EP0102441A2 - Pump or motor engine having conical ring elements - Google Patents

Abstract

According to the invention, piston shoes (502, 119) or conical ring elements (1, 2, 11, 12, 307) are used in pumps or motor engines (7, 48, 340). Formed inside the conical part (1, 2, 11, 12, 307) of the element is a working chamber (14, 61, 311) which has fluid flowing through it, which has inlet means (50) and outlet means (49) and which periodically increases and reduces its volume under the control of a drive system (52, 55, 96, 97) acting by means of reciprocating pistons (94). This makes it possible to achieve the volume change in a working chamber without moving, sealing pistons in the cylinders and to avoid any sealing due to sealing parts sliding on one another without lubrication, thereby making it possible for the working chamber to be capable of being filled and operating under high pressure with a nonlubricating fluid, for example water. The drive system is separated from the working chamber by means of the reciprocating piston and can be operated using a fluid having lubricating action. The detailed design can be such that pressures of over a thousand bar can be efficiently used with a nonlubricating fluid in the working chamber. Suitable high-pressure piston shoes (52, 21, 502) can be used in the drive system. The capability of pumping nonlubricating fluid for such high pressures in the working chamber can only be achieved if the constructions and design principles described in the patent application are followed. <IMAGE>

Description

The invention relates to hydrostatic or pneumatic units in which fluid flows through a periodically increasing and decreasing working chamber, such as pumps, compressors, fluid motors, internal combustion engines or gears. In such units, fluid is pumped or a rotor is driven by fluid in the motor.

Pumps and motors are used as hydraulic pumps and hydraulic motors in many industries. The simplest pumps are plastically deformable diaphragm pumps for low pressures, in which the diaphragm forms a conical ring element in places. Pumps for very high pressures are used in water jet snow machines, for example, and often have to deliver high water pressure of a thousand or several thousand bars.

Pumps with membranes, which can also be flexible metals, are known, for example, from US Pat. No. 3,861,277. Pumps for very high pressures, for example for water jets (water jet) snow machines are known from the catalogs of the specialist companies and consist of a hydraulic piston of large cross section for driving the water pump piston of small cross section or they are mechanically driven piston pumps with several pistons next to each other and the axes of the pistons mostly in a common plane.

The membrane pumps mentioned correspond to the preamble of patent claim 1. However, the diaphragm pumps have so far not been used as high-pressure water pumps for water-jet cutting systems, because they only let low pressures of a few, or in the best pressure-resistant versions up to a maximum of 100 bar. Until now there has been a lack of possibilities to make the membranes usable for pressures of over 100 bar in the cavity within the conical ring element. Obviously, this was considered so impossible that no efforts were made to develop diaphragm pumps for 1000 or more bars.

In the piston pumps described for high pressures of 1000 or more bar pressure, it is necessary to seal the piston, which periodically enlarges and reduces the piston, against leakage. The high pressure of the non-lubricating water acts on the plastic seal. If there is no lubrication, the plastic seal quickly wears out under the water pressure so high that aggregates of this type decrease in tightness and delivery quantity after just a few hundred operating hours. In addition, at such high pressures, the plastic seals create a high level of friction that reduces the efficiency of the system. After all, these systems are so expensive, even small ones of 45 Kw cost around one hundred thousand marks, so that despite the clean cutting of the water jet systems only a few hundred such systems have been used in the world so far. For the streaming of the cutting points of stone drills, these systems turn out to be too expensive and, moreover, the non-uniformity of the funding causes disturbing fluctuations at the cutting points of the stone drills, cutters and saws.

The invention effectively remedies this. Because it creates according to the characterizing part of claim 1 a centering and a support on the ring element with the conical part. The centering ensures the correct position of the element and the support prevents the conical element from deflecting away from the inner cavity to the outside axially. This gives the conical part of the element a limit on the possibility of deformation such that it cannot evade under the high internal pressure in the inner cavity, that is to say the working chamber, and is therefore pressure-resistant for high and very high pressures.

According to claims 2 to 4, the elements are designed in such a way that seals can be used which seal perfectly against high pressure from the working chamber without being exposed to any movement with sliding parts. The previous rubbing off of the seals is therefore completely eliminated, since the corresponding seal of the invention is at all times at rest, ie does not slide on a surface when the fluid is not lubricating.

The invention, as characterized in the claims, therefore solves the problem of replacing the seals which previously sealed under sliding against non-lubricating fluid and which rub off quickly with non-wearing seals which do not seal under sliding, and which are known from the preamble of claim 1 To make membranes or elements with conical parts for very high pressures reliable.

This increases the service life of the high-pressure units, in particular those with non-lubricating fluid in the working chambers, and at the same time increases the efficiency of the units, because the invention eliminates the friction of the previous seals, while at the same time the unit is more evenly conveyed in the fluid flow and the price of the unit can be reduced.

The object of the invention for high pressure can only be achieved by following the precise rules of the invention. Otherwise the elements will break under too high internal tensions. In addition, a corresponding control device suitable for the high pressures must be arranged for controlling the stroke of the elements. This control is called drive arrangement in the patent application, whereby this word should include that, when used in the engine, it is driven by the pressure effect of the fluid in the working chamber, ie it does not drive itself. The drive arrangement must be able to overcome or absorb the high forces acting on the elements and it is therefore expedient to use particularly high-pressure piston shoes in the unit in order to periodically move the support accordingly, or the reciprocating piston , which controls the movement of the conical parts of the elements, to drive periodically accordingly, or to absorb its driving forces and to utilize them in the engine.

The piston shoes, pistons, pressure pistons and propellants or auxiliary parts developed in this way for the elements of the invention also prove to be usable in general hydraulic pumps, hydraulic motors, compressors or gearboxes, or also in internal combustion engines, without the conical elements being arranged in them have to.

Further tasks and solutions of the invention, such as the training required to implement them, will be explained in more detail on the basis of the description of the preferred exemplary embodiments, and a geometrical-mathematical analysis will also be provided without the elements breaking quickly under high internal pressures in the working chamber would.

• Fig.1 einen Laengsschnitt durch Elemente der Erfindung,
• Fig.2 entsprechende Laengsschnitte durch Elemente und
• Fig.3 ebenfalls Laengsschnitte durch Elemente der Erfindung. Davon zeigen im Einzelnem :
• Fig.1-A einen Laengs schnitt durch ein erstes Element;
• Fig.2-B einen Laengs schnitt durch ein zweites Element;
• Fig.2-A einen Laengs schnitt durch ein weiteres erstes Element;
• Fig.2-B einen Laengs schnitt durch Ringeinlagen;
• Fig.2-C einen Laengsschnitt durch ein weiteres zweites Element;
• Fig.2-D einen Laengsschnitt durch einen Auflage-Ring;
• Fig.3 einen Laengsschnitt durch ein weiteres erstes Element;
• Fig.4 einen Laengsschnitt durch ein weiteres zweites Element;
• Fig.5 einen Zusammenbau mehrerer Elemente der Figur 1 mit den Figuren teilen 1-A und 1-B;
• Fig.2-E einen Zusammenbau der Einzelteile der Figur 2 mit den Figurenteilen 2-A bis 2-D;
• Fig. 6 einen Laengs schnitt durch ein Aggregat der Erfindung;
• Fig. 7 einen Laengsschnitt durch Teile der Elemente ;
• Fig.8 einen Laengsschnitt durch Teile des Standes der Technik
• Fig. 9 einen Laengsschnitt durch einen Elementenpoarsatz;
• Fig. 10 einen Laengsschnitt durch Teile der Erfindung;
• Fig. 11 einen Laengsschnitt durch Teile der Erfindung;
• Fig. 12 einen Laengsschnitt durch einen Teil eines Aggregates
• Fig. 13 einen Laengs schnitt durch einen Teil eines Aggregates
• Fig. 14 einen Laengsschnitt durch einen Teil eines Aggregates
• Fig. 15 einen Laengsschnitt durch einen Teil eines Elementes
• Fig. 16 einen Laengsschnitt durch einen Teil eines Elementes.
• Fig. 17 einen Laengsschnitt durch einen Teil eines Aggregates;
• Fig. 18 einen Querschnitt durch Teile eines Elementes
• Fig. 19 einen Laengsschnitt durch einen Teil eines Elementes;
• Fig.20 einen Laengsschnitt durch einen Teil eines Elementes;
• Fig.21 einen Querschnitt durch einen Teil eines Aggregates
• Fig.22 einen Laengsschnitt durch einen Teil eines Aggregates;
• Fig. 23 eine schematische Darstellung mit Mathematik;
• Fig.2 4 eine geometrische und mathematische Daten und Formeln;
• Fig.25 die inneren Spannungen in einem Element;
• Fig.26 eine Schematik einer Festbrennstoff Anordnung;
• Fig.27 einen Qaengsschnitt durch eine Haelfte eines Elementes;
• Fig.28 einen Laengsschnitt durch einen Teil eines Elementes;
• Fig.29 einen Querschnitt durch einen Teil eines Aggregates;
• Fig. 29-A die Figur 29, jedoch mit den Formeln fuer di e Berechnung;
• Fig.30 die Spannungen in einem Element;
• Fig.31 einen Querschnitt durch eine Anordnung; und;
• Fig.32 einen entsprechende Laengsschnitt dazu;
• Fig.33 einen Laengsschnitt durch eine Anordnung;
• Fig. 34 einen Laengsschnitt durch ein Aggregat;
• Fig.35 eine Abwicklung eines Teiles der Figur 34 ;
• Fig.36 einen Radialschnitt durch einen Teil der Figur 34 und eine auf einen Steuerflaechenteil der Figur 34 ;
• Fig.37 einen Laengsschnitt durch Teile eines Aggregates;
• Fig.38 einen Querschnitt durch Figur 37 entlang dem Pfeil II-II;
• Fig.39 einen Querschnitt durch Figur 37 entlang dem Pfeil IV-IV;
• Fig.40 eine Draufsicht auf Figur 37 von oben ;
• Fig.41 einen Laengsschnitt durch Teile eines Aggregates;
• Fig.42 einen Schnitt durch Figur 41 entlang der gepfeilten Linie;
• Fig.43 einen Schnitt durch einen Teil der Figur 41;
• Fig.44 einen Querschnitt durch Figur 43 entlang dessen Pfeillinie;
• Fig.45 einen Laenegsschnitt durch einen Kolbenschuh der Fig. 41 ;
• Fig.46 einen Querschnitt durch die Mitte der Figur 45;
• Fig.47 Laengsschnitte durch Teile der Figur 41;
• Fig.48 einen Querschnitt durch Figur 47 entlang der gepfeilten Linie in Figur 47 ;
• Fig.49 einen Laengsschnitt durch einen Teil eines Aggregates;
• Fig.50 Querschnitte durch die Figur 49 entlang der in der Figur 49 gezeichneten gepfeilten Linien;
• Fig.51 einen Laengsschnitt durch einen Kolbenschuhe mit einem Teile des Kolbens;
• Fig.52 einen Querschnitt durch die Mitte der Figur 51;
• Fig.53 eine Draufsicht auf Figur 51 von oben mit einer Defi = nierung der Abmessungen der Teile darin;
• Fig.54 einen Schnitt durch den Laufteil eines Kolbenschuhes parallel zur Kolbenhubfuehrungsflaeche geschnitten;
• Fig.55 eine Draufsicht auf einen Kolbenschuh von oben;
• Fig.56 einen Querschnitt durch Figur 55 entlang der in der Figur 55 gezeichneten gepfeilten Linie;
• Fig.57 einen Laengsschnitt durch ein Aggregat;
• Fig.58 einen Laengsschnitt durch einen Teil eines Aggregates;
• Fig.59 einen Querschnitt durch Figur 58 entlang dem Pfeil A-A;
• Flg.60-A einen Schnitt durch Figur 58 entlang der Pfeillinie B-B;
• F ig. 60-B eine Ansicht des Kolbenschuhes der Figur 58 von rechts;
• Fig.60-C einen Schnitt durch den Kolbenschuh der Figur 58 entlang A-A;
• Fig.61-A einen Laengsschnitt durch einen Kolben und Kolbenschuh;
• Fig. 61-B einen Querschnitt durch Figur 61-A entlang der Pleilinie darin;
• Fig.61-C eine Alternative zur Figur 61-B;
• Fig.62 eine Alternative zur Figur 61-B;
• Fig. 63-A teilweise Laengsschnitte durch einen Kolben und Kolbenschuh; und
• Fig.63-B einen Querschnitt durch Figur 63-A entlang der Pleilinie darin;

It show in the figures

• 1 shows a longitudinal section through elements of the invention,
• Fig.2 corresponding longitudinal sections through elements and
• 3 also longitudinal sections through elements of the invention. The following show in detail:
• Fig.1-A a longitudinal section through a first element;
• Fig.2-B a longitudinal section through a second element;
• Fig. 2-A a longitudinal section through another first element;
• Fig.2-B a Laengs section through ring deposits;
• Figure 2-C shows a longitudinal section through another second element;
• Fig.2-D a longitudinal section through a support ring;
• 3 shows a longitudinal section through a further first element;
• 4 shows a longitudinal section through a further second element;
• 5 shows an assembly of several elements of FIG. 1 with the figures sharing 1-A and 1-B;
• 2-E shows an assembly of the individual parts of FIG. 2 with the parts 2-A to 2-D;
• 6 shows a longitudinal section through an assembly of the invention;
• 7 shows a longitudinal section through parts of the elements;
• 8 shows a longitudinal section through parts of the prior art
• 9 shows a longitudinal section through a set of elementary poars;
• 10 shows a longitudinal section through parts of the invention;
• 11 shows a longitudinal section through parts of the invention;
• Fig. 12 shows a longitudinal section through part of an assembly
• 13 shows a longitudinal section through part of an aggregate
• 14 shows a longitudinal section through part of an assembly
• 15 shows a longitudinal section through part of an element
• 16 shows a longitudinal section through part of an element.
• 17 shows a longitudinal section through part of an assembly;
• Fig. 18 shows a cross section through parts of an element
• 19 shows a longitudinal section through part of an element;
• 20 shows a longitudinal section through part of an element;
• 21 shows a cross section through part of an assembly
• 22 shows a longitudinal section through part of an assembly;
• 23 shows a schematic illustration with mathematics;
• Fig.2 4 a geometric and mathematical data and formulas;
• 25 shows the internal stresses in an element;
• 26 shows a schematic of a solid fuel arrangement;
• 27 shows a cross-section through half of an element;
• 28 shows a longitudinal section through part of an element;
• 29 shows a cross section through part of an assembly;
• 29-A shows FIG. 29, but with the formulas for the calculation;
• 30 shows the stresses in an element;
• 31 shows a cross section through an arrangement; and;
• 32 shows a corresponding longitudinal section;
• 33 shows a longitudinal section through an arrangement;
• 34 shows a longitudinal section through an aggregate;
• 35 shows a development of a part of FIG. 34;
• FIG. 36 shows a radial section through part of FIG. 34 and onto a control surface part of FIG. 34;
• 37 shows a longitudinal section through parts of an assembly;
• 38 shows a cross section through FIG. 37 along the arrow II-II;
• 39 shows a cross section through FIG. 37 along the arrow IV-IV;
• 40 shows a top view of FIG. 37 from above;
• 41 shows a longitudinal section through parts of an assembly;
• 42 shows a section through FIG. 41 along the arrowed line;
• 43 shows a section through part of FIG. 41;
• 44 shows a cross section through FIG. 43 along the arrow line;
• 45 shows a longitudinal section through a piston shoe of FIG. 41;
• 46 shows a cross section through the center of FIG. 45;
• 47 longitudinal sections through parts of FIG. 41;
• 48 shows a cross section through FIG. 47 along the arrowed line in FIG. 47;
• 49 shows a longitudinal section through part of an assembly;
• 50 cross sections through FIG. 49 along the arrowed lines drawn in FIG. 49;
• 51 shows a longitudinal section through a piston shoes with a part of the piston;
• 52 shows a cross section through the center of FIG. 51;
• 53 shows a top view of FIG. 51 from above with a definition of the dimensions of the parts therein;
• 54 shows a section through the running part of a piston shoe cut parallel to the piston stroke guide surface;
• 55 a top view of a piston shoe from above;
• 56 shows a cross section through FIG. 55 along the arrowed line drawn in FIG. 55;
• 57 shows a longitudinal section through an aggregate;
• 58 shows a longitudinal section through part of an assembly;
• 59 shows a cross section through FIG. 58 along the arrow AA;
• Flg.60-A shows a section through Figure 58 along the arrow line BB;
• Fig. 60-B shows a view of the piston shoe of FIG. 58 from the right;
• 60-C a section through the piston shoe of FIG. 58 along AA;
• Fig.61-A a longitudinal section through a piston and piston shoe;
• 61-B shows a cross section through FIG. 61-A along the connecting line therein;
• Fig. 61-C an alternative to Figure 61-B;
• Figure 62 shows an alternative to Figure 61-B;
• Fig. 63-A partial longitudinal sections through a piston and piston shoe; and
• 63-B shows a cross section through FIG. 63-A along the connecting line therein;

As far as elements or aggregates are mentioned in the previous brief description of the figures, this means that they are elements or aggregates of the invention.

Fig. 64 is part of FIG. 17 and trimmed to such a format that this figure can be placed as a figure alongside the summary.

Figure 1-A shows an element of the invention with the conical part 1, at the radially inner end of which the approximately axial extension 21 is located. The ring element is hollow on the inside and forms the interior 22. The approximately cylindrical outer surface 59 can be attached to the radially outer end be. The inner axial extension can form an inner or outer cylindrical guide or holding surface 28. Each ring element with a conical part forms a hollow front side 91 and a bulged, non-hollow rear side 92 at the relevant axial end. These forward and back pages 91 and 92 are however only provided with the reference signs in FIGS. 1 and 2, since this is sufficient for understanding the general conical shape. In this description, the front of the conical part of a ring element forms an inner space 114, which is not identical to the space 22 radially within the inner diameter of the ring element. This is because both spaces 22 and 114 have associated functions which are to be calculated differently in units of the invention.

1-A therefore has the special feature that an approximately cylindrical extension 21 is formed in the axial direction at its radially inner end on a conical ring 1.

In the figure, 1-B, the conical ring element 2 has at its radially outer end of an approximately cylindrical Achsialfort = _'set 23 91. Vorseitenrichtung in the radial inside this element has a recess which can be limited radially by the cylindrical surface 29th The interior or the inner chamber 25 is thus obtained, and under the conical part 2 the working chamber or cone chamber 114. The axial extension 23 can form an inner seat for receiving an element of FIG. 1. If desired, a receiving space 24 is formed,

The special feature of FIGS. 1-B is therefore that an approximately cylindrical extension 23 is formed on a conical ring 1 in the axial direction at its radially outer end.

By viewing FIGS. 1-A and 1-B together, it can be seen that it is possible to provide the axial extension 21 of FIG. 1-A with an outer diameter that corresponds to the inner diameter 29 of the conical part 2 of the element of FIGS. 1- B corresponds. Then you can assign an element of FIG. 1-A with its back end 92 to the back end of an element of FIGS. 1-8 and insert the element of FIG. 1-A into the element of FIG. 1-B. The element set in FIG. 5 is thus obtained.

FIG. 5 shows a longitudinal section through a ring element composed of the ring elements of FIGS. 1-A and 1-B = set with conical parts 1, 2 in the ring elements and with self-centering of the elements in one another. The upper element 2 of FIG. 5 encompasses the radial outer surface 59 of the ring element 1 with the radially outer axial extension 23. The axial rear end of the ring element 2 therefore shows in the front of the ring element 2 of FIG. 1-B, so that there is between the two elements 1 and 2 Form two cone chambers 114 and unite to form a common cone chamber 14. At the lower axial end of the ring element 1, a ring element 2 of FIGS. 1-B is mounted in such a way that the radial inner surface 29 of the ring element 2 encompasses the axial extension 21 of the ring element 1. The ring element 1 therefore partially engages in the interior 25 of the ring element 2. This ring element set can be continued by any number of element pairs, in that an element 1 is assembled to an element 2 and a further element 1 to the element 2. The element set of FIG. 5 thus allows a plurality of elements in a self-centering and self-holding element set. It forms a plurality of inner chambers 22 and 25 and a plurality of cone chambers 114, all of which are connected to one another. They then form a common inner cone chamber 14 and a common interior space 2.25.

FIG. 5 therefore shows as a special feature that two elements containing conical ring parts (1, 2 or 3, 4) rotated 180 degrees axially one behind the other are arranged coaxially, for example according to FIGS. 5, 6 or 7.

The ring element set in FIG. 5 easily eliminates a disadvantage of the prior art known to me, which is described in FIG.

Figure 8 shows a set of conventional disc springs. To center them, they require a central guide pin 51, which holds the individual plate springs 52, 53 axially one behind the other. This central guide pin 51 is saved by the embodiment according to FIG. 5 of the invention. Friction of the disc springs 52, 53 on the guide pins 51 is also avoided. The grinding of the hardened pin 51 is saved. The exemplary embodiment of the invention according to FIG. 5 is simple and cheap, since the ring elements can be punched. However, it must be noted that the spring forces are indistinguishable from the commercially available and standardized disc springs, since the axial extensions 21 and 23 increase the resilience of the conical parts 1, 2 of the elements 1, 2. If one wishes to have soft blocks of FIG. 5, the thicknesses of the axial extensions 21, 23 are weakened or shortened.

The set of elements in FIG. 5 does not yet contain any seals for the sealing of the hollow spaces within the conical parts of the elements. This set of Figure 5 is therefore particularly suitable as a replacement for conventional plate television sets. Not necessarily as an element set for pumps or motor units, since it does not contain any seals to seal the working chambers between the elements. 5 therefore serves in particular to explain the simple assembly of elements. If it turns out that the elements of FIGS. 1-A, 1-B and the assembly of FIG. 5 are already known, protection from patent claims for these figures is dispensed with and these figures only serve to explain the technology used . However, if the elements of these figures prove not to be known in the examination procedure, the right is reserved to file a patent claim in accordance with the defined special features of these figures, if necessary in a divisional application.

FIG. 2 describes and shows a set of elements of the invention which is particularly suitable for use in pumps and motors, unless excessively high pressures in the fluid are required. The elements of FIG. 2 differ from the elements of FIGS. 1 and 5 in that they contain flat parts radially inside = half and outside the conical parts. These radial plan parts 27, 47 and 140 cannot be clearly defined in the German language, since the German language makes no difference between an independent, individual part and the part of a whole. In English, however, they are clearly definable as "portions" 47,27,140. Likewise, the conical parts 1 and 2 are "portions" of the elements in question, and also the axial continuations 21 and 48 are "portions" of the elements 1 and 2 of FIGS.

The radial inner end piece of FIG. 2-A is provided with the flat piece (portion) 140, while the radially inner end piece of FIG. 2-C is provided with the flat piece, portion, portion 140, at the inner end of which the axillary process 21 is located. Correspondingly, the element of FIG. 2-A has on its radially outer piece the plan piece, plan part, portion 47, on the radially outer end of which the axial extension 48 is located. The element of the figure 2-C has on the radially outer part, piece, portion the flat part, piece, portion 27. The flat parts, pieces, portions form the flat surface parts, pieces, portions 240, 340, 147 at their axial ends , 3,133,4,444 and the axial extensions form the cylindrical partial surfaces, surface portions 28,15,148,59, which can also be cylindrical partial surfaces at the radial ends of flat parts.

Figure 2-B shows an outer ring 8 and an inner ring 6, the inner ring being placed centrally in the outer ring and a chamber or a seat for receiving a seal 7 being formed between the inner ring and the outer ring, which (also) in the figure is denoted by 7, although the sealing ring 7 is not drawn in the seat 7 in order to show the parts 6 and 8 and the space 7 more clearly. FIG. 2-D shows the support 10 required according to the characterizing part of claim 1, which in this case is designed as a ring with a specific inner and outer diameter in order to perform the special task intended in this FIG fulfill. The purpose of the arrangement of what has been described so far for FIG. 2 results from the assembly figure 2-E, in which all parts of FIG. 2, that is to say the parts of FIGS. 2-A to 2-D, are combined are mounted.

First of all, the outer ring 8 is placed in the axial extension 48 of the element 1 and then the sealing ring 7, not shown, is placed in the sealing ring bed 7 within the inner diameter of the outer ring 8. The sealing ring 7 is somewhat thicker than the axially equally thick outer and inner rings 8 and 6. Then the inner ring 6 is placed in the sealing ring 7, which centers the inner ring 6 in the outer rings 8. Then you can insert the element 2 into the element 1 so that the outer surface 59 of the element 2 touches the inner surface 148 of the extension 48 of the element 1, and an axial end of the outer ring 8 touches the flat surface 3 of the element 2. The conical portions 1 and 2 of the elements of FIGS. 2-A and 2-C simultaneously define the numbers 1 and 2 of the elements of FIGS. 2-A and 2-C. The ring 10 is then placed as a support on the rearward end of the element 2, so that a part of it touches one axial end of the Plamflawchen portion 4 of the element 2. Then an element 1 can again be fitted, another element 2 and so on to the element 1, and the respective element 1 is centered with the inner surface 82 on the outer surface 15 of the element 2.

• Zwischen den Elementen 1 und 2 ist die Arbeitskammer 14 ausgebildet, die das zu pumpende Fluid enthaelt, oder in die beim Be= trieb als Motor Fluid hineingepresst wird. Die Arbeitskammer 14 besteht aus Teilen 14, die die inneren hohlen Raeume radial innerhalb der ko - nischen Teile, portions, 1,2 sind und die durch Bohrungen 65 miteinander derv verbunden sind. Der Dichtring 7 zwischen den Ringen 6 und 8 dichtet die Arbeitskammer 14 radial nach aussen ab. Die Abdichtung des Kammernteiles der einen assemblygruppe von Elementen 1 und 2 zur naechsten assemblygruppe der naechsten Elemente 1 und 2 geschieht durch einen nicht eingezeichneten Dichtring 777, der in den Dichtring= raum (Sitz) 111 zwischen den Teilen 10,15,21 ,4, und 240 herein gelegt wird.

The special meaning of the element - assembly of Figure 2-E is as follows, although it should be remembered that the German language has no word for an "assembly" and therefore the unsuitable word: "assembly" has been used. So the word "assembly" means an "assembly" of the English language; -:

• Between the elements 1 and 2, the working chamber 14 is formed, which contains the fluid to be pumped, or into which fluid is pressed as a motor during operation. The working chamber 14 consists of parts 14 which are the inner hollow spaces radially inside the conical parts, portions 1, 2 and which are connected to one another by bores 65. The sealing ring 7 between the rings 6 and 8 seals the working chamber 14 radially outwards. The chamber part of the one assembly group of elements 1 and 2 is sealed to the next assembly group of the next elements 1 and 2 by a sealing ring 777, not shown, which is in the sealing ring = space (seat) 111 between the parts 10, 15, 21, 4, and 240 is put in.

When designing the parts of the figure parts in FIG. 2, the axial thickness of the rings 6, 8 and 10 must be taken into account and the corresponding centering parts 48, 21 must be so long in the axial direction that the radial of the relevant element parts and the rings and / or Seals remain.

For use as elements for pumps or motors, or compressors or gears, it is important to observe all the details of the parts of the group of figures in FIG. 2. Because the axial thickness of the rings 6,8,10 must ensure the good effect of the seals in beds 7 and 111. The sealing rings in the beds 7 and 111 must rest on the relevant surface areas of the parts of the elements still to be pressed and pressed against them in order to be able to seal well and to guarantee the good sealing of the working chamber (s) 14. It should be noted here that without the arrangement of the rings 8 and 10, the assembly and thus the entire arrangement cannot work, because if no rings 8 and 10 acting as a spacer ring are arranged, the adjacent elements would axially on the Seal the seals in beds 7 and 111 and crush them. The arrangement of the rings 8 and 10 is an important feature of the present invention, without which and without their correct dimensioning together with the neighboring parts in FIG. 2-E no reliable pump or motor unit of the invention can be created . It should also be noted that the arrangement of Fig. 2 can be used for the subcritical area of the pump and motor units, but not for the supercritical pressure area of the pump and motor units, the difference between the two areas later is explained in the description of the figures.

The peculiarity of Figure 2 and its parts is therefore that between adjacent ring elements with conical portions spacer rings, for example outer rings and support rings are arranged, which force a spacing of parts of the elements from each other, so that sealing rings can be arranged seal an inner working chamber precisely and prevent the spacer rings from destroying the sealing rings.

FIG. 3 shows a ring element of the invention similar to FIG. 1 in longitudinal section. Here, the conical part 3, which forms the conical chamber 27, has a radially flattened radial flattening at the radially inner end with the bearing or hat or support surfaces 38, 41 and at the radially inner end of the flattened area between the axial surfaces 38, 41 there is the axial extension 42 with the approximately cylindrical outer surface 41 and the bore 39. At the radially outer end is the outwardly directed axial extension 24, which is on the outer side axial end merges into a radially outward directed radial extension 33, at the radially outer end of which the inward directed axial extension 32 is located. The extensions 34, 33, 32 thus form an annular chamber 31, which can serve the exception of a plastic sealing ring 75. For example, this can be an O-ring. In this description, pointing inward means that the direction points to the front of the conical part 1, 2, 3, 4, 5, 6, while pointing outward means that the direction points to the rearward end of the conical part 1, 2, 3, 3 , 4,5,6 to shows. So outward means in direction 92 of FIG. 1 and inward means in direction 91 of FIG. 2. Otherwise, inward and outward means the radial direction in question perpendicular to the axis of the conical part 1, 2, 3, 4, 5 or 6.

FIG. 4 is a longitudinal section through the element with the conical part 4 that is complementary to the element of FIG. 3. The conical part 4 merges at the radially outer end into the radially flat extension 47, at the radially outer end of which the axially inward axial extension 48 is formed. It can form a radially inner seat and space 49 can be formed within the axial extension 48, which can serve as a receiving space and as a centering for the element 3 of FIG. 3. The conical space 50 forms within the conical part 4, while the conical space 37 formed in the conical part of FIG. 3. At the radially inner end, the conical part 4 merges into the radially flat and radially inwardly directed radial extension with that of the bearing surface 45. At the radially inner end of the inner radial extension is the axial extension 43, is directed outward and may form the seat surface 44 cylindrically inside.

The outside seat 41 of FIG. 3 can be dimensioned such that it fits into the inside seat 44 of FIG. 4. And the outside diameter of the extension 32 of FIG. 3 can be dimensioned such that it fits into the inside diameter of the extension 48 of FIG. 4. Then an element set can be assembled together, as shown in FIG. 6, one element each 3 of FIG. 3 installed inside the seat 44 of the element 4 of FIG. 4, while an outer extension 48 engages around an outer extension of an element of FIG. 3. As a result, as in FIG. 5, a set of any number of mutually complementary elements 3 and 4 of FIGS. 3 and 4 can be assembled together in the axial direction.

In such element sets according to FIGS. 5 or 6 there are respectively outwardly directed ends of two elements and correspondingly inwardly directed ends of elements.

It is also important that the axial extensions 42 and 43 can be extended so long that an intermediate ring 64 according to FIG. 6 can be inserted between the inner, radially flat parts, which is then suitable for accommodating a sealing ring 75, in a seat between the surfaces 38, 45 and the extension 43 of FIGS. 3 and 4. Such an intermediate ring 64 is then expanded radially to such an extent that it can withstand internal forces from fluid pressure within the elements,

FIG. 7 shows external parts of a set of elements which FIGS. 3 and 4 mount similar elements to one another. The conical parts are designated in the set of Figure 7 with 5 and 6 and have at their radially inner ends the same parts as the ring elements of the Fi guren 3 and 4. Radially outward is the radially flat outer part, which connects to the conical part 5 3, so that a further radius extension 55 can be arranged on the radially outer part of the axial extension of the element with conical part 6 and parts 34, 33, 32, 31 known from FIG. 4, which can then also be arranged with may be provided with an outer axial extension 56, so that the element with conical part 6 in the extension 57 and 58 of the element the conical part 5 is mountable.

When using the ring elements with the conical parts of FIGS. 3, 4, 6 and 7 in practice, it should be noted that the projections have considerable forces and prevent the conical parts 3, 4, 5, 6 from being pressed together. You must therefore not calculate these elements like disc springs. If you give them too large axial lifts, they can break. But they are of great importance in the creation of high-pressure units in which high axial forces of the conical parts are required. As my later priority patent application dated July 14, 1981 in the United States, number 282,990, will show, there is a subcritical and a supercritical area of the operation of ring elements in high pressure pumps. The advantage of the design with the continuations of FIGS. 4, 4, 6 and 7 with regard to the ring elements is that they shift the critical point of the transition from the subcritical to the supercritical range into higher pressure ranges. This has an important positive influence on the units for higher pressures, for example that of FIG. 6. Because it saves external cohesion means between adjacent ring elements 3 and 4. However, practice is a delicate matter of experience. Without taking into account the deformations and forces occurring in the material, it is easy to get breaks or the ring element can become so rigid that it no longer compresses the conical part axially in the desired manner.

• oder, : dass die Fortsaetze 42,43 an den radial inneren Enden zweier konischer Ringelemente 3,4 unterschiedliche Durch= messer mit ineinander passenden etwa zylindrischen Sitzen 41,44 bilden.
• oder, : dass die konischen Elemente 3,4 mit den genannten Sitzen 41,44 aneinander geleg sind,sodass die radial nach aussen konischen Teile 3, 4 voneinander fortzeigen, also achsial nach aussen gerichtet sind.
• oder, : dass die genannten achsialen Fortsaetze 42,43 so lang ausgebildet sind und ausserdem zwiwchen den genannten Fortsaetzen 42,43 und den konischen Tei = len 3,4 radial plane Auflage oder Sitzflaechen 40,45 ausgebildet sind, sodass zwischen die genannten Fla echen 40,45 ein Ring 64 eingelegt werden kann und ist.
• oder, : dass der Innendurchmesser des Ringes 64 so gross ausgebildet ist,dass zwischen seinem Innendurchmesser und einer der genannten achsialen Fortsaetze 42,43 ein plastisch verformbarer Dichtring 75 eingelegt werden kann, waehrend der Innendurchmesser des Ringes 64 klein genug bleibt, um noch eine Auflage der genannten Flaechen 40,45 auf dem innerem Teile des genannten Ringes 64 zu gewaehr = leisten.
• oder, : dass die achsialen Fortsaetze 56,57 an den radial aeusseren Enden zweier konischer Ringelemente 5,6 unterschiedliche Durchmesser haben und ineinanderpassende Aussen- und Innenflaechen zum Beispiel nach Figuren 6 oder 7 bilden.
• oder, : dass zwischen den konischen Elementteilen 5,6 und den achsialen Fortsaetzen 56,57 an den radial auesseren Enden der Elemente 5,6 radial plane Ringflaechenstuecke 55,58 angeordnet sind, die aneinander liegen und eine Ausfoermung 34 zur Aufnahme einer plasti.schen Dichtung 31,75 bilden koennen.

The ring elements now described correspond more or less to one or more of the claims and and are, for. B. defined by
that seats 3, 45 are formed on the conical ring 1 for receiving a plastically deformable seal (for example O-ring) 75;

• or, that the extensions 42, 43 form at the radially inner ends of two conical ring elements 3, 4 different diameters with approximately cylindrical seats 41, 44 that fit into one another.
• or, that the conical elements 3, 4 with the said seats 41, 44 are placed against one another, so that the parts 3, 4 which are conical radially outwards point away from one another, that is to say are directed axially outwards.
• or, that the axial projections 42, 43 are so long and, in addition, between the projections 42, 43 and the conical parts 3,4, there are radially flat supports or seat surfaces 40, 45, so that between the surfaces mentioned 40,45 a ring 64 can be inserted and is.
• or, that the inner diameter of the ring 64 is so large that a plastically deformable sealing ring 75 can be inserted between its inner diameter and one of the above-mentioned axial extensions 42, 43, while the inner diameter of the ring 64 remains small enough to provide additional support of the said surfaces 40, 45 on the inner part of the ring 64 to be guaranteed.
• or, that the axial projections 56, 57 have different diameters at the radially outer ends of two conical ring elements 5, 6 and form interlocking outer and inner surfaces, for example according to FIGS. 6 or 7.
• or, that between the conical element parts 5, 6 and the axial extensions 56, 57 at the radially outer ends of the elements 5, 6, radially flat annular surface pieces 55, 58 are arranged, which lie against one another and have a shape 34 for receiving a plastic Can form seal 31.75.

Insofar as the practical, technical and economic significance of the ring elements of the invention has not yet been fully described, this may be made more understandable by the example of an aggregate that can be realized with the help of the ring elements. Such an assembly is partially shown in Figure 6.

FIG. 6 shows a longitudinal section in the radial direction through pump parts or motor parts of an assembly, insofar as these relate to the chambers or neighboring parts, and FIG. 6 is at the same time a cross section through the shaft with an eccentric body of the assembly. The cross step through the shaft 11 is thus a radial cut and thereby at the same time a longitudinal cut through the ring elements, since these are installed radially to the shaft axis.

The unit of FIG. 6 can be used as a pump, in particular also as a high-pressure water pump or pump for gases and non-lubricating media. But you can also drive the unit through appropriate media and use it as a motor if you control the inlet and outlet means, for example, the valves 11, 12 accordingly and have a drainage flow from the corresponding media.

A test unit corresponding to the example in FIG. 6 was tested in 1981. It used ring elements with clamping according to the already mentioned patent application from July 1981. At the end of the year, this unit reached over 1000 bar pressure in the water conveyed by the unit with 75 percent volumetric efficiency. It is hoped that this technical data can be further improved.

• oder, : dass mindestens ein Ein lassventil 11 und mindestens ein Auslassventil der in dem genanntem Ringelemnt 1,2,3,4,5 oder in den genannten Ringelementen 1,2,3,4,5,6 gebil - deten Kammer 14 zugeordnet und vernunden sind,
• oder, dass das Aggregat als Pumpe ausgebildet ist, die Anordnung nach Anspruch 14 einschliesst und die mindestens eine Ringelement 1,2,3,4,5,6 nach sei ner Zusammendrueckung die Arbeitskammer 14 etwa voll auf das Volumen null drueckt, um volumetrische Pumpverluste durch Zusammendrueckbarkeit des Fluids in der Kammer 14 zu vermeiden oder zu reduzieren.
• oder, : dass das Aggregat zum Beispiel nach Figur 6 als Pumpe, Motor, Kompressor, Entspanner oder Verbrennungsmotor ausgebildet ist
• oder, : dass die innerhalb des betreffenden Konus des konischen Elemententeiles 1,2,3,4,5,6 ausgebildete Kammer 14 mit einem nicht schmierendem Fluid gefuellt ist, waehrend die Aussenseiten des Elements 1,2,3,4,5,6 von Schmier = mittel umgeben sind.
• oder, : dass das Aggregat einen Kammernkopf 7 enthaelt, in dem sich Einlassmittel 11 und Auslassmittel 12 befinden, die zu der Kammer. 14 innerhalb mindestens eines konischen Ringelemententeiles 1,2,3,4,5,6 ausgebildet ist, mindestens einem der Ringelemnente 1,2,3,4,5,6 an dem dem Koerper 7 abgekehrtem achsialem Ende ein Antriebskoerper 8 zugeordnet ist und alle der eingebauten konische Teile 1,2,3,4,5,6 enthaltenden Ringel emente (das Ringelemeht) bei Zusammendrueckung auf der der Kammer 14 abgekehrten Seite eine volle Stutzauflage 7,8 auf mindestens dem groesstem Teil der radialen Ausdehnung des betreffenden konischen Elemententeiles haben;
• oder, : dass das Aggregat als Hochdruckpumpp ausgebildet ist, eine rotierende Welle 11 In einem Gehaeuse 7 lagert, der genannte Antriebskoerper 8 mit einer rueckwaertigen durch einen Radius um eine Mitte definierten Schwenkflaeche 83 versehen ist, die in einer Lagerflaeche 84 etwa gleicher aber dazu komplementaerer Form eines Zwischenkoerpers 9. schwenkbar lagert, der Zwischenkoerper an der angekehrtem Ende eine Laufflaeche 87 bildet, die auf einer zu einem Teile des Aggregates exzentrischen Treibflaeche 88 gleitet und bei Bewegung der Gleitfloeche 88 infolge ihrer genannten Exzent rizitaet die Spannung (Zusammendrueckung) und Entspannung des minde stens einem oder der mehreren konischen Teile 1,2,3,4,5,6 des konischen Ringelementes (der konischen Ringelemente) treibt oder steuert;
• oder, dass die Kammer(n) 14 unter dem betreffendem konischem Teile des betreffenden Elementes (der betreffenden Elemente) 1,2,3,4,5,6 dem genannten Einlassventil 11 und Auslass= ventil 12 verbunden ist (sind), ein nicht schmierdendes Medium, zum·Beispiel Wasser, in sich aufnimmt und aus sich abgibt (in sich aufnehmen und aus sich abgebert), der genannte Antrlebskoerper ein Hubkolben 8 mirt radialer Auflage-und Stuetzflaeche fuer die mindestens eine konische Teil des mindestens einen Elementes ist, der Zwischenkoerper 9 ein Kolbenschuh ist, in dem der Hubkolben kolben 8 schwenkbar lagert, die Treibflaeche 88 eine zylindrische Flaeche an einem um eine zentrische Achse 85 rotierendem Exzenterkoerper 10 mit der Gleitflaeche 88 um die exzentrische Achse 86 ist, dem genanntem Kolbenschuh 9 Schmier- und Druck-Fluid durch Leitung 73 zugefuehrt und in Druckfluidtaschen 68,69 70,71 zwischen dem Hubkolben, dem Kolbenschuh und dem Exzenterkoerper 8,9,10 geleitet wird, sodass die genannten Druckfluidtaschen und die sie umgebenden Dichtflaechen (scaling lands) die Kraefte der konischen Eelemente 1,2,3,4,5,6 und die auf sie ausgeuebten Kraefte zum groesstem Teile tragen und die Rotation des Exzenterkoerpers 10 um die zentrische Achse 85 das genannte mindestens eine oder die mehreren Elemente mit konischen Teilen 1,2,3,4,5,6 pro Umdrehung einmal zusammendrueckt und auseinander entspannen laesst.
• oder, : dass der Exzenterkoerper 10 mit einer zentrischen Welle 11 oder als Teil der zentrischen Welle 11 umlaeuft, der genannte Kammernkopf 7 am Gehaeuse des Aggregates angeordnet ist, das Aggregat einen Raum 80 mit einer Fuehrungsflaeche 81 zur Sicherung des Kolbenschu = hes 9 gegen Herausfallen aus dem Raum 80 bildet, mindestens ein Element mit konischem Teil 1,2,3,4,5,6 auf dem genanntem Hubkolben 8 zentriert ist, der Hubkolben 8 im genanntem Kolbenschuh 9 zentriert ist, mindestens zwei plastiche Dich - tungen 75 dem mindestens einen die Kammer 14 bildendem Ringelement 1,2,3,4,5,6 zugeordnet sind , und die Federkraft des (der) konischen Teils (der Teile) des Ringelements (der Ringelemente) 1,2,3,4,5,6 den Kolbenschuh 9 gegen den Exzenterkoerper 10 drueckt)druecken) und die dichte Auflage der Kolbenschuhlaufflaeche 87 an der Gleitflaeche 88 des Exzenterkoerpers 10 bewirkt (bewirken) .
• oder, : dass der genannte Raum 80 mit Schmieroel, insbesondere mit Hydraulikoel gefuellt ist, gegebenenfalls unter Druck, dass das genannte Schmieroel die Elemente 1,2,3,4,5,6, den Hubkolben 8, den Kolbenschuh 9, den Exzenterkoerper 10 und die Welle 11 umgibt, aber die Pumpkammer(n) oder die Motorkammer(n) 14 innerhalb des mindestens einen(oder der mehreren) Ringelemhtes (Ringelemente) mit Wasser oder einem nicht schmierendem Medium gefuellt sind, dieses pumpen oder von diesem getrieben werden und die Auflage(n) des (der) Ringelements (Ringelemente) 1,2,3,4,5,6 mit 31,33,32, 40, 41, 42, 43, 44, 45, 55, 58 usw. oder die genannten Dichtringe 75 das Schmieroel und d as Wasser oder die beiden betreffenden Medien innerhalb und ausserhalb des Ringelementes (der Ringelemente) voneinander trennen und die mindestens eine Arbeitskammer 14 abdichten.
• oder, : dass mei mehreren Elementen achsial hintereinander eine Bohrung (mehrere Bohrungen) 65 die mehreren achsial hintereinander befindlichen Teile 14 der Kammer 14 miteinander verbindet.

The features of the unit of FIG. 6 according to the invention are described in fairly precise detail and are understandable and also defined by the fact that at least one of the conical ring elements 1.2.3.4. 5, 6 at the axial end of which is assigned a body 7 containing at least one inlet = means 11 or one outlet means 12 and a drive to the other axial end of the ring element directly or by interposing at least one further ring element 1, 2, 3, 4, 5, 6 = organ 8 for compressing at least one of the ring elements 1, 2, 3, 4, 5, 6, which also allows and relaxes the relaxation of the ring element.

• or, that at least one inlet valve 11 and at least one outlet valve are assigned to the chamber 14 formed in said ring element 1, 2, 3, 4, 5 or in said ring elements 1, 2, 3, 4, 5, 6 and are connected
• or that the unit is designed as a pump, includes the arrangement according to claim 14 and the at least one ring element 1, 2, 3, 4, 5, 6 after its compression presses the working chamber 14 approximately fully to zero volume in order to avoid volumetric pumping losses to avoid or reduce by compressibility of the fluid in the chamber 14.
• or, that the unit is designed, for example, according to FIG. 6 as a pump, motor, compressor, expansion device or internal combustion engine
• or, that the chamber 14 formed within the relevant cone of the conical element part 1, 2, 3, 4, 5, 6 is filled with a non-lubricating fluid, while the outer sides of the element 1, 2, 3, 4, 5, 6 are surrounded by lubricant.
• or, that the unit contains a chamber head 7, in which there are inlet means 11 and outlet means 12, which lead to the chamber. 14 is formed within at least one conical ring element part 1, 2, 3, 4, 5, 6, at least one of the ring elements 1, 2, 3, 4, 5, 6 is assigned a drive body 8 on the axial end facing away from the body 7, and all of the built-in conical parts 1, 2, 3, 4, 5, 6, 6 containing ring elements (the ring element) when compressed on the side facing away from the chamber 14 have a full support support 7,8 on at least the largest part of the radial extent of the conical element part in question ;
• or, that the unit is designed as a high-pressure pump, a rotating shaft 11 is mounted in a housing 7, said drive body 8 is provided with a backward pivoting surface 83 defined by a radius around a center, which is approximately the same but complementary in a bearing surface 84 Form of an intermediate body 9 pivotally mounted, the intermediate body forms a running surface 87 at the opposite end, which on one to one Parts of the aggregate eccentric driving surface 88 slides and upon movement of the sliding surface 88 due to their eccentricity mentioned the tension (compression) and relaxation of the at least one or more conical parts 1, 2, 3, 4, 5, 6 of the conical ring element (the conical ring elements) drives or controls;
• or that the chamber (s) 14 is (are) connected under the relevant conical part of the element (s) 1, 2, 3, 4, 5, 6 to the inlet valve 11 and outlet valve 12 in question lubricating medium, for example water, absorbs and releases from itself (absorbs itself and removes from itself), the mentioned body is a reciprocating piston 8 with a radial support and support surface for the at least one conical part of the at least one element which Intermediate body 9 is a piston shoe, in which the reciprocating piston 8 is pivotally mounted, the driving surface 88 is a cylindrical surface on an eccentric body 10 rotating about a central axis 85 with the sliding surface 88 around the eccentric axis 86, said piston shoe 9 is lubricating and pressure -Fluid fed through line 73 and passed in pressure fluid pockets 68.69 70.71 between the reciprocating piston, the piston shoe and the eccentric body 8,9,10, so that the pressure fluid mentioned pockets and the surrounding sealing surfaces (scaling lands), the forces of the conical elements 1, 2, 3, 4, 5, 6 and the forces exerted on them bear the greatest part, and the rotation of the eccentric body 10 about the central axis 85 does the said at least one or more elements with conical parts 1, 2, 3, 4, 5, 6 are pressed together per revolution and can be relaxed apart.
• or, that the eccentric body 10 rotates with a central shaft 11 or as part of the central shaft 11, said chamber head 7 is arranged on the housing of the unit, the unit has a space 80 with a guide surface 81 for securing the piston lock 9 against falling out forms from the space 80, at least one element with a conical part 1, 2, 3, 4, 5, 6 is centered on the mentioned piston 8, the piston 8 is centered in the piston shoe 9, at least two plastic seals 75 at least a ring element 1, 2, 3, 4, 5, 6 forming the chamber 14, and the spring force of the conical part (s) of the ring element (s) 1,2,3,4,5,6 presses the piston shoe 9 against the eccentric body 10) and causes the tight contact of the piston shoe running surface 87 on the sliding surface 88 of the eccentric body 10.
• or, that said space 80 is filled with lubricating oil, in particular with hydraulic oil, possibly under pressure, that said lubricating oil contains elements 1, 2, 3, 4, 5, 6, reciprocating piston 8, piston shoe 9, eccentric body 10 and surrounds the shaft 11, but the pump chamber (s) or the motor chamber (s) 14 within the at least one (or more) ring elements (ring elements) are filled with water, a non-lubricating medium, pump it or are driven by it, and the support (s) of the ring element (s) 1,2,3,4,5,6 with 31,33,32, 40, 41, 42, 43, 44, 45, 55, 58 etc. or the mentioned sealing rings 75 separate the lubricating oil and the water or the two media in question inside and outside the ring element (the ring elements) and seal off the at least one working chamber 14.
• or, that with several elements axially one behind the other, a hole (several holes) 65 connects the several parts 14 of the chamber 14, one behind the other axially.

It is the case that the assembly of FIG. 6 can be a motor or a pump. Since pumps are still known as motors, it is described again below as a pump, namely as a water pump. What is meant here, however, is that instead of water (Water in FIG. 6), any other non-lubricating medium can also be pumped or used as an engine driving fluid. The surrounding lubricant is designated "Oil" in FIG. 6. Should be understood. also that, when the pump is described below, the unit is and can be a motor if a pressure medium is supplied to the chambers 14 or the chamber 14 under time control in relation to the downward stroke of the reciprocating piston 8 through the inlet means 11. In the engine, the control must of course be such that there is no high pressure behind the release means 12 during the upward stroke of the lifting piston 8. For the motor, therefore, a periodic control of the fluid outside the inlet and outlet means 11, 12, which is dependent on the angle of rotation of the eccentric body 10, is required, while these can work automatically with the pump,

Those features which have already been described or defined and which represent the possibilities in FIG. 6 are omitted in the further description. The following description therefore only describes the mode of operation based on the high-pressure water pumps = version,

In the pump housing there is a rotating shaft 11 with an eccentric body 10, which forms an outer surface 88 as a piston = stroke guide surface. Her the sliding surface 87 runs of the piston shoe 9. In Pumpengehaeuse or Kamnerndeckel 7 are the inlet and outlet valves 11 and 12 with ent ⁼ speaking Federbalsungsmitteln and channels sowei holders, or sitting, namely 60.6 _1, 62, 63.13. 13 is the fluid = pressure supply line of the high pressure pump for water.

The inlet valve 11 has a valve head with a seat 60, which is designed in such a way that totarum in the delivery chamber 14 is avoided. The valve head is therefore flat at the front and sits in an inclined seat 60. The outlet valve 12 is correspondingly close to the working chamber 14, so that no large dead space can form in the line to the outlet valve 12. Dead space is avoided in the chamber 14, since dead space causes internal compression in the fluid at high pressures and then the unit can no longer work effectively with many hundreds or a few thousand bars if dead space remains in the pump chamber 14. The ring elements of the invention and the parts assigned to them are designed in such a way that totarum is avoided or limited to an inevitable minimum volume.

In the housing, a corresponding housing part forms the space 80 for at least partially accommodating the pump parts. It is preferred to attach a guide or holding or securing surface 81 which delimits the individual space 80.

FIG. 6 shows only one of the spaces 80 with only one pump system in it. In practice, however, the pump has several rooms or pumping systems, for example 5.7, etc.

The piston shoe 9 is provided in the exemplary embodiment with the guide fingers 67, which always remain within the securing wall 81 of the recess 80, so that the piston shoe cannot fall out of the space 80. With this arrangement, a positive connection between eccentric body 10, piston shoe 9 and reciprocating piston 8, and the ring elements can be avoided. This makes the unit simple, cheap and reliable.

When the shaft 11 rotates about the axis 85, the central axis, the piston shoe is driven upwards, radially outwards for half a turn, since the eccentric body 10 forms the guide surface, piston stroke guide surface 88 eccentrically to the central axis 85, that is to say the surface 88 is a cylindrical surface about the eccentric axis 86. On the other half of the shaft rotation, the ring elements press the piston shoe 9 radially inward as they relax under the tension of their conical parts 1, 2, 3, 4, 5, 6 so that the running surface 87 of the piston shoe 9 is firmly pressed open at all times the piston stroke guide surface 88 rests.

Since the piston shoe performs a pivoting movement during the rotation of the shaft and thus during the radial inward stroke and outward stroke, a lifting piston 8 is arranged between the piston shoe 9 and the ring elements, which in turn has a swinging surface 83 in a swinging bed 84 at the other end of the piston shoe 9 pivoting = bar is stored. At the end facing the ring elements, the reciprocating piston is provided with a radially extending bearing surface which, when the adjacent ring element is fully compressed, supports the relevant ring element fully axially so that it cannot bend in the chamber 14 at high pressures. However, centering is also provided, for example as a recess, with which one of the axial extensions of one of the ring elements in the reciprocating piston or on it can be supported and centered. It is important, as 66 shows, that the chamber 14 must be closed from the reciprocating piston or to the reciprocating piston 8. The housing or commercial head of the chamber 80, which can also be a cover, has a corresponding surface for the secure mounting of the ring element adjacent to the head 7. The chamber 14 is also sealed from the head 7, for example by a seal 77 and the surface facing the adjacent sealing element, so that it fully supports the adjacent ring element axially when the ring elements are fully compressed. Again, so that the ring element cannot bend under high pressure in chamber 14. The intermediate rings 64 in the same way prevent the bending of adjacent ring elements under high pressure in the chamber 14 by pushing the adjacent ring elements 1, 2, 3, 4, 5, 6 when they are fully compressed.

In FIG. 6, three ring elements of FIG. 3 and two ring elements of FIG. 4 are installed in space 80. They are assembled into pairs from elements of FIGS. 3 and 4, as already described with reference to FIGS Seals 75 are inserted. The upper ring element does not form a pair, since it rests on the cover 7 as a single ring element. During the suction stroke, the piston with the piston shoe (8, 9) still runs under the relaxation suspension of the conical elements that are arranged in room 80. The element parts have in Figure 6 no reference numerals, since they have already been described with reference to Figures 3 and 4. FIG. 6 shows the lowest position of the reciprocating piston and the piston shoe, that is to say parts 8 and 9, in which the chamber (s) 14 have the greatest volume. After the pump pressure stroke has been completed, the axial inner sides of the pairs of ring elements lie directly against one another without an intermediate space, the lower ring element with the rear side on the support surface of the piston 8 and the inner surface of the upper ring element then lies closely against the end face of the head 7 without any space .

Lubricating oil is normally passed into room 80 and into the interior of the housing so that the drive parts and the ring elements do not rust on the outside. Inside they can be coated with rust-free layers or overlays,

Because of the often very high pressures in the chambers 14, which, as already reported, can be at or above 1000 atmospheres, the piston shoe is provided with hydrostatic pressure fluid pockets 70, 72, 71, 68, 69 which are provided by a pressure fluid supply line, for example 73 , for example, are fed from the axial end of the piston shoe 9 and which carry the radial forces on the piston shoe, the eccentric body and the reciprocating piston, that is to 8,9,10 together with the sealing surfaces and wings surrounding them and friction between these parts save up. The fluid pressure in the hydraulic oil in the pockets 68 to 72 is often similar to that in the chambers 14. The lubricating pressure pump therefore often follows the construction parts of the main pump, but in smaller dimensions. Corresponds to the dimension of the pump of Figure 6 on a scale of 1 ₁ 1, then forces of many tons can occur on the piston shoe, which are then often taken up to 98 or more percent by the pressure pockets, together with the mentioned sealing surfaces and wings .

The unit of FIG. 6 has many practical applications, for example it is used as a water pressure pump for water jet cutting systems. In addition, for rinsing the bite devices in tunnel stone drilling units, in which 1000 bar pressure in the water jet multiply the service life of the cutting teeth. It is also used for the spraying of asphalt markings, as well as for the high-pressure injection of fuels in engines, It is also intended to be used for injecting water into internal combustion engines,

The unit also replaces tons of previous pressurized water systems from Water-Jet cutting systems by building a small radial piston unit with a diameter of just under 400 mm. The testing and application of the unit and the ring elements has only just begun and therefore further training and applications are not excluded. Figure 6 is one of many aggregates that are made possible by the invention.

In FIG. 9, the ring element pairs consist of fiber materials, for example carbon fiber, the pairs being glued to one another, for example by means of epoxy resin. The elements 1 and 2 are flattened at their outer ends for the purpose of connection with epoxy resin, that is to say expanded radially so that they are glued together in the connection area, adhesive area 23 and form the pump chamber 61 between. The radially inner ends of the elements 1 and 2 are also flattened, that is to say provided with radially inwardly extending flat parts, the upper pair 1, 2 being connected to the lower pair 1, 2 by the connecting surface, adhesive surface 24. This execution of a set of the conical elements of the invention is particularly handy, easy to manufacture and cheap. The handiness arises in particular from the fact that one can glue a number of such element pairs directly to an element column by means of the inner bores or recesses 35, so that the column is then a finished installation piece with large pump or motor chambers 61 and large pump - or motor - stroke allowed. The fiber is very durable. The durability of the glued seams 23, 24 is determined by the radial expansion of the flat ring parts, because the gluing is parallel to the dimensions of the gluing surface, for example with about 8 kg per square meter = three millimeters, while the fibers of the elements are up to 300 kg per square meters of firmness. There are still such fibers in development in Japan that will still achieve twice the durability. The conical shape results from shapes in conical shapes in which the fibrous materials are inserted and coated with epoxy resin or other compounds and then dried.

It is explained on the basis of FIG. 10 that there is a subcritical and a supercritical range of the use of the elements as pump or motor elements. In the subcritical range, the pressure of the working fluid in the relevant chamber, for example 61, is so low that the clamping force of the elements is stronger than the fluid pressure exerted on them. The chamber 61 remains closed in that the element or the element keeps the chamber closed under pretension even when the element pumps or is used as a motor element. When the fluid pressure in the chamber 61 reaches a certain level, namely the critical pressure, the fluid pressure is so high that it compresses the element in question somewhat and your seal to the adjacent part more fully exists, some leakage of fluid then escapes between the element in question and the neighboring part, for example the pump head or the second, the neighboring element out of the working chamber 61. The pump or motor leaks at critical pressure. The height of this critical pressure depends on the preload, the thickness and the radial dimensions of the element in question. The material can also be important.

In order to make the working chamber 61 safe and leakproof for the critical pressure and the higher pressure above it, FIG. 10 forms a fluid-flowed unit with conical elements for the supercritical range, that is to say for the pressure range which lies above the critical pressure.

This unit for the supercritical range consists in that an outer ring is arranged in which a plastic seal 7 is inserted. The conical elements 11 and 12 have on their outer parts (radial outer parts) a radial plane surface, which is placed on the relevant axial end surface of the outer ring 8. If only a single element is used as a working unit, as for example in FIG. 29, then the relevant flat surface is firmly screwed onto the pumps or motors head 48 by means of a holder 91 on the radial outer part of the element. The working chamber 61 is then sealed by the relevant plastic seal, for example by the O-ring 7, as shown in FIG.

If, however, one or more elements are used in the unit - pairs, as in FIG. 10, then the two elements 11 and 12 with their chambers 61 are assigned to one another, placed on the radially flat surfaces of the outer ring 8 in question and by means of a holder 9 on the radial ones Wrapped around external parts and firmly connected so that the flat surfaces of the elements remain firmly placed on the flat end surfaces of the outer ring 8. Because of the radial deformation when the elements 11, 12 are pressed together in the axial direction, a small radial space 18 is left radially outside the elements 11, 12, to the adjacent inner wall of the recess in the holder 9, so that the holder 9 has the radial extent in the axial direction Compression of the elements 11, 12 does not interfere. The holder 9 must be very strong for high pressure in the fluid in the supercritical range. It may exceed the thickness of the elements 11, 12 and its radially outer part must have a minimum radial thickness, so that the holder 9 does not bend or break under the high pressures in the fluid in the chamber or chambers 61. In order to avoid internal compression losses in the fluid, which reduce the efficiency, an inner ring 6 is usually inserted, which has a bore for connecting the adjacent chambers 61 and which advantageously corresponds to the thickness of the outer ring 8 in terms of thickness and efficiency. In practice, the outer ring 8 and the inner ring are leveled together, for example face-ground. In practice, the radial dimensions of these rings are planned so that the 0-ring 7 fits in between them.

Under the high pressure in the fluid in the supercritical range, the elements would bulge axially. It is therefore expedient to prevent such bulging by placing the bearing rings 10 on the outer ends of the pair of elements or one of these bearing rings 10 on the element 11 or 12 in question. The elements may have radially inner, axially axially extending cylinder parts 5 with bores 13 and seat surfaces 15, 16. In this you can again insert a plastic seal, for example an O-ring and nest between, and you can also design the dimensions of the seats so that a seat 15 of one pair of elements can center in the seat 16 of the adjacent pair of elements and can hold.

In FIG. 11, elements 1 and 2 of a pair of elements are shown in a separate representation. Here one can clearly see the radial flat surfaces 3 on the radially outer part, with which the elements are placed on the flat end surfaces (axial end surface) of the outer ring 8 of FIG. 10. In addition, FIG. 11 also shows the alternative uniform elements, that is to say the use of uniformly dimensioned and shaped elements with the same inside diameter 25 in order to be able to assemble any number of elements into an element column. For this purpose, according to FIG. 11, the inner insert centering pieces (rings) are used, one of which has the seats 16 and 27 end of the middle part 19 and the other has a cavity with a seat 29 for receiving the seat 27 of the other centering ring of the other Couple. At the end of the main part 20, this second one of the centering rings has the seat 28, which fits into the seat 25 of the relevant element 1 or 2. If these insert centering rings are inserted between two adjacent elements which form chambers 61, then they must have bores or channels in order to connect the relevant fluid-receiving and dispensing chambers 61.

Figure 12 shows part of a high pressure pump for non-lubricating or rust-causing materials, for example for water. In the pump body 48, the pump cylinder for the non-forging medium, which is called water below, is located in each of the figures. Pump head 48 contains the inlet valve 50 and the outlet valve 49. The valves are mostly spring-loaded, for example with a spring 51. In the cylinder 61, the piston 58 reciprocates. Since it contacts the non-lubricating medium and the running surface in this water will rust and not would lubricate, the piston 58 is provided with the seal 62 near the cylinder 61. Piston 58 is held by means of a connecting bolt 70 with a head 64 and a base 71 at a piston piston 59, on the rear end of which the pump piston 58 rests and is sealed by means of a seal 72. The pin or the holder 71 connects the two pistons 58 and 59 to one another via the bolt 70 and holds them together in a force-locking manner. As a result, the pump piston 58 is reciprocated together with the drive piston 59, the pin 70 the lower tensile force or compressive force during the suction stroke and the support of the outer axial ends of the two pistons 58 and 59 on one another the greater force during the pressure stroke from the drive piston to the sealing piston or pump - Piston 58 transferred. The connecting bolt 70 is also sealed by means of a plastic seal 72 against at least one of the pistons 58 or 59. The pressure stroke is driven by the rotating eccentric ring 55. The pivotable piston shoe 52 runs with its running surface 57 on its outer surface 56. The piston shoe 52 is inserted between the driving piston 59 and the eccentric ring 55 and is pivotably mounted on the piston 59 . From channel 68, lubricating fluid, for example oil, is passed into chamber 67, which surrounds the outer axial end parts of the two pistons 58, 58, so that these piston ends dip into and reciprocate in them, from where the lubricating fluid through channels 74 into the sliding surfaces between the Piston shoe 52 and the eccentric ring 55, and in the swivel surfaces between the piston shoe 52 and the Treubkolben 59 is passed. It also enters corresponding pressure fluid chambers 73, if such are arranged. The drive piston is perfectly lubricated and can run well. From the chamber 67, however, the lubricating fluid also enters the punging gap between the pump body 48 and the sealing piston and pump piston 58. As a result, this piston is also lubricated almost over the entire length, at least when the seal 62 is arranged near the chamber 61, that is to say at the inner end of the piston 58. So it is in the of Figure 12 drawn. FIG. 12 therefore provides good lubrication of the running surface of a piston in a cylinder even when the piston pumps water or a non-lubricating medium. However, since the seal 62 occasionally wears or leaks with such media, in particular if high pressure is pumped from, for example, 1000 to 4000 bar, the drainage groove 66 with the mixed fluid collection chamber 65 is also arranged according to the invention. The chamber 65 surrounds a part of the middle part of the pump piston 58. If dirty or non-lubricating fluid escapes from the cylinder 61, this runs into the collecting chamber 65 and flows from there through the line 66, so that the space 67 remains filled with clear lubricating fluid . Because in chamber 67 the water cannot enter because the chamber 67 is filled with a higher pressure than the outlet channel 66. The inventive example of FIG. 12 therefore creates lubrication of the pump piston by means of the arrangement of a second piston and a lubrication chamber In addition, the example can create a drain device for the drainage of leakage fluid, whereby mixed fluid is drained and the two fluids water and oil are kept clean in their respective chambers.

FIG. 13 again shows a pump or motor unit with conical elements, pump head 48, valves 49 and 50, and a drive 55 and a piston or shoe 52. The special feature of this exemplary embodiment of the invention is that here the centering rings with support bodies 41 are united and, on the other hand, the inner rings are joined to the outer rings 43, 44 with the centering cylinder pieces projecting from both ends. The middle centerpieces are labeled 45, 46 and they are located on the support body. 41, while the outer centerings are designated 43.44 and are located on the filler body 42. Bores 13 for connecting the chambers 61 are arranged again and the elements 1 and 2 are each nested between two parts 41 and 42, or they touch the centering seats and surfaces 47, 53 in the head 48 or in the piston or shoe 52 in addition to one of these parts The other item numbers show parts known from FIG.

The example of the invention in FIG. 14 shows the pump body 48 with the pump cylinder 61 in which the pump piston 60 reciprocates. Inlet and outlet valve 49.50 are arranged again. The pump piston is here provided with a foot 86 with centering 85, on which the pressure spring 84 is mounted, which pushes the piston 60 out of the cylinder 61 during the suction stroke pulls out. It itself is advantageously mounted on a recess surrounding the cylinder 61 or in an annular groove 83, because this spring must be long in order to deliver a large piston stroke with a long service life. The outer end of the piston foot is radially flat to form a bearing surface for the driving piston. The driving piston 59, which drives the pressure stroke of the pump piston 60, is reciprocally mounted in a guide 148 and has a head with the pivot surface 76 with which the piston head is pivotably supported in the pivot bed with the pivot surface 75 of the piston shoe 52. The running surface 57 of the piston shoe hes 52 runs on the running surface 56 of the eccentric ring 55, as a result of which the driving piston 59 receives the pressure stroke via the piston shoe 52 and transmits this via the bearing surface of the piston foot 86 to the pump piston 60. The piston shoe has guide parts 81 with guides 79, in which it is guided in the recesses 80 of the guide 148 in order to prevent the piston shoe 52 from falling away from the piston 59 and nevertheless to enable a long piston stroke. The space between the pump body 48 and the guide body 148 is advantageously = again filled with lubricating fluid in order to allow good lubricated running of the two pistons 60 and 59 at least for a certain period of life.

FIG. 15 shows how one can advantageously insert or vulcanize a seal 38, for example an O-ring, into a groove 37 of the radially outer part of an element 1 in order to ensure a good seal of the element 1 on the piston, pump head or the described Ausoen = ring.

FIG. 16 shows the corresponding arrangement or vulcanization of a plastic seal (ring) on the radially inner part or end of the element 1.

FIG. 17 shows part of a Ratew pump arrangement for very high water pressures in a longitudinal section. This arrangement works in the supercritical, high pressure range. In the pump head 48, the connection 122 leads to the inlet valve 50 and the outlet channel 123 to the outlet valve 49 with spring 51. The inlet valve advantageously has spring 88 nested in piston 40, for example in its annular groove 88. A narrow ring groove, therefore, so that internal compression = losses are avoided. Between the piston 40 and the head 48, the pair of elements is substantially formed according to Figure 10, inserted. 17 shows the outer ring 8, the inner ring 6, the sealing ring 7 and the conical elements 1 and 2, the piston 40 is pivotable on the pivoting bed of the piston shoe 52 and in the exemplary embodiment of the figure it is secured against rotation by the pin 87 which projects into the bore to the outlet valve, so that the compression spring of the Inlet valve 50 can still be turned away from the inlet valve 50. The piston shoe 52 is arranged between the eccentric part 55, on the eccentric sliding or guide surface of which it lies and runs, and the piston 40. The shaft around the axis 97 carries the eccentric part 55 and its eccentric running surface generates the piston stroke when the shaft is circulated in the bearings 114 which are arranged in the housing 130, the shaft with the axis 97 is from an electric motor, internal combustion engine, or , as in the case of Figure 17 driven by a hydraulic gate in the housing 48. This motor has, for example, the control 120, the cylinders 116, the pistons 117, in the rotor 113, the piston shoes 119 and the piston stroke guide 121 in the housing 148. The mode of operation of this motor can be found in the inventor's patents, for example in De BP 25 00 779. The bed surfaces, swivel surfaces, bearing surfaces and running surfaces or piston stroke guide surfaces of piston 40, piston shoe 52 and eccentric ring 55 are lubricated by lubricating fluid, hereinafter referred to as "oil". Due to the high radial forces, pressure fluid pockets 73 are also arranged, which carry most of the radial load on the piston and shoe. The surfaces and pressure fluid pockets mentioned are fed with pressure oil from the pressure oil chamber 130 via channels 74. The pressure pistons axially press in the piston shoe 52 and seal the transitions of the channels 74. At the other end, a pressure bearing plate 115 or a further pressure piston 96 may be arranged axially movable in a pressure chamber 95. While a pump unit is shown in FIG. 17, in practice the unit of the figure mostly has 3, 5, 7 or 9 pump chambers 61, pistons 40, pairs of elements 1, 2 and piston shoes 52 with the corresponding pressing bodies 96 and valves 49 and 50 in corresponding number of pieces. The suction or supply channels 122 are usually connected to one another. In practice, the drain or delivery pressure channels 123 are usually combined to form a single delivery channel.

In FIG. 17 the following further special feature according to the invention is shown, which is further illustrated by the partial figures 18, 19 and 20

When elements 1 and 2 are pressed together, the radial diameter of the elements changes. They get a bit smaller inside, but a bit bigger radially on the outside. It is therefore not always possible in the case of onical elements to clamp them together by means of the clamping ring arrangement according to FIG. 10 on the outside diameters. Because the ring 9 of FIG. 10 expands radially less than the elements 1 and 2 due to its thickness, the ring arrangement 9 according to FIG. 10 cannot and does not follow the radial expansion of the elements 1 and 2 for very high pressures and deflections prevents these elements from free radial expansion. According to the invention, the ring parts 89, 90 and 91 of FIG. 17 are therefore cut into segments 32 A, B, C, etc. according to FIG. 17 with the parts in separate partial sections FIGS. 18 to 20. This is clearly visible in Figure 18. You first press the rings, drill the holes and cut the threads and then cut the rings into radial segments using disc milling. Occasionally, however, the segments are also produced as segments right from the start. For this purpose, the elements 1 and 2 advantageously have the recess ring grooves 30 on their radially outer parts, in which the clamping fingers 31 of the upper and the lower clamping ring 89 and 91 engage. This prevents the ring parts or segments of the rings 89, 90, 91 from sliding radially away from the elements 1 and 2. It should be noted that the locations at which the grooves 30 are machined are those stiffeners of the ring elements 1 and 2 at which they experience the lowest internal stresses when they are axially compressed. The groove 30 weakens the elements somewhat at the drawn and expedient point on the radial outer part of the elements 1 and 2, but this is not harmful to the life of the elements 1 and 2 at these points, because in spite of the grooves 30 they remain at these points experience lower internal bending stresses (tensile or compressive stresses) than at the radially inner and outer tips of elements 1 and 2. The middle ring is mostly plane-ground so that it is the axial number of the outer ring 8 in the Achsiolhoeche (Figure 17) and corresponds to the two elements 1 and 2 in order to ensure precise relentless axial clamping of the elements 1 and 2. The three rings are advantageously screwed together by screws 92, the tightening force being measured with a torque meter in order to achieve full tension. The middle ring or spacer ring 90 of the clamping arrangement 89-91 advantageously has an inner annular groove 93 for receiving the outer ring 8 Figure 10. Because without this ring groove, the outer ring 8 would thin in the radial direction, so that it would expand too much radially under the high internal pressure in the trough in the chamber 61 and thus cause internal compression losses and pumping losses. Or, on the other hand, the tensioning screws 92 would be too far away from the tensioning and holding fingers 31, so that the tension would lose its effectiveness as a result of axial compliance. The plastic seals 39, 40 in FIG. 17 are arranged between the piston 40, the head 48 on the one hand and the elements 1 and 2 on the other hand.

The unit in FIG. 17 thus already forms a rather ideal pump or motor unit for the supercritical range of the extremely high pressure in the fluid. The elements 1 and 2 can expand and contract radially freely, since the segments A, B, C ― X, Y, Z of the rings 89 to 91 ideally follow this radial expansion and contraction.

In FIG. 21, the rotor 98 has recesses, for example bores 107. The seats for elements 1 and / or 2 or for element columns 1, 2 bil. The elements 1, 2 have advantageously plastic seals 37, 38 between FIG. 16, for example, between their radially outer supports, and also advantageously, at their radially inner ends, plastic seals 39, 40, for example, such as FIG. 16, the piston or the pistons 36 have piston fingers that enter the chambers 61 and can also center the elements 1, 2 on one another. The pistons 36 carry the piston shoes 21 pivotably in pivoting pans. The piston shoes 21 run on the inner surface 156 of the piston stroke guide 99, as a result of which they form the piston stroke guide surfaces. The piston shoes have pressure fluid pockets with sealing gaskets surrounding them as hydrostatic bearings with pressure relief pockets 112 and such pressure fluid pockets 111 are also advantageously arranged between the socket in the piston and the swivel surface of the piston shoe. The pressure fluid pockets are fed from the working chambers 61 through channels 74 with pressure fluid. A distance is arranged between the axis 103 of the rotor 98 and the axis of the piston = stroke guide surface 156, so that the piston stroke = guide surface 156 is eccentric to the rotor axis 103, so that when the rotor 98 or the piston stroke guide 99 rotates, the piston stroke of the pistons 36 and the piston shoes 21 arises, the elements 1 and 2 periodically compressing and relaxing and thereby periodically enlarging and reducing the arbelts = chambers 61 once per revolution.

The fluid supply and discharge to and from the working chambers 61 takes place with the arrangement of rotor channels 161 by axial fluid flow or by internal radial fluid flow. For example, by entering fluid from channel 105 of control shaft 102 via control window 150 into channels 161 and from there into working chambers 61 and channels 74 as the pressure fluid pockets 11, 112 flow in and out of these through the corresponding further channels 161. Control window 149 in control body 102 and which flows through channel 106. However, an external radial flow is also possible such that the piston stroke guide receives a channel 101 through which fluid from the space between rotor 98 and piston stroke guide 99 or from a container connected to channel 101 through the pressure fluid pockets 112 and channels 74 into the Working chambers 61 flowing. The particular advantage of the unit according to FIG. 21 is that, in the case of multi-element columns with elements 1, 2, long working chamber lifts of the chambers 61 are permitted, thus allowing a large flow rate in a small space. In addition, this unit is particularly simple and inexpensive to manufacture, since it does not require any pistons with a tight fit and is therefore simpler and cheaper than the conventional radial piston units with pistons which are tightly fitted in cylinders and are provocative therein. However, this unit is only for the subcritical, low pressure range in the fluid if it has no clamping arrangements according to FIGS. 10 or 17. It is converted into a high-pressure unit for the supercritical high pressure range by assigning elements 1 and 2 clamping arrangements 9, 89 to 91 of FIGS. 10 or 17.

FIG. 27 shows an element 1 or 2, here with 307 in a half radial section, approximately natural size for the supercritical high pressure range. This figure is given in order to show the annular groove 358, which corresponds to the groove 30 in FIG. 19, particularly clearly and, above all, to show that the inner flange surface 359 and the outer plane surface 354 must be arranged. The surface 359 for storage on the piston, the pump head or the element of the next element pair or the next element and the surface 354 for storage on the outer ring 8 of FIGS. 10 and 17 or for storage on a piston or pump head of one of the figures or one aggregates not shown in the figures. In order to reduce the internal tension and thus the risk of breakage of the elements, the inner edge 357 is advantageously rounded,

Figure 28 describes another problem. If the elements have no flats 359, 354, then they are common disc springs and then lie on a line. At the high pressure in the supercritical pressure range, this receives a pressure of many thousands of kilograms per square millimeter, namely an infinitely high internal tension because the line of contact does not form any surface at all, not even a total area of one square millimeter. The material melts away under this infinitely high tension in the material. The libnie deforms and damages the surface and the outer layers of element 1 or 2. The flattening to the flat surfaces 359,354 reduces this danger and appearance, but does not completely eliminate it. It is therefore advantageous, in order to further limit this phenomenon, to provide the support counterpart 360 with a bulge 355, which is shaped and dimensioned such that the edge of the element 1 or 2, here designated 307, slides on it during radial expansion and Contraction under the axial collapse and expansion of the element 1,2,307. The shape should also be such that at least approximately the line support is converted into an approximate surface support. If the axial assembly is only in size according to angle alpha, then the counter bearing receives a bearing surface in the WinKel beta, so that after successful compression, the entire element 1 or 2 lies well on the support 360 and cannot bulge axially. After the working chamber 307, a sealing surface (layer, sheet metal) 309, for example made of copper, Teflon, etc., is placed on the element 307, so that it is not affected by the rust-causing fluid. The plastic seal 356 is arranged accordingly, it being expedient for it to encompass the sealing layer or protective layer 309. The tip of element 1 or 2.307 must not lift off the support 360 and curve 355 too much so that the seal 356 or 309 cannot enter the gap. In the high-pressure practice, the tip must not stand mm as o, o ₀ 3 to 1 more. Otherwise the seal 356 becomes a thin black paper layer which enters the gap and destroys the seal. While the seals in FIG. 28 are hatched, the seals 356, 309, 317, etc. in FIG. 22 are not drawn hatched, but are left open without lines, because FIG. 22 would become too indistinct by hatching lines.

FIG. 22 shows a particularly effective and particularly high-pressure unit capable of the invention, and a particularly important finding of the invention is described on the basis thereof.

It is namely the case that elements 1 and 2 of FIGS. 10 or 17 plate springs are similar and therefore can only be used for limited high pressures. After this current invention, it is recognized that conventional plate springs are absolutely unsuitable for effective use in the high supercritical pressure range, because they break after only a short operating time. The cause of the cracking could not be found because the plate springs still have the formulas were calculated by Almen and Laszio. These Americans published a math for the calculation of the internal stresses in disc springs in 1935, which was later summarized in Germany. After this summary, it became easier to calculate, but the deeper connections, which were still clearly recognized by the pastures and Loscio, were lost. The disc springs and their stress calculations were later standardized in DIN and JIS (German and Japanese Industry Standards). According to this standardization, elements 1 and 2 should have a long service life if the standardization, i.e. the standard sheets, is observed.

After a long search, the current invention has recognized that the standard beds and the standards DIN and JIS are absolutely impossible and unusable for the calculation of the lifespan and the stresses for elements 1 and 2 according to this invention.

On the right in FIG. 29 you can find the calculations according to Imen and Lascio, which are more precise and extensive than those according to DIN and JIS. The curve 361 in FIG. 25 shows the greatest stresses sigma within element 1 or 2 as a result of the compression above the Circulation angle alpha of the eccentric ring of the piston stroke drive. This calculation is based on that of Almen and Lasczio.

The invention now recognizes that the high film pressure in the supercritical range causes a much higher bending stress and a much more sudden bending stress within the element 1 or 2. It is this tension that causes the elements of FIGS. 10 and 17 to break quickly, even after 45 minutes at an internal pressure of 1000 bar, if they are approximated in radial dimension to the disk spring.

The invention recognizes that these further internal stresses in element 1 or 2 result from the fluid pressure in chamber 61. This fluid pressure is shown by means of the arrows "q" in FIG. 23 and it the additional bending stresses sigma B shown in FIG. 23 around the center point "O". In the supercritical, high pressure range, these bending stresses are many times higher than the internal stresses of the disc springs after breathing and Lascio, which are simply labeled "sigma" without "B" in the figures.

The invention has now recognized this previously unknown cause of the disc springs breaking very precisely and mathematically very precisely. This can be seen from FIG. 23 which, according to the inventor, records the moments and tensions differentially and integrally. Figure 23 gives the exact geometric and mathematical relationships, as well as their integrations with the help of the differential and integral calculation. Based on equation (1), the approach of the bending moment under fluid pressure, the mathematics finally leads to formulas (12) and (13) with the values of the stresses. The indices "I" and "o" after the indent "B" show the meaning whether they have been viewed radially from the inside or radially from the outside.

In FIG. 24, it is demonstrated methematically and geometrically where the radii of the same stresses lie when one starts to calculate radially from the inside or from the outside, that is to say from the outside radius or inside radius of the element. The values "Rmc" and "RMC" show the bending moment under fluid pressure without considering the tensioners or bearings, while the values "RCMH" and "Rcmh" take into account the moments with brackets or supports. The extensive calculations and investigations can be found in the extensive Rotary Engine Kenkyusho reports RER-8109 and RER-8206. One can see from FIG. 24 the final calculation form in accordance with the piff erentations and integrations, and one also sees that these values all deviate from the orithmetic mean radius "Rm" and also from the pressure point radii according to the inventor's control body patents , for example from the Rgc value of the inventor's De-Patent 23 00 639. This is due to the fact that the center points of the area apply to the control body, whereas here in the unit with elements 1, 2 of the invention it is not the area values but the fluid pressure moment values that apply.

The invention recognizes from this that conventional disc springs = areas for use as elements 1, 2 are only possible and usable for low pressures. The elements according to the invention must therefore still meet the condition for the supercritical high pressure range that the difference between the inside and outside radii of the elements is more than three times smaller than the outside radius of the element 1 or 2 in question. In the figures for high performance = aggregate, FIGS. 22 and 29, the fluid pressure working range of this radial radius difference is approximately five times smaller than the outside = radius of the element in question.

If one looks at the breathing and Lascio equation in FIG. 29, then, according to the knowledge of the invention, the difference "(C minus eta)" below the fraction has the most important meaning. It follows from this that the internal stresses "sigma" become smaller the larger the diameter of the element 1 or 2, while the thickness, radial difference and the angle of attack or deflection of the element are otherwise constant. In order to make the element usable for the supercritical range of high pressure for a long service life, one must make the radial difference very small, for example about ten millimeters, the deflection "f" also very small, for example below 0, 5 millimeters and make the element very thick, for example 5 to 10 millimeters, in order to keep the bending stresses "Sigma B" still low according to FIG. 23 of the invention and at the same time also to make the diameters and radii large by small stresses "sigma" Alms and Lasczio according to Figure 29.

However, according to the knowledge of the invention, the problem arises that the radial loads then become so large under the high fluid pressure in the chambers or in the chamber (working chamber) 61 that there are no longer any rolling bearings which carry these loads with a sufficient service life Could bear in tolerable dimensions. The invention thus recognizes that neither conventional disc springs nor conventional rolling bearings in the standard series can provide any useful elements with a long service life for motor or pump units for the supercritical range of high pressure, in short, that the previous technology does not provide motors or pump units for can create the supercritical area with the high pressures contained therein.

Therefore, in FIG. 22, a first piston 302 is reciprocally arranged in the cylinder, the first cylinder, 301, around a fluid pressure column, which is mostly hydra-oil, but can also be another fluid, is conveyed through the channel 303 into a second cytinder 304 of larger diameter and onto which the Second cylinder reciprocable second piston 305 presses. The second piston 305 carries the element 307, compresses it axially and thus conveys the pressure medium out of the working chamber 311 through the outlet means 313. Several elements 307 can also be arranged and clamped together by brackets or clamping arrangements 318, 320, 321, 319 and held together. When the first piston 302 moves outward in the first cylinder 301, the pressure fluid flows out of the second cylinder 304 through the connecting channel 303 between the first cylinder and the second cylinder First cylinder 301 back. So there is periodic transport of a pressure fluid pack from the first cylinder to the second cylinder and then back from the second cylinder to the first cylinder. The second piston periodically oscillates in reverse, parallel to the first piston. If the first piston is pushed into the first cylinder 301, then the second piston 305 is pushed outwards in the second cylinder 304 and vice versa, if the second piston, for example, presses in under the relaxation pressure of the element (elements) 307 in the second cylinder, then the first piston in the first cylinder is pressed out. In practice, this happens in that the first piston 302 is forced to a piston stroke by a piston stroke drive 336, for example via a piston shoe 334. For example, the piston stroke guide 336 rotates in the bearings 338, so it rotates in the bearings 338. In addition, the piston stroke guide may be driven for rotation by the drive 345 346, for example, by an electric motor, combustion motor or fluid motor. For example, if the inner surface 347 of the piston stroke guide 336 is arranged eccentrically to the bearings 338, so that the bearings 338 have a central axis, but the inner surface 347 has an eccentric axis that is parallel to the central axis but radially distanced from it When the piston stroke guide 336 rotates, the eccentric piston stroke guide surface 347 causes a radial stroke by the sliding surface of the piston shoe 334 on it, which the piston shoe 334 transmits to the first piston 302. The first piston 302 is moved in and out once in the first cylinder 301 per revolution. This radial movement of the first piston, namely the piston stroke of the first piston by means of the channel 303 and the fluid column between the first piston and the second piston, is reversely transmitted in parallel to the second piston 305. In practice, the e _r stzylinder 301 and the Erstkolben 302 obtains a smaller diameter and the second cylinder 304 to the second piston 305 a substantially larger diameter. This makes it possible to keep the radial forces of the first piston 302 so low that standard roller bearings 338 can still be used for the piston stroke guide and still have a sufficiently long service life. In this arrangement according to FIG. 22 of the invention, the second piston 305 does not require any roller bearings. The big problem is that for the high forces of the second piston 305 there are no longer any commercially available rolling bearings, which completely overcome the tens of tons forces of the second piston with a rotating camshaft or a rotating eccentric ring, as in FIG. 17. First pistons and second pistons now run in Figure 22 in non-rotating, solid, stable bodies with stationary first and second cylinders 301,304 in it. In the example in FIG. 22, the first cylinder with the first piston is a radial arrangement, but it could also be an axial arrangement. The second cylinder and the second piston could also be a radial arrangement, as shown in FIG. 17, but in FIG. 22 they are an axial arrangement. This makes it possible, for example, to arrange 3, 5, 7, 9 or any other number of axial cylinders around the central axis 330 of the unit and to arrange the corresponding number of first cylinders and first pistons. It should be borne in mind that at least one first cylinder must be connected to a second cylinder through the connecting line or the connecting channel 303. In the case of a plurality of first cylinders and second cylinders in the unit in FIG. 22, separate first and second pistons each oscillate, without these having to be connected to other first or second pistons. The channels 303 must remain unconnected with other first and second cylinder arrangements. Each first-second piston arrangement in a common housing thus has a pressure-fluid column in a channel 303 which vibrates independently of other fluid columns and which projects into the connected first and second cylinders, but not to other ones of the first and second cylinders of the unit may be connected. However, this does not exclude that, for example, two or more first pistons can or can work together with a single second piston and corresponding cylinders.

It is also possible to make the operation of the unit according to FIG. 22 continuously variable, that is to say to make the piston stroke of the first piston and, as a result, to make the piston stroke of the second piston infinitely variable. For this purpose, the drive from drive 345 to piston stroke guide part 336 in FIG. 22 is made, for example, radially flexible. For example, by inserting variable entry pins of the tooth 344 of the shaft 345 into the teeth 346 of the piston stroke drive, or by arranging an intermediate wheel movably between the toothed wheel 344 of the shaft 345 and the toothed wheel 346 of the piston stroke guide 336.

Finally, in practice it is often important to always ensure the correct amount of fluid in the fluid column of channel 303 with connected cylinders 301 and 304. This is achieved, for example, by the arrangement of a control 326 to 329. The first piston 301 here has a control extension 326 which is provided with control grooves 328 which periodically regulate the fluid supply line 329 as a function of the piston stroke of the first piston 302 with the first cylinder = 301 connect and disconnect from it. The S _t your extension-326 appears to sealing in the control cylinder 327 and travels in it.

It can thus be achieved that whenever the first piston arrives in its outer position in the cylinder 301 and the second piston 305 has approximately reached its inner position in the second cylinder 304, the fluid supply line 329 via the control channel 328 with the first and second cylinders 301, 304 is connected and fills this and the channel 303 with the required amount of fluid, or refills if some fluid from the column of rooms 301,303,304 should have been lost through leakage during the previous work cycle. In order for this to function properly, it is useful to provide the second piston 305 with inner end position stops 306 which strike the cylinder bottom of the second oil cylinder and thus determine a precise inner end position of the second piston 305 in the second cylinder 304. This is important together with the full filling of the fluid in the fluid column mentioned, so that the subsequent pressure stroke of the first piston 302 results in an exact length and position of the pump stroke of the second piston 305 in the second cylinder 304 and thus the elements 307 are pressed together in the precisely desired stroke length will. This is important because the elements 307, 1.2 in these high pressure ranges of the supercritical range only make very short strokes of less than one millimeter per element 1,2,307. The strokes of the elements 1, 2, 307 are rarely longer. The safe operation of the fluid column is therefore of crucial importance for the reliable operation of the unit of FIG. 22, as well as for full high-pressure delivery with good efficiency.

FIG. 22 also has the inlet means 316 to the working chamber 311, the outer ring 320, the inner ring 308, the bore 350 therein for connecting the two working chambers 311, and the seals 309, (protective skin) 348, 322, 317, etc., FIG. 28 being the most perfect form of a Part shows and may be an enlargement of the re-line 348 of Figure 22. Axis 331 shows the eccentric axis, that is the axis of the piston = stroke guide surface 347 and its distance (radial distance) 332 from the central axis 330. The inner spaces 351 and 352 can be lubricated again. Fill fluid to avoid rusting of the parts inside the unit.

In Figure 23, the bars "H" indicate the bearing of the element on the piston or pump head, or the tension between two of the elements. The important meaning of FIG. 23 is that it teaches that conventional disc springs can only be used for the low pressure ranges, but the difference (R minus r) for the supercritical range of the high pressure, but about a fifth or less of the outside. knife should be "R". "S" shows the thickness of element 1,2,307.

A comparison of the teaching from FIG. 23 with FIG. 22 shows that the main part of the flow rate through the working chamber 61 is now achieved by compressing the chamber 61 in the axillary direction. The elements are now only involved in a small percentage change in the volume of the working chamber 61.311. And that's how it should be in the ideal case. The elements in FIG. 22 are now more means of limiting the working chamber in the radial direction than fluid conveyors = elements. In the subcritical area, on the other hand, the elements 1, 2 are often significant participants in the change in the volume of the working days and their conveying effect is then greater than that of the pure axial movement of the piston in question.

FIG. 29 shows the mathematical development of the calculation of the change in chamber, that is, the quantity of chamber 61, on the left. Here one sees as "V" the change of the volume of the working chamber 61 by the element 1,2, while "Q" is the sum of the full change by elements 1,2 and axial movement of the piston concerned. If the unit works as a pump, "V" is the amount conveyed per stroke by the element 1,2 in question, while "Q" is the sum of the amount conveyed per stroke from element 1 and the axial movement of the piston (e.g. 40.305).

FIG. 29 also shows that two or more elements 1 "2 do not always have to be arranged, but that a single element 1 or 2 can also be arranged between a piston 40 and the pump head 48. Here, the protective skin 777 can also be clearly seen, the protective layer, which can be inserted as a sheet or so of appropriate material, for example copper, teflon, rubber, in order to prevent the element 1, 2 from being touched by water or the like The seal 888 appropriately encompasses the protective skin 777 and the seal 7 is touched through the protective skin in order to ensure that the chamber 61 is properly sealed and the outer part (in the ring 3) of the element 1, 2 is properly seated.

In the upper right part of Figure 29 you can see the numbers 1,2,3 in circles. These mean the relevant places (locations, positions) of the internal stresses sigma (Ring 1), (Ring 2), (Ring 3) for calculation according to the breathing and Lasczio equation.

FIGS. 25 and 30 also show that the bending stresses "sigma with index B", that is to say the stresses under fluid pressure in work chamber 61, increase much more suddenly than the stresses sigma when element 1 or 2 are compressed, because the full stresses occur due to fluid pressure already when the fluid, for example the water, is fully compressed to the high pressure. It is therefore very important to consider the rotation angle alpha of the rotary part that produces the piston stroke. Water, for example, roughly compresses four percent at 1000 bar, or about 16 percent at 4000 bar. The maximum voltage g in element 1, 2 due to fluid pressure therefore occurs suddenly, for example 362 in FIG. 25 or according to sigma Bi in FIG. 30. The maximum voltage due to fluid pressure is therefore often reached at less than a twentieth of the rotor revolution, while that by compression of element 1, 2 is reached by piston 40, 305 only after half a rotor revolution. Therefore, the rapid increase in stress due to fluid pressure has a greater impact on the life of the element than the stress caused by compression of the element by the piston. These things had to be examined intensively according to the invention and brought into balance according to FIGS. 25, 30, so that the hitherto impossible service life, which disc springs cannot offer, is achieved for the elements 1, 2, 307, etc. of the invention. In FIG. 30, the sigma B curve drops slightly on the right, because in this figure it is taken into account that the element near the completion of the compression stroke already partially comes to rest on the support, the piston, or the pumps, motor heads. which reduces the tension somewhat, but only gradually over the circumferential angle.

For the calculation of the inertial forces and the fluid flow velocities, the mathematical formulas for the stroke "S", the piston velocity "Vs" and the piston acceleration "bs" are given in FIG. 29 and again over the rotation angle alpha.

Thus, the patent application gives a full lesson on technical action combined with the knowledge that conventional means are not aimed. thus cannot lead to the solution of the task and the new means and knowledge of the present invention must be used for the supercritical area of high pressure.

Above around ten thousand atmospheric water pressure, it must be taken into account that the sound waves (pressure waves) have reached the speed of propagation in the water. The specification in German-language catalogs of some companies that a water jet emerges from the nozzle at twice the speed of sound can be misleading, because the speed of the water is around 1400 meters per second, but not around 33o meters per second, like that of the air.

• oder; dass zwei Elemente 11,12, zwischen sich einen Hohlraum 61 bildend, an den radial aeusseren Enden mittels einer achsial starken Umgrei fung 9 aneinander geklemmt sind; (Figur 10).
• oder; dass zwischen den Elementen 11,12,1,2, ein Aussenring 8 , ein Innenring 6 mit einer Bohrung und zwischen dem Innenring und dem Aussenring eine die Elemente beruehrende plastische Dichtung (Dichtring, O-Ring) 7 angeordnet sind; (Figur 10 )
• oder; dass achsial endwaerts der genannten Elemente Stutzkoerper 10 mit Auflageflaechen und mit Ausnehmungen 17 angeordnet sind, deren Radialabmessungen aussen der Umgreifung nahe sind;
• oder; dass Zentrierkoerper 19 oder 20 mit Zentriersitzen 27,26, 28,29 angeordnet sind, die teilweise in Sitze 4,25 an Elemen = ten 1,2 ansetzbar sind und so jeweils mindestens zwei Elemen = te 1,2 zueinander oder Paare von Elementen 1, 2 zueinander zentrieren und halten; ( Figur 11 ).
• oder dass ein Treibkolben 59 mit einem Pumpkolben 58 in Achsial = richtung druckfaehig und in Radialri chtung relativ zueinander etwas nachgiebig, verschiebbar, verbunden ist, wobei der Treibkolben in einem Zylinder und der Pumpkolben in einem anderem Zylinder 61 reziprokierbar ist und zwischen den genannten Zylindern ein die benachbarten Enden der Kolben 58, 5 9 umgebender Raum 67-angeordnet ist, der durch eine Lei = tung 68 druckarm oder druckleer gehalten sein kann; (Figur 12).
• oder dass die beiden Kolben 58 und 59 du ch einen etwa achspara = llelen Stift 70,64,71 miteinander verbunden sind und zwischen einer Bohrungswand in einem der Kolben und dem genanntem Stift ein Raum 69 angeordnet ist, der radiale Beweglichkeit der beiden Kolben zueinander gestattet, ohne die achsiale Kraftschluessigkeit in mindestens einer der achsialen Bewegungs - richtungen aufzuheben; ( Figur 12 )
• oder; ein Teil des Pumpkolbens von einer Ringkkammer 65 mit Abflusskanal 66 umgeben ist und diese Kammer zur Abfueh= rung von Leckage oder Mischfluid eingesetzt sein mag. (Figur 12).
• oder; dass Elemente 1,2 zwischen Radialplatten 42,41 mit radial innen oder aussen vorstehenden Zylinderteilen 43,44, 45,46 zentriert und gehalten sind, wobei die endwaertigen Elemente 1,2 in Sitzen 47,53 benachbarter Teile 48,52 gehalten sein moegen; ( Figur 13.)
• oder; dass ein federbelasteter Kolben 60 einen Planflaechenkopf 86 bildet, auf den die plane Endflaeche eines Zweitkolbens 59 drueckt, wobei radiale Ungleichheit der Kolbenachsen in Kauf genommen werden kann und / oder ein Kolbenschuh 52 mit Fuehrungsfingern 81 versehen ist, deren Gleitteile 79 an Laufflaechen 82 einer Ausnehmung 80 in einem Koerperteil fuer einen langen Kolbenschuh - Hub gefuehrt sind; ( Figur 14 ) .
• oder; dass an einem radialem Endteil eines Elementes eine plastische Dichtung 38 in das Element 1 eingearbeitet ist, und / oder in das radial innere Teile des Elementes 1 eine plastische Dichtung 39 eingearneitet ist, wobei die genannten Dichtungen in die Betten 37 oder 40 eingelegt oder eingeklebt oder ein vulkanisiert sein moegen; ( Figuren 15 und 16) .
• oder; dass die genannte Umgreifung 9 in einzelne Segmente A,B,C, .. ..... X,Y,Z durch etwa radiale Schnitte untertei it ist, und / oder die genannte Halterung aus einem oberem Spannteil 89, einem mittlerem Distanzteil 90 und einem unterem Spannteil 91 besteht, wobei auch diese Teile in Segmente unterteilt sind; (Figuren 17 bis 20.)
• oder dass der obere und/oder der untere Spannteil 89,91 mit Haltefingern 31 versehen ist, die in eine entsprechend geformte Nut 30 am radial aeusserem Endteil des betreffenden Elementes 1 oder 2 ausgebildet ist, eingreifen und dadurch das radiale Ab = gleiten des betreffenden Heltesegmentes 89 A-Z oder 91 A-Z vom Element oder 2 vermieden ist, und/oder dass die genannten Hatteteile oder Spannteile 89 bis 91 durch Halte- oder Spannmittel wie z. B. Bolzen 92 miteinander gespannt verbunden sind; (Figur 17.)oder Figur 22 .)
• oder; dass das Aggregat fuer den superkritischen hohen Druck = bereich eingesetzt ist oder einsetzbar ist und/oder der genannte Aussenring 8, plastische Dichtring 7 und der genannte Innenring 6 zwischen den beiden Elementen 1 und 2 angeordnet sind;
• oder; dass ein Fluidmotor 113,117,119,121 eine Welle treibt, die einen Exzenterring mit zur Wellenachse exzentrischer, zy - lindrischer Kolbenhubfuehrungsflaeche am Exzenter 55 bildet, auf der ein Kolbenschuh 52 gleitet, dessen Druckfluidkommern 73 durch Kanaele 74 aus achsialen Anpresskammern mit abdichtenden Druckkolben 95,96 gespeist werden, auf der Schwenkflaeche des Kolbenschuhes ein Kolben lagert und dieser Kolben 40 auf eines der Elemente 1 oder 2 drueckt und die Zusammendrueckung des betreffenden Elementes und damit den Pumpvorgand in der Arbeitskammer 61 treibt oder die Arbei tskammer den Kolben und Schuh und damit den Exzenterring 55 treibt und in rotierende Bewegung versetzt; (Figur 17 oder 22.)
• oder; dass in einem Koerper 98 Sitze 107 ausgebildet sind, die Elementenpaare 1,2 halten, eine Kolbenhubfuehrung 156 fuer den radialen Kolbenhub des Kolbens 36 ueber Kolbenschuh 21 zwischen dem Elementensatze 1,2 und der Fuehrung 156 ange ordnet ist und Fluidzuleitungskanaele 102,105 und Abtei = tungskanaele ueber einen Umsteuervorgang den zwischen den Elementen 1 und 2 gebildeten Arbeitskammern 61 verbunden sind, wobei ein Kolbenfortsatz des Kolbens 36 die Elemente zentrieren oder halten mag und jede dichtene Einpassung von Kolben in Zylindern vermieden ist, um so das einfache und billige Pump - oder Motoren - Aggregat der Figur 21 zu verwirklichen; ( Figur 21 .)
• oder; dass an dessen Achsialenden radial innen oder aussen radial etwa plane Flaechen, Auf age-Flaechen 354 und / oder 359 angeordnet sind; ( Figur 27.
• oder; dass nach Figur 28 eine Formgebung und eine Ausbauchung 355 die Linienberuehrung in eine fast Flaechenberuehrung umwandelt um groessere Tragkraft zu erzielen und / oder Schutzschichtplatten, sheets, Bleche, 309 und / oder Dichtmittel 356 angeordnet sind; ( Figur 28.)
• oder; dass ein Erstzylinder 301 angeordnet ist, in dem ein Erstkolben 302 reziproklert, ferner ein Zweitzylinder 304 angeordnet ist, in dem ein Zweitkolben 305 reziprokiert und der Erstzylinder mit dem Zweitzylinder durch einen Verbin = dungskanal 303 verbunden sind, die Zylinder und der Kanal mit Fluessigkeit gefuellt sind und die Reziprokierbewegung des Erstkolbens durch die Fluessigkeitssaeule in dem Kanal und den Zylindern auf den Zweitkolben uebertragen wird; ( Figur 22.)
• oder; dass der Erstkolben 302 kleinen Durchmesser, der Zweit = kolben 305 3inen groesseren Durchmesser hat, wodurch die Druckkraft des Zweitkolbens groesser, als die des Erstkol = bens wird und die Bewegung des Zweitkolbens umgekehrt parallel zum Erstkolben erfolgt, indem der Zweitkolben im Zweitzylinder einwaerts laeuft, wenn der Erstkolben im Erstzylinder auswaerts laeuft und umgekehrt (vice versa);
• oder; eine Steuerung 326,329,328,327 zur korrekten Auffuellung der genannten Fluidsoeule oder Fluessigkeitssaeule in den Raeumen, Zylincern, Kanaelen, 301, 303, 304 ange= ordnet ist, die zur Zeit niederen Druckes, bevorzugt in der aeusseren Kolbenlage oder der Naehe derselben, des Erst = kolbens 302 die Zyl inder 301 und 304 und den Verbindungs= kanal 303 mit Fluid aus dem Zuleitungskanal, z.B. 329 heraus fuellt, damit eine einwandfreie Uebertragung der Bewegung des Erstkol bens 302 auf den Zweitkolben 305 erfolgt;
• oder; dass der Kolbenhub des Erstkolbens 302 stufenlos regel = bar angeordnet ist und dadurch der Kolbenhub des Zweit = kolbens 305 auch stufenlos regelbar wird;
• oder; dass das Element 1,2,307 usw. einen Auseendurchmesser und einen Innendurchmesser hat, deren Radien die Haelfte des betreffenden Durchmessers sind und die Differenz Aussenradius minus Innenradius mindestens dreimal kleiner, als der Aussenradius ist. ( Figur 22 ) ; (Entstanden aus Figuren 23, 24, 25, 29, 30.)
• oder; dass der Erstkolben 302 mit einer Kolbenhuh - Antriebs = vorrichtung, z.B. 334, 347, 336, 346, 344, 345 oder der= gleichen versehen ist, die den Hub des Erstkolbens 302 er= zwingt; ( Figur 22 ) .
• oder; dass nur ein Element 1 zwischen einem rezl = prokierbarem Kolben 40 und einem Kopfe 48 angeordnet ist; ( Figur 29.)
• oder; dass zwecks Erreichung einer maximalen Lebensdauer der Elemente die inneren Spannungen in den Elementen 1,2,307 usw. durch Zusammendruecken und durch Durchbiegung unter innerem Fluiddruck aus der Arbeitskammer 61 gegeneinander angeglichen sind. (Figuren 25,30) .

Summarizing the previous figures with conical ring elements, it can be seen that the special designs and features of the invention also consist in the fact that a pair of elements 1, 2 made of fibrous materials with connecting substances between them at the radially outer ends, a cavity 61 between the forming two elements, glued or bonded; (Figure 9)

• or; that two elements 11, 12, forming a cavity 61 between them, are clamped together at the radially outer ends by means of an axially strong circumference 9; (Figure 10).
• or; that between the elements 11, 12, 1, 2, an outer ring 8, an inner ring 6 with a bore and between the inner ring and the outer ring a plastic seal (sealing ring, O-ring) 7 touching the elements are arranged; (Figure 10)
• or; that the axial end values of said elements support body 10 with support surfaces and with recesses 17 are arranged, the radial dimensions of which are close to the encompassing outside;
• or; that centering bodies 19 or 20 are arranged with centering seats 27, 26, 28, 29, which can partially be attached to elements 4, 25 at elements 1.2, and thus at least two elements 1, 2 to one another or pairs of elements 1 , 2 center and hold to each other; (Figure 11).
• or that a drive piston 59 is connected to a pump piston 58 in the axial = direction capable of pressure and in the radial direction relatively flexible, displaceable, displaceable, the drive piston in one cylinder and the pump piston in another cylinder 61 being reciprocal and between the cylinders mentioned the adjacent ends of the pistons 58, 59 surrounding space 67 is arranged, which can be kept low-pressure or low-pressure by a line 68; (Figure 12).
• or that the two pistons 58 and 59 are connected to each other by an approximately axially parallel pin 70, 64, 71 and a space 69 is arranged between a bore wall in one of the pistons and said pin, which allows the two pistons to move radially with respect to one another without canceling the axial frictional connection in at least one of the axial directions of movement; (Figure 12)
• or; a part of the pump piston is surrounded by an annular chamber 65 with a discharge channel 66 and this chamber may be used for the removal of leakage or mixed fluid. (Figure 12).
• or; that elements 1, 2 are centered and held between radial plates 42, 41 with cylinder parts 43, 44, 45, 46 projecting radially inwards or outwards, the final elements 1, 2 being able to be held in seats 47, 53 of adjacent parts 48, 52; (Figure 13.)
• or; that a spring-loaded piston 60 forms a flat surface head 86, on which the flat end surface of a second piston 59 presses, whereby radial inequality of the piston axes can be accepted and / or a piston shoe 52 is provided with guide fingers 81, the sliding parts 79 of which on sliding surfaces 82 of a recess 80 are guided in a body part for a long piston shoe stroke; (Figure 14).
• or; that a plastic seal 38 is incorporated into the element 1 on a radial end part of an element, and / or a plastic seal 39 is introduced into the radially inner parts of the element 1, the seals mentioned being inserted or glued into the beds 37 or 40 or a may be vulcanized; (Figures 15 and 16).
• or; that said gripping 9 is divided into individual segments A, B, C,... .. X, Y, Z by approximately radial cuts, and / or said holder comprising an upper clamping part 89, a middle spacing part 90 and a lower clamping part 91, these parts also being divided into segments; (Figures 17 to 20.)
• or that the upper and / or the lower clamping part 89, 91 is provided with holding fingers 31 which are formed in a correspondingly shaped groove 30 on the radially outer end part of the element 1 or 2 in question, and thereby the radial sliding of the relevant holding segment 89 AZ or 91 AZ of the element or 2 is avoided, and / or that said hat parts or clamping parts 89 to 91 by holding or clamping means such. B. bolts 92 are tensioned together; (Figure 17.) or Figure 22.)
• or; that the unit is used or can be used for the supercritical high pressure = range and / or that the outer ring 8, plastic sealing ring 7 and the inner ring 6 are arranged between the two elements 1 and 2;
• or; that a fluid motor 113, 117, 119, 121 drives a shaft which forms an eccentric ring with a cylindrical piston stroke guide surface which is eccentric to the shaft axis and on which a piston shoe 52 slides, the pressure fluid comers 73 of which are fed by channels 74 from axial pressure chambers with sealing pressure pistons 95, 96. a piston is supported on the swivel surface of the piston shoe and this piston 40 presses on one of the elements 1 or 2 and drives the compression of the element concerned and thus the pumping element in the working chamber 61 or the working chamber drives the piston and shoe and thus the eccentric ring 55 and set in rotating motion; (Figure 17 or 22.)
• or; that seats 107 are formed in a body, hold the element pairs 1, 2, a piston stroke guide 156 for the radial piston stroke of the piston 36 via piston shoe 21 is arranged between the element sets 1, 2 and the guide 156, and fluid supply ducts 102, 105 and abbey duct ducts The working chambers 61 formed between the elements 1 and 2 are connected via a reversal process, a piston extension of the piston 36 being able to center or hold the elements and any tight fitting of pistons into cylinders is avoided, in order to simplify the simple and cheap pump or motor operation. Realize the aggregate of Figure 21; (Figure 21.)
• or; that at its axial ends radially inward or outward radially approximately flat surfaces, on age surfaces 354 and / or 359 are arranged; (Figure 27.
• or; that according to FIG. 28 a shape and a bulge 355 converts the line contact into an almost surface contact in order to achieve greater load-bearing capacity and / or protective layer plates, sheets, sheets, 309 and / or sealants 356 are arranged; (Figure 28.)
• or; that a first cylinder 301 is arranged, in which a first piston 302 reciprocates, further a second cylinder 304 is arranged, in which a second piston 305 reciprocates and the first cylinder is connected to the second cylinder by a connecting channel 303, the cylinders and the channel are filled with liquid and the reciprocating movement of the first piston is transmitted to the second piston through the liquid column in the channel and the cylinders; (Figure 22.)
• or; that the first piston 302 has a small diameter, the second piston 305 3 has a larger diameter, as a result of which the compressive force of the second piston becomes greater than that of the first piston and the movement of the second piston takes place in reverse parallel to the first piston in that the second piston runs into the second cylinder, if the first piston runs outwards in the first cylinder and vice versa (vice versa);
• or; a controller 326, 329, 328, 327 for correct filling of the named fluid column or liquid column in the rooms, cylinder core, channels, 301, 303, 304 is arranged, which at the time of low pressure, preferably in the outer piston position or near the first piston 302 the cylinders 301 and 304 and the connecting channel 303 are filled with fluid from the supply channel, for example 329, so that the movement of the first piston 302 is transferred to the second piston 305 without any problems;
• or; that the piston stroke of the first piston 302 is arranged in an infinitely variable manner and the piston stroke of the second piston 305 is thereby also infinitely variable;
• or; that the element 1, 2, 307, etc. has an outer diameter and an inner diameter, the radii of which are half of the diameter in question and the difference between the outer radius and the inner radius is at least three times smaller than the outer radius. (Figure 22); (Made from Figures 23, 24, 25, 29, 30.)
• or; that the first piston 302 is provided with a piston crown drive device, for example 334, 347, 336, 346, 344, 345 or the like, which forces the stroke of the first piston 302; (Figure 22).
• or; that only one element 1 is arranged between a piston 40 which can be protocated and a head 48; (Figure 29.)
• or; that in order to achieve a maximum service life of the elements, the internal stresses in the elements 1, 2, 307, etc. are matched to one another by compression and by deflection under internal fluid pressure from the working chamber 61. (Figures 25.30).

FIG. 26 shows a schematic of a work system for a solid material internal combustion engine. The pump units of the invention can advantageously be used therein. In the tank (for example the tank of the vehicle) 806 there is the solid fuel 807, which is not a liquid and not a gas, but a solid substance, for example powder, magnesium, coal or cleaned and pressed coal or the like. The first transport device 809 serves to constantly transport the solid fuel to the tank outlet and fuel inlet 805, 804. The second transport device 805 conveys the solid fuel through the inlet 804 into the combustion chamber or pre-combustion chamber 800. There, the solid fuel may encounter a pump of the invention, which is principally designated in 808 and which directs a fluid jet (jet), for example a water jet 802, through the jet nozzle 803 at the incoming solid fuel 801. The fluid jet jet 802 hits the solid 801 with great force of a few thousand atmospheric dynamic pressure and smashes the solid fuel into dust. This results in the mixed stream 810 of solid fuel dust intermingled with the fluid from the fluid jet stream 802. This mixed stream is extracted in the combustion chamber 800 and burns in it in compressed or other air. If the fluid jet stream 802 is a liquid fuel, then the liquid fuel and the solid fuel dust in the combustion chamber 800 burn together. If the jet stream 802 is a high pressure water jet stream, then the water droplets of the water in the flame in the combustion chamber 800 evaporate, while the dust parts of the solid fuel stream 801 burn in the air and convert the water of the jet into steam. The steam then takes part in the expansion of the gas together with the air that heats up during combustion, which provides the drive for the pistons or expansion devices of the combustion engine. A particularly elegant solution is, for example, to strongly press the solid fuel into a rectangular cross-section 815, for example to a carbon filament of any cross-section, but the rectangular or square cross-section 815 is preferred. Because the rectangle or square cross section can be rolled up into a spiral (radial spiral), as shown by 25. With such a spiral, the tank 806 can be filled completely. Then, since a cubic centimeter of pressed coal has a little more than the doubled calorific value of a cubic millimeter of gasoline, you can drive almost twice as far with a tank of the same size if you use the coal or solid fuel according to the invention instead of gasoline or diesel fuel. The second conveying device 805 rolls the fuel spiral 825 continuously and conveys the solid fuel filament 835, for example of the cross-section 815, rapidly and continuously through the brake fuel introducing nozzle 804 as the firing thread 801

Combustion chamber 800 into where the fuel filament 835, 801 then meets the fluid jet stream 802 and is crushed by it under the high back pressure into powder or dust and entrained with the gluid jet stream 802.

It is particularly preferred to flow a hot flame in the combustion chamber 820, for example made of hydrogen, gasoline or the like and air, through the flame flame inlet 824 as a flame flow 821 into the breanreum 820 and thus within or around the radial center or axis to generate very hot continuous flame 831 and to maintain it continuously. The solid fuel filament 835 then moves continuously and continuously, with the speed in car may be regulated with the known accelerator pedal, through inlet guide 804 into the combustion chamber, referring to the fluid stream Jet, e.g. the water jet stream hits from its nozzle 823. At point 822 the fuel filament and the fluid jet, for example the water jet stream, meet, the solid fuel filament being pulverized into powder or dust and entrained with the fluid jet stream directly into the hot flame 831 passing through the line 824 is streamed in.

Since the flame 831 is kept very hot by this arrangement, it has enough calorific value to immediately convert the water of the jet stream from 823 into steam, that is to say vaporize it, without the water stream being able to kill the flame 831. As the mixture of air, steam and fuel gas continues to flow along the price within the combustion chamber 820, the fuel gas is preferably further swirled by means of the rotating blades 826 on the rotor shaft 825 and this rotor arrangement 825, 826 also serves to serve as a foreign body or to throw non-combusted solid particles radially outwards and to collect them in collecting chambers in the radially outer region of the combustion chamber 820. The fuel gas that has become so perfect with at least partially achieved expansion then emerges from the outlet 828 from the combustion chamber in order to enter the chamber (s) of the expansion device of the combustion engine, for example the expansion stroke cylinder of the engine and the pistons therein or to drive the piston in the expansion stroke, i.e. in the work delivery hub.

FIGS. 31 and 32 show matching cuts along the relevant center lines of the figures of a piston-piston shoe - arranging eyes with parts of the neighboring parts surrounding them. This arrangement may be used, for example, in the motors or pumps of the application, or may serve in general for pumps and motors which are used outside the other units in the other figures of this patent application. The task of these figures and FIG. 33 is to create the largest possible, or more precisely, the maximum possible contact surface of the swivel joint between a piston with a piston shoe that can be pivoted thereon. This is necessary in order to achieve particularly high pressures in the unit. So high pressures of many hundreds or at least three hundred bar, which are occasionally necessary. In the aggregates of the other figures you need 500 or 1000 bar for the pistons and shoes. This high pressure can no longer be carried in the swivel joints of DE-OS 30 41 367. because the contact area between the piston and the piston shoe is too small. According to the invention, the piston receives 50% of the bearing bed surface 510 with the radius 508 about the pivot axis 505. It is now a partial cylinder surface that extends over the entire cross section of the piston. The piston shoe is provided with a complementary oscillating surface 511, which rests on the piston bed and has the radius 509, which corresponds to the rudius 508. The piston shoe bearing on the piston is provided with pressure fluid pockets 515 fed by channels 516, 517, and these are also arranged in the outer surface of the piston shoe, with which the shoe slides on the piston stroke guide 514. The piston stroke guide 514 has the piston stroke guide surface 512, on which the outer sliding surface 513 of the piston shoe runs. The swivel bed surface of the piston with the radius 508 about the swivel axis is designated by 510 and the complementary cylindrical hollow part swivel surface of the piston = shoe is the swivel surface 511.

• a) Eine groesstmoegliche Lagerflaeche des Schwenkgelenkes;
• b) Ein Eintauchen der Stifthalterung in den Zylinder, und
• c) Herausziehen des Kolbens beim Saughub mittels der Zugflaechen wodurch gleichzeitig die folgenden Vorteile erzielt werden :
• d) die Anordnung ermoeglicht hoechste Drucke infolge der grossen Tragfaehigkeit der Schwenklagerflaechen ;
• e) der Kolbenhub bleibt gross, da ein Teile der Verbindungsanordnung zwischen Kolben und Kolbenschuh in den be reffenden Zylinder eintauchen kann ; und;
• f) einen einwandfreien Selbstansaugehub, da ausgedehnte und praezise wi rkende Zu gflaechen fuer das Herausziehen des Kolbens in Verbindung mit dem Gelenkbolzen beim Saughub gewaehrleistet sind.

This arrangement, like that of FIG. 33, should also have the advantage that a relatively large, long piston stroke can also be achieved so that the pivot axis can enter the cylinder 503 of the unit. The calf axis is 504, the piston crown 533, the swivel axis of the swivel joint between the piston and the piston shoe has the number 505. In order to achieve the described immersion goal, the piston has a transverse bore 507 with the swivel axis 505 as the center line, which is perpendicular to the piston axis 504. The mounting bolt 506 is inserted into it. In addition, the piston 501 has recesses 518 at the outer ends of the bore mentioned, which are radially expanded around the bore 507 and the bolt 506. The ends of bolt 506 enter these recesses of the invention, 518, but are the bolts 506 in the transverse bore 507 are shorter than the diameter of the piston 501 and the cylinder 503 so that the pins 506 do not abut the cylinder walls and cannot damage them. Retaining eyes 520 of the intermediate brackets 519 are inserted into the recesses 518 and they grip around the described ends of the bolts 506. Radially outside the pivot axis 505, the intermediate parts 519 protrude axially and form the tensile surfaces 531 there, while the intermediate parts otherwise radially follow the piston axially are extended until they meet and rest on the bearing surface 511 of the piston shoe. Axially outside of the intermediate parts 519 are the outer parts 5, which lie with their radially outer seats on the piston stroke guide surface 512 of the piston stroke guide. The outer parts 530 form the encompassing traction pieces and encompassing traction surfaces 532, which grip around the traction surfaces 531 of the intermediate parts 519, touch them and let them slide on them. The end parts 530 thus serve as traction parts, which pull the piston-piston shoe arrangement radially out of the cylinders 503 during the intake stroke. The inventive arrangement of FIGS. 31 and 32 thus simultaneously achieves:

• a) The largest possible bearing surface of the swivel joint;
• b) immersing the pen holder in the cylinder, and
• c) pulling out the piston during the suction stroke by means of the pulling surfaces, whereby at the same time the following advantages are achieved:
• d) the arrangement enables the highest pressures due to the large load-bearing capacity of the swivel bearing surfaces;
• e) the piston stroke remains large, since a part of the connection arrangement between the piston and the piston shoe can be immersed in the reffecting cylinder; and;
• f) a flawless self-priming stroke, since extensive and precisely working surfaces are ensured for pulling out the piston in connection with the hinge pin during the suction stroke.

In FIG. 33, part of the construction of FIGS. 31 and 32 has been changed, whereby one of the parts can be saved and a different method of production for these tasks and solutions is made possible. Piston, rotor 508, cylinder and Kotbenhubfuehrung are the same as in Figures 31 and 32. The pin 506 and the recesses 518 are the same. The parts 519 and 530 of FIGS. 31 and 32 are, however, replaced by the holders 529, the eyes of which encompass the piston ends of the bolts 506 and which again engage in the recesses 518 of the piston 501.

flaechen 527 der Halteringe 525 zwischen Lagern 528 eingeschachtelt gehalten werden und gegen Achsialverlagerung gesichert werden, indem die genannten Innenflaechen 527 der Ringe525 gegen die radial planen Achsial-Endflaechen 526 der Verbindungsteteile 529 lagern und halten.What differs from FIGS. 31 and 32 is that the holding parts 29 are provided with outer grips, rims 522. The piston shoes have the recesses on the outside at the axially outer ends which form the holding surfaces 523, on which the ribs 522 with their holding surfaces 524 lie. Thus, the rims 522 of the parts 529 hold the piston 501 and the piston shoe 502 together and enable the swiveling of the shoe 502 on the piston 501. The whole arrangement can be shown in FIGS. 31 and 32, as well as in FIG plan radially facing one another

surfaces 527 of the retaining rings 525 are kept nested between bearings 528 and secured against axial displacement by storing and holding said inner surfaces 527 of the rings 525 against the radially flat axial end surfaces 526 of the connecting parts 529.

Figure 34 shows the longitudinal section through a hydraulic unit that can be used as a pump or motor for high pressures. Very high pressures are required in the units of the invention, which the units with roller bearings can usually no longer meet for a sufficiently long service life. The assembly of FIG. 34 with its sub-figures 35 and 36 can therefore be used particularly for the assemblies of the invention as a pump or as a motor, but also generally as a hydraulic assembly, for example for excavator and press construction, as can be used in general hydrostatics. The main shaft 443 has a center L portion 401 which extends radially outward and forms an outer surface, preferably a cylindrical shape, which is used to place a hydrostatic bearing around the central portion, which alwaerts the high radial forces from the cylinders 439,440 of the two axles of the central part 401 arranged chamber groups 439,440. On the other hand, the shaft is mainly supported in the end bearings 445 and 444 for centering purposes, the bearings 445 axially centering the shaft and the bearing 444 allowing the shaft to expand axially under heat. On both ends of the central part 401 on the shaft 443 there is a body 441, 442, each containing a rotor or chambers, which the working chambers, e.g. cylinders 439,440 of chamber groups 439,440. In the middle part there are also the pressure chambers 402, 403, in which axially movable pressure bodies 404, 405 are arranged, which, under the pressure in the chambers 401, 403, press the rotor in question with its other end surface, the rotating control bottle or rotor surface against the control surface arranged in the housing 447. The body 404 the rotor 441 against the upper control surface in the figure, the piston 405 the rotor 442 against the lower stationary control surface in the figure 34,

As far as we have already tried to design such units, they have encountered difficulties in that they did not work properly or did not work for all applications. The present invention according to FIGS. 35 to 36 overcomes the difficulties that have arisen and powerful units with high operational reliability are created for a wide range of applications. In particular, pressure chambers 402 and 403 are assigned pressure fluid pockets in the stationary control or storage compartments at the other end of the unit. This prevents the control surfaces from overheating.

According to the invention, a channel 409 to a secondary pressure chamber 410 is arranged from the respective pressure chambers 403, the secondary pressure chamber 410 being open out of the rotor in the opposite direction, like the pressure chamber 403.A channel 413 is correspondingly assigned to the pressure chamber 402, which leads into the secondary pressure chamber 412 leads, which is again open in the opposite direction from the center plate 401, like the pressure chamber 402. In the secondary pressure chambers 410 and 412, the secondary pressure pistons 611 or 411 are arranged, provided with a passage and they press on the respective adjacent rotor 441 , or 442, seal this from and lead into the relevant rotor secondary channel 433 or 618, which passes axially through the rotor 441 or 442 in question and at the other end of the rotor 441 or 442 in question into the relevant pressure fluid pocket 432, 420, 434 or 435 the relevant stationary control surface of the unit must be opened. As a result, pressure fluid is directed from chamber 403 into pocket 432 or 420, depending on the position in the rotor circulation of the pressure chamber 403 in question. Correspondingly, pressure fluid from the pressure chamber 402 in question is passed into the pressure fluid pocket 435 or 434 in question of the control surface on the other side of the unit. What is achieved by this arrangement according to the invention is that the respective rotor 441 or 442 between its own rotor channel 421, 424, its own control port 423, 426 is subjected to its own cylinder pressure and at the same time is also pressurized with the pressure from the pressure chamber of the other rotor ashslal from the pressure fluid pocket 432, 420, 434 or 435 in question, ES is therefore prevented that one of the rotors or both rotors 441 or 442 is pressed too strongly by strong pressure in one of the chamber groups 402 or 403 and low pressure in the other of the working chamber group and the control surfaces hot running. For example, the channel 421 and control pocket 423 have the pressure from chamber 439, while the pressure fluid pocket 432 has the pressure from the other working chamber 440 at that time.

The same applies simultaneously to rooms 424, 427, 440, 420, and 424, 426, 440, 432 and 439, 421, 423, 434 or 424, 427, 440, 420 and so on. The previous hot stamping of the control surfaces, especially in the case of different pressures in the working chambers 439 or 440, has thereby been avoided and the unit is working now, with the correct dimensioning and position of the parts described, with appropriate relative speeds and pressures.

The storage of the central part has also been redesigned according to the invention for reasons of operational safety. The middle part 401 thus fits tightly around it, the inner race 460, which runs in the slide bearing ring 461 of the housing 462. Between the inner race 460 and the middle part 401 there are 180 ° around the middle part 401 the neck spiral channels 406 and 408 and the like, which are shown in the development in FIG. 35. There you will also find the outlets 414, which extend radially outwards from the secondary chamber channel 409 through the inner race 460 into the relevant pressure fluid pocket 407 in the inner race 460. From the respective secondary pressure chamber 412 or the secondary channel 413, the pressure therefrom is passed through the radial channel 414 into the relevant pressure fluid pocket in the radial outer surface of the inner race 460. As can be seen in FIG. 35, a pressure fluid storage pocket 409 is connected via channel 415 via channel 406 to a pressure chamber 403 and a working chamber 440, while the respective pressurized fluid storage pocket 477 can be connected via a channel 414 or 415 and a semi-spiral channel 406 to one Pressure chamber 402 and a cylinder 439 is connected. As a result, the pressure from the relevant cylinder 439 or 440 is passed through 180 degrees around the central part 401 into a diametrically opposite pressure fluid pocket 407 or 417. In the running surface of the inner race 460, which rotates in the bearing ring 461, one has to alternate a pressurized fluid bearing carrier bag with pressure from a diametrically opposite cylinder 439 and an adjacent one with pressure from a diametrically opposed cylinder 440. The rotor, or that The middle part 401 therefore floats radially between the forces from the cylinders 439 and 440 on the shaft and the oppositely directed forces from the pressure fluid showers 407 and 477 on the middle part 401. The radial loads on the shaft, rotors and middle piece thereby cancel each other out and the bearings 444 , 445 can be weak. The unit, however, allows very high pressures without the bearings 444, 445 failing under pressure load. The goal according to the invention has thus been achieved.

FIG. 36 also shows the important knowledge of the invention that the pressure chambers 402, 403 must lie on the radius “rgc”, which must still be calculated and found in the formula shown in the figure. Otherwise they run Control surfaces of the unit are still hot. And accordingly the diameter of the pressure chambers 402 or 403 must correspond to the equation for "dth" according to FIG. 36 if the control surfaces are not to run hot. These equations are therefore important and new conditions and findings within the scope of the invention according to FIGS. 34 to 36. In the right half of FIG. 36, one can see the control pocket 422 and the pressure fluid pocket 420, the relief groove 458 between the control mirrors around 422 and 420 , as well as the radii "Ro" and "Ri" important for the calculation according to the equations. It is also important that for most applications the control levels around 422 and 420 should give the same pressure and the secondary pressure chambers should be on the "Rgc" radius of the outside control level around 420. The other three control mirror halves around 423, 432-424, 435-426, 434 are designed accordingly. It can also be seen from FIG. 35 that it is sometimes expedient to separate the pressure fluid pockets and their surrounding # the sealing surfaces, that is to say the pressure fluid pocket zones 407 and 477 from one another by means of drainage or separation channels or grooves 453, in order to simplify and more precisely calculate the Bearing forces and pressure fluid pockets 407, 477 with their sealing surfaces 452, which surround them.

Further details on the figures of the patent application can be found in the partly very extensive and partly also expensive Rotary Engine Kenkyusho reports, the RER reports.

und fuer das Aussenmaß, 57gilt der Durchmesser "d_ta" nach der folgenden Berechnung:

mit : fb= Balanierungs- Fakfor; pi = 3,14; Z= Drucktone. ( Warum das "G" in der Gleichung ist, hat der Erfinder z.Zt. vergessen.)The calculation _formula applies to the radius "r _gc ":

and for the outside dimension, the diameter "d _ta " applies according to the following calculation:

with: fb = balancing factor; pi = 3.14; Z = pressure tones. (The inventor has currently forgotten why the "G" is in the equation.)

The numbers 459,480,482 and 483 show the reversing bends between the relevant tax pockets of the relevant tax index.

For the evaluation of Figure 24 during the practical construction of the unit, the following calculations must be observed:

For the practical implementation of the unit of the invention, the following calculations are important for FIG. 29 and must be observed:

In FIGS. 37 to 40, the piston shoe 502 is connected to the piston 501 in a manner similar to that in FIGS. 31 to 33. The reference numerals 501.502.504.505.506.507.508.509.510, 511.513.515.516 and 517 basically show the same parts as in FIGS. 31 to 33 the piston, the piston shoe, the piston axis, the swivel bed axis, the cross pin, the cross hole, the two radii, the swivel bearing bed surface, the swivel surface, the outer surface of the piston shoe, the pressure fluid pockets and the channels through the piston to the pressure fluid pockets, these parts compared to those of Figures 31 to 33 may have had constructive changes if necessary.

While the holding arrangement for the piston and the piston shoe by means of parts arranged on the rotor was possible in FIGS. 31 to 33, FIGS. 37 to 40 show a self-retaining connection of the piston shoe to the piston. For this purpose, the intermediate holder pieces 519 of FIGS. 31 to 33 are replaced by the holder pieces 6f 9 in FIGS. 37 to 38. But the pieces 519 and 619 serve the same purpose, namely to connect the piston 501 and the piston shoe 502 so that they can pivot relative to one another. Only the eye 520 is in the recess 518, the parts 518 and 520 being practically identical to those of FIGS. 31 to 33, so attached to the transverse bolt 506 that the pivoting movement cannot be prevented, the middle pieces or intermediate pieces 619 but are still held firmly on the cross pin 506 and thus the connection between piston 501 and piston 502 remains secured. Correspondingly, within the recesses 518, the eyes 520 grip the ends 606 of the bolt 506, which are kept smaller in diameter, held at the thicker central part of the bolt 506 and firmly connected at their axially outer ends by means of brackets 570 to the bolt 506. Once this arrangement has been carried out, the connection and permanent pivoting mounting and mounting of the pivoting piston shoe on the piston no longer require any further aids. Instead of gripping the piston shoe as in FIGS. 31 to 33 _j , the gripping can also be carried out as in FIGS. 37 to 40, in that the central parts 685 of the pieces 619 are provided with bunches 574 radially on the outside engage in recesses 573 of the piston shoe 502 and advantageously use collars 574 which are provided with a holding surface 572 with a radius 571 around the pivot axis 505 in order to store and hold the piston shoe 502 on a complementary surface.

on the piston shoe 502 and to hold it. In comparison to the exemplary embodiment in FIGS. 31 to 33, it can also be seen in FIG. 37 that the piston 501 can be provided with the cross head 575. The bed area 510 extends in Figure 37 over the entire length of the crosshead. The crosshead can be designed with the radius 508 around the swivel axis 505 so far parallel to the swivel axis 505 that the axial ends of the crosshead 575 together with the axial end parts of the bearing bed surface 510 protrude beyond the outer diameter 533 of the piston 501. With such an arrangement, one obtains a larger surface-supporting part of the bearing bed surface 510, so that the complementary piston shoe 502 mounted on it can transmit correspondingly high radial forces without swiveling the pivot surface 511 on the bearing bed surface 510.

mit "Kf = Fliehkraft in Kg; die betreffenden Radien ( Rz= aeusserer und Ri = innerer) der innersten und aeussersten Teile des Kolbens 501FIGS. 37 to 40 also show further knowledge of the invention and a solution to the problems identified. When the rotor of a pump or a motor rotates, the pistons 501 and piston shoes 502 sliding in the radially arranged cylinders 503 are subject to the centrifugal force. The centrifugal force is:

with "Kf = centrifugal force in kg; the relevant radii (Rz = outer and Ri = inner) of the innermost and outermost parts of the piston 501

in meters, if it had the same diameter from ra = diol inside to outside; "γ" = specific weight of the material of the piston; "δ" = (γs / g) = mass of the piston shoe with "Rs" = center of gravity of the piston shoe and "γ _s " its specific weight; also with pi = "π = 3.14" dp "= outer diameter of the piston 501 (see FIG. 51) and" ω "= the angular velocity = 0.1047x rpm.

mit " e " = Exzentrizitaet = Abstand der Achse des Rotors von der Achse der Kolbenhubfuehrungsflaeche,z.B.513, siehe zum Beispiel der Wert "e" auch aus der europaeischen Patentanmeldung 0 064 563.The radii are not constants, however, they change with the circumferential angle "α" of the rotor 608, namely the radius of the distance between the swivel axis "Rc" and the rotor axis according to Eickmann technology from older Eickmann patents:

with "e" = eccentricity = distance of the axis of the rotor from the axis of the piston stroke guide surface, eg 513, see, for example, the value "e" also from European patent application 0 064 563.

The values "R3", "R4", "Rc" etc. from FIG. 38 can also be used for calculating the centrifugal forces of individual sections of the relevant piston 501. These are then summed up in order to maintain the total effective centrifugal force.

From the European patent application of the applicant and inventor just mentioned it emerges that for a high performance in a small space, that is to say with a small external dimension of the unit, the piston stroke "S" in comparison to the radius or inner diameter "da" of the piston stroke guide surface 513 is as large as must be possible. Since the piston stroke is "S" = "2e", the written eccentricity of equation (28) must be as large as possible in order to obtain great performance with low weight and a small external dimension of the unit in question. The consequence of this is a high fluctuation with a high serving height of the current value of the relevant radius "R" around the zero value (mean value at e = 0) "Ro" of the relevant radius. The consequence of this is a large fluctuation in the centrifugal force around the mean value of the centrifugal force "Kfo". This fluctuation was present in previous radial piston units, but it was only so high in Eickmann units. When using other non-Eickmann units, the value of the angular velocity "ω" did not play a major role, since these units were mostly driven by electric motors at the same speed. Because as engines with variable speed, units without the deep-diving piston shoes of the E ickmann system are not efficient and therefore hardly used. In the current units of the invention, however, the units are often driven by hydraulic motors and the speed is regulated by pumps that can be regulated without a pin. Therefore, in the current radial piston units, speed differences from O rpm to 10,000 rpm can occur. If one now looks at equations (27) and (28), one finds that, for example, at 10,000 rpm the angular velocity is 1000 times as high as at 10 rpm and I follow the square of the angular velocity and consequently according to the equations mentioned the centrifugal force of the piston 501 with the piston shoe 502 at 10,000 rpm must be one million times as great as at 10 rpm.

However, the previous outer surfaces of the piston shoes, for example according to patent DE-PS 2 500 779, are no longer sufficient for fluctuations in centrifugal force of millions of times and amplitude fluctuations of more than 20 percent. New means must be used to remove the treads 512 of the piston shot in question hes 502 usable for a sufficiently large speed range without the surfaces 512 and 513 overheating under excessive force fluctuations. Although it is generally not possible to make the piston shoe of the radial piston machine usable for all speeds from 0 to 20,000 rpm, it is possible to use the measures of the current inventive features to paint the area between a highest and a lowest rotation = expand the number of applications.

This is achieved in accordance with the invention of FIGS. 39 to 40 and FIGS. 54 to 56 by either working the wing webs 579 into the pressure pocket 515 into the pressure fluid pocket 515 of the outer surface 512 of the piston shoe 502, or the front part and back part 580 of the relevant part The outer surface 512 of the piston shoe 502 beyond the drain grooves 577 can be provided with means to enable larger speed ranges, or both measures can be arranged at the same time.

The arrangement of the support web surfaces 579 in FIG. 40 has the advantage that these surfaces are lubricated from both ends of the air pressure with pressure from the respective adjacent pressure fluid pocket parts 515. This gives these surfaces 579 a higher load capacity per surface cross-section than the sealing surfaces (Sea = ling lands) 578, because the sealing lands 578 are only pressurized with fluid at one end and are therefore less well lubricated, so that they also have less load-bearing capacity per surface cross-section have as the flank parts 579. It is expedient to make the webs 579 very short in the air direction, for example to arrange 1 to 5 mm and for this purpose to arrange many webs 579 because the forced lubrication from the pocket parts 515 acts only a few millimeters deep. If the webs 579 were too wide in the direction of travel, the forced lubrication would fail and the running surface 512 would run hot when the speed became high.

For the exact calculation, the area "L x W" of FIG. 40 is assumed to be the high pressure zone and this area of the invention is made even larger than the Kolberg cross section d ² pi / 4 of the piston 501. In practice, the dimension "L x W" is approximately the sum of the centrifugal force Kf divided by the difference between "L x W" and d ² pi / 4 and the difference mentioned multiplied by the fluid pressure in the pressure fluid pocket 515 and the relevant cylinder 502 from which this pressure acts on the piston crown 533.

The corresponding feature of FIG. 40 is therefore to make the dimension "LxW" larger than the piston cross section d ² pi / 4, if the unit is to run at a correspondingly high speed, the support web surfaces 579 within the pressure fluid pocket 512 transversely to the air direction to be arranged, to clearly delimit the sealing surfaces 578 by means of the drain grooves 6 and to arrange the stabilizing surface parts 580 arranged in front of and behind the relevant drain groove 577 in the direction of the lay and, if appropriate, in the direction transverse to the direction of the run, as viewed in the direction of travel. The surface parts 580 are then, as will be described with reference to FIGS. 54-56, converted from a support surface into a load-bearing surface, so that they can contribute to the absorption of the centrifugal force of the piston 501 and the piston shoe 502.

The figures just described still show the important radius "da" as the radius of the running surface = piston stroke guide = surface diameter "da" as number 901, as well as the swivel joint = distance from the rotor axis as radius "Rc" = 902 and the running direction 903 of the piston shoe relative to piston stroke guide surface 514.

In FIGS. 41 and 42 parts with references already known from the other figures, reference number numbers show parts with the same functions or the same parts as in the other figures, in which the same numbers appear. FIGS. 43 to 48 show the parts of FIGS. 41 and 42 in a single part = separate representation in order to be able to see better the radii and surfaces in question and the shape of the parts in question.

The special features of FIGS. 41 to 48 are that the piston shoe 502 is pivotally held on the head of the piston 501 by means of supports 581 fastened to it. The brackets 581 can be fastened to the piston shoe 502 with fastenings 582. To hold the piston shoe 502 on the piston 501, a holding surface 583 is formed on the piston head and the holder 581 has a collar 584, the holding surface 586 of which is placed on the holding surface 583 of the piston 501 in order to partially grip it. These arrangements take place at each axial end of the piston head and parallel to the pivot axis 505. The surfaces 583 and 586 receive the only slightly different radii 587 around the pivot axis 505.

A further peculiarity of these figures is that the piston 501 ver on its head in the axial direction parallel to the pivot axis 505 beyond the outer surface 637 = piston diameter "dp" Longer piston cross heads 588, over which the swivel surface 510 is extended, that is to say a continuous contact surface = swivel bed surface 510 over the entire piston head of the piston 501 formed from the piston cross section and piston cross head.

The wing webs 579 can also be arranged on one of the surfaces 510 or 511 between the piston 501 and the piston shoe 502. Corresponding channels 71-6 can conduct fluid from the relevant pressure fluid pocket 515 into those between the surfaces 583 and 586, as well as connect the channels 616 pressure fluid pockets 515 through the piston shoe or through the piston 501 to the relevant cylinder 503 of the unit. The surfaces 583 and 586 described have approximately the same radii 589 about the pivot axis 505. If the fastening 582 is a screw, the threads 590 are arranged in the piston shoe 502 and, in addition, either the piston shoe 502 or the holders 581 can pull the tension surfaces 531 with the radii 592 around the axis 592 of the guide surface 513 of the piston stroke guide 514.

Also in FIGS. 49 to 63, the reference numbers already described, referentials, have the same meaning and show the same functions or corresponding parts as in the figures in which the reference number numbers have already been described.

The special feature of the invention in FIGS. 49 and 50 is that the piston 501 is provided near its upper end with a transverse bore 59e, the axis 505 of which forms the swivel hole, passes through the axis 504 of the piston 501 and, as well in the other relevant figures, perpendicular to this. The transverse bolt 595 is inserted into the transverse bore 594 and carries the piston shoes 1102 and 1202 at its axial ends. These are provided with a bore into which the ends of the transverse bolt 595 fit so that the piston shoes about the axis 505 of the bolt = can pivot 595, or pivot pin 595 with piston shoes 1102 and 1202 around axis 505, the center piece of pin 595 then pivoting in transverse bore 594 of piston 501. The piston shoes then have the already known outer surfaces 512 with the pressure fluid pockets 515 and the other accessories already known from the other figures. Figures 49 and 50 therefore use two piston shoes 1102 and 1202 instead of the previous ei = Nem _K ofbenschuhes 502, The manufacture of such piston shoes 1 ₁₀ 2 or 1202 is a particularly simple because it can be turned from rings and the cross hole can be drilled to accommodate the ends of the cross pin 595. However, if the training is to absorb particularly high radial forces or allow particularly high speeds, then it is also expedient according to the invention to also use the piston head for the radial support of piston shoe parts. Then the piston head of the piston 501 receives, in addition to the transverse bore 594, the bearing bed surface 510, as is known with the radius 509 around the swivel axis 505. The piston shoes 1102 and 1202 then receive the piston shoe axial extensions 1302 and 1402, which have the swivel surfaces, facing one another 511 are provided and store and swivel on the swivel bed surfaces 510 of the piston 501. Corresponding pressure fluid pockets and connecting lines 515 and 515 can be arranged in parts of the piston shoe, the piston head and / or the transverse pin 595 and are shown in the drawings at locations, for example. FIG. 50 shows partial sections along one or more of the arrows A, B or C of FIG. 49, the sections being laid out and the cross-sectional parts being shown in FIG. 50 in such a way that the important arrangements can be seen. Parts that are not specifically described here are those with reference number that are already known from the description of other figures. Pull rings 731 can be placed under the pull surfaces 531 in order to pull the piston shoes radially outwards during the suction stroke, for example in excavator pumps, and thereby also pull the pistons 501 connected to the piston shoes radially outwards in the cylinders 503. The swivel surfaces 511 of the piston shoe axial extensions 1302 and 1402 can merge into knurled surface parts 597 in order to simplify the manufacture and to enable perfect swiveling of the relevant piston shoe parts on the bearing bed surface 510 of the piston 501. The pull surfaces 531 run on the guide surfaces 931 of the pull rings 731.

The piston piston 502 of FIGS. 51 to 53 corresponds in principle to that which is known from German patent 2,500,779 and can be used in units of German patent specification 1,302,469, the basic potential for deep-diving piston shoes.

But the piston shoes of the German patent 2 500 779 are not suitable for speeds that require many thousands of revolutions per minute. In addition, they lack stability. According to the invention, new arrangements are therefore made in order to make the deep-diving piston shoe even more stable, so that it lies more precisely with its running surface 512 on the piston stroke guide surface 513 of the piston stroke guide 514 in question, as a result of which its outer surface parts come into effect better and achieve less leakage and friction, and , so that the piston shoe can be used for even higher speeds without running hot. The new arrangements consist in the fact that the piston shoe guide location 1502 is carried out in the peripheral direction, that is to say in the direction of rotation, as long as possible, so that a long contact surface of high systems = stability and with a large cross section is created. In addition, a distance "B" is observed, which is calculated from the inner edge of the guide point 1502 to the swivel axis and which also determines the distance "G" de swivel axis 505 from the outer surface = running surface - smooth surface 512 of the piston shoe. These two distances "B" and "" G "are now too short, as possible. In the piston shoe for about 40 cc with 7 pistons, for example" B = approximately 2 mm "and" G = approximately 8 mm " The length is "L." These data, namely "B", "S", "Rs", "G", "L" are shown in the figures, since = with the reader of the patent applications, answers to questions about the corresponding size of the piston shoe provide precise answers Furthermore, according to the invention, the equation for the pressure fluid pockets must be observed, namely equation (29), which also appears in FIG

The pressure fluid pockets 515 are now partially radially above the cross-section of the piston 501 and the slots 702 between the surfaces or sliding pieces or legs of the "H" of the diving piston shoe, i.e. the parts 602 and 602, are now shorter according to the invention than in the German patent 2,500,779.

The piston shoe guide parts 602 are therefore located on the piston shoe central part 302 and are separated from one another by the slots 702 at both ends of the piston shoe central part, so that the piston arms of the pistons 502 and the radial webs of the rotor can enter them. The piston arms and the radial webs are known from the cited patents. The running direction of the piston shoe outer surface 512 is designated with: "Directlons" Mf "and" Mo "of for = ward and oppositional movements" in FIG. 53. The width of the slot 702 is designated with "S" and the pressure fluid pockets 515 have the cross sections "fp1" and "fp2" together with half the surfaces of their sealing lands, that is to say their sealing surfaces 578. The central part 302 of the piston shoe carries the swivel roller 902 with the swivel surface 911, which extends over the entire swivel roller 902 extends and pivots and supports in the swivel bed 510 of the piston 501 in question. The swivel roller 902 extends axially, ie para = || e | to the pivot axis 505 beyond the center piece 302 and there is in one piece with the slide pieces 602 and supports them. As a result of the large length "L" of the new piston shoe, Jen = on the side of the drain grooves 577 a larger number of support surfaces 999 are arranged, which are separated by drain slots 577 from one another. The greater number of sealing grooves promotes the load-bearing capacity of the several support webs 999. Current tests have shown the load-bearing capacities of the piston shoes for different speed ranges and this also shows the radial forces that are available on the surfaces 999, 578 or 579 at what pressures and speeds bear.

FIGS. 54 to 56 explain in particular which measures can be arranged according to the invention in order to make the piston shoe of one or the other type of this patent application or the general piston shoe usable for more extensive speed ranges. FIG. 54 shows the arrangement of a large number of support surfaces 999 beyond the inner drainage grooves 577 and their interruption by further drainage grooves 577. Care must be taken to ensure that the grooves 577 are properly filled with lubricating fluid if the unit is to work gurly. For this, we is often advantageous to the Cranes = teilflaechen 999 with lubricating fluid _- to provide Einflussnuten 1577 that promote the influence of lubricating fluid in the direction of the piston shoe. These are advantageously laterally offset from one another in different adjacent pieces 999, so that the grooves 577 to be filled well.

um den Durchmesser der gedachten Welle zu er j alten. In der Gleichung (30) bedeuten : "fv" = Berichtigungsfaktot, "pi" = " " und "dv" = den Durchmesser der gedachten Welle. Der Ber ichtigungsfaktor "fv" liegt zwischen 1 und 2, naeher an 2. Hat man so den Durchmesser der Welle, dann kann man, wenn man die Relativgeschwindigkeit zwischen den Flaechen 513 und 580 gleich der Umfangsgeschwindigkeit der Welle mit dem Durchmesser "dv" gleichsetzt, die hydrodynamische Tragkraft des Passungsspaltes zwischen den Flaechenteilen 513 und 580 zum Beispiel nach der Huette oder nach dem Buche : "Die Grundlagen der Lagerschmierung" von Werner H.Kara (Erdoelbuecherei) berechnen. Daraus laesst sich der notwendige Abstand zwischen den Flaechen 513 und 580 vom Beginn an der Nut 577 zu berechnen und wenn man fuer jeden Platz der Flaeche 580 diesen Abstand hat, dann kann man die Kruemmung der Flaeche 580 berechnen und damit ihren Radius oder ihre Radien und ih= re Mittelachse oder ihre Mittelachsen. Wird das richtig ausgefuehrt, dann kann die betreffende Flaeche 580 so ausgebildet werden, dass sie eine maximale Tragkraft fuer den gewuenschten Drehzahlbereich erhaelt. Man hat also beim Kolbenschuh der Figuren 55-56 einen hydrostatischen Tragtail zwischen den Nuten 577, der den Hauptteil der Radiallast traegt und der vom Fluiddruck im betreffendem Zylinder 503 abhaengig ist, waehrend man perpherial ausserhalb der Abflussnuten 577 mindestens ein hydrodynamisches Tragfaeld erhaelt, das nicht vom Fluiddruck Im Zylinder 503 abhaengig ist, sondern von der Drehzhal des Aggregates abhaengt. Bei richtiger Bemessung und Ausbildung ergaenzen sich beide Flaechen-Tragteile so, dass der erreeichbare Drehzahlbereich mit gu = tem Wirkungsgrade ausgedehnter wird und eine Maximalausdehnung sichert.In contrast, FIGS. 55 and 56 show how support surface fields 580 can also be appropriately designed in other ways in order to achieve the object of the invention. This is understandable by looking at FIG. 55 together with the sectional figure 56. The part of the outer surface of the piston shoe between the drain grooves 577 of FIG. 55 has the radius which is the radius of the diameter "da" = 513 of the piston stroke guide 514, after which the Support surface (the support surfaces) 580 receive another curvature according to the invention, namely one by which the support surfaces 580 are converted into wings 580, that is to say are converted into hydrodynamically supporting surfaces. In order to be able to form a hydro = dynamic supporting field, the surface 580 must not have the same radius as the middle part between the drain grooves 577. Instead, the gap between the guide surface 513 of the piston stroke guide 514 and the support surface 580 must be in the direction of travel to narrow a certain relationship. Therefore, the support surface in question, which now becomes the wing 580, is given a radius 913 instead of the previous radius 513. In a first approximation, the correct radius 913 and its center (center axis), which is different from the rotor or stroke axis of the hybrid 514, can be found by the length "LL" of the corresponding surface 580 than half the U _m fangsflaeche sees a circular cylindrical shaft. Of course, only for the calculation. So you calculate:

to get the diameter of the imaginary shaft. In equation (30): "fv" = correction factor, "pi" = "" and "dv" = the diameter of the imaginary shaft. The correction factor "fv" is between 1 and 2, closer to 2. If you have the diameter of the shaft, you can, if you equate the relative speed between the surfaces 513 and 580 equal to the peripheral speed of the shaft with the diameter "dv" , calculate the hydrodynamic load-bearing capacity of the fit gap between the surface parts 513 and 580, for example according to the hut or according to the beech: "The basics of bearing lubrication" by Werner H.Kara (petroleum oil storage). From this, the necessary distance between the surfaces 513 and 580 can be calculated from the start at the groove 577 and if one has this distance for each place of the surface 580, then one can calculate the curvature of the surface 580 and thus its radius or its radii and ih = re central axis or their central axes. If this is carried out correctly, the surface 580 in question can be designed in such a way that it receives a maximum load-bearing capacity for the desired speed range. 55-56 there is a hydrostatic support tail between the grooves 577 which bears the main part of the radial load and which is dependent on the fluid pressure in the cylinder 503 concerned, while at least one hydrodynamic bearing field is obtained peripherally outside the drain grooves 577, which is not is dependent on the fluid pressure in cylinder 503, but depends on the speed of rotation of the unit. With correct dimensioning and training, the two surface support parts complement each other in such a way that the achievable speed range is expanded with good efficiencies and ensures maximum expansion.

Bei so hoher Radialausdehnung des Innendurchmessers des Zylinders kommt es vor, dass der Kolben oder dessen Dichtung nicht mehr einwandfrei dichten kann. Auch bei Verbrennungsmotoren mit hohem Innen= druck im Zylinder kann diese Erscheinung auftreten. Ausserdem ver= schlingen dicke Waende viel Material, machen teuer und schwer. Daher wird nach der Erfindung um den Zylinder 102 eine mit Druckfluid ge= fuellte Kammer 103 herum angeordnet, die durch die Aussenwand 104 gebildet und verschlossen ist. Der Druck in der Kammer 103 kann jetzt so bemessen werden, dass jede Radialausdehnung der Zylinderwand 102 verhindert wird, oder deren Radialauswsitung unter Druck im Zylinder 100 auf ein ertraegliches Mass verringert wird. Da die Ausdehnung der Aussenwand 104 nicht schaedlich ist, koennen nach der Erfindung duennere Waende 102 und 104 verwendet werden, sodass das Aggregat leichter, billiger und betriebssicherer wird.FIG. 57 serves to overcome another difficulty which the invention recognizes and which also results from the particularly high pressures in the fluid which enable or secure the units and elements and the piston shoes of the invention. At such high pressures, the walls of the cylinders expand very noticeably from the inside under the high fluid pressure if the wall thicknesses are not very thick. The expansion of the cylinder under internal pressure is, for example, according to a formula obtained from Mr. Igarashi from Riken Seiki (Ojia, Japan)

With such a large radial expansion of the inner diameter of the cylinder, it can happen that the piston or its seal can no longer seal properly. This phenomenon can also occur in internal combustion engines with high internal pressure in the cylinder. In addition, thick walls swallow a lot of material, making them expensive and heavy. Therefore, according to the invention, a chamber 103 filled with pressurized fluid is arranged around the cylinder 102, which chamber is formed and closed by the outer wall 104. The pressure in the chamber 103 can now be dimensioned in such a way that any radial expansion of the cylinder wall 102 is prevented, or its radial expansion is reduced to an acceptable level under pressure in the cylinder 100. Since the expansion of the outer wall 104 is not harmful, thinner walls 102 and 104 can be used according to the invention, so that the unit becomes lighter, cheaper and more reliable.

Since the pressure in the chamber 103 counteracts the pressure in the cylinder 100, the cylinder wall 102 can no longer expand radially as desired. The supply of the fluid and pressure into the chamber 103 can take place through the inlet 106. Inlet 107 directs the relevant pressure or fluid into chamber 108. Channel 119 shows the inlet to cylinder 100, which may also act as an outlet. The figure also shows that a pump unit can be built directly with the cylinder 100 and the arrangement according to FIG. 57. FIG. 57 shows the pump housing 109, the rotor 11, the cylinder groups 112 and 116 with the piston groups 113 and 117, and the piston shoe groups 114 and 118. If, for example, pressure fluid is sent through inlet 110 into the cylinder 112 of the unit, the action then takes place group 112, 113, 114 as a motor and drives group 116, 117, 118 as a motor so that the motor feeds through line 119 into cylinder 100. A pressure ratio can be generated in this way by giving the group with the cylinders 112 a larger swallowing volume than the group 116, 117, 118 conveying volume. The desired high pressure can then be generated in the cylinder 100 and / or in the chamber 103 from a low or medium pressure unit. The drawing therefore shows a channel 120 which may conduct the pressure from line 119 into the outer chamber 103 (via connection 106) in order to have the same pressure in the cylinder 100 and the outer chamber 103 so that the radial expansion of the cylinder wall 102 becomes zero, even then if this wall has only a small wall thickness. The following values apply in equation (31)

FIGS. 58 to 60 show sections and views through a deep-diving high-pressure piston shoe for radial piston units of the invention. These are particularly suitable for the pumps and motors of this patent application, but they can also be used in general in the high-performance radial piston units of the applicant and inventor, which have arisen in particular through the patent specification of the applicant and inventor, DB-PS 1,302,469. After this, the rotor 608 has the radial webs 708 for guiding the long piston stroke and the piston shoe has seen from above the "H-shape", as the German Patent Office calls it.

This "H-shape" characterizes the "deep-diving piston shoe" of the applicant and inventor, which enables the large piston stroke in a small space and thus for pumps and motors for the invention. Because the high performance with low weight comes through the "deep diving" possible H-shape together with the design of the piston stroke guide and the rotor 608.

The piston shoe of the invention according to FIGS. 58 to 60 remains a deep-diving piston shoe in the above sense, but is said to provide greater resistance to deflection under high load and can therefore be used not only for aircraft, but also for presses and excavator pumps. It is still a finding of the inventor here that conventional piston shoes show a tendency to tip over because they require too long piston shoe feet stored within the piston and are therefore too far away from the outer sliding surface 512 of the piston shoe. So it must be doubted whether the piston shoes that appeared in the FRG around 1970 for high speeds could ever overcome this tendency, which the inventor now recognized and which must lead to leakages. Because the distance between the center of the swivel joint is too far from the outer surface. This cannot be prevented if the piston shoes are not deep diving. In the case of the deep-diving piston shoe, which was introduced by the applicant and inventor at the beginning of the sixties, the angle between the pivot center (axis) in 505 of FIG. 59 from the outer edge (the outer accounts) of the sliding surface 512 can be so acute (see FIG. 59). that such a tendency to leakage can never occur.

On the other hand, the deep-diving piston shoe has a tendency to bend, i.e. the side guide parts are bent away from the piston stroke guide under high load and constant load changes. Not millimeters, but in the order of a thousandth of a millimeter and depending on the number of load changes and the load wax speed. The piston shoe of FIGS. 58 to 60 is to overcome or restrict these defects, in particular restrict or prevent the deflection of the side parts of the deep-diving piston shoe. For this purpose, the rotor 606 according to the invention preferably receives the further recesses 752 for receiving the support 751 of the new piston shoe of the invention. The new marking of the piston shoe of the invention consists in that the slots between the side legs of the "H-shape" are no longer open in the running direction of the piston shoe, but are closed by a bridge that connects the outer ends of the legs of the "H" with each other. The deep-diving mop shoe of the "H-shape" thus has at its front and rear ends of the side guide parts 602 the bridges 751 connecting them and mostly in one piece with them. The slots of the "H" between the legs of the "H" are therefore radial replacing the piston shoe penetrating two windows 750, they are located on both sides of the piston shoe central part 302 and thus between the central part 302: in each case one of the bridge 751 and the side parts 602. When the rotor rotates, one of the rotor-radio webs 708 is immersed in each of these windows, one in each of the windows 750. If, as in FIG. 53, pistons according to our DE OS 30 41 367 are used, then the piston fingers 741, 742 also engage in these windows 750, as can be seen in FIG. 59. The fingers 741, 742 and the webs 708 pass partially and temporarily completely through the windows 950 when diving into the pen, that is to say during the long piston stroke. The pistons 501 slide in the cylinders 503 of the rotor 608. In the piston swivel bed, which today is mostly a partially cylindrical surface of a hollow cylinder, the central part of the piston shoe is supported by means of the swivel joint 302, which has a cylinder part surface which is complementary and matches the surface 510. Piston bed 510 and piston shoe swivel roller (at the center web) 302 thus form sliding surfaces with a swivel radius 509 around swivel axis or swivel point 505. Today, the piston shoes are mostly cast in this form and are mostly made of a certain bronze. The piston shoe beds are ground in series with shape grinding wheels, whereby a number of pistons with axially aligned beds are clamped in one device on the surface grinding machine. In the figures, the new piston shoe has also wrung the lateral radial inward extensions 951 which can engage in the rotor recesses 552 and which can be provided with the recesses 952 for the arrangement of pull rings for the suction stroke for their sliding on the inner pull surfaces, for the rest the piston shoe 302 in the outer surface, that is to say in the sliding surface 312, the drain grooves 577 of our DE patent 25 00 779 between the surrounding sealing surface of the pressure fluid pockets 515 and the front and rear piston shoe support surface parts 580. They are through the channels 616 Piston and shoe from cylinder 503 are fed with pressurized fluid. But they need something new Piston shoe of the current invention no longer the longer extension in the circumferential direction of the inventor's patent 25 00 779, since the new piston shoe in the direction of the pivot axis 505 is considerably strengthened by the bridges 751 according to the invention. The support surfaces 580 can now either be provided with further 'drainage grooves to create interstatic bearings according to the systems of the inventor, or hydrodynamic tread parts can now be formed over the support surfaces 580, which then act and are designed in the sense of FIGS. 55, 56 of this patent application. The central web, as the upper part of the swivel joint 302, has bevels 740 which enable the swiveling between the radial webs 708 of the rotor or the fingers 741, 742 of the piston 503 without bumping into them. You can also see them in Figure 60-A. This figure also shows that the new piston shoe can be extended so long in the axial direction, i.e. parallel to the axis of the rotor 608 and the pivot joint 50 or the swivel axis 505, that very large and load-bearing parts of the sliding surface of the sliding surfaces 602 remain. They can be so far in the axial direction mentioned that the windows 750 of the invention appear to be almost short. However, the windows 750 of the invention must not be made too short, so that a sufficient encirclement of the pistons and their arms 741; 742 are encompassed by the wall of the radial web 708 of the rotor 608 in order to prevent lateral tilting or a tendency to do so, because this would Clamp the piston fingers or piston arms 741, 742 of the piston 503 on the radial webs 708 of the rotor and in the cylinder 103.

FIGS. 61 A to C show a further embodiment of a piston-piston shoe arrangement according to the invention. Here, the piston shoe of FIGS. 1 and 2 of our Eurôpa-OS 0 064 563 has been modified such that the central part 12 of the E-OS, which in FIG. 61 has the number 302, has a completely full cylindrical roller in the radius 509 about the pivot axis 505 . The shoe is secured here against falling out of the piston bed by the pin 762 which engages in the piston arms, on which the swivel roller 302 rests and swings with its swivel surface 511. Above the central part 302, which here constitutes the swivel roller with a completely cylindrical cross-section, the surface 511 is at a distance from the stem 762 or touches it only in one point. This arrangement is usually sufficient for normal engine operation. It is also cheap and prevents jamming in fits that have become too tight during production. On the other hand, however, self-priming pumps are occasionally required, and for these, as well as for motors when using them in special machines or vehicles, sudden excess speeds occur, it is therefore better to hold the swivel roller 302 more firmly in the piston bed. Therefore, the holding block 761 is arranged in FIG. 61-C and with the pin 761 in the piston fingers, which are also called piston arms in the publication mentioned. It is then expedient to match the radially inner surface of block 761 with the radius of the swivel surface and the bearing bed surface, that is to say with the radius 509 or. 508 of the roller 302 and the bed 510 to be provided. This inner surface now has the reference number 710 and the surface 511 slides on it.

In FIG. 62 it is shown that the pivot axis 505 can also lift a greater distance than that of the radius 509 from the block 761. Then the inner surface 910 of the block 961 is given a larger radius than the radius of the swivel roller lower surface, namely the radius 909. The upper part of the swivel roller or the central web of the piston shoe then receives the corresponding radius 948, which is almost the same with the radius 909, which forms the upper outer surface 911 which slides on the inner surface 910 when the piston shoe swings in the piston. So that no parts collide, the block 961 and the piston shoe swivel roller 302 beyond the mating surfaces 910 and 911, with the radii 908 and 909, can be provided with bevels or recesses 963 and / or 967.965.

FIGS. 63 A and 63 B show a further design option for connecting the piston to a piston shoe. It can also be used for non "H-shaped" piston shoes. According to the invention, the piston receives the recesses 967 somewhat wider in the radial direction than the radial extension of the pin 966. After the pivoting roller 302 of the piston shoe has been inserted into the piston 501, the pin 966 protrudes through the pivoting roller 302, projecting into the recesses 967, used. Since it is longer than the swivel roller, but the recesses are closed radially upward, the pin 966 prevents the piston shoe from falling out of the bearing bed 510 of the piston 501. The ends of the Pin 966 can move freely in the recesses 967 when the piston shoe 502 swings with the swivel roller 302 in the bearing bed 510 of the piston 501. It is preferred then to arrange the line channels 516, 517 from the relevant cylinder through the piston and the swivel roller, as well as through the central part of the piston shoe, not in the piston axis, but laterally therefrom, for example as shown in the figures. The pressure fluid pockets 968 in the swivel roller 302 are then placed such that they hit the channels 516, 517 through the piston 501 and the piston shoe 502 when the piston shoe is pivoted. The underside of the piston shoe guide part can have recesses 969 so that pistons - radial fingers can engage or immerse in them and collision of piston and piston shoe parts is avoided.

FIG. 64 is a detail from FIG. 17. FIG. 64 is supplied so that it can be used as the summary for the published specification because FIG. 17 would exceed the scale or the place in the published specification. The description of FIG. 17 therefore also applies to FIG. 64.

Claims (24)

1.) Unit with at least one conical ring element, which contains a tapered portion between its radially inner and outer parts (a tapered portion between radial outer and inner portions) with an inner cavity radially inside said conical part ( wherein the cavity may also be called chamber, characterized in that said element (1,2,5,6,11,12,307) has a centering (15,19,20, 21,23,41,43 , 48,56,57) and at least one edition (7,8,10,41,42,48, 52,94, 305, 315) are assigned. 2.) Unit according to claim 1, characterized in that said element (1,5, 11) is assigned at least one further element (2, 6, 12) and the two elements have at least one seat (34, 48, 57 ) to form a spacing part ((8, 32, 34)) determining an axial distance and form a sealing space (7, 31) for receiving a sealing ring (7, 75) for sealing said inner cavity (14, 37, 51, 61, 311) is arranged. 3.) Unit according to claim 1, characterized in that two elements (eg; 1,2) with their inner cavities = men (61, 14, 311) are arranged facing each other, with at least one outer ring (8, 320) between the is placed, the interior of which (for example: 7) accommodates a sealing ring (7, 75, 317) for sealing the two aforementioned internal cavities of the aforementioned elements. 4.) Unit according to claim, characterized in that the two elements (for example: 1, 2) on their radially outer parts (for example: 59) are fixed together in the axial direction, the fastening (9, 89, 90, 91, 318) for holding together the radial outer parts (for example: 59) of the two elements mentioned, following the possible radial expansion of the named outer parts of the elements mentioned and being sufficiently strong to withstand internal pressure of over 100 bar to allow the aforementioned interior spaces without the fastening giving way. 5.) Unit according to claim 4, characterized in that said attachment (9,89,90,91,318,320,321) is divided radially into several parts, for example in segments (37-A, B, C, D, E, F, etc .), so that the parts of the attachment can follow the radial expansion of the elements (112, 307, etc.). 6.) Unit according to claim 3, characterized in that the outer ring (8,48,56,57,310) is designed as parts of one or more elements (1, 2, 5, 6, 11, 12), ie with the element in question (the elements) is in one piece. 7.) Unit according to claim 1, characterized in that said support (for example: 8) is designed as a reciprocating piston (8,52,36,94,305) and said reciprocating piston by means of a mechanical device, preferably by means of an eccentric = part (55, 99) is driven on a revolving shaft (55 - 97), for example via a piston shoe (52, 21, 9) to the pumping stroke and, if necessary, means are arranged, such as contact pistons (95, 96, 115 ), Lines (69, 72) and a pressure fluid generator, through which the sliding surfaces of the said piston shoe and its neighboring surfaces are lubricated, possibly with a temporal change in the lubricating fluid pressure parallel to the pressure in the pumping chamber (eg: 14, 61) and / or parallel to the resistance of the element in question to its compression. (Figure 17). 8.) Unit according to claim 1, characterized in that said support (305, 315) is a 7-piston (305) which can be reciprocated in a second cylinder (304), the unit is also a first cylinder (301) with a first piston which can be reciprocated therein (302) contains, said first cylinder is connected to said second cylinder by a line (303), means for the reciprocation of said first piston (55,334,336,345 etc.) are arranged and liquid is present in said line and cylinders, so that the movement of said e _r stkolbens by means of wear of said fluid to said second piston and thereby the said inner cavity (14,61) of said elemene - tes (1,2,307 etc.) is periodically enlarged and reduced. (Figure 22) 9.) Unit according to claim 8, characterized in that said first piston (302) and said first cylinder (301) have smaller diameters than said second piston (305) and said second cylinder (304), the fluid in the ge = called line (303) and said cylinders (301, 304) is a liquid, said first piston via a piston shoe (ZB9, 21, 52) by means of a drive, for example by means of a shaft with a rotating shaft (97, 11) with eccentric disc (55, 10) is reciprocally reciprocated, the fluid mentioned transfers the reciprocation of the first piston to the second piston in relation to the diameter mentioned, thereby reciprocally reciprocally reciprocating the second piston and the second piston to the relevant element (307 ) acting, whose interior space (14, 311) and thus the pump chamber (14, 311) periodically enlarged and reduced. 10.) Unit according to claim 8 or 9, characterized in that a plurality of the elements (1,2, 307) is assigned to the drive (10,11,55,98,99,52,36,336,345 etc.) and said Interior spaces (14, 61, 311) or chambers are connected to a common delivery line (314) for the delivery of pressurized fluid, and / or automatic filling agents (for example (326 to 329) are assigned in the unit of claim 9, the automatic = ensure that there is always a sufficient amount of liquid in the pipe and the cylinder mentioned for the precise operation of the transfer of the above-mentioned reciprocation of the first piston to the second piston, and / or in the units of the claim 8 or 9 safety valves are arranged to prevent breaks, and / or that in the unit of claim 9 said liquid is a lubricating liquid, for example oil, while said interior or the said chamber is filled with non-lubricating = the fluid, for example water, and the named interior or chamber (14, 61, 311) is thereby used as a pump of a non-lubricating liquid or slurry, 11.) Unit according to claim 3, characterized in that said elements consist of fibrous materials with connections = means, for example made of carbon fiber and the radially outer parts of said elements (1, 2) according to FIG. 9, for example by means of epoxy resin are glued. 12.) Unit for example according to claim 1 or without the element of claim 1, characterized in that two pistons (59, 60 or 58, 59 of Figures 12 or 14) rest on each other in a radially freely movable manner and means (for example 83, 84 or 64,70,72,71) are arranged to hold the two pistons together when the suction stroke is depressurized. 13.) Unit according to claim 12 or unit with a pump piston, for example 58, characterized in that the piston (58) is acted on at both ends with different fluids, wherein at least one fluid can be a non-lubricating liquid and an annular groove in the middle of the piston Example 65 is arranged with a drain line (66) (FIG. 12) which serves as a collecting arrangement for collecting leakage of one, the other, or both fluids. 14.). Unit according to claim 1, characterized in that a plurality of elements (1, 2) form a plurality of inner spaces, chambers (14) 61) arranged one behind the other axially, one of said supports a piston (36) with piston shoe (21) and a further support is a seat (107, 98), the piston shoe slides on a running surface 156 of a piston stroke guide (99), a guide extends from the piston, for example a hollow tube (74, 108) through the chambers or interior spaces of the elements and optionally guided in a bore (161), the piston shoes (21) have extensive contact surfaces for guidance on the piston stroke guide, pressure fluid may be conducted in bearing pockets 112 of the piston shoe and one of the supports is subject to a periodic movement or constant rotation, so that the latter Interiors, or. Chambers (14, 61) form a pump or a motor and act as such an aggregate without a piston seal or an element guide having to be arranged. 15.) Unit according to at least one of the patent claims, characterized in that the unit is used to generate a fluid stream (802) and said fluid stream for cutting or atomizing onto a body or a jet onto fluid or powder, or. Solid material (801) is directed. (Figure 26.) 16.) Unit according to at least one of the claims, characterized in that the unit corresponds to the conditions of one or more of the calculation formulas of this patent application or a definition or condition of the description of the exemplary embodiments of this patent application. 17.) Unit with a piston, a piston shoe and a piston stroke guide, characterized in that the piston shoe (2, 502) is arranged between the piston (5, 501) and the piston stroke guide (514) and with its outer surface (512) on the piston stroke guide surface (513) of said piston stroke guide slides, said piston forms a head as a bearing bed (510) with radius (508) around the pivot axis (505) of the piston shoe on the piston (501) on which the pivot surface (511) has the same radius (509) rests and swivels, a holding surface (513, 531, 532, 523, 524, 572) is present in the unit or on the piston shoe, the piston (501) is perpendicular to its axis (504) and to the swivel axis (505) para = Hele forms recesses (518) into which pins (507) arranged in its transverse bore (506) protrude and holders (529,619) are arranged which touch the holding surface with a tite (574,537,538) and the holder with one into the named A recess (518) of an immersible eye (520) is provided, which engages around the relevant end of said pin (507), the arrangement of the eye within the recess making it possible for the eye to be inserted into the cylinder ( 503) a pump or a motor with rotor or body (608) can occur temporarily or continuously. 18.) Unit, characterized in that a rotor (401, Figure 34) forms an outer bearing (461,462) with pressure fluid pockets (407,477), which can be acted upon with different pressures from different working chambers (439,440) and / or in the rotor called pressure = chambers (402, 403) are arranged with pressure pistons (404, 405, FIG. 34), to which auxiliary pressure pistons (411, 611) in axially diametrical or opposite auxiliary pressure chambers (410, 412) are assigned and / or designed according to FIG. 36 = double control mirrors with pressure fluid zones around 422 and are arranged around 420. 19.) Unit with a piston stroke guide and a piston shoe on a piston, characterized (FIGS. 37 to 40, 52 to 56) that in the outer surface (512) of the piston shoe (502) a pressure fluid pocket (515) with a surrounding sealing surface (578) is arranged whose pressure fluid zone has a larger cross section parallel to the piston stroke guide (514) than the cross section through the piston (501) is perpendicular to its axis (504). 20.) Unit with a piston and a piston shoe according to Figures 41 to 48, characterized in that the piston forms a head as a bed with the bed surface 510 with the radius 508 about the pivot axis 505, on which the pivot surface 511 of the piston shoe 502 with Radius 509 is pivotable and / or the piston head forms axial projections 588, which protrude beyond the diameter 637 of the piston 501 and / or holding surfaces 583 are arranged and, in addition, the piston 501 and the piston shoe 502 are pivotally connected to one another by means of brackets 584. 21.) Unit with a piston stroke guide and a piston shoe between this and a piston according to FIGS. 49, 50, characterized in that a cross pin 595 is arranged in the piston, the ends of which pivotally support piston shoes 1102, 1202 and pressure fluid pockets 515 are assigned to the piston shoe, which are periodically or continuously fed with pressure fluid from the relevant cylinder 503 and which lubricate the sliding movement or the swiveling movement of the piston shoe and reduce its friction. 22.) Unit with a in a cylinder (100) reciprocable piston (101), characterized in that the cylinder wall (102) is surrounded by a pressure-filled chamber (103) (Figure 57), whereby the said chamber with the a radial expansion or breakage of the cylinder wall (102) under internal pressure in the cylinder (100) is prevented in its pressure. 23.) Unit with a rotor, a piston and a piston shoe, for example according to FIGS. 58 to 60, characterized in that the rotor 608 is provided with radial webs 708 which are immersible in window 750 of the piston shoe and the named piston shoe in Direction of movement in front of and behind the named and arranged windows 750 are the legs 602 of the deep-tacking, H-shaped, piston shoe connecting bridges 751 which increase its rigidity and rigidity and which can dip into recesses 752, or 752 and 952 arranged in the rotor 608 . 24.) Unit according to at least one of the figures of this patent application, characterized in that at least one embodiment, which is shown or described in at least one of the figures or in the description, is arranged,

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