EP0031002B1 - Rotary machine with two non-parallel axes in respect of one another - Google Patents

Abstract

A rotary piston displacing machine for use as a pump compressor or power engine, as well as a hydrostatic coupling. The machine has a disk-shaped rotor rotatable in a housing, several similar diametrically opposed rotary vanes which penetrate the annular groove of the working space, which vanes can be joined or formed together in a second rigid rotor, the impeller, the disk-shaped rotor having a rotational axis forming an acute angle with the axis of the impeller. The disk-shaped rotor is positioned obliquely on the working space and is provided with radial slots for receiving the vanes which reach down to the bottom of the working space to sealingly lock the adjacent working chambers formed in the working space. The displacement operation takes place by the rotation of the vanes and the changing cross-section of the groove of the working space. If the cross-section of the working space approaches zero on one point of its periphery, i.e., when the disk-shaped rotor touches this point at the bottom of the working space, this displacing machine has neither a dead space volume nor squeezing points. It is sufficient if only one vane locks sealingly the adjacent chambers of the working space within the area of greatest cross-section since a stationary separating point exists already there. The shape of the cross-section of the working space, the shape and number of the vanes, and the shape of the rotors can be selected freely within a wide range. However, a certain symmetry of the rotation must be maintained, and the parts must be naturally adapted one to another. This rotary piston machine is suitable for use as a machine for displacing all kinds of freely flowing media, as well as for use as a power engine in the form of a displacer turbine.

Description

The invention relates to an angular-axis rotary piston machine with an axially vane rotor rotor arranged rotatably in a housing and a disk rotor having radial slots, the axes of rotation of which enclose an acute angle, the vanes reaching through the slots of the disk rotor and on the walls of the working space, from the Disc rotor is covered, run along, the outer diameter of the disc rotor is larger than the outer diameter of the vane rotor. It can be used as a pump, compressor, compressed air or hot gas engine, flow meter, hydrostatic coupling or retarder.

Such machines are already known from the following publications: US-A-2828695 and US-A-2242058.

In these rotary piston machines, working spaces are arranged on both sides of the disc rotor and none can do without completely difficult to manufacture spherical walls, because the necessarily spherical edges of the slots of the disc rotor create blowholes at their radial ends, which are covered there by spherical wall parts, because the points of contact between The vane and disc rotors all lie on a spherical surface during their movement. The radial blowholes could only be avoided with a mathematically thin disc rotor. However, since each disc rotor that can be produced has a finite thickness, these displacement machines are either leaky or difficult to produce. Other problems resulting from the inclined axes of the two axes of rotation with respect to one another have not yet been solved in a simple manner. The necessary angular spacing of the slots for rigid wings or vice versa changes constantly as a function of the angle of rotation, because in general an angle changes when projecting onto an inclined plane. The only exceptions are the angles 0 ° and 180 °.

The object of the invention is to eliminate these disadvantages.

The aim is to simplify the rotary piston machine mentioned at the beginning and to solve the sealing problem so well that it is not only superior to all other rotary piston machines, but can even compete with the reciprocating piston system in terms of tightness.

The stated object is achieved by the characterizing part of claim 1 in conjunction with the features reproduced in the preamble.

Since the sealing problem can only be completely solved on one side of the disc rotor, the work area above the disc rotor is initially dispensed with. As a result, the sealing lines on the disc rotor can be placed from its center plane in its end face, which at the same time forms a contact surface with the groove edges. In the simplest case, all sealing lines then lie in the plane of contact between the disc rotor and the obliquely cut groove edges. The cross-section of the slits is V-shaped in such a way that the narrowest point lies in the plane of contact or surface so that the sealing lines on the groove edge, the wings and the slits converge exactly at one point.

Angular-axis rotary piston machines with vane rotor and disk rotor with only one-sided working space are known per se from DE-C-8 263 381 and GB-A-967 636.

In order to be able to accommodate the inclination of the wings in the slots, the walls of the slots are slightly more inclined than the two axes of rotation to each other. In the radial direction, the wings also incline in the slots, which is why they are longer than the wings in the radial direction are wide.

So that there is no unnecessary rotation-dependent displacement of the blades relative to the slots in the sealing plane of the disc rotor, the intersection of the axes of rotation of the two rotors must lie in the sealing surface or plane. (Claim 1)

Although two opposing work spaces are dispensed with, a two-stage displacement machine can easily be implemented without increasing the number of moving parts by accommodating several or two coaxial axial ring grooves in the side of the housing. (Claim 2) The blades rotate here on different sized concentric circles. Compared to the work rooms arranged one above the other, the advantage here is that the cross-sectional shape, but above all the size of the two work rooms can be made different independently of one another.

Cylindrical walls can now be used as easy-to-produce walls due to the lack of radial blow holes. (Claim 3) On the other hand, a simple automatic adjustment option with even sliding sealing for the wings relative to the walls of the work area is obtained if the cross-section of the annular groove tapers towards the floor, e.g. the lateral walls are conical surfaces or the annular groove is toroidal. If you press the axially displaceable vane rotor against the groove base, for example by an axially working spring (the delivery pressure itself could also generate pressure), the vanes have a very good sealing effect and wear is automatically compensated. (Claim 8) This pressure can, if you want, even during the operation of the machine, be set to the desired level (including zero pressure) and remains independent of the speed and the delivery pressure!

The bottom of the ring groove can, because its cross-sectional shape is also freely selectable, e.g. be frustoconical. If the oblique angle of this cone coincides with the angle between the two axes of rotation and if the cone tip of the completed cone lies at the intersection of the two axes of rotation in the inclined plane, the surface of the bottom of the annular groove merges with the oblique plane of the housing at a circumferential point, So where the ring groove is interrupted, that is, the fixed separation point between the suction and pressure chamber. In this case there is no dead volume. (If the cross-section of the annular groove does not completely disappear at a circumferential point, a certain dead volume is created and the delivery rate of a pump would be smaller.) The sloping groove edges can in any case be milled to such an extent that in a more or less long circumferential area (this length is basically also arbitrary) the cross section of the ring groove disappears completely. Since the disc rotor only has a sealing function in the circumferential direction at this circumferential point, where there is no ring groove at all, it is clear that its shape can also be selected independently of the shape of the ring groove. The surface of the disc rotor located on the housing wall can e.g. be conical in shape so that a surface line touches the bottom of the annular groove, which is then made from a practical point of view, at a circumferential point (Claim 6). However, a flat disk rotor is easiest to implement. The inclined surface of the housing must of course be adapted to that of the disc rotor.

The number of wings is basically arbitrary and can be adapted to the respective problem. For good tightness in the slots, however, it must be taken into account that even fixed angles between the vanes in the oblique disc rotor plane constantly change somewhat depending on the angle of rotation. (For an observer in the disk rotor plane, the penetration points of rigid wings through the disk rotor move back and forth somewhat.) To solve this problem, only movable seals or elastic wings have been proposed so far, which makes this machine unsuitable for many applications. The simplest and best solution is of course the one in which these shifts do not occur. This is exactly the case with a wing spacing of 180 °, because this is the only angle (except 0 °) that remains invariant when projected onto an inclined plane, i.e. it does not change. (A straight line remains a straight line for any projection onto another plane). So if you only use two diametrically positioned wings, the problem is completely solved and the seal in the slots is good. (Claim 7)

The much smaller expansion of the slots due to the inclination of the wings is another problem and can be easily compensated in this case by the disc rotor consisting of two separate half-discs, which are held together by a suitable tensioning device and at the same time are placed somewhat elastically inwards on the wings . (Claim 10)

In this way, one obtains such tight working chambers that this displacement machine can even compete with the reciprocating piston system without the use of additional movable sealing parts or elastic parts. This also applies when using several concentric annular spaces. (Claim 2)

If you want to use more than one pair of diametrical wings, you again have the problem of displacements of the wings relative to the slots for all other wings, which can be solved again by sliding or elastic sealing parts, or by resiliently attaching the other rigid wings Attaches the main body of the vane rotor. (In contrast to the already proposed elastic wings.) (Claim 9) Also all other wing pairs only had to be arranged to be somewhat rotatable relative to the first.

This principle has a very high variability and can meet all conditions for the applications already mentioned.

For example, Not only realize very tight working chambers, but also a contactless run with an externally mounted disc rotor, which greatly increases the scope of this principle. This means that not only dry-running compressors, compressed air motors, etc. to build; even a pump is absolutely safe to run dry, while remaining pressure-increasing and self-priming. It can be designed to be very insensitive to foreign bodies, has no pinch points and can even crush solids carried along; Fibers are chopped, stones etc. Broken.

Some exemplary embodiments of this invention are explained in more detail below with reference to drawings.

• Fig.1 eine Rotationskolbenmaschine in einem Längsschnitt;
• Fig.2 einen Querschnitt nach der Linie 11-11 von Fig.l;
• Fig.3 den Längsschnitt einer veränderten Maschine;
• Fig.4 einen Flügelrotor in einer Draufsicht;
• Fig.5 eine Dichtung in einer perspektivischen Ansicht;
• Fig.6 dieselbe Dichtung im eingebauten Zustand nach einem Querschnitt VI-VI von Fig.7;
• Fig.7 die Draufsicht VII von Fig.6;
• Fig.8 eine Draufsicht einer anderen eingebauten Dichtung
• Fig.9 einen Querschnitt derselben eingebauten Dichtung nach der Linie IX-IX von Fig.8;
• Fig.10 eine zweistufige Rotationskolbenmaschine im längsschnitt X-X von Fig.11;
• Fig.11 dieselbe Maschine im Querschnitt von Fig.10 mit teilweise eingezeichnetem Scheibenrotor;
• Fig.12 eine andere Ausführung eines Verdichters in einem Längsschnitt;
• Fig.13 denselben Verdichter im Querschnitt XIII-XIII von Fig.12.

Show it:

• 1 shows a rotary piston machine in a longitudinal section;
• 2 shows a cross section along the line 11-11 of Fig.l;
• 3 shows the longitudinal section of a modified machine;
• 4 shows a vane rotor in a plan view;
• 5 shows a seal in a perspective view;
• 6 shows the same seal in the installed state according to a cross section VI-VI of Figure 7;
• 7 shows the top view VII of FIG. 6;
• 8 shows a top view of another installed seal
• 9 shows a cross section of the same installed seal along the line IX-IX of Figure 8;
• 10 shows a two-stage rotary piston machine in longitudinal section XX of Fig.11;
• 11 shows the same machine in cross section from FIG. 10 with the disk rotor partially shown;
• 12 shows another embodiment of a compressor in a longitudinal section;
• Fig. 13 the same compressor in cross section XIII-XIII of Fig. 12.

The embodiment of Figs. 1 and 2 shows e.g. a simple pump. In a cylindrical housing 1 with a cover 2, the two interlocking and inclined axes rotors are housed. The power unit is the vane rotor 4, which is rigidly connected to the shaft 3. It consists of a disk-shaped base body 4a, to which four vanes 13 are rigidly fastened on a concentric circle, which completely fill the cross section of the annular or working space 11.

The disc rotor 7 has only a sealing function; it lies on the inclined plane 6 with its flat end face 7d and seals the working space 11 towards the open side at least on the pressure or suction side and is carried along by the wings 13 which penetrate it through the radial slots 14.

The working space is worked into the housing part 1 in the form of an annular groove 11 with cylindrical wall parts 11b, 11c and a cone-shaped groove bottom 11a and is delimited at the top by the inclined plane 6, which is just inclined so that the inclined plane 6 in at a circumferential point 11e the surface of the groove base 11a merges where a linear or areal seal is created between the suction and pressure chamber. At the same time, the axes of rotation and symmetry 9, 10 of the disk rotor 7 and vane rotor 4 intersect at the intersection S in the inclined plane 6 and form an acute angle a. The disc rotor 7 is held on the surface 6 by a retaining screw 8. In operation, it is already pressed on the suction side onto surface 6 by the pressure prevailing in space 5, which is sufficient for sealing.

The slots 14 of the planar disk rotor 7 are cross-sectioned in a V-shape in order to intercept the angle of rotation of the blades 13, which is dependent on the angle of rotation, and to prevent blowholes from being created.

2 shows a plan view of the division of the annular space or the annular groove 11 or the working space. The actual conveying area is 13 90 ° long with four blades 13. This is followed on both sides by large-area inlet and outlet channels 12a, b, which extend as far as the separation point 11e.

3 shows the longitudinal section of a pump similar to the first, only that the surface 6 of the housing part 1 is formed by an obliquely lying cone and the end face 7d of the disk rotor 7 is correspondingly conical. The bottom 11 of the annular space 11 is flat and touches a surface line of the conical disk rotor 7 at a circumferential point. If one wishes to dispense with elastic slot edges, the other two rigid vanes 13b must be compared with the first rigid diametrical pair of vanes 13a via circumferentially elastic arms 13 Connect 'b to the remaining vane rotor 4 or shaft 3. The two wings 13b can then follow the displacements of the slots 14.

If you want to use rigid parts, you can use the seals of Fig.5, 6, 7, 8, and 9, which perform two separate tasks simultaneously; they can be displaced in the circumferential direction and at the same time lie elastically around the respective wing in order to intercept the displacements of the slots and their widening.

The seal 15 of Fig.5-7 consists of two plates 15a, b, which form the slot edges in a recess of the disc rotor 7 in the slot 14, are elastically connected by two arcuate parts 15c and otherwise have so much play together in the circumferential direction that they can follow the displacements of the slots 14.

The seal 15 'of Figures 8 and 9 is housed in a circular recess in the disc rotor 7. Two half disks 15'a and 15'b are stretched around the wings 13 by a circular wave spring 15'c and at the same time are supported against the wall 7a of the recess.

In Fig. 10, 11 e.g. shows a two-stage compressor for oil-free compressed air. Two ring grooves 11 and 11 'are arranged concentrically one inside the other in the housing part 1. The disc rotor 7 runs here without contact because it is also supported by a shaft 18 which leads to the outside. (The disc rotor 7, however, requires only a very small drive power to overcome the bearing friction, since it is not a power part).

The vane rotor 4 consists of the base body 4a, on each of which a diametrical pair of vanes 13b, 13c for an annular space 11 or 11 'is arranged along a diameter.

Two wings 13 and 13c reach through a common slot 14a.

The gas passed through the large inlet 12a into the outer annular space 11 of width B. The outlet 12b of the first stage lies next to the annular groove and is only connected to the annular groove 11 after a certain internal compression by the groove 17a in the disk rotor 7. The gas passes through the inlet 12'a into the inner second stage, the annular or working space 11 'and finally through the control groove 17 to the outlet 12'b in the indicated direction of rotation 16.

The seal 15 in the slot 14a is not absolutely necessary, since with this arrangement of the wings there are no displacements between the wings and the slots.

FIG. 12 shows a machine running with contact between the moving parts, for example a compressor. The four wings 13 of the wing rotor 4 are tapered by the spring 19 on the shaft 3 into the bottom Ring groove 11 pressed. The disc rotor 7 is guided in the radial groove 20. For this purpose, the housing part 2 is enlarged by the cylindrical piece 2a, which has been turned out obliquely and receives the oblique groove 20.

An annularly offset part of the disc rotor 7 also runs in a flat axial annular groove, whereby the flat pin la of the housing part 1 is also formed.

The slot edges of a slot 14 are not parallel because the cross-section of the wing 13 is not rectangular here, but trapezoidal. The wearing parts automatically adjust themselves here.

The inlet and outlet channels 12a and 12b lie behind or in front of the fixed separation point between the suction and pressure space, where the cross-section of the annular groove disappears.

Claims (8)

1. An angled-axis rotary piston machine comprising a bladed rotor (4) which is arranged rotatably in a housing and which has axial blades (13), and a disc rotor (7) having radial slots (14), the axes of rotation of which rotors include an acute angle, wherein the blades (13) extend through the slots in the disc rotor (7) and are guided either with clearance or with sliding sealing contact at the wall of the working chamber which is covered by the disc rotor, and wherein the outside diameter of the disc rotor (7) is larger than the outside diameter of the bladed rotor (4), characterised in that

a) the working chamber is formed on one side as an axial annular groove (11, 11') arranged in the wall of the housing;

b) the radial slots (14) of the disc rotor (7) are of a V-shape cross-sectional configuration in such a way that their inclined walls are inclined with respect to the central plane at least to the same degree as the two axes of the rotors are inclined relative to each other and the narrowest parts of the slots are at the surface (6) at which there is contact between the disc rotor (7) and the housing (1); and

c) the point of intersection (S) of the two axes of rotation lies at the contact surface (6) between the disc rotor (7) and the housing (1) (Figures 1, 2, 3, 12 and 13).

2. An angled-axis rotary piston machine comprising a bladed rotor (4) which is arranged rotatably in a housing and which has axial blades (13), and a disc rotor (7) having radial slots (14), the axes of rotation of which rotors include an acute angle, wherein the blades (13) extend through the slots in the disc rotor (7) and are guided either with clearance or with sliding sealing contact at the walls of the working chamber which are covered by the disc rotor, and wherein the outside diameter of the disc rotor (7) is larger than the outside diameter of the bladed rotor (4), characterised in that

a) the working chamber is formed on one side as axial annular grooves (11.11') arranged in the wall of the housing;

b) the radial slots (14) of the disc rotor (7) are of a V-shape cross-sectional configuration in such a way that their inclined walls are inclined with respect to the central plane at least to the same degree as the two axes of the rotors are inclined relative to each other and the narrowest parts of the slots are at the surface (6) at which there is contact between the disc rotor (7) and the housing (1); and

c) the point of intersection (S) of the two axes of rotation lies at the contact surface (6) between the disc rotor (7) and the housing (1); and

d) the blades (13) are arranged on the main bcdy (4a) of the bladed rotor (4) in concentric circles which extend into the correspondingly arranged grooves (11,11') (Figures 10 and 11).

3. An angled-axis rotary piston machine according to claim 1 or claim 2 characterised in that the annular grooves (11, 11') are each defined by a radially inward and a radially outward cylindrical wall (11b, 11c) (Figures 1,2, 3, 10 and 11).

4. An angled-axis rotary piston machine according to claim 1 characterised in that the annular groove (11) tapers inwardly towards its floor (11 a) (Figure 12).

5. An angled-axis rotary piston machine according to one of claims 1 to 4 characterised in that the floor (11 a) of the groove is of a frustoconical configuration such that the tip of the completed cone lies at the point of intersection (S) of the two axes of rotation (9) and (10) (Figures 1, 2, 10, 11, 12 and 13).

6. An angled-axis rotary piston machine according to claim 1 characterised in that the floor (11 a) of the angular groove is flat and the surface of the disc rotor (7) which is towards the wall of the housing is conical and the wall of the housing which has the groove is of a correspondingly conical configuration (Figure 3).

7. An angled-axis rotary, piston machine according to claim 1 or ciaim 2 characterised in that there are two diametrally oppositely disposed blades (13) in a groove (Figures 10 and 11).

8. An angled-axis rotary piston machine according to claim 4 characterised in that there is provided a spring (19) urging the bladed rotor (4) against the floor of the groove (Figure 12).

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