1) an axial guide bearing (30) mounted directly on the housing for receiving aeT acting axially on this part of the motor Has forces and the other rotor is supported as the first in the axial direction (plain bearing 51/52). 4) Unit according to any preceding claim, characterized in that each of the outer ring (54) of the outer roller bearing (14 or 15) has a mounting flange (S?) And one Centering shoulder (55) for attachment ie outside Has rotor (I?). 3 # S * -2- 5) Unit according to one of the preceding claims * shows "that the eccentric ring (10 * J eit (ILI ¹ J is a single component {110> fatldefc (mis * 3Ϊ Heidenbcls (Br «ni) _# den
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