EP0216956A2 - Units with a fluid flowing through them and with elements resilient in an axial direction and defining chambers for pressures up to several thousand atmospheres - Google Patents

Abstract

The invention is concerned with providing a unit with a fluid flowing through it even for high pressures of several thousand bar, which unit works in an operationally reliable manner and with high efficiency but is nevertheless inexpensive and space-saving. Such a unit is preferably to work between 400 and 4000 bar in order to simplify and improve measures which are disclosed in European Preliminary Published Specification 0,102,441. For this purpose, novel conical ring parts are proposed, tested and set in certain proportions to pressures in inner chambers and/or outer chambers. The faults of previous units, which limited their pressure, are recognised and overcome, in the course of which the design, elimination of dead spaces, dispensing with locations to be sealed and better seals for high pressures are tested and their theoretical principles determined. W-elements, V-elements, conical rings with projections for radial limits and other means made the units operationally safe during testing and produced high efficiency. <IMAGE>

Description

Diaphragm pumps, which are mostly used for low pressures, have been known in the art since the last century. Occasionally literature is also published on allegedly high-pressure units with disc springs, but when testing the invention it was found that these fail even at a few hundred atmospheres of pressure. A high-pressure version was proposed in the European disclosure document (hereinafter: E-OS) E-OS- □ 102 441. This unit was built and tested in the course of the preparation for the current invention in several examples and designs. It has proven itself for prints up to. around 1500 bar good, also allowed higher pressures, but became too precise and expensive to manufacture for higher pressures. On the other hand, water pumps for high pressures of several thousand bars are particularly required, for example for stone drilling, water jet cutting and the like. Because there are no pumps for it, Axial Boosters were used, which are expensive and voluminoes. There is therefore an urgent need for a pump for water for several thousand bars, which does not exist until today.

The invention is therefore based on the object to provide a pump for non-lubricating media, such as water, for pressures up to several thousand bars, for example up to 4000 bar, which is inexpensive to manufacture, space-saving, reliable and durable , as well as works with good efficiency. Further objectives, subtasks or tasks will appear from the description of the exemplary embodiments of the invention explained in the figures.

• Fig.1 einen Laengsschnitt durch eine bekannte Anordnung;
• Fig.2 einen Laengsschnitt in schematischer Darstellung;
• Fig.3 einen laengsschnitt durch eine Anordnung;
• Fig.4 ein Diagramm;
• Fig.5 ein Diagramm;
• Fig.6 einen Laengsschnitt durch einen konischen Ring;
• Fig.7 einen Laengsschnitt durch eine Anordnung;
• Fig.8 einen Laengsschnitt durch eine Pumpanordnung und die
• Fig.9 und Fig.10 sind Laengsschnitte durch alternative Ausbildungen zu einigen der genannten anderen Figuren.
• Fig.11 ist ein Laengsschnitt durch ein Aggregat der Erfindung.
• Fig.12 ist ein Laengsschnitt durch ein Ausfuehrungsbeispiel;
• Fig.13 ist auch ein Schnitt durch ein Ausfuehrungsbeispiel;
• Fig.14 ist ebenfalls ein Schnitt durch ein Ausfuehrungsbeispiel der Erfindung.
• Fig./5 ist ein Diagramm mit technischen Daten.
• Fig.16 ist ein Diagramm mit weiteren technischen Daten;
• Fig.17 ist ein Schnitt durch ein weiteres Ausfuehrungsbeispiel, und :
• Fig.18 ist ein Schnitt durch einen Teil der Erfindung.
• Figuren 19 bis 32 zeigen laengsschnitte durch 14 Aus fuehrungsbeispiele der Erfindung oder durch ihre Teile.
• Fig.33ist ein Laengsschnitt durch die bekannte Technik.
• Figuren 34 bis 37 sind Laengsschnitte durch Teile von Ausfuehrungsbeispielen nach der Erfindung.
• Fig.38 ist eine technische Erklaerung der Erfindungswirkung.
• Figuren 39 bis 43 zeigen Laengsschnitte durch erfindungsgemaesse Teile oder Ausfuehrungsbeispiele.
• Figuren 44 bis 47 zeigen Laengsschnitte durch alternative Ausfuehrungsbeispicle oder Formen der Erfindung.
• Figuren 48 und 49 zeigen entsprechende Querschnitte durch Laengsschnitte der in den Figuren dargestellten Ausfuehrungsbeispiele.
• Fig.50 ist ein Laengsschnitt durch eine Anordnung der Technik.
• Fig.51 ist ein Laengsschnitt durch eine Anordnung der Technik.
• Fig.52 ist ein Laengsschnitt durch eine Anordnung der Technik.
• Fig.53 ist ein Laengsschnitt durch eine Anordnung der Technick.
• Fig.54 ist ein Laengsschnitt durch eine Anordnung der Technik.
• Fig.55 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.56 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.57 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.58 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.59 ist ein Laengsschnitt durch eine Anordnung der Technik.
• Fig.60 ist ein Laengsschnitt durch eine Anordnung der Technik.
• Fig.61 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.62 ist ein Querschnitt entlang der gepfeilten linie durch Figur 61.
• Fig.63 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.64 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.65 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.66 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.67 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.68 ist. ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.69 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.70 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.71 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.72 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.73 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.74 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.75 ist ein Laengsschnitt durch, eine Anordnung der Erfindung.
• Fig.76 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig. 77 ist ein Laengsschnitt durch. eine Anordnung der Erfindung.
• Fig.78 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.79 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.80 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.81 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.82 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.83 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.8; ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.85 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.86 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.87 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.88 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.89 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.90 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.91 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.92 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.93 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.94 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.95 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.96 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.97 ist ein Laengsschnitt durch eine Anordnung der Erfindung, und, :
• Fig.98 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.99 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.100 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.101 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.102 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.103 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.104 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.105 ist ein Querschnitt durch Figur 103 entlang der Pfeillinie.
• Fig.106 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.107 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.108 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.109 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.110 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.111 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.112 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.113 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.114 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.115 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.116 i₅t ein Diagramm.
• Fig.117 ist ein Diagramm.
• Fig.118 ist ein Diagramm.
• Fig.119 ist ein Laengsschnitt durch eine Anordnung der Erfindung.
• Fig.120 ist ein Laengsschnitt durch eine Anordnung der Erfindung, und
• Fig.121 ist ein Laengsschnitt durch eine Anordnung der Erfindung.

The invention is described in more detail with reference to the figures, in which:

• 1 shows a longitudinal section through a known arrangement;
• 2 shows a longitudinal section in a schematic representation;
• 3 shows a longitudinal section through an arrangement;
• 4 shows a diagram;
• 5 shows a diagram;
• 6 shows a longitudinal section through a conical ring;
• 7 shows a longitudinal section through an arrangement;
• 8 shows a longitudinal section through a pump arrangement and
• 9 and 10 are longitudinal sections through alternative designs to some of the other figures mentioned.
• 11 is a longitudinal section through an assembly of the invention.
• Fig.12 is a longitudinal section through an exemplary embodiment;
• Fig.13 is also a section through an exemplary embodiment;
• Fig.14 is also a section through an exemplary embodiment of the invention.
• Fig. 5 is a diagram with technical data.
• Fig. 16 is a diagram with further technical data;
• 17 is a section through another exemplary embodiment, and:
• Figure 18 is a section through part of the invention.
• FIGS. 19 to 32 show longitudinal sections through 14 from exemplary embodiments of the invention or through its parts.
• Fig. 33 is a longitudinal section through the known technique.
• FIGS. 34 to 37 are longitudinal sections through parts of exemplary embodiments according to the invention.
• Fig. 38 is a technical explanation of the effect of the invention.
• FIGS. 39 to 43 show longitudinal sections through parts or exemplary embodiments according to the invention.
• FIGS. 44 to 47 show longitudinal sections through alternative exemplary embodiments or forms of the invention.
• FIGS. 48 and 49 show corresponding cross sections through longitudinal sections of the exemplary embodiments shown in the figures.
• Fig. 50 is a longitudinal section through an arrangement of technology.
• Fig. 51 is a longitudinal section through an arrangement of technology.
• Fig. 52 is a longitudinal section through an arrangement of technology.
• Fig. 53 is a longitudinal section through a Technick arrangement.
• Fig. 54 is a longitudinal section through an arrangement of technology.
• Fig. 55 is a longitudinal section through an arrangement of the invention.
• Fig. 56 is a longitudinal section through an arrangement of the invention.
• Fig. 57 is a longitudinal section through an arrangement of the invention.
• Fig. 58 is a longitudinal section through an arrangement of the invention.
• Fig. 59 is a longitudinal section through an arrangement of technology.
• Fig. 60 is a longitudinal section through an arrangement of technology.
• Fig. 61 is a longitudinal section through an arrangement of the invention.
• Fig. 62 is a cross section along the arrowed line through Fig. 61.
• Fig. 63 is a longitudinal section through an arrangement of the invention.
• Fig. 64 is a longitudinal section through an arrangement of the invention.
• Fig. 65 is a longitudinal section through an arrangement of the invention.
• Fig. 66 is a longitudinal section through an arrangement of the invention.
• Fig. 67 is a longitudinal section through an arrangement of the invention.
• Fig. 68 is. a longitudinal section through an arrangement of the invention.
• Fig. 69 is a longitudinal section through an arrangement of the invention.
• Fig. 70 is a longitudinal section through an arrangement of the invention.
• Fig. 71 is a longitudinal section through an arrangement of the invention.
• Fig. 72 is a longitudinal section through an arrangement of the invention.
• Fig. 73 is a longitudinal section through an arrangement of the invention.
• Fig. 74 is a longitudinal section through an arrangement of the invention.
• Fig.75 is a longitudinal section through an arrangement of the invention.
• Fig. 76 is a longitudinal section through an arrangement of the invention.
• Fig. 77 is a longitudinal section through. an arrangement of the invention.
• Fig. 78 is a longitudinal section through an arrangement of the invention.
• Fig. 79 is a longitudinal section through an arrangement of the invention.
• Fig. 80 is a longitudinal section through an arrangement of the invention.
• Fig. 81 is a longitudinal section through an arrangement of the invention.
• Fig. 82 is a longitudinal section through an arrangement of the invention.
• Fig. 83 is a longitudinal section through an arrangement of the invention.
• Fig.8; is a longitudinal section through an arrangement of the invention.
• Fig. 85 is a longitudinal section through an arrangement of the invention.
• Fig. 86 is a longitudinal section through an arrangement of the invention.
• Fig. 87 is a longitudinal section through an arrangement of the invention.
• Fig. 88 is a longitudinal section through an arrangement of the invention.
• Fig. 89 is a longitudinal section through an arrangement of the invention.
• Figure 90 is a longitudinal section through an arrangement of the invention.
• Fig. 91 is a longitudinal section through an arrangement of the invention.
• Fig. 92 is a longitudinal section through an arrangement of the invention.
• Fig. 93 is a longitudinal section through an arrangement of the invention.
• Fig. 94 is a longitudinal section through an arrangement of the invention.
• Fig. 95 is a longitudinal section through an arrangement of the invention.
• Fig. 96 is a longitudinal section through an arrangement of the invention.
• Fig. 97 is a longitudinal section through an arrangement of the invention, and:
• Fig. 98 is a longitudinal section through an arrangement of the invention.
• Fig. 99 is a longitudinal section through an arrangement of the invention.
• Fig. 100 is a longitudinal section through an arrangement of the invention.
• Fig. 101 is a longitudinal section through an arrangement of the invention.
• Fig. 102 is a longitudinal section through an arrangement of the invention.
• Fig. 103 is a longitudinal section through an arrangement of the invention.
• Fig. 104 is a longitudinal section through an arrangement of the invention.
• Figure 105 is a cross section through Figure 103 along the arrow line.
• Fig. 106 is a longitudinal section through an arrangement of the invention.
• Fig. 107 is a longitudinal section through an arrangement of the invention.
• Fig. 108 is a longitudinal section through an arrangement of the invention.
• Fig. 109 is a longitudinal section through an arrangement of the invention.
• Fig. 110 is a longitudinal section through an arrangement of the invention.
• Fig. 111 is a longitudinal section through an arrangement of the invention.
• Fig. 112 is a longitudinal section through an arrangement of the invention.
• Fig. 113 is a longitudinal section through an arrangement of the invention.
• Fig. 114 is a longitudinal section through an arrangement of the invention.
• Fig. 115 is a longitudinal section through an arrangement of the invention.
• Fig. 116 i ₅ t a diagram.
• Fig. 117 is a diagram.
• Fig. 118 is a diagram.
• Fig.119 is a longitudinal section through an arrangement of the invention.
• Fig.120 is a longitudinal section through an arrangement of the invention, and
• Fig. 121 is a longitudinal section through an arrangement of the invention.

The calculation of the conical rings or disc springs according to Almen and Lascio is known from EP OS - 0 102 441. This document also provides the calculations of the amount of conveyance under the conical ring and the loading of the conical ring by flood pressure according to Eickmann, if the conical spring is used as a similar conical ring as a pump element. This document also shows examples of the use of the conical rings as pump elements, and also together clamp ring parts for ring pairs.

The invention recognizes that the highest load on the conical ring occurs in the line with which the conical ring lies on a flat surface. Because the total load of the body of the conical ring during its compression or relaxation plus the eventual load on the cross-sectional area of the conical ring due to possible fluid pressure under the ring surface falls when resting on the flat plate in an infinitely thin line together. The load on the support line becomes infinitely high and so high that the material from which the ring is made can no longer bear the load. This load on the line becomes particularly high with conical rings used as high-pressure pump elements. However, it is not enough to cope with the high load on the line support alone, because when the conical ring is compressed or relaxed, the inner diameter of the support line decreases and the outer diameter of the support line increases. This creates a radially moving line support both on the inside diameter and on the outside diameter of the conical ring or the plate spring. This radial movement takes place under the infinitely high load. The radial movement is only very small, for rings with a difference of about 10 millimeters = difference between inside and outside - radius and a deflection of about 0.3 millimeters, it is only about 0.003 millimeters radially inwards and outwards. Under the infinitely high load, especially on conical rings used as high-pressure pump elements, friction arises, the overcoming of which requires up to ten times more force than the compression of the respective conical ring. This is a very high waste of power that the previous technology has not recognized and for their Swirl she gave no lessons.

The invention is therefore based on the object of reducing the frictional forces on the axial supports or brackets of the conical rings, thereby saving forces and friction and at the same time increasing the operational safety of the conical rings used in this way and the clamp rings for making conical ring elements cheaper in production.

This object is achieved on the disc spring described in the preamble of claim 1 or on the conical rings according to the characterizing part of patent claim 1.

Helpful configurations are achieved according to subclaims 2 to 13.

In the figures, the end digits 1 show a conical ring or, which is basically the same, a disc spring with special dimensions; 2 a radially flexible ring part; 3 an overlying axial end of a conical ring; 4 the axial inner surface and 5 the axial outer surface = before a conical ring. The plate spring is also a conical ring, so that the term conical ring is used in the following and that includes the plate spring.

In Figure 1, the conical rings with their hollow conical inner surfaces 4 facing each other are arranged axially aligned. The flat plate 8 is located between them. Above the ring 1 is the upper plate 6 and below the ring 11 is the lower bearing plate 7. If you now press the top plate 6 with sufficient force from above, then the conical rings 1 and are pressed together in the axial direction. The same arrangement is shown in FIG. 2 = matically and in such a way that the conical rings 1 and 11 are shown as straight, oblique lines.

When compression, also called compression, of the conical rings 1 and 11, these bend around their respective centers, so that, as the bevel now becomes a plane, the radial outer ends of the conical rings 1 and 11 radially outward by the dimension 16 and the radially inward ends radially inward around dimension 17. The radially outer and inner ends of the conical rings 1 and 11, the radially directed paths 16 and 17 on the plate 8, respectively on the plates 6 and 7 back. Since the inner tensions arise when the conical rings 1 and 11 are pressed together, the radially inner and outer ends of the conical rings press onto the plates 6 to 8 and the radial movements 16 and 17 cause friction under load.

This friction is not small because the load rests on the ring lines 9 and 10 of FIG. 2. The load on a line is always infinitely high because the line is not a surface. A surface support is not only not created with lines 1 and 11 in FIG. 2, but also with the current rings 1 and 11 in FIG. Because, indeed, you can grind the axial ends of the conical rings 1 and 2 on the desired support = places 3 and 13 so that they form flat surface supports 3 and 13 in the untensioned condition, which is shown in FIG. But as soon as the compression begins, the conical rings 1 and 11 bend, so that the angle of attack to the plates 6 to 8 changes. However, if this angle of attack changes because the conical rings 1 and 11 bend, the ground axial bearing surfaces 3 and 13 also bend at approximately the same angular extent as the conical rings 1 and 11 bend themselves. So there is an angle between the Axial bearing surfaces 3.13 of the conical rings 1.11 and the plates 6 to 8. If this angle arises, which arises even with the slightest compression of the conical rings 1.11, even if it initially appears very small, then the conical in question lies Ring 1.11 no longer with the support surface 3.13 on the plate 6 to 8 in question, but only with the ring line which lies between the support surface 3.13 and the conical part beginning there, the outside or inner surface 4 or 5 of the relevant ko = African ring 1.11. In any case, there is a line support instead of a surface support and the load on the line, which is infinitely thin, becomes infinitely high.

At low loads, the line may transform into a surface support due to the plastic deformability of the piece of the conical ring 1, 11 and the plate 6 to 8 in question. With strong deflection and in any case when the conical ring is loaded by fluid pressure of the hollow conical axial inner surface 4, the material from which rings 1, 11 and plates 6 to 8 are made can no longer yield sufficiently and gives rise to an intolerable. high local load, similar to the line support.

In conventional disc spring use, this technical functionality may have gone unnoticed because either the loads were not very high, the load, material destruction and friction were accepted, or they were not taken into account, and above all because spring columns made of many springs were mostly used , where these problems do not occur, because only the last plate spring rests on a flat ring or on a plate 6, 7 or 8.

In the case of thick conical rings, however, the forces and friction described become very high, especially in the high pressure pumps of the European patent application mentioned at the beginning.

Figure 6 shows a Beisoiel a conical rings used in these pumps EP OS in mass letter 1: 1 with 60 mm inner diameter and 7 mm ingdicke ^R. The nose 12 is, however, one according to the invention and is not present in the rings of the EP OS mentioned. In Figures 6 to 8, this conical ring is exaggerated only in relation to the angle of the cone, because it is so up to date small is that you can not draw it to scale. Because the ring is only 0.3 millimeters conical. So it can only be pressed together by 0.3 millimeters until it is completely flat. With this compression of 0.3 millimeters, the inner diameter is reduced by a measure of 17, slightly less than o, o3 millimeters, i.e. from 60,000 mm to 59,997 millimeters, and the outer diameter is expanded from 87,000 mm to 87,003 millimeters, that is by UM the size 16 to just under 0.003 millimeters.

The force calculated in the sense of Almen Lascio, which is required to compress the conical ring of FIGS. 6 to 8 by the amount of 0.3 millimeters, is approximately 3200 kilograms. With an oil pressure or water pressure of, for example, 1500 atmospheres within the hollow conical part, that is to say acting on the inner surface 4, the force exerted on the ring by fluid pressure is approximately 22,000 kilograms. The total load on the ring line 9 is therefore somewhat higher than 25000 kilograms. This high load is not on a ring-shaped surface, but on a ring line, as was previously carried out. The line can never carry such a high load. On the one hand, the material is destroyed and, on the other hand, with this load, even with a radial movement of only 0.003 millimeters, considerable friction forces are created that are not recoverable losses. In a pump set of conical rings to the EP 06, for example, the figure 8 were required for each 0, ₃ mm at 700 Atmos = eral water pressure in the pump chamber 50 is already approximately 30,000 kg force for compression of the two conical rings for the ring of the size, as the current invention recognized.

According to FIG. 7, the first measures of the current invention are therefore taken. On the one hand, the axially extended ring part 12 is arranged on the conical ring of FIGS. 6 to 8 on the radial outer edge of the conical ring 1, 11 and extends from the hollow conical part, i.e. from the axial inner surface 4 in the direction of the hollow conical ring end 4 and at the axial end of the cylindrical one Ring part 12 arranged the pad 13. According to FIG. 7, the two contact surfaces 13 of the conical rings 1, 11 are placed on top of each other so that they form the common support 23. The conical rings 1, 11 are directed in opposite directions to form the conical ring pair 1, 11, the hollow conical inner surfaces 4 facing each other and the hollow conical space 50 being formed between them. which can be used later, if desired, as a pump room or as a motor work room. When the supports 13 rest on one another in the common support 23, any friction between the supports 13 is avoided, because during the compression and relaxation, both conical ring elements 1 and 11 experience the same radial expansion or contraction at the same time. In practice, the nose 12 has a rounding at the end of the cylindrical part, because sharp edges at the high forces lead to cracks in the material which would break the conical rings; on the axially outer part, however, the nose 12 is designed as a cylindrical ring part with a cylindrical inner surface, so that the centering ring 20, which centers the ring parts 12 on one another, can be inserted radially into it. Because of the rounding at the root of the lugs 12, the centering ring 20 must be shaped in an adapted manner on its outer surface or bevelled at the ends of a cylindrical central part of its outer surface. The plastic sealing ring 26 can be arranged radially within the centering ring 20 in order to seal the pump chamber 50.

So that the described friction is also prevented on the radially inner support 3, axially the axial ends of the conical ring pair 1, 1, 1 are arranged in each case a radially flexible or resilient, essentially = cylindrical, ring 2; Ring 1 and the other on the conical rings 11. When the conical rings 1, 11 are pressed together, the cylindrical ring 2 at the end abutting the conical rings is pressed radially inward as a result of the radial inward movement 17 of FIG. 2, as in FIG. 3 represented by dashed lines in an exaggerated measure. The other axial end of the ring 2 remains resting on the plate 6,8 concerned. The deformation of the Rin = ges 2 takes place in the plastic material area, so that the ring acts as an axial support and a radial spring.

The forces required for the plastic deformation of the relevant part of the resilient, essentially cylindrical, ring 2 are lower than those required for the compression of the conical rings 1, 11 and many times smaller than those required to overcome the friction of the conventional type in the Ring line 9 required.

In FIG. 5, curve E shows the measured forces for compressing the conical rings 1, 11 in the ring pair arrangement according to FIG. 17 of EP OS 0 102 441, but with a 7 mm thickness of the conical rings, as in FIG Curve A, ie the dash-dotted line in FIG. 5, shows the forces calculated according to Almen and Lascio for compressing the conical ring pair. Line C of FIG. 5 shows the measured forces for the compression of the conical ring pair according to FIG. 1, that is to say with a flat ring 8 between. between conical fingers 1 and 11. Curve B of FIG. 5 shows the measured forces for the compression of the conical ring pair after the arrangement according to the invention of FIG. 3 with the masses according to FIG. 7 and with cylindrical rings 2 of 3.6 mm wall thickness and 20 mm length = ge. It can be seen that in the embodiment according to the current invention according to FIGS. 3 and 6.7, with full compression of the ring pair 1.11 by a total of 0.6 mm, the forces required for the compression are almost ten times less than in the arrangement according to the aforementioned figure 17 of the mentioned 'EP OS and differ only by approximately 30 percent from the theoretically calculated values according to Almen Lascio. This approximately 30 percent additional force will be the force that deforms the relevant part of the cylindrical ring 2 in question. It is also important here that this deformation force is resilient, in the same way that the deformation force for the conical rings 1, 11 is partially recovered when operating as a pump in the sense of FIG. 22 of the aforementioned EP OS with master pistons and follower pistons when the system is in operation can because the tension in the conical rings and the cylindrical rings 1,11,2 press the working fluid from the pump chamber 50 onto the stroke drive of the master piston of the compression pump and thus act as a motor for driving the sensor stage, for driving the stroke ring 336, respectively. of the rotor 336 of FIG. 22 of the aforementioned EP OS. The forces according to curve B of FIG. 5 are therefore not always fully injured, whereas the friction that lies between curve A and curve E in FIG. 5, that is to say the execution of the previous ring pair arrangements according to the EP OS, was completely lost and was not recovered -can be.

It is known from the above-mentioned EP OS that the radial outer ends of the conical rings must be clamped together for the supercritical range.

Within the scope of this invention, sunaschet was fumigated, the necessary cleat rings dimensioned so that the intermediate rings 8 and the clamp rings suffer the same radial expansion. Although this equality can be produced, it makes no sense, because FIG. 4, which essentially corresponds to the Prinsip of FIG. 25 of the aforementioned EP OS, shows that the radial changes are not carried out on the same side, because according to FIG. 4, curve F slopes the sudden , early or rapid pressure increase in the pumping chamber 50, which expands the cattle 8 and the curve G shows the sinusoidal all-round compression of the conical rings 1 and 11 over the circumferential angle alpha of the transmitter stage. This means that the ring 8 rapidly expands radially, while the radial ends or supports 13 slowly expand in comparison with the time of the expansion of the rin. tot 8, (if the plate 8 is a ring 320 of Figure 22 of the mentioned EP OS), If the same radial expansion does not occur after the same time, then the friction on the supports 13 is still present. So gagemaess invention must be followed different ways.

FIG. 8 therefore shows further arrangements according to the invention on the conical ring pair 1, 11, then the clamp rings or tension rings 27, 28, which are held together by the screws 30 - they can also be rivets - with radially resilient, essentially cylindrical ring parts or ring pieces 42 or 32 and 42, which are the holders for the supports 33 of the conicals Form rings 1, 11 for the supercritical working range of the pump, motor, compressor or expansion valve. These ring parts or ring pieces 32 or 32 and 42 are radially resilient in the same way as the rings 2 in FIGS. 3, 7 and 8.

Since the force on the supports 33 is higher than the force required for the radial suspension or deflection of the ring parts 32 or 32, 42, the tips of the ring parts or ring pieces 32, which contact the supports 33, follow the radial movement of the supports 33 and thus the radially outer ends of the conical rings 1 and 11. This spring force can also be partially recovered in the encoder-follower mode of FIG. 22 of the EP OS mentioned, since it can act as a motor drive on the encoder stage. It should also be noted that the forces on the supports 13 of the common support 23 are not as high as that of the supports 3, because the fluid pressure in the working chamber 50 cancels the compression forces of the spring. Thus, only the prestressing pressure of the conical rings acts on the supports 23, and the force acting on the supports 13 from this is quickly eliminated during pump operation by the rapidly increasing fluid pressure in the chamber 50. The fluid pressure from the chamber 50 acts on the supports 33 less the clamping force of the conical rings 1 and 11. So, in the numerical example 22,000 kg minus the relevant parts of the 3,200 kg clamping force of the conical rings 1 and 11 plus the clamping force of the holding means 30, 27, 28, 32 and 42.

In order to realize the resilient ring parts or ring pieces or cylinders or cylinder parts or cylinder pieces 32, 42, it is practical to arrange the ring grooves 29 and possibly the ring grooves 36 and 37 in the clamp rings 27 and 28. This is simple and cheap in terms of production, for example cheaper than dividing the rings into segments according to the EP OS mentioned. Conveniently, the recess 38 is also arranged in at least one of the clamping rings 27, 28 in order to enable simple clamping by means of the screws 30 and to allow axial tolerances for cheap manufacture. A space or a recess 47 is advantageously to be arranged radially inside the cylinder or rings 2 in FIG. 8, so that the rings 2 can also follow the radial inward movement of the supports 3 and are not prevented from doing so by solid bodies.

The seal arrangement 22, 49 within the conical ring pair of the radial movement of the zylinc is also inventive to adapt the inner surface 60 of the conical ring in question 1 or 11. For this purpose, the plastic sealing ring 49 is used according to the invention in a part = radially resilient cylinder piece or ring part 22. In order to be able to produce this ring part in a body, it is expedient to arrange the recesses 48 radially within the lips or ring parts 22 axially so that the cylindrical ring parts 22 can also spring radially inwards if the cylindrical inner surfaces Spring 60 of the conical rings radially inwards. This design also has the advantage that the fluid pressure from the pumping chamber 50 radially from the inside out of the recesses 48 to the ring parts 22 and can press them against the inner surface 60 of the conical rings 1, 11 because the sealing rings 49 prevent them yes, the penetration of pressure fluid between the inner surfaces 60 and the ring parts 22. It is also expedient to arrange the line or bore 77 at the upper end of the recess (s) 48 and to guide it to the delivery line 70 so that no air cushions can form in the groove 48 , or the air escapes through line 77 and outlet valve 70. Also within the scope of the invention, an air discharge line 76 is arranged from the upper end of the inlet valve 69 to the outlet valve 70.

In order not to limit the clarity of the figures, lines of edges directed radially inwards are not shown in them, although this is common in technical drawings. In the patents drawings they would interfere with the clarity of the figures. For the same reason, the filling parts required in fluid spaces according to the aforementioned EP OS are not shown, but are used in practical implementation, as is known from the aforementioned EP OS. FIG. 8 also shows the piston 66 for driving the compression of the conical rings 1, 11 in the cylinder 67, the pressure chamber 68 of which receives its pressure fluid via the line 46 and delivers it through it to and from the transmitter stage of the EP 06 mentioned Line 46 thus corresponds to connecting line 303 of the EP OS, for example whose figure 22.

F he _u even better efficiency of a high pressure pump, it is expedient to replace the arrangement of the 9 Klampringe the figure 8 by the Klampring 80 of FIG. Because this ring 80 of FIG. 9 is lighter in weight and opposes the axial movement less mass forces, which must be accelerated in the axial direction during the compression and expansion of the conical rings. In addition, the embodiment according to FIG. 9 is cheaper in mass production. The lower bracket 86 of the clip ring 80 may be worked on the ring 80 from the beginning. The upper bracket 87 initially remains cylindrically straight upward. The conical see pair of rings 1, 11 is inserted into the clamp ring 80 after inserting the centering ring 20 into it until it lies on the holder 86. This should be done mechanically, because the Klampring 80 is very warm. After the conical ring pair has been automatically inserted in a matter of seconds, the upper holder 87 of the warmed clamp ring 80 is quickly and automatically flanged to the encompassing form of the holder 87 of FIG. 9 and then the assembly is automatically thrown into the cooling fluid. The ring 80 contracts axially and clamps the conical rings 1 and 11 firmly together. Since this work has to be carried out in such a short time that the heat of the clamp ring 80 is not transferred to the coated conical rings 1 and 11, it is expedient to build an automatic machine for the production of the arrangement according to FIG. 9 and, as long as it does not is available to use the arrangement of Figure 8. The arrangement according to FIG. 9 cannot be solved without destroying the ring 80. However, it does not have to be detachable either, because after the unit has been cooled, the plastic sealing ring 26, which cannot withstand the heat of the ring 80, is inserted radially from the inside into its place radially inside the centering ring 20 can.

In FIG. 10, the pair of rings 1, 11 is replaced by a one-piece spring body 111, in that the conical rings 1 and 11 form parts of this one-piece spring body. The ring parts 1 and 11 are connected by their connection 112, so that the parts 1, 112 and 11 form the common hollow spring body 111.

The radial chamber 550 is formed in the spring body 111 between the conical inner surfaces 4 of the conical ring parts 1 and 111, because without this ring chamber the body could not be a spring body. The cylindrical ring parts 2 can also be formed in one piece with the spring body 111 or they can be placed on its supports 3. Since the connection 112 between the conical parts 1 and 11 is elastic and since the conical ring parts 1 and 11 are also elastic, that is to say springy, the spring body 111 can be compressed in the axial direction and then expand again. The spring body 111 can therefore be used as a pump, in particular a high pressure pump, containing the pump chamber 50 with 550. In the case of thinner walls or more plastic material, this version is also suitable as a low-pressure pump or motor. This spring body can also be made of solid spring steel, since in pump or motor arrangements according to this document and according to those of the EP OS mentioned, the radial dimensions are relatively short compared to the inner diameter. It is therefore easy to turn the inner conical surfaces 4, the conical inner ends 4 and the radial annular groove 550 into the spring body 111 with a strong turning tool from the inside. With plastic design, the production is even easier and when using fiber adhesive material, such as glass fever, carbon fiber fever, carbon fiber, etc., you can insert a still soft cylinder into an outer mold and the material for the spring body into the mold using fluid pressure or compressed air pressure Push in, which then creates the shape of the body 111 of Figure 10 in a simple and inexpensive manner by drying the material.

FIG. 9 is drawn to scale for approximately 1500 bar fluid pressure in chamber 50. Because the Klampring 80 must not be too thin, so that it does not stretch too far in the axial direction, but it must also not be so thick that it does not spring sufficiently radially, or make the total suspension force unnecessarily high. Because, the forces are not full, but only partially recoverable as motor drive of the pump of the encoder stage, but only partially, because the pump and motor effect of the encoder stage also have an efficiency with a few percent losses.

Further details of the invention are partially described in the patent claims, so that the patent claims, which contain reference numerals, are to be regarded as belonging to the description of the exemplary embodiments of the invention.

The figures and diagrams relate to only one size of the parts of the invention. Based on the numerical examples and diagrams of the only size dimension, the effects of the invention are clearly visible. The invention relates not only to this single dimension = size and shape, but also to all other smaller and larger ones. The use of the invention is not further explained in this document because the use in industrial practice is sufficiently known from the EP OS cited, the arrangements of which are partially improved by the present invention.

The invention also relates to a high-pressure unit with elements which are spring-loaded or deformable in the axial direction for particularly high pressures of up to approximately 5000 bar, the fluid which is pumped or used can be a non-lubricating liquid, such as water.

In the previous figures, conical ring elements are held together by cleat rings that have radially resilient retaining lips. These rings and elements are suitable for pressures of over a thousand bar, but they do not allow unlimited higher pressures.

Therefore, the ring arrangements are housed in a strong housing and the housing is controlled in time in parallel with the pressure in the working chamber in the ring arrangement. The ring arrangement is thus surrounded by a fluid pressure which is approximately half the pressure in the working chamber.

As a result, the pressure in the system can be approximately doubled and reach several thousand bars. According to a further exemplary embodiment, a pump for, for example, water with unlimited service life and several thousand bar pressure is created by pumping the pump piston into a liquid arranged above the water with lubricating and rusting properties.

Pumps with conical ring elements for high pressures have become known from the previous figures and previous publications by the applicant or the inventor. Such units have been built with pressures of over a thousand bar and are still in development for higher pressures. However, the pressure cannot be increased indefinitely, since the ring elements become thicker and the pump strokes smaller the more the pressure is increased. The at such high pressures of the pump nat _/ urgemaess low flow causes any small shape alteration already considerable Foerderverluste.

The known technology is therefore burdened with limits that do not allow any further pressure increases with sufficient effectiveness, so that there is a need for new solutions in order to be able to increase the pressure of the high-pressure units, in particular the high-pressure pumps, for non-lubricating liquids even further.

The 'invention is therefore based on the object of increasing the pressure range of the pumps and motors above a thousand bar with a good level of efficiency and at the same time enabling the operation of the unit for water and, if possible, a pump or a motor for non-lubricating or to create rust-causing liquids for an unlimited service life with simple and reliable technical means.

This problem is solved according to the characterizing part of patent claim 14 and further preferred solutions of the task are carried out by subclaims 15 to 32.

The above-mentioned exemplary embodiments are exemplary embodiments according to the invention and the cuts are essentially longitudinal sections through the units, although parts, for example the drive shafts, are cut transversely because they are perpendicular to the relevant longitudinal section plane.

Figure 11 shows essentially all parts of Figure 8. Since this
are repeated, the description is not repeated here. See, for example, parts 1, 2, 27, 28, 29 and 32. An improvement compared to FIG. 8

consists in that the grooves 29 are deeper and the support lips 32 are longer than in FIG. 8 of the main application. However, the grooves are omitted radially outside the groove 29. This is achieved by the fact that no thin-walled parts remain under tension. The support lips 32 are only subjected to pressure. So that sufficient radial resilience nevertheless arises, they are correspondingly longer, which requires a deepening of the grooves 29. In addition, the twists under the sealing lips of the previous figure 8 are now in FIG. 11 = registration omitted. Because they are difficult to manufacture, because the filling blocks 5 have to be made of rustproof material in water aggregates. But such material is tough and the turning tools break easily when turning narrow deep grooves in such material. Instead, the sealing ring support tube 3 is arranged according to the invention in FIG. It surrounds the filling block 5 in such a way that a narrow gap 4 of a few hundredths of a millimeter is formed between the outside diameter and the inside diameter of the tube 3, which should in any case not exceed 0.1 to D.2 mm. Because with this gap width sufficient amounts of pressurized fluid penetrate from the working chamber into the gap to fill it and thus to load the support tube 3 radially from the inside. The relevant sealing ring support tube 3 has the sealing ring groove 93 for receiving the plastic sealing ring (not shown) made of rubber, Teflon or the like. This sealing ring in groove 93 seals between the element 1 and the support tube 3. Radially outside the support tube 3, there is therefore less pressure than radially inside the support tube 3. In addition, the support tube 3 is radially thinner than the pumping elements 1, the conical ring parts 1 , are. The sealing ring support tube 3 therefore expands more radially outwards under the internal pressure than the elements 1 do. This automatically ensures a good seal that is effective at all times, regardless of how far the elements 1 also radially under the working pressure in the 'May expand the working chamber. This is very important and a new finding of the invention, because according to Japanese calculations the elements 1 expand further radially than would be expected according to the German specialist literature.

A further feature of the invention in FIG. 11 is that the arrangement is mounted in a thicker housing 6, for example in a thick-walled tube 6, and this housing 6 is provided with a pressure fluid line 7 that can be controlled over time. The housing 6 is completely closed and through line 7 is in the interior in the housing 6 at the same time as the pressure rise and descent in the Work / chamber between the elements 1 is filled with a fluid pressure which is about half as high as the work chamber pressure. As a result, the elements 1 and all other parts of the arrangement between the chamber pressure of the working chamber and the pressure inside the housing 6 can work. The parts of the arrangement are therefore only half as loaded under the internal pressure chamber as in the execution of the main application. As a result, in order to obtain equally loaded parts with the main application, the working chamber pressure can be doubled compared to the main application. As a result, the pressure is doubled without having to use a double-stage arrangement. However, the housing tube 6 must be correspondingly thick-walled so as not to bend too radially when it is filled with the half-pressure.

Figure 12 shows the Laengs section through the simplest unit of the invention. The working chamber 17 is located in the housing 11 and has an inlet and an outlet valve 20 and 21, wherein corresponding connecting channels 22 and 23 can be arranged. It is important that the axis of the working chamber is vertical. Because below in the chamber 17, the non-lubricating or rust-causing medium to be pumped, for example the water, is to be pumped. Above the chamber part 17 is the chamber part 16, which according to the invention is filled with a lubricious fluid which, compared to the fluid in chamber part 17, has a lower density or a lower specific weight. This liquid of the lower specific weight is called the first liquid and the liquid in the chamber part 17 with the higher specific weight is called the second liquid. The first is the lubricating liquid, the second the non-lubricating liquid. As a result of the difference in the specific weights of the liquids, the first one always floats at the top in the chamber part 16 and the second one below it in the chamber part 17. The two different liquids therefore always automatically separate from one another by their different specific weights.

Therefore, the operation of the motor or the pump can be shifted into the area of the lubricating, upper, first liquid in the chamber parts 16. Parts 16 and 17 are parts of a single, common chamber in this figure. The pump piston 15 can therefore be arranged and reciprocated above the chamber part 16. One may operate his reciprocation movement by hand or by motor. Motorized, for example, by the arrangement of the revolving shaft 12 with an eccentric lifting part 13, the outer surface of which can then drive the piston via a piston shoe 14 pivotably mounted in the piston. The water or another fluid is now pressed into the chamber 17 through the inlet valve 20 under slight initial pressure, as a result of which the piston 15 is pressed back into its starting position. Instead, the piston 15 could also be pulled back into its original position by a sliding guide or by a spring means. Conveniently, inlets or control openings 18 and 19 are arranged to ensure that the correct amounts of fluid of the first and second fluids are in the chamber parts 16 and 17.

The same system is shown in FIG. 13, but it is indicated by the several stroke eccentrics 13, 23 and 24 that several work units are located one behind the other and are operated in time by the shaft 12 with its stroke parts 13, 23 and 24. Through the connection 27, the stroke eccentric chamber 25 can also be filled with pre-pressure fluid, which temporarily, when the control groove 26 hits the bore or the channel 28 in the piston shoe when the shaft 12 rotates, through the groove 26, channel 28 and the channel penetrating the piston 15 30 can be passed into the center line 31 in order to fill it with the correct amount of fluid.

The central channel 30 leads from the cylinder in which the piston 15 runs, specifically from the cylinder bottom thereof, to the working chamber 32 also arranged in the housing 11. In its upper part, the follower piston 33 is sealingly reciprocally supported. The piston 15 is the first piston, while the piston 33 is the second piston. The fluid column 31, which fills the central channel 31 ′, is located between the two pistons and transmits the movement of one of the pistons to the other piston. In the example in FIG. 3, when the unit is used as a pump, the first piston 15 is the master piston and the second piston 33 is the follower piston. The pistons can have different diameters in order to achieve a gear ratio. The first piston of smaller diameter but longer stroke thus produces a greater force with a shorter stroke of the follower piston or second piston 33. Below the follower piston 33, the fluid chamber 33 is formed, into which the follower piston 33 can be immersed and which forms the first chamber part, which forms the first Fluid is filled, that is filled with the lubricating fluid, so that the. Piston 33 and its fit in the liner 45 can not be damaged by non-lubricating or rust-causing fluid. Below the chamber part 33, which corresponds to the chamber part 16 of FIG. 2. there is the chamber part 37, which corresponds to the chamber part 17 of FIG. 2 and contains the non-lubricating second fluid to be pumped. The chamber part 37 is accordingly again provided with an inlet valve 38 and an outlet valve 39 — possibly spring-loaded. In this figure, these valves are connected to manifolds 41 and 42 for the inlet and outlet of all working units. As a special feature in comparison to the basic FIG. 2, a separating means 36 is arranged in FIG. 3 between the chamber parts 35 and 37 in order to avoid mixing by splashing the first and the second liquid. The separating means 36, which may be a disk, can be provided with sealing ring groove means 43 for receiving plastic sealing ring means, not shown. Such sealing rings are not hatched in the figures because they are small in cross section and would impair the overview of the figures.

Since it is very important in the embodiments of the invention according to FIGS. 12 to 14 that the relevant chamber parts 16, 17, 35, 37 and the central channel 31 always contain exactly the right amounts of fluid, it is expedient to open the openings or connections 34, 44 , 46 and / or 47 or some or one of the same lockable. For example, the connection 34 to the central channel 31, also the connection 44, the connection 46 to the first fluid chamber part 33, 16 and the connection 47 to the second fluid chamber part 37, 17. The purpose of these connections is to fill the relevant parts of the chamber or the central channel, or to check or correct their fluid quantity. This control or filling is particularly expediently designed automatically, for example by means of electronic sensors and appropriately controlled filling or control units. The arrangement of the parts 12, 13, 23, 24 causes regulated conveyance via the circumferential angle of the shaft 12,
the arrangement of the part 36 avoids the mixing of the first with the second fluid and the arrangement of the part 33 enables a corresponding increase in force.

FIG. 14 shows the design for the highest pressures as a pump and for a practically unlimited service life. The piston drive parts 12, 13, etc. for the transmitter parts can be built with the means of the applicant's hydrostatic units for an unlimited service life because they do not touch any non-lubricating or rusting fluid. The separating body 36, which is already known from FIG. 13, has an unlimited lifespan because it is not exposed to any loads. It only swims between two fluids of the same pressure. The valves and channels, like the chamber parts 35 and 37, are arranged and act ^analogously, as in FIG. 13. Likewise, the connections.

The master piston 15 has a relatively small diameter in comparison to the follower piston 49 driven by it via the fluid column in the central channel 31. As a result, because of its larger cross-sectional area, the follower piston 49 is moved with a multiple force relative to the force of the master piston 15 and is moved down in the figure. The front or lower end of the follower piston 49 opens into the preferably unpressurized intermediate chamber 50. It may be kept depressurized by the connection 51, which may be connected to the atmosphere or better to a low-pressure chamber of the unit. The special feature of FIG. 14 in comparison to FIG. 13 is that in FIG. 14 the follower piston 49 acts on a high-pressure pump piston 52 of smaller diameter. The high-pressure pump piston 52 is arranged axially under the follower piston 49 in the figure and is guided in the bushing 45 so that it can be tightly reciprocated from rustproof material. It dips with its front, lower end into the chamber part 35 with the first fluid therein and its backward, upper end is supported on the end face of the follower piston 49. The other parts of FIG. 14 correspond in principle to those of FIG. 13 and therefore need will not be described again here. The arrangement of the high-pressure pump piston 52 with a small diameter compared to the follower piston 49 ensures that the follower piston 49 has a large cross-section, while the high-pressure pump piston 52 has a small cross-section. As a result, the high-pressure pump piston 52 reaches a substantially higher pressure in the chamber 35-37 than the follower piston could reach in it, because, due to the cross-sectional differences, a force transmission between. the follower piston 49 and the high pressure pump piston 52 is arranged. The hydrostatic transmitter stage of the first piston 15 works efficiently when the units and parts are installed according to the inventor's patent specifications, with an oil pressure of 500 to 1000 bar. If you now make the cross-section of the high-pressure pump piston 52 about four times smaller than that of the follower piston 49, you have a fourfold pressure ratio, which means that the high-pressure pump piston 52 then works at 2000 or 4000 bar, i.e. in the chamber parts 35 and 37 a pressure of 2000 or 4000 bar is generated when the master piston 15 generates a pressure of 500 or 1000 bar. Other pressure ranges and ratios can be chosen as long as the system is sufficiently stable.

The figures are drawn in such a way that the necessary parts can be easily recognized, but not always to scale. The cleat rings and elements with their inner parts, as well as the housing tube 6 of FIG. 11, are approximately true to size. The pistons and wall thicknesses on the right-hand side of FIG. 14 can also be regarded as roughly true to size. In contrast, the shafts and eccentric lifting parts of Figures 12 to 14 are drawn completely immeasurably. In practice, the shafts 12 are much thicker and they are supported in bearings according to the inventor's US patent 4,310,203 for the high pressures if they are to have an unlimited lifespan. The bushings are preferably used for water operation in the chamber part 37 made of VEW stainless steel and in thick-walled housings, but the housings can also be made of the aforementioned stainless steel.

In FIG. 17, the separating body 36 of FIGS. 13 and 14 is replaced by a clamped membrane 61. This is firmly held in seats for its board 62 by means of the insert 91 in the housing 1. the screws 92 may be used to secure the holding insert 91. It should be noted here that it is not a pumping membrane of conventional use, but a fluid

Separating diaphragm. Conventional diaphragms as pumps would break at the high pressures that the invention intends to use long before the pressure was reached. As a separating membrane for preventing the mixing of the first fluid with the second fluid in the chamber parts 35 and 37, however, the membrane is loaded with the same pressure from both ends. It therefore does not carry any pump load and is not exposed to any pump load. But their diameter has to be chosen big enough and their thickness has to be kept thin enough so that they can bend without high internal tension conditions and the up and down movements of the two fluids in the chambers 35 and 37 can follow. This membrane 61 is advantageously made of stainless steel or carbon fiber if you want to drive with water in the chamber part 37. Carbon fiber has the advantage that, by choosing the heat during the production of the fiber, there is a large selection range for the elasticity module of the membrane 61.

FIG. 18 shows that the separating body 36 of FIGS. 3 and 4 can be replaced by a separating body 136 of FIG. 8. The peculiarity of the separating body 136 is that it has two grooves 82 and 83 for the use of plastic sealing rings which are spaced axially apart from one another. Between them is the leakage collecting groove 80 for collecting any leakage via plastic sealing rings of the grooves 82 or 83 that have become leaky. The line or outlet or. the connection 81 is set in order to be able to discharge any leakage from the collecting chamber 80. It is advisable to set automatic, for example, electronic, sensors to line 81, which have the task of notifying the people concerned that sealing rings have leaked and are to be replaced, or which have the task of automatically closing the entire system set if leakage occurs, which could cause mixing of the first and second fluids in the chamber parts 35 and 37.

In Figure 14 it is finally indicated that the system can be built in three parts from the middle housing 11, base 111 and cover 1111 in order to be able to produce and assemble all details cleanly.

FIGS. 15 and 16 provide important “know-how” for the construction of the units of the invention.

mit n = D/d = Aussendurchmesser/Innendur,chmesser bei n= 2 mehr als doppelt so hohe Aufweitungen gibt, als die einfache Formel nach J. Thoma. Die hoeheren Aufweitungen werden umso bedeutender, je dicker die Wand relativ zum Innendurchmesser wird. Da bei den hohen Drucken, die in dem Aggregat der Erfindung auftreten, Radialaufweitungen von einigen hundertstel oder Zehntel Millimeter bereits Foerderverluste der Pumpe von vielen Prozent bringen, kann es passieren, dass die Foerdermenge null wird, wenn man nach den beiden Formeln oder einer der beiden Formeln der oben diskutierten deutschspra= chigen Literatur rechnet. Um wirklich Foerderung des Aggregates bei den angestrebten hohen Drucken zu erreichen, sollte also nach der Igarashi Formel gerechnet werden.In the European patent application EP 0 102 441, exact calculations for the axial loads, deflections and tensions of the conical ring elements 1 are given in FIGS. 23, 25 and 29-A. In later buildings and trials, it was recognized that the protective hoods underneath occasionally seemed to widen and leak. A widening of about 0.1 mm was assumed at 1000 bar; but this cannot be measured exactly. However, the further, current, new investigations show that the cause of this unreliability seems to be somewhere else. It is the case that the radial widening of the inside diameter of the pipes under internal pressure according to the German literature and according to the German DIN norms due to the formula sigma given by Profesor E. Siebel and published in the book by Juergensonn "elasticity and strength in pipeline construction" = pd / 2s were calculated. Although the book does not provide a calculation of the radial widening, the inventor assumes that the radial widening of the tube should be calculated by multiplying the tension by the inner diameter of the tube and dividing by the elasticity modulus E. For the expansion of the pipe is in German-language hydraulic books, for example in the book "Oelhydraulik" by Dr. Jean Thoma, currently a professor at the Water 100 University in Canada, stated on page 211 that the expansion = pR / It should be with s = wall thickness. Apparently, the radial diameter widenings of the thick-walled tube are much larger. For example, with a ratio of outside diameter D to inside = diameter d of 2, the radial expansion appears to be more than twice as high as it would be according to Professor Dr.Jean Thoma's formula. This follows from Mr. H's formula. _I garashi (Riken Seiki), which he developed from Japanese-language literature. These formulas have therefore been compared in FIG. For this purpose, the factor "fR" has been introduced, which gives the formula which has to be followed according to Pd / E in order to radially expand the inside diameter of the pipe, of the pump element 1, the sealing ring support tube 3 or the housing housing = res 1 and so on. It can be seen from FIG. 6 that the "fR" factor according to Mr. Igarashi, namely

with n = D / d = outer diameter / inner diameter, the diameter at n = 2 gives more than twice the expansion than the simple formula according to J. Thoma. The larger the widening, the more important the thicker the wall becomes relative to the inside diameter. Since at the high pressures that occur in the unit of the invention, radial widening of a few hundredths or tenths of a millimeter already results in delivery losses of the pump of many percent, it can happen that the delivery rate becomes zero if one uses the two formulas or one of the two Formulas of the German-language literature discussed above. In order to really promote the aggregate at the desired high pressures, the Igarashi formula should be used.

Furthermore, it is hardly known from the literature how much the plastic sealing rings made of rubber etc. compress their volume under pressure. The extensive catalogs of many specialist companies specify the elasticity module and many other details of the sealing ring material, but they do nothing to reduce the volume of the material at high pressure. If you ask them, they often answer that you do not know this and do not need it either, because in the practice of delhydraulics, the sealing rings, for example the O-rings, behave roughly in the same way as the oil. But if this were so, then every sealing ring, for example the grooves 93, 43, etc., would suffer similar internal compression under pressure, like the Del or the water. Since these grooves, despite their narrowness and thinness, raise considerable volume in the overall system, these plastic seals, such as O-rings made of rubber-like materials, would cause the unit to lose losses of 5 to 30 percent at the high pressures of the unit. After a long search, the compression ratio of the rubber - like materials has now been successfully achieved partially experienced. FIG. 16 shows this, namely in curve 1, the decrease in volume of the O-ring code 90 according to the Japanese standard JIS B 2401 according to measurements by T. Makita; S.Matsuo and K. Inoue. Curve 2 shows the volume decrease of the rubber Duprene according to measurements by Mr. Bridgman at the Massashusetts Institute of Technology. The curve is intended to indicate that the material becomes brittle and discontinuous at around 5000 bar. Mr. Bridman measured the compressions (volume decreases) of many substances, including metals and many types of rubber, but only at intervals of 5000, 10000 atmospheres etc. to 25000 bar. In the range of 1000 to 5000 bar, which is important for the aggregate of the invention, one can assume that over 1000 bar plastic sealants lose about half as much volume as water or oil if the right substances are selected and used.

The sealing ring grooves should therefore be kept so small in cross-section that they can still hold well-sealed sealing rings and the thin sealing rings are not too thin or too expensive to manufacture.

It can be seen from the considerations that, for example in FIG. 11, practically all parts spring under the high pressure in the unit. For example, expand radially and contract when you relax. It is expedient to utilize the effect of the resilient radial contraction and the axial relaxation to the efficiency of the unit. This is achieved by letting the fluid column in the central channel 31 act on the master piston 15 in order to allow it to be pressed against the guide surface of the linear actuator, for example 13, 23, 24, in its return stroke. The first piston 15 then acts on its return stroke on the shaft 12 as a hydraulic motor driving hydraulic piston pushing piston. Without taking advantage of this effect, the efficiency of the unit of the invention would be very low at very high pressures above 1000 bar. The basics of Figures 15 and 16 give the calculation options for this. In order to achieve a good hydraulic motor efficiency of the piston 15 during the return stroke, it is expedient to use the one from the inventor's patent specifications known systems to use.

With regard to FIG. 12, it should be borne in mind that this is drawn in such a way that the system can be easily recognized from the figure. This does not mean, however, that you can simply copy them to scale in order to obtain a high-efficiency unit. Assume the following, mass in Figure 12: piston diameter (15) = 10 mm; Inner diameter of the housing (11) = diameter of the chamber (16, 17) = 24 mm; Piston stroke of the piston (15) = 4 mm; Volume of the lines 22.23 = 4.25 cc. The volume of the liquids is then obtained at atmospheric pressure = 16 cc; Promotion of the piston 15 = 0.312 cc. That gives 0.312 / 16 = 0.019; that is 1.9 percent of the liquid volume as a delivery quantity through the piston 15. Since water, see FIG. 16, compresses by more than 1.9 percent even at 1000 bar, the pump on the scale of FIG. 12 cannot even reach 1000 bar pressure. It would only deliver up to about 700 bar and then the amount would be zero. In reality, it becomes zero at an even lower pressure because the wall of the housing 1 widens radially outwards under the internal pressure.

As a result, the chambers 16, 17; 35.37 must be dimensioned so small that at the end of the pumping stroke there is almost no dead space with liquid in it. The amount of the first fluid must be kept so small that the piston in question is still running in the first fluid without touching the second fluid. The lines 22, 23, etc. up to the inlet and outlet valves must have as little volume as possible. In practice, the valves are mounted directly on the chambers 17.37 to avoid dead space. In addition, the wall thickness of the cylinders must be very thick. In short, in practice the components are tolerated in hundredths of a millimeter, because otherwise the desired prints can never be achieved with sufficient efficiency.

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new conical ring elements are presented that have axially aligned lugs on their radially inner and outer end parts. Sealing ring beds are formed radially inside and outside the lugs, into which plastic sealing rings are inserted. The inside diameter and outside diameter of the lugs create a cross-sectional area of the lugs, and the radial dimension of the fluid chambers is sharply delimited radially inside and outside the lugs. The elements are inserted into a bore in a body, which is closed at the top by a head cover, which contains an inlet and an outlet valve. A master piston is arranged below the bore, the fluid into the closed bore. pumps. The upper element of a column of elements lies sealingly against the head cover. This creates an inner chamber connected to the valves and an outer chamber connected to the master piston. The design of the elements guarantees that the pressure in the chambers does not separate the elements of the column of elements from one another, but rather compresses them in a self-sealing manner. As a result, the invention succeeds in creating a pump for non-lubricating media with an efficiency of up to around 4000 bar and which is reliable in operation. Further alternative examples show possible related embodiments of the invention.

In the previous figures, a high-pressure fluid unit has been described, which separates two different media, one of which can be a non-lubricating fluid, by means of an axially expandable ring element which keeps the two media separate from one another if the one fluid at one end of the element exerts a pumping stroke on the element, thereby pushing the other fluid out of its pump chamber at the other end of the element. In the main patent, the element could also be a membrane, because the prints on both axial ends of the element are basically the same after the main patent and differ only in the resistance of the element when it is deformed.

However, the design of the element of the previous figures has the disadvantage that the stroke of the element is relatively short because the membrane would tear due to overvoltage if the stroke were long. In addition, the membrane of the main patent is a weak one with no particular strength and resistance. This means that the aggregate of the main patent has a performance limit due to its element, i.e. its membrane.

The invention therefore also has the task of creating a resistant element and useful parts of a unit with high durability and long axial stroke of the element, reliable and with simple means to increase the service life and performance of high-pressure units.

This object is achieved according to the characterizing part of claim 33. Further advantageous solutions to the problem emerge from claims 34 to 62.

FIGS. 19 to 32 show longitudinal sections through 14 different exemplary embodiments of a high-pressure unit according to the invention or through parts of the unit.

FIG. 19 shows in a cover 1.11 the second pump chamber 37 with an inlet valve 38 and an outlet valve 39. The lines 41 and 42 lead to the valves. The valves can be tensioned by springs 40. An insert 91 is clamped in the cover 1 and held, for example, by means of screws 92, which clamps the fluid separating element 61 in the cover 1 by forming the fastening 104 of the element. In the insert 91 there is the cylinder 35, which is connected to the first pump chamber 35 between the element 61 and the insert 91 and in which the reciprocating piston 52 moves up and down. The fastening 104, with its inner diameter, forms the outer diameter of the first and second pumping chambers 35 and 37. In FIG. 19, the chamber 35 is not visible because the element 61 rests with its base on the base support 101, which forms the upper end of the insert 91 . Said fastening 104 is advantageously provided with sealing grooves 102 and 103 in cover 1 and insert 91 for inserting sealing rings, which effect the sealing of the element and the two chambers 35 and 37 from one another. The second pump chamber 37 is formed between the upper end face of the element 61 and the head rest 100, the head rest 100 being formed on the cover 1. In FIGS. 19 and 20, the head system is a weak-angled hollow cone, the axial depth of which must not be longer than the maximum permissible stroke of element 61. If the reciprocating piston 52 presses upward, then fluid is pressed out of the cylinder 35 against the bottom of the element 61 and the element lifts upward, pumping ingress of fluid via valve 38 out of the second chamber 37 via valve 39 until the upper end face of the Elements 61 abuts the Kopaf system 100. In this state, the first pump chamber 37 is fully formed under the element 61. The piston 52 has done its full stroke.

While in the past the membrane swung freely between the two media of the chambers 35 and 37 without touching mechanical end supports, the element 61 of the invention now has end installations 100 and 101 between which it moves axially. This has the advantage that the systems 100 and 101 can be placed in such a way that the permissible stroke of the element 61 can never be exceeded. The element 61 thus has a long service life and operational reliability. The shape of the systems 100 and 101 are dimensioned such that the element retains allowable stresses in all parts. The head rest is therefore bulged radially in the middle than at the radial outer ends. The support of the element 61 on the floor support 101 prevents dead space and thereby loss of compression in the fluid. These are also prevented by the element 61 abutting the head system 100. The angle of the hollow cone under the head rest 100 is shown greatly enlarged in the figures. In practice, the element on the scale of the figures is about 2 mm thick (plus minus 1.5 mm) and consists of flexible material, for high pressure water pumps of up to 5000 bar but often made of the Japanese SUS 630 steel or stainless steel from VEW . In Figures 1 and 2 is a stroke of the element from O, s. permitted up to 0.4 mm if the. mentioned steels are used.

However, what is often desired is an even longer travel of the element.

Therefore, Figure 21 shows on a 1: 1 scale a high-pressure unit for up to 5000 bar water pressure from the second pumping camera 37 for about 10 cubic centimeters of conveying quantity per stroke. The element 61 makes about 4 mm stroke with a thickness of 3 mm in the radial center. The amount conveyed is calculated according to the formulas in FIG. 29-A of European Offenlegungsschrift 0102441.

The long stroke of the element 61 and thus the large delivery volume of the chamber 37 at the high pressure is achieved according to FIG. ZI in that the element 61 with ring shafts (161, 261, 361) is formed, the waves form valleys and mountains. These are very pronounced in the figure and form almost axially parallel or only slightly inclined element pieces 361 between the shaft heights 161, 261 and the shaft depths 461. In the radial direction, this shape of the shaft parts creates a length of the element 61 that defines the radial dimensions of the chambers 35, 37 far exceeded. The element 61 is therefore particularly elastic, although it consists of tefton, other materials or stainless steel. The wave heights and wave depths merge into intermediate pieces 361 in good arches. The radially outer wave crests and troughs are conveniently axially shorter than the radially inner ones. Automatic venting is thus achieved by placing the outlet valve 39 at the highest point of the second pumping chamber 37, where the high wave crest 161 is located. The figure is drawn to scale. The cover 1 is correspondingly shaped with the head rest 112, which limits the stroke of the element 61 and the upper end face of the element 61 bears against the head rest 112 after the end of the stroke of the element 61. The head system therefore has waveforms that are complementary to the element, but these move away from the untensioned position of the element 61 by the local axial mass in question. The insert 91 has at its upper end the floor support 111, which is complementary to the bottom of the element 61, thus also having the waves valleys and mountains 191 and 192 and on which the base surface of the element 61 rests in its untensioned state. It can be clearly seen in the figure that the mountains of the cover 1 and the mountains of the insert 91, for example the parts 191 and 212, penetrate deep into the corrugated valleys of the element 61. Dead space is avoided in order to achieve high efficiency of the promotion. In the figure, the valves are designed so that there is little dead space and the valves still work well. The holes 105 and 106 are used to discharge air that would otherwise collect in the heights and would prevent pumping. Bores 105 and 106 connect the heights of chamber 37 to the exhaust valve. The heights around 191 under the element 61, that is in the chamber 35, can be reduced by the ventilation

Hole 120, which is arranged for this, are vented. It should end at the highest point under element 61, as shown, in order to be able to fulfill its venting effect.

Positions 461,312,291. show further valleys, heights or support surfaces in connection with the shape of the element or the contact or support surface. The resilience of the element 61 also results from the long axial webs 361, which can spring in the radial direction.

The cover 1 and the insert 91 are held together by the connections 92. The inlet valve 38 may be tensioned with the springs 40 and the ports are shown by 41 and 42, with 32 being the inlet and 41 the outlet.

The element 61 is provided with the flange 104, with which it is stretched between the cover 1 and the insert 91, the sealing by sealing rings — not shown — in the sealing ring grooves 102 and 103 being able to take place. The ventilation bores 105 and 106 provide for the ventilation of the mountain waves. The ring nose 110 shows the deep engagement in the wave valley above the valley floor 291.

The piston 52, which periodically fills and empties the chamber 35, runs in the cylinder 35 of the stroke pressure chamber 35. The piston 52 is driven, for example, in accordance with the aforementioned European disclosure document or by means of a pressure piston 124 in a cylinder 125 with inlet 123. Instead of using the pressure piston 124, a mechanically driven pressure piston 128 can also be used, for this purpose a piston shoe 127 is pivotally contained in the piston 128, while the piston shoe is driven on a running surface of an eccentric 126. The piston shoe may contain hydrostatic bearing pockets 130 and connecting lines 129. A measuring stick is shown on the left in the figure to show the size for the specified amount of material. If the piston 124 is arranged in the cylinder 125, a vent hole 122 is arranged at the upper cylinder end. Of particular importance in practice is the fill control bore 121, which is located in the bottom dead center position of the piston 52 and opens into the cylinder 35 there. In the bottom dead center position, the piston 52 clears this bore so that the chamber 35 can be filled with fluid from the outside through the bore 121. After a short stroke, the piston 52 closes the bore 121 and thus begins the stroke promotion of the pressure fluid in question from the cylinder 35 into the Chamber 35 under element 61 to push element 61 upward and thereby deliver the other fluid from chamber 37 through outlet valve 39 and outlet 41. The element 61 keeps the two different fluids in the chambers 35 and 37 separated from one another so that they cannot mix.

FIG. 22 essentially corresponds to FIG. 20, but the outlet valve 39 is arranged close to the inlet valve 38, which is simple to manufacture but can be inferior to FIG. 20 in terms of efficiency because the ventilation in FIG. 22 is not as automatic as in FIG. 2 ₀ because the connection of the valve 39 is not in Figure 22 at the upper point at which the air collects. If you turn the figure 27 90 degrees to the left, then the automatic ventilation is secured again.

FIG. 23 shows one of the most effective exemplary embodiments of the invention for large quantities. The special feature of this exemplary embodiment is the arrangement of the multi-axial element of FIG. 24. It is shown separately in FIG. 2e. With the flange 210, 284, the element 210 is clamped between the seals 209 and 211 between the cover 201 and the housing 222. The flange is adjoined by a conical ring part radially inwards, which bends into the valley floor 281, from where a conical ring part extends conically radially outwards in the opposite direction until it ends in an outer ring arch 280, to which another radially follows internally extended conical ring part, like .. the first mentioned, connects. The entire element 284, 210 is formed in the exemplary embodiment from a single part. For example, it is made from the Japanese stainless steel SUS 630 or from a VEW stainless steel. The inner and outer arches are not sharp tips so that they do not break. A bottom 218 may form the other end of the element. The production by turning from a workpiece is relatively simple and can also be done automatically. However, the element would have high conveyor losses due to internal compression, because the double-conical interiors 282 cannot be filled with incompressible fillers and form a dead space in which the fluid compresses and thereby would lose the amount of conveyor. However, this disadvantage has been overcome by the current invention. For example, you then cast the element or the element column 210 inside with aluminum or another suitable substance. Aluminum is well suited because it has such a low melting temperature that when pouring out with the aluminum melting temperature the stainless steel from which the element usually consists is not yet damaged and also / because the aluminum loses little volume under pressure (compression) . It loses slightly less than the 16th of the volume that water would lose under the same pressure. At 5000 bar, water already loses almost 20 percent in volume, lead about 2.3 percent, but aluminum only about 0.55 percent. The loss of output of the unit when the interior is filled with aluminum thus reduces the compression loss almost thirty to fourfold compared to water. After the interior of the element has been poured out with lead or aluminum, the filler, for example the aluminum, is turned out of the element to the inside diameter of the inner bends 281. The element is then heated to the kneading temperature of the filler after the outer spaces 283 have also been filled with the filler. When the kneading temperature is reached, the element is axially compressed to the desired stroke length under a press, with the filler also compressing accordingly. After cooling, it is turned again and again to the inside diameter of the inner arches 281 and radially outside to the outside diameter of the outer arches 280. As a result of the compression of the filler, there are then the spaces between the filler and conical parts of the element are formed, which now form part of the working chamber. The element then works between the relaxed state of FIGS. 5 and 6 and the tensioned state in which the above-mentioned spaces have disappeared because element walls and filler walls then lie against one another. The interior of the element then receives an interior filling block. For example, 216 and the spaces mentioned are connected to the first working chamber 212 and form parts of it. A cylinder piston 217 can also be inserted and fastened to the element base with the bolts 221. This has the advantage that the lifting piston 227 can then be immersed in the cylinder space 220 of the filling piston 217, 219 in order to obtain a short overall length of the unit. The head cover held on the housing 222 by means of the fastening screws contains the inlet and outlet valves 202, 204, 206 and 2087, which can also have the tension springs 203. The exterior of the double valves are housed in inserts 205, 207 in the head cover 201 for manufacturing reasons. The first working chamber 212 for the fluid to be pumped, not lubricated, for example the water, and the second working chamber or lifting chamber 213 are located in the unit, the latter being connected to the cylinder space 220. The stroke chamber is filled with the stroke pressure fluid by means of the stroke piston 227, which is usually a lubricating liquid, for example: oil. The reciprocating piston 227 may be hydraulically or pneumatically driven, as is known from the European patent application or from the main application or from other figures. However, the drive can also take place mechanically via a crankshaft with connecting rods or via a piston 226 with piston shoe 230 and a long stroke eccentric 232 with stroke surface 233 on a shaft 231 according to DE OS 33 30 983, for example FIG. 30, the piston shoe having pressure fluid pockets 228, 229 may be assigned. The piston shoe 230, which can be pivoted in the piston bed, runs with the sliding surface 234 to the piston stroke guide surfaces 233 of the eccentric 232. It is again important to fill the bore hole 223, which should end in the innermost dead center position of the piston 227, so that the lifting chamber 213 can be rationally used without disturbance and losses be filled. During the pressure stroke of the reciprocating piston 227, the element arrangement 210 is compressed upward under the fluid pressure in the lifting chamber 213, as a result of which the first working chamber 212 is compressed and the non-lubricating fluid from the chamber 212 is discharged from the chamber via the outlet valves 206 and 208. Conveyor out. Because of the high pressure in the chamber 212, the reciprocating piston 227 has a relatively small diameter compared to the element set 210, but has a long stroke. It is therefore occasionally expedient to assign a guide piston 226 in the guide cylinder 224 to the reciprocating piston, which is held by springs 225 in the middle between the piston 226 and the upper end of the cylinder 224. The piston 226 mostly has the pressure fluid pockets 227 for running on the cylinder wall of the cylinder 224. This unit is also in the dimension of the scale for the promotion of about 10 cubic centimeters at about 4000 bar. Consider the high pressure because of the thickness the wall of the housing 222 so that it does not expand radially, which would result in conveyor losses.

FIG. 24 has already been described together with FIG. 23.

An alternative to the element of FIG. 6 is shown in FIG. In this figure, the element is made of fiber-reinforced plastic, for example made of carbon fiber. At the flange 250 there is again a conical ring element. At the radially inner end, this first element is glued together with a second symmetrically conical ring element 252, that is to say joined together under pressure, for example with epoxy resin, the binding material in the carbon fiber. At the radially outer end, the first element is again glued to the second element at 253 and so on, down to the bottom 256. It is important that the inner connecting points 254 can be produced easily by gluing one element 251 and one element 252 together under the press . Then the external connections 263 can then be made by placing a radially split ring 255 radially from the sweet between two adjacent ring elements 252. The ring 255 then forms the base for the pressing together when the adjacent elements 252 are bonded in the connection 253.

In FIG. 26, a Sinngomasssar element set is made from purely mechanical individual parts. It consists of symmetrically placed konisehan rings, such as disc springs, 260 and 266 with. Distance rings 263 and 270 between the adjacent radially inner and outer ends of the elements. The piastic sealing rings 264 and 268 or 269 and 271 are located radially inside and radially outside of the diet rings. The radially inner and outer ends of the conical rings 260 and 266 are axially encompassed and held together with flange rings 264 and 272, thereby measuring the rim rings are turned radially smaller or larger and rolled up radially inwards or outwards in order to encompass the relevant ends of the conical elements. It is important here that the spacer rings 263 and 270 must be surrounded radially from the inside and radially from the outside by plastic rings. The sealing rings 271 and 264 must encompass radially their respective spacer ring and two conical ring elements in order to ensure the pretended sealing effect for the unit.

FIG. 28 shows, on a large scale, an English-speaking conical ring element of the invention and the important parts of its exemplary embodiment of the invention assigned to it. Element 301 has the recess 371 for receiving the centering ring and the sealing ring of Figure 27 or one of the previous figures. The conical chamfer 370, which forms the pump chamber and to which the cylindrical inner surface 379 adjoins, extends radially inward, which in the exemplary embodiment has the cone 378 of very small angle ha ⁺ at the far end ^. This chamfer (the cone) is important because the element is pressed axially together and this axial pressure brings an inner diameter reduction that is greater at the rear end than at the front end of the element. After the compression, the inner surface would therefore no longer be cylindrical. Next is the back support surface, to which the reinforcement bulge 374 is connected, and finally the element 301 still has the holding surface 373 for attaching the cleat rings of the main application and FIG. 27 for assembling two adjacent, symmetrically arranged elements 301 into one element pairs. The elements rest on the support rings 375 of the distance piece 376. According to this exemplary embodiment of the invention, the spacer is in one piece with the sealing lip / pentraeger 386, specifically so that the sealing lips 380 cannot undergo any axial relative displacement relative to the element 301, because such displacement could damage or wear down the sealing lips 380 and the sealing rings 387.

An important feature of the invention in this exemplary embodiment is the sealing lip carrier 381 with its complementary parts. The sealing lip carrier has the sealing edge (the sealing web) 380 lying against the inner surface 379 of the element, in front of which the working chamber has the sealing ring seat (the sealing groove) arranged to receive the plastic sealing ring 387. The sealing lip 380 is closely fitted into the inner surface 379 of the element. The sealing ring groove is arranged near the working chamber, i.e. at the very front in the element 301, in order to avoid the radial expansion of the element 301 under high internal pressure, because such a radial expansion of the element 301 limits the service life, and then the sealing effect of the sealing lip and the sealing ring 387 is also unsafe makes and finally the amount of the pumping unit decreases when the element 301 expands radially.

For the same reasons, the sealing ring groove with the sealing ring 387 is kept short in the axial direction, because the plastically deformable sealing ring 387 would increase the pressure radially from the inside. transfer to the radial inner surface 380 of element 301. The sealing ring 387, which is inserted into the sealing ring groove, can be held by the flange of the holder 383. The bracket 383 is also designed as a dead space filling block, because the sealing lip carrier 381 must be pressurized radially from the inside, so that the sealing lip 380 can follow the radial steering movements of the inner surface 380 of the element 301 by the inner pressure pressing them against the inner surface 380 and keeps pressed when the element 301 changes radially in diameter. In this exemplary embodiment, the sealing lip carrier 381 is therefore a thin tubular part 381 which extends axially from the body 386 and which is formed on the body 386 in that the body 386 has the recess 382 into which the filler block 383 is inserted. Between the filling block 383 and the sealing lip carrier 381 there remains a narrow annular gap 382, to which the bore (s) 388 lead through the retaining surface of the block 383 to the working. Keep chamber connected to the annular gap 382, so that the pressure of the working chamber also acts in the annular gap 382 at all times. Backward of the sealing lip 380, the sealing lip support often has the diameter reduction 377, which serves to prevent the part of the inside diameter 379 of the element 301 from bumping against the sealing lip support 381, 386. The sealing lip 380 of the sealing lip carrier 381 is again very short in the axial direction, because axial length in the suspension of the element 301, which periodically transforms the cylindrical inner surface 379 into a conical shape according to the finding of the invention, the sealing lip 380 either at the front or at the rear axial end periodically lifts by a few thousandths or hundredths of a millimeter from the inner surface 379, which leads to a gap in which parts of the plastic sealing ring 387 enter, as a result of which the sealing ring 387 is scraped off and, after a few hours of operation at several thousand bars in the working chamber, renders it unusable.

The formation of the sealing lips, like the formation of the element and the surrounding parts, requires a great deal of attention, because without harmony of all the details, the unit cannot achieve any efficiency or lifespan. The depth of the annular groove 382 causes the pressing force between the sealing lip 380 and the inner surface 379 If it is too deep, ie the sealing lip carrier 381 is too long, then the sealing lip 380 wears out too quickly as a result of the surface pressure being too high. If it is too short, however, the fluid pressure in the gap 382 is not sufficient to press the sealing lip 380 sufficiently strongly against the inner surface 379 of the element 301. The filling block 383 can, for example, be held in the middle of the tubular rivet 384 in and on the body 386, the tubular shape of the rivet containing the bore 385 for connecting several working chambers.

In FIG. 27, the pump elements 301 are located as element pairs with their cleat rings 327 and 328 under the head cover (not shown) with the inlet and outlet valves. The cleat rings have the annular grooves 329, through which the radially spring-loaded holding holes 332 for attacking the clamping surfaces of the Elements 301 are formed so that the element pairs 301 are held together symmetrically to one another to form the pumping chamber (s). The bolts hold the cleat rings together. The dead space filler blocks including the blocks 359 are arranged and so are the sealing rings 393, the fluid grooves 361, the sealing ring carrier 360 and the spacer rings 302. The special feature of this exemplary embodiment of the invention is that the interior 350 of the housing is acted upon automatically and parallel to the pressure increase and Waste occurs in the main pumping chamber (s) between the elements 301 with an appropriate pressure. To achieve this invention goal; by means of which the elements 301 spring between two pressures and thereby allow higher pressures in the main working chamber between the elements, the pressure is passed from the lifting cylinder 352 under the lifting piston 354 through the connecting bore 351 into the housing interior 350. This bore or fluid line 351 is therefore an important feature of the invention. The reciprocating piston 354 for compressing the pump elements 301 and thus for conveying out of the main working chamber, presses on the bottom of the working chamber system, is axially movable in the cylinder 352 and compresses the elements 301 when pressure fluid is conducted into the lifting cylinder 354. For this purpose, the cylinder 354 has the line connection 355. In this exemplary embodiment, the lifting piston 354 is designed as a differential piston with the main part 354 and the piston part 357 of smaller diameter. The piston portion 357 is surrounded by a chamber 356 which is through bore 358 keeps this chamber under low pressure or under atmospheric pressure. In order that the differential piston 354-357 can be mounted, the housing 306 is provided with a removable base 362 which is held on the housing 306 by means of the holder 363 (eg screws). The difference in the diameter of the piston parts 354 and 357 determines the difference in the pressure in the working chamber between the elements 301 and the pressure in the lifting cylinder 352 and the pressure in the interior 350 which is the same. If the unit is used, for example, as a pump with 3200 bar in the working chamber elements 301 and if the piston diameter difference is such that half of this pressure prevails in cylinder 352 with space 350, then elements 301 hold at 3200 bar for exactly as long as they would hold at 1600 bar if there was no pressure in interior 350 would. At 3200 bar in the working chamber and 1600 bar in the interior 350, the elements are subject to the same loads as at 1600 bar in the working chamber and atmospheric pressure in the interior 350. In this way, that is, by arranging the differential piston 354-357 and the line 351 It has thus become possible to run the unit with higher pressures, for example with double pressures, than in the units according to the European publication mentioned. At the same time, it is ensured in this embodiment that the pressure increase and decrease in the working chamber and in the interior 350 take place parallel to one another, so that at the relevant times, apart from stresses in the elements 301, the pressure in the interior 350 is always a certain one, due to the diameter ratio 354-357 determined percentage of the pressure of the working chamber. Filling blocks 362 between parts within 306 redact the dead space in room 350 to a minimum 363 is a sealing ring.

Another sealing lip arrangement is shown in FIG. The sealing lips 408 do not lie radially within the inner surface of the element 401 in question, but rather form an axial bearing seal on the axially inner walls of the elements 401. The sealing lip supports 408 therefore form the sealing lips 408 and the sealing ring grooves 406 arranged radially therefrom for receiving the plastic sealing rings , with retaining rims 407 for holding the sealing rings, which are inserted into the grooves 406, can be arranged. In this embodiment according to this exemplary embodiment, the radial expansion of the elements 301 in FIG. 28 and thus their problems continue. The elements 401 lie against one another with surfaces 402 and are joined together by the centering ring 403 other centered. Several pairs of elements are again put together by the spacer rings 405. In this exemplary embodiment, the sealing lip carriers 409 thus form radial projections 417 as sealing lip parts, which form the bearing surfaces 415, which are then also the sealing lips and which bear against the radial flat surfaces inner partial surfaces 416 of the elements 401 and form the axial support and seal 408.

The sealing lip carrier 409 cannot be in one piece for two elements 401 in this embodiment. Each element 401 therefore has its own sealing lip carrier 409 in the form of a ring. A filler block 410 with a fluid line bore 412 is inserted in two of these annular sealing lip supports 409. The supports 409 have precise cylindrical inner surfaces, so that sealing rings in sealing ring grooves 411 between block 410 and support 409 provide the seal from a support 409 to the noticeable one and thus can seal the working chambers between the elements 401. The element pairs 401 are again held together by the cleat rings 327, 328 of FIG. Holding rims 413 can hold two adjacent sealing lip supports 409 together through the filling part 410.

FIG. 30 shows a U element after one of the Uoran applications. It has the pump element made of two symmetrical conical ring parts, which together form the outer arch 423 radially on the outside. Radially on the inside they have the bearing attachments or contact surfaces 424, 425. The problem with these elements was that the. Inner space 426 in the U-ring was filled with fluid and formed a dead space in which the fluid was compressed under pressure during the pumping process, as a result of which there was a loss of delivery quantity. According to the invention, the element is now. filled with a filler, for example aluminum, lead, or the like. The filling is carried out as described with reference to FIG. 24. By casting, then turning, heating to the kneading temperature and pressing together until the displacement 426 is formed. The filling is designated 427 in the figure. The U-element can be provided with cylindrical inner surfaces for the use of sealing lip supports, or the flat surfaces 424 and 425 can seal against one another if several U-elements are placed next to one another, so that in each case one contact surface 425 rests on the contact surface 424 of the adjacent U-element and and seals under pressure by preloading the element or under piston pressure.

In FIG. 3 / it is shown that the pump elements of FIG. 26 can also be produced in a single piece. They then correspond approximately to the element set in FIG. 24, but then have edges instead of arches between the conical ring elements. The first conical element 266 adjoins the flange 250 in order to pass into the inner connection 270 to the next, to the first symmetrical conical ring element 260. This connects by means of the external connection to the next element 266 and so on.

FIG. 32 shows a ring element set from FIG. 24 in connection with a pulling device according to the invention. On the bottom 440 of the element set 210, 284, 280, 281 with conical ring parts 510, 610, a draw bolt 441 is attached to the head 442. The draw bolt protrudes through the cylinder lock into a cylinder 444 and carries a piston 443 therein which, together with the bolt 441, is axially movable in a sealed manner in the cylinder 444. The pressure fluid line 445 leads to the cylinder 444. The cylinder piece formed on the other side of the piston 443 is released from pressure by the relief bore 446. When the element 210 has tensioned the element 210 by the pressure fluid supplied by the piston 227 in the cylinder 213, the first fluid having been conveyed from the interior 710, the element 210, that is to say from the working chamber 710, pressure fluid is introduced through bore 445 into the cylinder 444 directed and pushes the piston 443 down. The element base 440 is pulled downward by the head 442 of the bolt 441 and the element 210 is relaxed until it has reached the position shown in the figure. It is thereby achieved that the fluid can be sucked into the working chamber 710 through the inlet valve (of the other figures). This is particularly useful for thin-walled elements because they do not have such a high voltage that they are sure to draw new fluid through the suction valve quickly enough, because pushing out the fluid in the chamber around the element requires force, especially if the Reintroduction of fluid into the working chamber 710 should take place quickly. This arrangement can also be used in other figures.

Parts recognizable from one of the figures are usually no longer shown in other figures because they can already be recognized from one figure. It is therefore the case that parts of one of the figures also apply, at least in part, to others.

Finally close

in the context of the invention, fluid-aggregates for high pressures of 400 to 5000 atmospheres were investigated. A comparison of the known technology and the prior applications associated with this invention shows that the known technology cannot achieve such high pressures without considerable effort and without significant losses in efficiency. These deficiencies can be partially overcome if the conical ring elements are used in the formation of the working chamber and the ring elements are given a special shape and additional means are assigned to them that increase operational safety, pressure and efficiency or simplify the unit so that it is also suitable for low prints becomes economically efficient.

From EP - O] S - 0 102 441 of the applicant and inventor it is known that conical ring elements can be used to form pumping chambers. This reference teaches that the elements are only suitable for the subcritical range, but that for the supercritical range cleat rings must be arranged, which firmly connect the outer edges of adjacent pairs of elements to one another, because otherwise the elements will lift apart from one another in the supercritical range and fluid from the chamber escapes within the elements. In the meantime, it was recognized by the main application that the elements are only 11 for pressures up to about 1500 bar, because they would become too thick and give too short strokes at even higher pressures. The main application then showed a way to obtain double pressure by placing a first pressure radially outside around the elements, which is about half the pressure inside the elements.

Both arrangements according to the literature references mentioned have the disadvantage that they require high construction costs and nevertheless remain limited to a few thousand bars in pressure. Even more painful is the disadvantage of the designs according to the patent applications mentioned that the cleat rings are heavy because they have to be durable with large forces and therefore oppose the axial movement with resistance in the periodic axial acceleration, which results in a loss of efficiency. The versions of the cited references are therefore heavy, voluminoes, complicated and time-consuming, expensive to manufacture and still have defects which limit their efficiency and their operational reliability or their service life. The technology of high pressure units therefore still requires perfection and simplification.

The invention is therefore based on the task of creating a high-pressure unit in a simple and inexpensive design with high efficiency and high operational reliability and service life.

This object is achieved in the technique of the generic term of claim 63 according to the characterizing part of claim 63.

Further advantageous perfections and simplifications can be obtained according to claims 64 to 87 or other patents

The June 1985 issue of the US magazine "Popular Science" describes the current state of the art of "water jet cutting", ie the cutting of materials with thin high pressure water jets. After that, the so-called "booster" is still used today to generate the high water pressure of around 4000 bar. A number of hydraulic pumps are driven by means of electric motors, which conduct high-pressure oil of a few hundred bars into a double-directional cylinder of large diameter, in which a piston of large diameter is then reciprocated under the oil pressure. Piston rods of small diameter connect to the piston, which then bring the water to the high pressure and convey it in cylinders of small diameter. Sealing the axial movement of the piston rods in water under high pressure is very difficult and expensive. Solutions have been found in recent years, but the piston rods can only run slowly because the seals do not allow high speeds. Therefore, these plants are still very large and they are very heavy and expensive. As a result, the application of water jet cutting remains limited to the industry, which can afford such expensive and heavy equipment. The craftsman cannot use the systems because they are far too expensive for him. The European patent application of the applicant and inventor mentioned at the outset therefore creates a simple pump for high pressures by means of the use of tonic ring elements without sealing the water level under movement and friction. The seal is purely stationary. However, this advantage is associated with the construction costs of using cleat rings, which make the elements usable for the supercritical area. The strong cleat rings counteract the axial movement and thus reduce the efficiency. They are also expensive. Despite all efforts and the need for water cutting systems for craftsmen, fishermen, bakers, butchers, carpenters and so on, it has not been possible to create sufficiently light, space-saving and cheap water pumps for cutting water with around 4000 bar. The long-standing need, the long-awaited hope for a corresponding technology has so far not been met. Therefore, the object of the invention is as described, because there is no simple, cheap and reliable pump for this need.

However, such a pump is created by the present invention. This is understandable on the basis of the techniques and arrangements described in the exemplary embodiments.

In FIG. 33, the reciprocating piston 103 carries the plate spring 101, which is a conical ring element in the sense of this patent application. The spring 101 rests sealingly on the top cover 1. The cover has the inlet valve 38 and the outlet valve 39. Valves of this type also have the exemplary embodiments of the invention with the same number 38 and 39, respectively. The head cover is also contained in the examples of the invention, as is the body or the housing 91. These parts recurring in all examples are therefore no longer mentioned in the description of the other figures. If pressure fluid is supplied to the cylinder 102, the reciprocating piston 103 pushes upward and presses the element 101 together, so that pressure fluid is conveyed out of the chamber 37 within the element 101 from the outlet valve 39. This thing works well in the subcritic area. However, as soon as the pressure in the chamber 37 becomes so high that the tensioning force of the spring 101 can no longer withstand it, the high pressure pushes the element 101 away from the head cover 1 in the direction of the arrows in FIG. The fluid escapes from the chamber 37 through the gap that then arises between the cover 1 and the element 101, instead of conveying through the outlet valve 39. The aggregate therefore no longer delivers. What happened is that there was a transition from the subcritical area to the supercritical area. In the supercritical Area, the outer edge of element 101 must therefore be attached to cover 1. If two elements 101 lie next to one another, cleat rings from the Europa stove laying specification mentioned at the beginning must be used to screw the elements together. Since one of the objects of the invention is to save the cleat rings, the basic solution of the invention according to FIG. 34 is obtained according to the invention.

In FIG. 34, the element 501 of the invention has the ring nose 502 with the sealing ring seats 503 and 504 radially therefrom, as well as the closed base 505. The features 502 to 505 are thus decisive features of the invention of the conical ring elements 501 according to the invention. The element 501 is as in Figure 33 of the known technology, applied to the head cover 1. The housing 91 forms a closed first chamber ₃₅ around the element 501. The fluid line 506 leads to the first chamber 35. The second chamber 37 is formed between the element 501 and the cover 1, as long as the element 501 with the nose 502 on the flat surface of the lid 1 is applied. It is important according to the invention that the nose 502 has the inside diameter "d" = 519 and the outside diameter "D" = 518. The. Nose therefore has the cross-sectional area or cross-section 520. This cross-section is sealed radially inwards and outwards by the plastic sealing rings in the sealing ring seats 503 and 504. The chamber 37 is filled with fluid without pressure. If fluid is now passed under pressure through line 506 into the first chamber 35, the element 501 is pressed axially together, as a result of which the volume of the second chamber 37 decreases and the chamber 37 now conveys fluid out of the chamber 37 via the outlet valve 39 to the outside. As far as this happens, as in the subcritical area according to the known technology. FIG. 33. The surprise that occurs according to the invention is that when the transition to the printing of the supercritical area, the element of FIG. 33 of the known technology took off and the second chamber opened, but the element 501 of FIG. 34 according to the invention did not lift off at this pressure of the supercritical area and does not open, that is, the second chamber 37 is kept closed, because it remains sealingly on the surface of the cover 1, even in the supercritical pressure range.

The invention thus brings the surprising result that the element 501 of the invention no longer needs to be screwed onto the head cover 1 even in the supercritical pressure range. But this is precisely the result that you always longed for but could not fulfill because you did not know the solution. It is therefore expedient now to examine in detail what has achieved this surprising effect of the invention. This happens on the basis of the next figures.

FIG. 35 shows the preferred element 501 of the invention in a longitudinal section. The element has the conical ring part 501 with the radially inner and outer end piece. The element is conically hollow towards the front axially, and towards the rear axially it has the conical bulge radially to the center. So the top is in front in Figure 35, the bottom is in the back. The radially outer piece will in future be called the outer piece and the radially inner piece the inner piece. The nose 502 is formed on the outer piece toward the front and the nose 508 on the inner piece toward the rear. These noses form cylinders which are axially extended by the element. They are arbitrarily called "noses" because they have to be named somehow. The roots of the noses are followed by radially flat surface pieces which can also be somewhat conical or curved and which form the sealing ring seats 503, 504, 507 and 508.

In FIG. 36, several such elements are placed axially one behind the other with their lugs in order to form a column of elements about a common axis. The column has the reference symbol 526. Two elements facing each other at the front form a pair of elements. The last element of the column bears. a shutter 514, which also has a nose. The lugs 502 are connected to the common seal 509 on each other, while the inner tabs 508 are connected to the common seal 5 ₁ 1 together. The sealing seats already mentioned are dimensioned axially in the column between adjacent elements 501 in such a way that they form common sealing seats 510, 513 or 512 and 612 between two adjacent elements.

In FIG. 37, the left half of FIG. 36 is shown in an enlarged view, a pair of elements resting on the head cover 1 with its utensils. The sealing rings 516, 517 and 524.525 are inserted in the sealing seats. The former are the short sealing rings for you tion on the cover, while the last-mentioned sealing rings 524, 525 are the axially longer ones for the common sealing seats between two adjacent elements 501. These designs serve to achieve the effect according to the invention of maintaining the seal of the chambers in question in the supercritical range without the need for retainers or cleat rings. FIG. 38 explains why this effect is achieved by the invention.

In FIG. 38, the element touches the inner or second pump chamber 37 at the top and the outer or first pump chamber 35 at the bottom. The pressure in the inner chamber is called "Pi", that in the outer chamber is called "Po". The inner nose has the inner diameter 521 and the outer diameter 522 with the cross-sectional area 523 lying in between. The outer nose has the inner diameter 519, which also forms the torque axis 515, the outer diameter 518 and the intermediate cross-section 520. Since the plastic sealing rings are deformable and consequently how fluid acts (see the parallel patent application P -3446107.8) the pressure ranges "Pi" and "Po" are radially sharply defined. "Po" goes from 522 to 518 and "Pi" goes from 521 to 51'5,519. The diameters are given the names a, A, b and B according to the figure. The cross section of the " _P o" pressure zone is then:

Since the diameter of the "Pi" zone is smaller than that of the "Po" zone, the equation (1) of the figure is obtained, namely:

The difference zone "F _A B" is located between "B" and "b" and can be calculated according to equation 2, while equation (3) is obtained for the corresponding inner difference zone "FΔA".

From equation (1) it can already be seen that due to the distance between the diameters of the lugs in question, the outer pressure zone presses the element against the cover at all times, or always presses two adjacent elements against one another from the outside, even if the prints in the inner and outer chambers are the same because the cross-section to which the pressure acts is larger in the outer chamber than in the inner chamber.

- It can be seen that in Figure 37 the same pressure in the outer chamber at all times presses the upper element against the cover 1 and also presses the two lower elements together in the outer support (509 of Figure 36).

However, this could give the impression that the same pressure in the outer chamber would then push the inner support (511 of FIG. ₃ 6) apart, that is to say the two lower elements of FIG. 37 would be lifted apart and the inner chamber would open.

The investigation shows that this cannot happen, because if one looks at the moments around the moments axis 515 at the same pressure in the outside and the inside chamber, then the moment of the inside chamber is obtained according to equation (6) as: "M Pi ( 515) larger than the moment of the outer chamber "M Po (515). This explains why the element is fixed radially outside of 515, so it cannot escape. Consequently, only the force "Po x (b - A) pi / 4 can attempt to lift the inner seal while the force: (b - a) pi / 4 presses the inner seal between the adjacent elements. Since the difference (bA) is smaller than the difference (ba), the force pressing the inner seal together at the same pressures in the inner chamber and in the outer chamber is greater than the force trying to push them apart from the outer chamber Element 501, the inner chamber and also the outer chamber are always closed, because the inner and outer layers of the elements always remain in contact and never open when the pressures in the inner and outer chambers are the same.

The force with which the elements in their supports 509 and 511 remain pressed against one another at the same pressures in the chambers depends on the size of the differential cross sections "F4B" and "F4A". The greater the distances B and b or A and a from each other, the greater the holding force. However, there is a structural limit to these distances, because radial distances that are too wide when the elements are bent through, i.e. when they are axially compressed, lead to conical gap openings into which parts of the sealing rings would enter. The periodic opening and closing of this conical column would gradually scrape the sealing rings over time and render them unusable.

An exact differential equation of the moments about the moment axis 515 has not yet been established. It would be analogous to the torque calculation according to the EP OS mentioned at the beginning, but it is not currently necessary because the above explanations already prove that both the outer and the inner supports 509 and 511 of FIG. 36 are the same according to the invention The pressure in the neighboring chambers is always self-moving and remains closed, so that this present invention has made the cleat rings superfluous.

FIG. 39 also shows a longitudinal section through the “U element” according to the invention, in which two adjacent elements are made in one piece from one piece of material, so that the inner support 511 is removed. The inner back 529 carries conically and symmetrically to one another the two element parts which, on their outer parts, again form the lugs 502 with the sealing ring seats 503, 504. The "U-element" has the reference symbol 527 and between the legs of the element there is the outer annular chamber 528. It can be provided with a filling block which reduces dead space by fitting an annular space 528 into it, in the compressed state of the element 527 Filling ring 530 produces and sucks (divides) this in the radial direction, so that the two half rings can be inserted radially from the outside into the annular groove 528. The U-element of the invention is particularly simple, reliable, saves the inner support and the inner sealing ring seats with the sealing rings, and several of these elements can be put together axially coaxially one behind the other to form a V-element set by using the lugs 502 puts one against the other and inserts the sealing rings 524 and 525. Finally, an inner fill block 548 can be inserted into the V-element. The basics of the invention are essentially described. Figures 40 and 4l show an alternative solution. Figure 41 shows an example of the radial division of a ring. It can now be considered how the elements of the invention can be used in a pump or in a motor.

FIG. 42 therefore shows a longitudinal section through an assembly of the invention using the elements 501 of the invention, wherein the element set can also be replaced by a V-element set, the element arrangement of FIGS. 40, 41 can be used or a corresponding element or membrane set in parallel Registration P - 35 34 811.9 can be used if it is dimensioned accordingly. The housing (the plate, the ring) 91 is connected to it by screws 539, the head cover 1 with its valves and the drive housing 536 at the bottom. In the housing 91 there is the bore 534, which forms the outer chamber or first pump chamber 35. At the bottom of the bore 35 is the reciprocating piston 549, which carries the element set and weakly pre-compresses it. The reciprocating piston can move axially in the bore. In a first cylinder 538, the master piston 535 is arranged to be axially movable and sealing. It is provided with a drive device 540 to 544, through which it is reciprocated up and down. Through the filling groove (control hole) 544, the first, the outer pump chamber 35 is filled with fluid in its state of its greatest volume (outer dead center position or close to it). A vent hole with connector, 550.551, can be used to let air out of the outer chamber. In the outer pot point, the elements relaxed due to their internal tension, gave the second, the inner pumping chamber 37 their greatest volume, and thereby let fluid in through the inlet valve 38 and filled the inner chamber 37 with fluid, the second fluid in the inner Chamber 37 can be a non-lubricating fluid. If the master piston 535 now begins its pressure stroke, it presses the piston 549 against the element set and compresses the element column. The speed of the reciprocating piston and the last, the lower element, however, are not the same, because when the elements are compressed, fluid is pressed downwards radially from the spaces outside the elements and forms between the reciprocating piston and the lower one, which is locked downwards. The last element, the end element, is a fluid cushion that increases in thickness as the stroke increases. During this pressure stroke to its end, the second fluid is pressed out of the second, inner chamber, 37, via the Russian valve 39 and supplied by the pump ₉ .

In practice, the housing usually has not only one bore 534, but several, for example 5, 7 or 9 axially parallel bores 534, which are arranged at equal angles about the axis 545 of the housing 91. This has the advantage that a swash plate 542 can be rotated in the drive housing 536, which then drives or controls the number of master pistons 535 corresponding to the number of bores for the pressure stroke and return stroke in succession in one of its rotations. The master pistons 535 have very small diameters and cross-sections, the cross-sections in 4000 bar systems 10 being about ten times smaller, and that being the outside diameter of the elements, if you want to drive the master pistons at about 400 bar oil pressure. The guide of the 535 master piston is long to ensure a good seal at 4000 bar. The fluid in the first, the outer chamber, is preferably Del in order to have good lubrication and running properties. In practice, most of the master pistons usually have a radially greatly expanded piston foot 540, which pivotably supports a piston shoe 541 in its swivel bed, which slides on the stroke surface of the swash plate 542. Since no running surfaces that are well sealed and have little loss are known for 4000 bar, the piston feet and piston shoes of the large diameter are used in order to be able to work with pressures of less than 1000 bar in the drive device in the drive housing 536. The execution of the drive arrangement is only exemplary and preferred today. You could also use a radial piston design or a crankshaft drive or the like. The swash plate for the master piston stroke may be formed on a drive shaft 553 and mounted in bearings 554, 555 so that it can circulate. Lubrication grooves or hydrostatic pressure fluid pockets may be arranged in the piston foot and the piston shoe. If a guide chamber is formed for it above the piston foot, a channel 543 prevents excessive pressure from building up in this room.

It is particularly important that the fill control hole 544 hits and opens into the master cylinder 538 in such a way that the master piston 535 only releases its opening near its outer dead center, so that the control filling process does not consume too much of the master piston stroke. Without a fill hole (channel) 544, the unit cannot be permanently reliable because oil deficiency in chamber 35 could occur.

The exemplary unit in FIG. 42 is essentially drawn to scale and conveys about 2 cubic centimeters per stroke per element column, or about 5 .CC per revolution for 5 element sets in 5 bores 534, ie per revolution of shaft 553. At 500 rpm, about 5 liters of water from the second chambers 37 or 537 with, for example, 4000 bar. The diameter of the unit is about 300 millimeters, the axial length is about 450 mm. Note that a large number of thick screws (e.g. 15 pieces of M 30) are required as screws 539 in order to hold the unit together at the high pressure of 4000 bar. The wall thickness of the housing ring 91 is thicker than the diameter of the respective bore 534 and thus as the outer diameter of the elements, in order to prevent radial widening and widening of the first chamber 35, which would lead to losses in terms of delivery and efficiency. It is also important that the radial clearance between the outer diameter of the elements and the inner diameter of bore 534 (chamber 35) is very narrow, for example less than one millimeter, to avoid dead space with internal compression in the fluid. Likewise, any number of elements can be built into the columns if the unit is lengthened or shortened, so that other amounts and outputs can be obtained with the same diameter and dimensions of the elements of the invention. Likewise, you don't necessarily have to drive 4000 bar, but you can also use the unit efficiently for low pressures. At 4000 bar, it requires around 50 HP drive, e.g. through electric motor and V-belt to shaft 553, so that the entire unit including the electric motor drive can be accommodated in a housing of approximately the size of a desk. Note that at 4000 bar and the described delivery rate, very thick screws are required to hold parts 1.91 and 536 together. For example 15 pieces of M 30 screws or 5 pieces of M 42 screws. The wall thickness of the housing 91 is thicker than the diameter of the bore 534 and the elements in order to avoid radial widening of the housing 91, which would lead to conveyor losses and thus to efficiency losses.

The outer chamber 35 is sealed by sealing rings 556 against the head cover 1 and the drive housing 536. The same applies to the control line 544 if it is set by several parts. The interior space between the elements 501 of the element column 526 is cleared of dead space by a filling block 557. Line 106 automatically ventilates the inlet valve space by directing the air therefrom to outlet valve 39.

FIG. 43 shows a longitudinal section through an aggregate with a larger amount of conveyor. Those reference numerals in the figure which are the same as those in FIG. 42 show the same or corresponding parts, so that they are not repeated in the description of FIG. 43 because they are already known from the description of FIG. 42. The difference from FIG. 10 is that the elements 501 in FIG. 43 have larger diameters, which leads to a housing diameter of approximately 350 mm. 43 shows a filler ring 532 for the intermediate spaces on the outside between the adjacent elements and a filler ring 531 in the inner spaces between adjacent elements 501. Such filler rings are inserted everywhere in the relevant intermediate spaces in FIGS. 42 and 43, but not drawn in, because otherwise the figures would become too confusing. Likewise, only the sealing ring seats are shown in these figures, but no inserted sealing rings. However, the sealing rings are installed in all sealing seats in FIGS. 42 and 43. However, they are not provided with reference numerals and are not hatched because there is no space for them in FIGS. 42 and 4. FIG. 43 also shows that the shaft 553 can also be extended through the housing 91. FIG. 43 furthermore shows that it is possible to assign a plurality of beber pistons 535, 635 and 735 to a single outer chamber 35, 535. These then receive corresponding, radially expanded piston feet 540, 64C, 740 with their piston shoes 541 pivotable therein for running on the stroke surface of the swash plate 542. The bore 543 for depressurizing the piston chamber running chambers is again drawn in, as is the important filling control bore 544 for correct filling the outer chamber 35.535. Also shown is a pressure oil connection 558 for conveying lubricating oil under pressure to the piston channels 560, 561, 562 for supplying pressure fluid pockets 563 and 562 in piston feet and piston shoes, so that hydrostatic bearings are formed which bear the large axial and oblique forces which act on the piston shoes and on the Pistons or piston feet occur. The arrangement of several Reciprocating piston per individual outer chamber 35 has the advantage that the unit can be made shorter, in order to still achieve the required delivery rate for pistons of small diameter. Moreover, this has the advantage that the unit gleichmaessiger and quieter work because the sinusoid support can be arranged so that one of the plurality of reciprocating piston after the other starts to operate, so that the f _u enfkammerige machine can receive the Foerdergleichheit 15 kammerigen machine and consequently works with very little fluctuations if each of the 5 chambers receives three reciprocating pistons. Accordingly, you get 21 reciprocating pistons for the 7 chamber machine and so on. It is particularly important in FIG. 43 that the master pistons 535, 635 and 735 work directly in the first, the outer chamber 35, without a piston 549 being arranged as in FIG. It is the case that the piston 549 of FIG. 42 lifts from the bottom of the elements during the stroke anyway, because the column of elements compresses faster than the piston reciprocates, because the fluid from the outer spaces between the elements beneath the bottom of the element column flows when compressed. Figure 43 shows. So that you can get by without the piston 549 of Figure 42. The aggregate of FIG. 43 makes about 8 cubic centimeters of conveyance at 4000 bar water, if 5 of the element columns are installed, one obtains 8 times 5 times 500 = 20 liters per minute or 40 CC per revolution at 500 rpm. The. Construction length is about 450 mm and the outside diameter is about 350 millimeters.

• a) die Aufgabe, die schweren und teuren Achsialbooster der Wasserstrahl Schneidanlagen und deren schwere Druckspeicher durch kleine, leichte, billige Aggregate zu ersetzen;
• b) eine Hochdruckwasserpumpe zu schaffen, die den Bau billiger, leichter und raumsparender Wasserstrahlschneider ermoeglicht und die die Verwendung solcher Aggregate in anderen Techniken, zum Beispiel beim Steinbohren usw. ermoeglicht;
• c) eine Hochdruckpumpe zu schaffen, die die Wasserstrahlschneidanlagen so klein und billig macht, dass der Handwerker sie sich leisten kann;
• d) die Klampenringe der genannten Europa Patentanmeldung einzusparen;
• e) die Wirkungsgradverluste durch Beschleunigungswiderstaende der schweren Klampenringe zu sparen;
• f) ein Aggregat zu schaffen, dass bei Verwendung einfacher Prinzipien die Niederdrucktechnik der plastischen Membranen' der Aerzte, Niederdruck Techniker usw. fuer hohe Drucke , von mehreren tausend Bar wirkungsgradhpch und billig bei einfacher Fabrikationsweise betriebssicher zu verwirklichen.
• g) diejenigen Aufgaben, deren Loesungen sich aus den Figuren und deren Beschreibung ergeben.

The described exemplary embodiments of the invention show that solutions have been brought about for the following objects of the invention which belong to the described object of the invention:

• a) the task of replacing the heavy and expensive axial boosters of the water jet cutting systems and their heavy pressure accumulators with small, light, cheap units;
• b) to create a high pressure water pump which enables the construction of cheap, light and space-saving water jet cutters and which enables the use of such units in other techniques, for example in stone drilling, etc.;
• c) to create a high pressure pump that makes the water jet cutting systems so small and cheap that the artisan can afford them;
• d) the cleat rings of the mentioned European patent application save;
• e) to save the efficiency losses due to acceleration resistance of the heavy cleat rings;
• f) to create an aggregate that, using simple principles, the low-pressure technology of the plastic membranes of the physicians, low-pressure technicians, etc. for high pressures, several thousand bar efficiency and cheap to implement in a reliable manner with simple manufacturing methods.
• g) those tasks whose solutions result from the figures and their description.

The other figures show alternative solutions to the object (s) of the invention. ,

Figure 40 is a longitudinal section through a one-piece multi-chamber element of the invention. Instead of axially juxtaposing and sealing the elements, in this figure they are made in one piece from one piece of material. This can be plastic or stainless steel or metal. On the left you can see the flange 583 for clamping the element 582 between the head cover 1 and the housing 91. At the other end you can see the bottom 584 separating the first and second chamber. This figure also shows a special manufacturing method for the multi-chamber element. Instead of turning individual ring chambers radially from the inside and outside, the element is designed like a thread with an axial pitch, but the thread is not conical, but cylindrical. The element narrows backwards. Therefore, it can be manufactured with a thread lathe with a cone device or shaped in corresponding conical thread shapes. The particular advantage of this is that the filler rings for the radially inner and outer intermediate spaces between the conical ring parts can also be produced in one piece, like the element itself. The filler rings can then be screwed into the element from the inside and outside. Corresponding parts of the inner filling blocks are shown by 586 and 585 shows outside filling blocks. The filling blocks are only drawn in one of the intermediate chambers, but installed in all of them.

FIG. 41 shows that the one-piece filler blocks 585 or 586 can be cut open by radial slots 587, so that they become several suitable ring parts, which with their internal compression and expansion movement of the element 582 of FIG. 40 can follow external and external spaces.

FIG. 44 shows part of a radial arrangement of the invention. The piston 568 feeds into the cylinder 535. At the piston, the piston shoe 567 is pivotally mounted, which slides with its tread on the stroke surface of the eccentric 565 of the shaft 564. The channels 570 and 571 go through the piston and the piston shoe to fill the first chamber 35. With this system, the cylinders of radial pumps can be filled with fluid through the channels through the piston and piston shoe. A groove is then made in the eccentric 565, which reaches approximately half the circumference of the eccentric, namely half the inlet stroke. That has worked well, even with 750 bar pumps. However, when these grooves were used to drive the outer chamber of the invention, the elements suddenly relaxed as soon as the channels reached the groove. Under this sudden relaxation, the fluid shoots out of the outer chamber like a cannon and bubbles form, so that the first chamber cannot be filled with good fluid quickly enough. Therefore, in order to ensure a good effect, it is necessary for the groove 566 in the eccentric 565 to enter the eccentric, breaking through the lifting surface, and therefore to design it as a short control filling groove which connects the outer or first chamber 35 via the corresponding lines only reached at the time of the position of the master piston in its outer dead center or in its vicinity. This is shown in principle in the figure.

FIG. 45 shows that several master pistons 569.669 and 769 can work on a single outer chamber 35, even in radial piston pumps or motors. They then work one after the other in that they are driven one after the other via their piston shoes 567, which run on the lifting surface of the eccentric 565, thus ensuring that the aggregate is conveyed equally and that the short piston stroke is made possible.

FIG. 46 shows a pulling device for withdrawing the separating piston 572 between the first chamber 35 and the second chamber 37. This allows fluid to be sucked in through the inlet valve 38. The separating piston 572 has the sealing ring 588 for separating the fluid in the first chamber from the one in the second chamber. It is important that the pressure in the first chamber is the same as that in the second chamber to avoid mixing the different fluids. However, if you now arrange a piston rod to pull the piston down, the cross sections of the first and second chambers are no longer the same, so that pressure differences should or could occur. Therefore, in this figure of the invention, the separating piston 572 is provided with the piston rod 573 in such a way that it has the pulling piston 575 in the pull cylinder 574, but the piston rod extension 578 extends from it and plunges into the additional chamber 579. To effect the pull of the piston, pressure fluid is passed through channel 576 into the pull cylinder 574 and, accordingly, the other chamber beyond the pull piston 575 is depressurized through the relief channel 577. According to the invention, the filling line 580 for filling the first chamber is now connected not only to the first chamber 35, but also to the additional chamber 579 through line 581. The sum of the cross sections of the first chamber 35 plus the additional chamber 579 is then equal to the cross section of the second chamber 37 and the desired pressure equality and the desired cross-sectional equality of the first chamber and the second chamber on this side and beyond the separating piston 572 is then given.

FIGS. 47 and 48, FIG. 48 being a cross section along XUI-XUI through FIG. 47, shows a preferred placement of three master pistons for the common first chamber 35 of a radial piston machine. Depending on the direction of rotation of the shaft in the direction of the arrow in FIG. 16 or in the opposite direction, two pistons act first or one first.

Figure 49, which is a cross section for example. can be through the housing of Figures 42 or 43, shows the corresponding placement of three master pistons to a common first chamber. The reference numerals are as in FIGS. 4-7 and 48. The arrangement of a plurality of master pistons compared to a single master piston per first chamber 35 still has the advantage that the axes of the master pistons are eccentric and consequently more space is created for larger piston shoes. Because for the high pressures in the first and the second chamber of several thousand bars, large running surfaces of the pistons are required shoes, in order to be able to manage with a few hundred bar pressure in the lubrication of the running surfaces, or in order to carry the running surface of the piston shoes at all hydrodynamically and thereby save the hydrostatic pressure fluid aggregates, for hydrostatic bearings, hydrostatic bearing of the running surfaces of the piston shoes.

For the rest, FIG. 49 also shows the bearings of the several first chambers 35 around housing 91 around its axis 545, evenly placed at an angle. It is shown that a shaft 553 can extend through the housing 91.

• Fuer die Berechnung der Wandstaerken der Gehaeuse 91 sollte man nicht die ueblichen bekannten Formeln verwenden, weil diese fuer dickwandige Rohre nicht voll gueltig sind, sondern die von Herrn Igarashi von Riken Seiki erhaltene der DE Patentanmeldung P - 34 46 107.8.

The following may also be of interest for the practical use of the invention:

• For the calculation of the wall thickness of the housing 91 one should not use the usual formulas, because these are not fully valid for thick-walled pipes, but rather the DE patent application P - 34 46 107.8 received from Mr. Igarashi von Riken Seiki.

The pressure "Pi" in the second or the inner chamber 37 arises from the compression of the elements due to the pressure increase in the outer, the first chamber 35. Since the elements 501, which are installed about 10 percent or more preloaded, resist the compression , which results from the internal tension of the elements (read in the EP OS mentioned at the beginning), the second pressure "Pi" in the inner chamber 37 remains somewhat lower than the pressure "Po" in the outer chamber 35. The pressure "Pi" in the Inner chamber is therefore the pressure of the outer chamber reduced by the resistance of the elements 501 under their internal tension. The following therefore applies: P _i = (Po minus Fsigma) with Fsigma equal to the resistance of the elements to axial compression. This increases with the extent of the compression. In practice, this force is much lower than the two pressures, so that in practice the internal pressure Pi is almost always over 90 percent of the external pressure Po. This fact must be taken into account in order to prevent the inner lugs 508 from lifting apart.

Since the prints Po and Pi are over 90 percent the same, in practice, thin-walled elements 501 can be used in the invention and thus the thick-walled elements of the aforementioned EP OS can be saved in the context of this current invention.

The thinning of the wall thickness of the elements of the invention compared to the thick ones of the EP OS also has the advantage that the elements can now make longer strokes with the same internal stresses according to the present invention. In addition, the elements of the invention are much simpler than the elements of the EP OS. In particular, the difficult problem of prevention and wear of the sealing rings is eliminated.

The invention also solved the further problem of replacing the expensive and precise thick-walled elements of the EP OS by thin-walled elements with a larger stroke.

If the elements 501 become too thick-walled, there is a risk that the inner lugs 508 will lift apart from one another, because then the pressure difference between Po and Pi can become so great that the self-sealing of the inner lugs 508 of two adjacent elements will cease. Then you have to use the V-element of Figure 39.

The aggregates of the invention are mostly used for pumps. Nobody has asked for motors for 4000 bar so far, because they usually work in the hydraulic system under 400 bar. But it is possible to use the units of this invention as motors, to operate them with up to 4000 bar and also with non-lubricating Liquids, for example with water. During engine operation, however, the inlet and outlet valves 38 and 39 must be controlled because they do not automatically open and close during engine operation. It is preferred to do this by mechanical means, such as in internal combustion engines. The non-lubricating or the propellant fluid is thus guided into the second, inner chamber 37 during engine operation by opening one of the valves and closing the other and out again by opening at least one of the valve parts 38 or 39.

Several dozen companies around the world have worked on developing high pressure boosters. The EP OS has been publicly known for several years. The development of the pumps with the conical elements according to the EP OS has so far devoured around 30,000 working and machine hours.

Diaphragm pumps for medication, for spraying and so on, with low pressures, have been known for many decades and in principle, apparently, have been for centuries. Despite the use of dozens of industrial companies and despite the desire of the market, it has not been possible to make the current invention, to recognize the theoretical technical basics, or even to guess how simple the high-pressure technology for non-lubricating media is can be, if an inventive step takes place.

The invention has also solved the further object of realizing an automatic suction stroke, so that if sufficiently strong elements or V-elements are used, the retraction of the pistons and a forced expansion of the volume of the inner chamber become superfluous because of the internal tension the strong elements automatically do this work. The tension work lost during the compression _is partially recovered in the units of FIGS. 4-2 and 43 during the intake stroke, in that it is partially transferred to the swash plate and thus drives the shaft as well. The invention also overcomes the possible error that one could connect a follower piston or master piston with a membrane or element set, because the invention teaches that the bottom of the element column or element is moved faster than the piston would follow, because that Fluid from the spaces radially outside the elements moves in the outer chamber from the spaces below the bottom of the element or column of elements.

The use of bellows and disc springs to create a volume-changing chamber within the bellows, membranes or disc springs in the axial compression and expansion of these agents has long been known. The bellows and membranes are often made of plastically deformable materials, such as rubber or the like, while the plate springs are made of metal. Thin-walled metal parts are often used as membranes or bellows. However, these units were mostly built for gauntlet pumps or for compressors with a relatively low pressure and were mostly only usable for low pressures because they lacked the ability and principle to control high pressures. Such units are known, for example, from patent documents, patents, laid-open documents or interpretation documents.

As far as the cited references are not directly the bellows. Diaphragms or disc springs show, they contain parts that can be used in pumps, e.g. Pistons and piston shoes. However, the literature locations mentioned are only for low to medium pressures because they lack the means to deliver fluid with good efficiency at high pressures of 400 to 5000 bar or because they lack the means to convey non-lubricating agents such as water to be able to. An attempt has also already been made to use an oil column in order to convey another liquid, if necessary, via a separating agent. Such technologies can be found, for example, in US Pat. No. 1,473,924; 2,207,226; the Europa OS 0.036, 945 or the DE OS 2,258,819. For low pressures, fluid has also already been fed into a chamber surrounding the disc springs in order to press the disc spring column together, for example in the large one

However, this is also only intended for low pressures, namely for the compression of air and for high fluid pressures from 400 to 5000 bar, e ₅ cannot be used because there are no means of realizing such high pressures. Oil has also already been filled between a piston and a membrane, with air being compressed beyond the membrane. However, the membrane is connected to the piston, does not create a large delivery rate and cannot be used for the high pressures mentioned because the piston must be separated from the membrane for this.

! Pumps suitable for very high pressures with conical ring parts similar to disc springs, called elements, can be found for the first time in the European patent application E-OS 0,102,441 by the applicant or the inventor, which corresponds to the GDR patent 207.403 and in the analogous DE OS, as well as in succession Disclosure documents of the applicant or inventor in the FRG or Japan, which, if not yet disclosed, are expected to be published in 1986 or 1987.

From the E-OS (the GDR patent), conical ring elements are found to be suitable for high pressures in the inner chamber if the elements are at least about half as thick as their cross-section is extended in the radial direction. The expected publications of the applicant or the inventor will lead to the realization that at pressures of more than 2000 bar the stroke of such elements becomes so short that the operation is limited by the then decreasing efficiency and the construction costs due to the costs. Therefore, the expected publications mentioned will also teach that the pressures can be efficiently increased to about 4000 bar if pressure is passed into a chamber that surrounds the conical ring elements.

However, all of these solutions still have technical difficulties which cannot be overcome from the known prior art. For example, the known seals cause significant losses in efficiency through internal compression of the plastic sealing ring material, through still remaining, non-fillable dead spaces with fluid, which then result in internal compression losses in the fluid, which reduce the efficiency and, above all, result in tiny, opening and closing Gaps of the order of 0.01 millimeters or less, which after a short time remove the material of the sealing rings and make the unit unusable. The known means of gluing, soldering or welding disc springs together on their radially inner or outer planes can be loosened at the required high stroke rates of approximately 10 million strokes per required service life of the unit, or they break. The membranes made of plastic material are unsuitable to suck in water or to relax axially enough with sufficient low pre-pressure in the inner chamber and this also applies to the thin conical ring parts made of metals for low pressure operation. The inner chamber within the elements must be capable of being filled with a low pre-pressure or self-priming, because the unit becomes too expensive if a pre-pressure pump has to be used at high cost to fill the inner delivery chamber. There is therefore an urgent need for a high pressure pump for 400 to 4000 or 5000 bar, which is easy to manufacture, is not too expensive in price, does not build too voluminoes and which can operate reliably for several million strokes in operation with sufficiently good efficiencies.

The invention is therefore also based on the object in the generic term of high-pressure pumps with elements which are resilient in the axial direction to create a unit which is flowed through by fluid and which can also be operated at high pressures of over 400 bar and up to about 4,000 bar with little construction expenditure and with simple to produce means can work reliably for at least about 1000 hours or at least about 30 million strokes with a sufficiently high level of efficiency, or that the unit can be produced from such a simple and inexpensive design with such simple means that it can also be obtained and used for low pressures at a sufficiently low price becomes.

TECHNICAL BASICS :

In FIG. 50, a substance 602 is stored in the cylinder 601. It is loaded with "O" from above. The volume of the material is then: "L". In Figure 51, the fabric in the same cylinder is loaded with the load "P". This load compresses the fabric so that it loses height in the cylinder and shrinks by the height difference "Delta L" to height "1". The fabric received an internal compression under the load "P". This is low for metals, very high for gases and only low for liquids up to a few hundred bar, but of very high importance at high pressures of over 400 bar. Plastic sealants are also subject to this compression through internal compression. For rubber, this is given in the inventor's literature. For oil and water it can be found in the general literature. In the following, the coefficients "Fcw" for water or another fluid to be extracted "Fco" for oil or another fluid; "Fcg" for rubber or another plastic sealant and "Fom" for filler metal or another metal or other substance introduced. For the exact calculation, these values have to be taken from the literature references by conversion, taking into account the dependency of pressure and temperature. However, in order to get a rough overview of the technology, the following rounded coefficients are used for very rough calculations:

When the substance is compressed, it undergoes a volume reduction by V = initial volume times the coefficient Fc (with index for the substance). This volume is a loss volume that cannot be pumped, but remains in the pump as part of the remaining volume or dead space volume. This loss of volume due to internal compression is the volume of the cross section of the cylinder space times the height "Delta L" of FIG. 51; namely; Δ V cross section × pruck “P” × coefficient “Fe”.

52, the cylinder with the inner radius "r" is filled with a substance with the pressure "0". In the lower part of FIG. 52, the material has the pressure "P", as a result of which the cylinder wall widens radially outwards by the difference "Delta R" to the larger radius "Rp". The radius difference “ΔRp” is also called “δ” and is calculated using the formula (5) in FIG. 59.

These technical basics are simple schoolgirl knowledge that every specialist engineer uses every day.

Nevertheless, there is not a single high-pressure pump with a sufficiently high efficiency and structural simplicity on the market and therefore not commercially available. The result of this is that it has not yet been fully recognized where these foundations occur in the above direct or in modified forms in technology and must be applied correctly. It will probably be the case that they can be used once it has been recognized where they appear. The failure to recognize where they appear unexpectedly and unrecognized in the technology for high-pressure, fluid-flowed aggregates will probably be the reason why there is still no high-pressure pump with good efficiencies for 2000 to 4000 bar pressure.

Piston pumps, the majority of which have three pistons driven by connecting rods and eccentric crankshaft parts, are in widespread use for water up to 800 bar. Some special designs reach 1500 bar and very sophisticated ones reach 2100 bar. Sapphire pistons or hard ceramic pistons are sometimes used. In principle, the increase in pressure of this system is already limited by the fact that the hydrostatic crankshaft bearings of the Eickmann patent application and the tangential balancing of the pistons are not used.

. For the high pressures up to about 6000 bar the general axial booster of Figure 54 is used. In the housing 603 the hydraulic piston 605 runs in the master cylinder 604 and is provided with the smaller diameter piston rods which act as reciprocating pistons in the water cylinders 606, run in them and admit water via the inlet valves 38 and deliver them via the outlet valves 39. A motor "M" drives a pump "PV" which either reverses itself, therefore PU with the control arrow above the pump for reversing, or the pressure fluid via a reversing valve (Pressure oil) alternately via the lines 607 and 608 into the relevant chamber of the cylinder 604 and thereby alternately to the piston 605 and apparently lead back from the relevant chamber of the cylinder 604. Although these plants initially. had considerable difficulties in sealing the high pressure water level, they have been relatively reliable in the past decade and are now recognized as reliable. Nevertheless, these systems have a significant disadvantage in principle that cannot be overcome because it results from the principle. This disadvantage is that the pressure fluid compresses in the cylinder 604, that is to say it is subject to the phenomenon explained with reference to FIGS. 1 and 2. Even if the pressure oil in the relevant chamber of cylinder 604 only has 350 bar, you already get 350 bar times Fco (= 0.0055) = 1.925 percent compression of the fluid volume in the chamber of cylinder 604 under pressure. Since the pressure in the Water level but should be 4000 bar, the cross section through the cylinder 606 = 4000/350 = must be at least 11 times larger than the cross section through the cylinder 606 of the high pressure stage. This means that the oil volume in the relevant cylinder chamber 604 must be at least 11 times larger than the delivered or maximum deliverable high pressure volume of the cylinder 606. The loss in the relevant chamber of the cylinder 604 is then the above 1.925 percent times at least 11 = at least about 21 percent converted to the current high-pressure production from cylinder 606. This type of high-pressure system therefore has at least about 20 percent non-recoverable losses due to internal compression in the driving fluid in master cylinder 604. In addition, there are losses due to internal compression in the fluid in the relatively long lines from the pump PV to the master cylinder 604. Even if the losses due to friction are also disregarded and the losses due to dead space as a result of the valve arrangement in the slave cylinder 606 are also disregarded, each of these systems must therefore have at least about 20 percent of output based on the principle of Arrangement he give, so that the efficiency at 4000 bar can never exceed about 80 percent, but in reality drops to about 75 percent or to an even lower efficiency because of the further losses.

In FIG. 55, a pair of disc springs is axially oppositely directed, folded together, the radially outer ends of which are face-ground. The spring 609 lies in the flat surface 610 on the spring 611. The angle of attack of the disc spring is "alpha". In this figure, the disc spring is in its original shape, unstressed.

Figure 56 shows the same part of the plate spring as Figure 55, but the plate spring is now completely compressed in the axial direction, so that 'the previously conical. Inside surfaces touch in surface 618. The previous surfaces 610 of FIG. 55 now form a fork with the same angle alpha, so that a conical annular gap with the angle 2 times alpha is formed between the surface parts 610. This fact is an important finding of the invention.

In FIG. 57, the common annular groove 613 for receiving a plastic sealing ring is incorporated into the radial outer parts of the springs 609 and 611, which in turn is a feature of the present invention. In FIG. 8, the plate springs are again not under tension, so that part of the surface parts 610 are again against one another.

In FIG. 58, the plate spring pair of FIG. 57 is fully pressed together in the axial direction, so that the previously conical inner surfaces 618 are in contact again. The conical annular gap 612 therefore opens again between the surface parts 610. The plastic sealing ring inserted into the recess 613 partially enters the annular gap 612 under the fluid pressure from the outside. When the springs 609, 611 relax, this gap 612 clamps back together and in the process eats away part of the material from the plastic sealing rings in the recess 613. The clamped sealing ring material is later in the system than mostly black powder (0-ring powder) and the plastic sealing ring is usually completely scraped away after an hour of operation of the springs and converted into powder. The unit is unusable after one or a few hours. Therefore, according to the present invention, a "back-up" ring = support ring 616 or 617 is inserted into the recess 613. This support ring, which serves to support the sealing ring and prevents the penetration of plastic sealing ring parts into the annular groove 612, is made of metal in high pressure systems of the invention for 4000 bar, the metal having a strength of over 45 kg per square millimeter, usually around 60 up to 80 kg per square millimeter. In the case of the perfect design, the support ring 616 or 617 has the radius "R" on the inside of FIG. 58 around the root of the gap 612 and the radius "r" on the outside around its radially inner center the radially inner contact surface. In practice, the support ring may have the angular cross-sectional shape of the ring 617, when the ideal shape of the support ring 616 cannot be realized for reasons of price. The plastic sealing ring, which is inserted into the recess 613, adapts to the shape of the ring part layer 614 from the outside radially under the fluid pressure and fills the current spatial shape 615 of the recess 613 without being able to enter the gap 612 , because this gap is closed by the support ring 616 or 617.

The shape of the support ring 616 with the radii “R” and “r” described in this way prevents parts of the plastic sealing ring (not shown in the figures) from entering gaps between the springs and the support ring, because the shape of the support ring 616 prevents them from occurring Column prevented. The support of the Type 617 gradually forms under the movements and pressures to the radius "R" and is therefore a makeshift solution of a cheaper design for the practice of. The support rings are an important embodiment of the present invention.

FIGS. 59 and 60 show the mathematical foundations for calculating and changing the dimensions of the disc springs, while the strength and the conveyance of such conical ring elements can be found in FIGS. 23, 25 and 29a of the European patent application 0,102,441 by the applicant and inventor. Figure 59 shows the calculation of the dimensions "S", Delta R "and" LR "of the relevant half of the plate spring shown as a line. Figure 11 shows the calculation of the radial expansion of the plate spring or a tube under pressure from the radial inside. When the spring is pressed flat 59, the outer diameter of the disc spring increases, if the inside diameter remains unchanged, by the difference LR minus Delta R. With internal pressure and otherwise the same conditions, the radial changes are superimposed, so that the difference "δ" = "Delta D" at most To add the original outer diameter "D" plus the difference LR minus delta R "of FIG. 59. Equation (5) for calculating the radial expansion" δ "under internal pressure is explained in more detail elsewhere in the Eickmann patent literature.

The other examples:

After it has been demonstrated in the description of the principles of the invention that the previous systems have insurmountable efficiency and thus performance deficiencies, it becomes apparent, taking into account the description of FIG. 54 in particular, that the embodiment according to FIG. 17 of the aforementioned European publication (the aforementioned GDR patent) the best efficiency solution for a 4000 bar high pressure, pump would have to bring, if it were complete. In order to make it complete, the piston 52 would have to be precisely guided and, in addition, its cross-sectional area would have to be about 5 times larger than the cross-sectional area through the chamber between the conical ring elements 1. This cross-sectional difference is because the hydraulic hydrostatic bearings, which are essential, up to about 750 or 100 bar are reliable, while the pressure in the water-promoting chamber should be 4000 bar. Since the hydrostatic bearing of the reciprocating piston and the piston swallows only a few percent efficiency and the dead space in the water level is a minimum, up to 90 percent efficiency can be achieved in this version according to the basic figure 17 of the Europa OS, if you perfect and improve it Realization assigns the relevant features of the current invention. These means are primarily the sealing of the open gaps, that is, the prevention of scraping away of the plastic sealing rings and the arrangement of FIG. 61 with FIG. 62. It is namely the case that the forces in the eccentric drive according to FIG. 17 of the Europa OS are such get high that the roller bearings can no longer support them without resulting in a huge voluminoese construction. In addition, such strong bearings are usually not in stock and would have to be specially built. They are too expensive too. It is important not only for FIG. 1 of the E-OS, but also generally for the current invention that part of the internal compression losses of the overall system is recovered. This is made possible by the eccentric long-stroke drive of FIGS. 61 and 62, in which the eccentric lifting surfaces act as a hydraulic motor while releasing the fluid under internal compression. An arrangement which can absorb the high radial forces on the shaft is therefore shown in FIGS. 61 and 62. Figure 62 is a section through Figure 61 along the arrowed, dash-dotted line through Figure 6f. The shaft 619 is in the bearings 634 stored in circulation, the right bearing is only indicated by dashed lines to show the cutting line more clearly. The bearings 634 can be provided with hydrostatic pressure fluid pockets 635. The shaft has two axially outer eccentric discs 620,621 and. in between two axially inner eccentric discs 622,623, which are rotated in the radial direction with respect to the outer by 180 degrees. Each eccentric disc is provided with the central groove 628 for entry of the guide webs 628 for guiding the pistons 631 thereon. The guide webs are formed on the housing or on the cylinders which guide the Kolbeh 631 for the compression of the conical elements in the radial direction. Through the entry of the piston guides 628 into the ring grooves 629 between the parts of the eccentric disc in question, the long piston stroke is achieved, which is important in order to use the unit temporarily as a hydraulic motor to recover internal compression from the fluid and in the conical ring elements, sealing lips, etc. to be able to. The eccentric discs thus form the lifting surfaces 624 and 625 for the piston stroke, on which the running surfaces of the piston shoes 630 run. The piston shoes 630 are pivotable in the piston 631 and they are provided with pressure fluid pockets and channels 632 and 633 for hydrostatic bearing. The supply of this bearing results in principle from Figure 17 of the Europa DS mentioned, the shaft with the eccentrics, the piston guide, etc. results in principle from DE-OS 35 02 220 and 33 30 589.

The use of this long stroke eccentric in the current invention is useful because, without a long piston stroke with a small diameter of the piston stroke guide surfaces, use as a hydraulic motor to drive the shaft 619 during relaxation and the internal compression is not rationally possible. For this reason, for example, swashplate axial piston units are not suitable because they have too small angles of attack and piston strokes that are too short to be efficient as a motor. With such swash plates of the axial piston design, a long piston guide, as was previously not possible with webs 629 in radial piston units (FIGS. 61 and 62), and consequently at high pressures, as required here, no sufficiently long piston strokes are possible for efficient engine operation to be recovered of energy used for internal compression. The high-pressure capability for 4000 bar in FIGS. 61 and 62 results from the fact that the adjacent piston stroke surfaces Radially diametrically opposite one another, that is to say the lifting surfaces 624 cancel the radial loads of the lifting surfaces 625 and vice versa, in such a way that the shaft 619 does not experience any radial deflection and the radial bearings 634 temporarily run under no or only a low load. Each of the eccentric discs 620 to 623 'drives several pistons, for example 3 or 5 in the radial direction and guides them on the return stroke, during which they temporarily take up the expansion work from the internal compression described as a hydraulic motor and therefore as a rotary drive on the shaft 619 gives good efficiency, because the angle of attack of the piston shoes on the lifting surfaces 624,625 becomes large due to the lifting surface shape with long radii 626 around the eccentric axes 636 and 637.

FIG. 63 shows that, compared to the previous figure 12 in question, the inside diameter of the cylinder 638 may only be a little larger than the outside diameter of the piston 639 in order to make possible the smallest amount of oil which brings about the least internal compression loss in order to do this To achieve the goal of the invention. In addition, this figure shows that the inlet and outlet valves 38 and 39 must be arranged so close to the water delivery chamber that the fluid-filling dead space becomes a minimum in order to keep the internal compression losses to a minimum.

64 shows even better inlet and outlet valves 38 and 39, which form even less dead space, because the valve surfaces lie directly on the cylinder wall surface and reduce the dead space to almost zero. In addition, this figure shows that in addition to the hydrostatic pressure fluid pockets 632 and the lines 633 in the piston shoe 630 and piston 631, the Tangeetiol balancing pressure fluid pockets 640 with the lines 641 must also be arranged if high efficiency and high operational reliability are to be achieved. For the rest, Figures 14 and 15 work like Figures 12 and 13.

FIG. 65 shows a longitudinal section through a W element of the invention installed in an assembly with the cleat rings according to FIGS. 80 or 11. From FIGS. 8, 11 it was found that the sealing of the conical ring elements against the inner chamber to convey the water or fluid therefore Difficulties because small conical ring gaps periodically occur during compression and expansion form the conical ring elements which scrape off the material of the plastic sealing rings, as was also explained with reference to FIGS. 55 to 58. This disadvantage is completely overcome by the W element of the invention according to FIG. 65, namely that the element 646 approximately forms the shape of a "W" in cross section. The element 646 of the invention therefore has a front element 643 of FIG. 6 and a back element 644 of FIG. 6 in one piece together with the radially flexible ring parts 646 of FIGS. 3, 7, 9 and the central radial reinforcement 645, in which the figures used earlier in this Application or appear in one or more of the pre-registrations and the parts mentioned have different reference numerals therein. The front and rear parts, that is to say the actual conical ring parts 643 and 644, have the axially projecting ring lugs 647, which correspond to those of the reference number 13 in the cited figures 3, 7, 9 and are the important features of the technology disclosed in the invention. The parts 646 enable the radial deformation, the radial breathing when compressing and expanding the actual conical ring elements 643 and 644. The central radial support 645 prevents excessive radial expansion under internal pressure and thereby losses in delivery.

Since the W element 642 is a one-piece element, it is impossible to install the cleat rings that are required to hold adjacent conical ring parts together.

Therefore, FIG. 66, which is a section through FIG. 65 along the dash-dotted and arrowed line through FIG. 65, shows that the cleat rings can still be used and assembled if they are broken down into at least two parts by radial slots 647 according to the invention. It is useful to rotate the upper cleat ring 27 by 90 degrees relative to the lower cleat ring 28 and to incorporate an even number for the number of screw seats and threads at the same angle in the upper and lower cleat rings 27 and 28. In this way, it is possible to screw together two axially adjacent W elements of the invention, as the figure shows, and thus to form the working chambers between two adjacent conical ring parts 1,643,644. A filler shaft 648 is reinstalled. The centering rings and sealing rings 20 and 26 of FIG. 66 must be fitted into the chamber 50, but they are not shown in FIG. 65 for the sake of clarity.

The invention of the W-element makes it possible to build an assembly without opening and closing conical ring gaps, thus preventing the plastic sealing rings from being scraped away, as shown in FIG. 67.

FIG. 67 shows a longitudinal section through a housing 91 with a built-in follower piston and some shown W elements of the invention. The head cover 1001 contains the inlet and outlet valves 38 and 39 and is firmly screwed to the housing tube, also called the outer tube, or in one piece. The follower cylinder 650,651 with the follower piston or reciprocating piston 649,652 which can be reciprocated therein is located in the bottom of the housing or in its base plate or bottom cover. In the figure, these cylinders and reciprocating pistons are designed as differential cylinders and as differential pistons in order to ensure that the piston 649 is guided by its piston rod 652 so that it does not tilt. However, both cylinder chambers 650 and 651 are connected to one another by a channel 660, so that they act as a single cylinder with the same pressure. The propellant fluid from the master piston is fed through line 659 into the lifting cylinder 650 in order to push up the follower piston and thus press the W element set together. Since the elements may tire after a long period of operation, a retraction device according to the invention is provided in FIG. This consists of the piston extension 655 of the reciprocating piston 649, the extension 655 protruding through a seal into the withdrawal cylinder 656 and carrying the withdrawal piston 657 therein. If pressure oil of low pressure is passed through line 658 into pull cylinder 656, piston 657 pulls piston 649 back to its starting position, in which it is shown. As further special features of the invention, the W elements are screwed together by means of cleat rings, as in FIGS. 65 and 66. Only the upper and lower W elements are shown in FIG. 67. As a special feature, these are screwed onto the piston 649 or the head cover 1001 by means of the bolts 50. To facilitate assembly, the upper cleat ring 28 is extended through the head cover _. Screw bolt 30 screwed tight to the head cover 1001. Since all W elements are held so firmly, they cannot separate from each other, so that the column of elements is connected to each other in a stroke and pull-tight manner.

Since the contact surfaces would form conical ring openings with the angle "alpha" as shown in FIG. 56, metallic support rings with bevels of approximately 45 degrees are installed in the chambers 50 and labeled 653 in order to protect the plastic sealing rings 654 against that them in the opening conical ring gaps on the ring lugs 13. can partially enter between this and the head cover 1001 or the piston 649 and scrape there. The opening conical ring gaps are so narrow that they cannot be seen with the eye and they could only be recognized by the geometrical-mathematical considerations of the invention. The plastic sealing rings in the chambers 50 press under the fluid pressure from the inside radially outwards against the support rings 653 and due to the beveling of the support rings, they are simultaneously axially upwards or under tightly against the base surface of the head cover 1001 or the top surface of the reciprocating piston 649 forced to form an effective seal against crushing plastic sealing ring parts. Filling blocks, not shown in the figure, are again inserted into the bores in the W-rings.

In the description of the figures, parts, effects and tasks which have already been discussed with reference to a previous figure are not discussed repeatedly in this application, with a few exceptions, because they are already understood from the previous description of the previous figure.

In the figure it is shown that, particularly in the case of units with an action on the outer chamber 35 and in the case of soft conical ring elements or in the case of tiring conical ring elements, a pull rod through the. Reciprocating piston can or must be set. The pull rod 661 may be in one piece with the head 670, with the head hold or be fastened to a base element or a base element 501 sealed by a sealing ring 681. The tie rod head or bottom member 501 may have a central thread 671 upward to secure the middle filler block in chamber 37 thereon or to hold the entire set of elements together by means of a screw. The pull rod 661 extends through the chamber 735, through a suitable bore 662 in the piston 652, through a suitable bore 1062 in the piston 649, through the chamber 651, through the seal and guide 664 and through the pull chamber 666 to hold the pull piston 668 in the pull chamber at the end of the pull rod. A spring means 669 may be arranged between the holder 664 and the pulling piston 668 in order to push the pulling piston back and pull the element set 501 back into the starting position via the piston rod 662. In addition or alone, the feed line 667 may be arranged in order to conduct pressure fluid of low pressure into the pull chamber 666 and thereby act upon the pull piston 668 at the appropriate time and press the piston rod back with the elements attached to it into the starting position of the elements.

FIG. 69 shows an advantageous embodiment for the upper element which bears against the end face of the head cover 1001. The upper element 527 is here provided according to the invention with a ring nose 684, the diameter of which is different from the other elements, in order to fulfill the purpose of support, mounting and sealing relative to the head cover 1001. The housing has an annular recess into which the annular flange 684 of the element 527 protrudes and fits therein and is firmly clamped therein. An annular groove 683 for receiving a sealing ring is also arranged. Also shown in this figure is the annular space 820 between the outer diameter of the element 527 in question or its encirclement 682. According to the invention, this annular groove 820 is of great importance for the efficiency of the unit. According to the invention, it must be so narrow radially that, when the element is tensioned, there is hardly any distance between the outer diameter of the element arrangement and the. The inside diameter of the housing 91 remains because this annular gap is a dead space in which the fluid compresses to internal compression and causes losses of considerable magnitude. However, the radial dimension of the 820 ring groove should still be a tenth of a millimeter so that some fluid can flow through it.

Figure 69 repeats in principle an example for the drive of the reciprocating piston and also shows the arrangement of a short central retraction device. The pull rod 1003 again has the head 670 with the sealing ring seat 681 in order to hold the base element 514 in a sealing manner or to be fastened to it. The pull rod 1003 then extends around the central axis 1002 through a part of the housing 91 or its base cover 91 in order to enter the pull chamber 672 and to hold the pull piston 673 in it at the end of the pull rod. The spring means 699 between the parts of the housing 91 and the pulling piston 673 pushes the pull rod and thus the elements 527, 501, 1, etc. back into the starting position. The passage 1004 is used to empty the chamber 672 of pressure. Since the retraction arrangement in this figure is arranged centrally around the Kammmernachse 1002 and this must usually be so because the elements are arranged centrally in the chamber 35, in this figure the reciprocating pistons 535, 735 are arranged radially offset relative to the axis 1002 and run closer Fit in corresponding holes in the base cover or in the housing 91. Since it is difficult for such high pressures to drive the pistons directly without designing them as differential pistons 535,735, special driving pistons 540,740 are usually arranged, which act on the bottoms of the reciprocating pistons 535,735.

The driving pistons have larger diameters compared to the reciprocating pistons in order to achieve a power transmission between the lubricating fluid of less than 1000 bar and the lifting fluid in the outer chamber of several 1000 bar. The driving pistons in the figure have the piston shoes 741 with hydrostatic bearing pockets 632, 678 and pressurized fluid lines 633, while they are driven and back by a stroke drive 677, 542. be left. The lifting drive may be connected to the central shaft 553 about the central axis 674 or may act together and act on a number of chambers 35 which can be arranged distributed around the central axis. Bearings or pressure fluid means 676,554, 675,1005,555,685 or the like may be arranged.

Figures 70 and 71 show very important features of the invention, namely sealing arrangements radially of the contact between the elements. As already described, when the conical ring elements are compressed and expanded, narrow conical ring gaps open up which, although they only reach dimensions of a few hundredths or less than a hundredths of a millimeter, open the plastic sealing rings quickly. The figure therefore shows an outer seal and FIG. 22 shows an inner seal for use in the corresponding sealing ring seats 615,50,3,4,503,504 etc. of the relevant elements 1,501,527 etc. The outer seal in FIG. 70 has a fixed support ring 686 which is suitable for 4000 bar solid metal of over 45 kg per square millimeter strength, but is otherwise softer and a plastic sealing ring 687 surrounding it radially inwards and axially in both directions, the parts 688 and 689 of which are the axial Form encompassing the support ring 686. In the radial direction, the arrangement of FIG. 71 has the fixed support ring 690 with the plastic sealing ring 691 and its axial gripping parts 692 and 693. The sealing ring parts expand radially and contract radially parallel to the radial change of the elements when the elements are compressed and expanded. The axial gripping parts 688, 689, 692 and 693 are important according to the invention, because without them the seal is not as good as it would have to be for use in units of the invention. Conventional cylindrical sealing rings are not suitable because conical gaps, which are not visible to the eye, open and close at the axial ends and would scrape off the plastic sealing ring. This is prevented by the design according to FIGS. 70, 71 and the subsequent related figures, because the plastic sealing ring material of the rings 686 and 691 can no longer touch any opening conical gaps. The pressure radially inside or radially outside of the rings presses these sealing arrangement rings firmly against the radial end parts of the element in question and the metallic rings, which are stronger than the pressure in the fluid, seal the opening conical ring gaps between the elements or between an element and a neighboring part.

FIG. 72 shows important arrangements for the operational safety and the effectiveness of the relevant unit of the invention.

In order for the outer chamber 35 to act effectively, it is extremely important that it is always filled with the correct amount of Del (fluid) and free of air bubbles. A fluid supply line 709 is therefore led to the chamber 35, into which a check valve (one-way valve) 706 is switched on, near the chamber 35. For this purpose, for constructional and structural reasons, the bore 705 can be arranged in the housing 91 and the valve holder 707 with seals 708 can be inserted into it, it being possible to hold these parts with the connection 710 in the housing 91. The pressure line 709 is supplied with pressure fluid from the outside or out of the unit. Furthermore, the outlet bore 795 is arranged at a location in the head cover 1001 which is left free by the seals 694, 696 and which may lie above the gap 697 and is directed to a valve which closes automatically at a certain pressure. The self-closing valve sits in the recess 1006 and consists, for example, of a sleeve 1012 and a valve body 696 with a load, for example a spring, 701. The valve body 703 also has the thicker head 696 and the thinner end 703. Both parts can be moved axially in the cylindrical walls surrounding them and the load 701 presses the valve body in the figure below. When the pressure in the outer chamber 35 rises above the load 701, the fluid pressure lifts the valve upwards. If the pressure in the chamber 35 is even lower, then fluid flows out of the chamber 35 through the throttle bore 1013 of small diameter via bores 699 and 702 and 704. The throttling by means of a small cross section of the bores prevents an excessive amount of fluid from flowing out of the chamber 35. In any case, the chamber 35 is emptied of air bubbles since the arrangement is at the upper end of the chamber 35. If the pressure in the chamber 35 increases more, not much more fluid can escape due to the throttling action, so that the valve body 703 rises upward against the load 701, the bore 702 entering the cylindrical wall of the sleeve 1012 and being closed by it. so that no more fluid can escape. This arrangement therefore keeps the chamber open at low pressure and closes it at high pressure. This means that during the return stroke of the elements, at which there is a low pressure in the outer chamber 35, the chamber is filled with some fresh fluid from the line 709, air and excessive amounts of fluid escape through the valve 703 in this state, but the chamber 35 is solidly closed is as soon as the pressure stroke for compressing the elements begins to work. It is preferred to set the pressures so that the inner chamber 37 never has higher pressure than the outer chamber 35 so that the elements can press themselves together without cleat rings. Most of the time, the valves are set so that the pressure in the inner chamber when the elements are lifted back is 2 bar (plus minus 5 bar) below that of the outer chamber 35. In order to be able to arrange the bore 795 in such a way that it meets the chamber 35, the upper element 527 often receives a ring nose 695 with a somewhat smaller diameter than the ring nose 502 of the remaining elements 501, 527.

This is desired so that the sealing ring seat 696 has a sufficiently small outside diameter so that the bore 696 is not closed by the sealing ring.

FIG. 73 shows a retraction device for the element column in the chamber 35. The reciprocating piston 712, which fits tightly in the cylinder wall 711, is sealed, runs in the axial direction and is driven by the driving piston 649 to the pressure stroke, has the piston rod 713 closely fitted in the axial direction into the cylinder wall of 1007 of the bore in the driving piston 649. The piston rod thus extends through the driving piston 649 upd and also through a seal 715 into the pull chamber 716, within which it carries the pull piston 717 at its end. If pressure fluid of lower pressure is passed through bore 718 into the pulling chamber 716 when the outer chamber 35 is under low pressure, the pulling piston 717 pulls the elements back into their starting position via the piston rod 713. The bores 665 and 659 are inflow and outflow bores for the chambers 663 and 650,651, the chamber 650,651 being the pressure chamber for driving the driving piston 649 which presses on the reciprocating piston 712.

74 shows the V-element of FIGS. 33, 34, but with a modification according to the invention. In Figure 74, the BV element has a nose with a radially flat surface 723 at one axial end and a curved surface with a ring line tip 719 at the other axial end. As a result, when two V elements are placed axially on top of each other, a metallic line lies on a metallic plane and if so If the line lies on the level under load, it forms a metallic seal, so that plastic sealing rings can be avoided. However, this type of seal only works with high pressures if the line and the surface are perfectly made, so that there is no gap between them.

In FIG. 75, the nose is formed by a radially very short flat surface 720, from which conical surface parts run radially outwards and inwards, which are shown by 721 and 722. The nose 719 in FIG. 75 thus consists of a plurality of parts of the surface positioned at an angle to one another, while the nose 719 in FIG. 74 is formed with a surface with a constant radius around the center of the nose, so that the cross section of the nose forms a semicircular surface.

FIG. 76 shows one of the most elegant solutions of the support of the adjacent elements on top of one another, but this is only pleasant if a metallic ring, which has the shape of a standard round cord ring, is available or can be bought cheaply. The ring must have a perfectly round cross-section or at least a cross-section with the same radius around the round axis of the ring; at least in the area in which it is drawn to support the adjacent elements. In addition, it must be made of such strong metal or material that it can bear the forces that occur, which at 4000 bar are well over 50 kilograms per square millimeter, without deforming its figure of the same radius around the ring axis. The problem nowadays is that round rings 727 of this type are not to be found like sand by the sea and also do not appear to be cheaply available on the market. In principle, however, they can be manufactured precisely, especially if they are formed radially inside and outside the masses b 0̸ and B 0̸ because then the remaining ring remnant can be clamped in and grinded precisely with grinding machines with swivel arrangements. The diameters b 0̸ "and" B 0̸ "with their distance delta B" then cause the elements according to FIGS. 33, 34 and so on to self-compress. The seal, although a purely metallic one, should then be precise and absolute, because a sufficiently extended surface area is formed, provided that mirror-image ring grooves with radii around the common ring axis 1016 of the ring 727 are incorporated in the adjacent elements 724 and 725. Since no conical ring gaps open in this version, this version is the ideal version if it is manufactured precisely and firmly enough. Nevertheless, plastic sealing rings can be placed radially on the outside and inside in the gaps 1014 and 1015. There is no danger that these plastic sealing rings would scrape off, because no opening and closing gaps form during this training.

The ring axis is shown by line 1016. It should also be noted that in the embodiment according to FIGS. 74 to 76 with a metallic seal, it must always be ensured that the pressure in the inner chamber 37 plus the resilience of the elements never reaches or exceeds the pressure in the outer chamber 35.

FIG. 77 shows adjacent elements 501, 527 installed in the housing 91, these elements showing the sealing arrangement of FIG. 71 installed in their sealing ring seats. The arrangement according to FIG 7 ₀ is omitted here because instead the lugs are provided 502 with conical bevels 738 radially inwardly, so that a metallic deposit less radial dimension, is in the extreme case of a circular line formed, which then itself seals when the pressure in the outer chamber 35 always exceeds the internal pressure in the inner chamber 37 plus the clamping pressure of the elements. Under these circumstances, the inner seal is omitted in FIG. 77, that is, saved,

Since it is important that the pressure in the Russian chamber 35 always exceeds the sum of the pressure in the inner chamber 37 plus the clamping pressure of the elements, a corresponding self-regulating differential pressure valve is installed in FIG. 77, which is axially movable in the control cylinder 729 and with 731 is designated. From the inner chamber 37, the line (bore) 728 leads, for example, through the head cover 1001 to one end of the cylinder 729, while from the other end of the cylinder 729 the line (bore) 730 leads to the outer chamber 35. The control piston 731 is thus acted upon from above with the pressure of the inner chamber 37 and from below with the pressure of the outer chamber 35. It has an upper, thinner piston part 735 and a lower, thicker piston part 734 fitted into corresponding dimensions of the diameter parts of the cylinder 729, in which it is axially movable and the difference in diameter of the parts 734 and 735 is the height of the difference in the pressure difference in the inner chamber 37 and in the outer chamber 35 determined. If the pressure in the inner chamber 37 becomes so great that the pressure sum of the inner chamber pressure plus the clamping pressure of the elements approaches the pressure in the outer chamber 35 too much, then the valve 731 is pressed down and gives the overflow slots 736 to the drain hole 733 and the annular chamber 732 free. Then fluid escapes from the inner chamber 37 through the annular chamber 732 and the drain 733 until the pressure in the inner chamber has dropped sufficiently. Once this has been achieved, the pressure in the outer chamber 35 pushes the piston 731 up again and closes the valve, so that the system can continue to operate reliably.

FIG. 78 shows a cross section through the same elements as that which are installed in FIG. 76, but with the difference that clamping rings 739 are installed to hold adjacent elements together. The radially outer ends of the elements are thinned so that the ring encirclement can engage in the recesses in the elements created by the thinning. This is desirable because the outer filler blocks can become flat rings and the dead space can be filled in radially outside the conical ring parts of the elements. This is also possible according to this figure of the invention, since the full clamping force of the elements is required to extend radially outwards up to the nose 502. The parts adjacent to the sealing ring groove, in which the ring arrangement 690, 691 is installed, can thus be kept thinner in the axial direction than the other wall thicknesses of the elements, in order to be able to realize the encompassing by means of the relevant parts of the encircling ring 739.

FIG. 79 shows a longitudinal section of the preferred embodiment of the arrangement of the upper element 501, 527 on the radially plane end face of the head cover 1001. The elements 1,501, 527, 642, etc. have the ring nose 502, 695. The head cover again has the bore 795 and the seal 694 is installed between the head cover and the housing 91. The diameter of the chamber 35 is again so small that the gap 762, 780 between the elements and the housing is so narrow that any undesired dead space is avoided. Since here, too, opening and closing conical ring gaps are created on the flat surfaces of the noses; if the elements compress and expand, a suitable seal must be provided to prevent scraping of the plastic sealing rings 654 and 761. avoid. The seal according to FIGS. 21 and 22 is not suitable here. Instead, metallic sealing rings 760.653 have to be installed, which have about 45 graceful bevels against the plastic sealing rings, so that the plastic sealing rings press the metallic sealing rings 653 and 760 against the nose 502, 695 and also against the end face of the top cover 1001 under the fluid pressure to secure or prevent the full sealing and the closing of the opening and closing conical ring gaps between the nose 502, 695 and the head cover 1001.

FIG. 80 shows an embodiment of elements with radial ends into which a round ring 763 or a radial half of the same is inserted, the half being formed by line 764. This gives the sealing supports 766 of the element with the sealing surface parts 769 between the element and the round ring 763,764, which form the radial dimensions of the diameters 'b φ' and "B φ" with their difference "delta B" according to the invention the radial ends 768 of the elements, which lie against one another in the area 770 and can also be glued or welded there.

Figure 81 shows the corresponding design for the radially inner ends of the elements with the parts 771,772,773,774,775 and 776, which correspond to the corresponding ones of Figure 60 in the radially opposite direction and thus the radial sealing dimensions a φ "and" A φ "with the diameter difference" delta A "of the invention. This overcomes the disadvantage of the preliminary technique that the glued or welded element ends loosen or break under the internal pressure. The sharp openings between adjacent elements of the preliminary technique are avoided by the designs according to these figures and the contact surfaces are enlarged. This version is therefore also suitable for gluing or welding the adjacent elements for higher pressures than was possible in the low pressure primary technology.

FIG. 82 unites FIGS. 80 and 81, but additionally places the encircling ring 784 with the axial encasements 785 around the outer parts 783 of the elements. Plastic sealing rings can be inserted in the Raeuma 782 and 779, but this is not necessary if the parts 727, 1780 and 1781 are perfect and durable. Wrapping rings can also be used on the inside diameter, but they are not shown in this figure.

FIG. 83 shows the formation of adjacent element ends in an enlarged representation in order to make the details clearer than in the previous figures. One can see the radially shortened support of the lugs, the bevels 794 and 795 for the conical annular gap 612 created here intentionally radially inwards, the used metallic and plastic sealing arrangement rings 690, 790,691,791,692,792,693,793 and the encompassing arrangement 783,784 and 785.

790, 691, 792, 692, 792, 693, 793 and the encompassing arrangement 783, 784 and 785. The important bore 796 is also formed here, which directs fluid and its pressure from the outer chamber 35 against the sealing arrangement, the bore being set through the encapsulation 784. Radially reversed arrangements are also expedient at the radially inner ends of the elements which are required in the radially opposite direction but these are not shown in the figure because they are in the radially opposite direction according to the embodiment shown for the radial emission of the elements also for the radial inner ends of the elements Elements can be built.

Figure 84 shows the preferred embodiment of adjacent elements made of fiber-reinforced plastic, for example made of carbon fiber, that is to say made of carbon fiber material. The round ring or semicircular ring 801 is preferably made of the same material. The shape essentially corresponds. that of FIGS. 80 and 81 for the outer and inner ends of the elements, only the senders being shown in FIG. 84. The fiber layers are overlaid with the adhesive, for example epoxy resin, and glued together and dried. It is the case that fabric parts 812 to 815 or 802 to 805 do not stop at the same places, but instead radially offset from one another, end in 806 to 809, so that uncut fibers in adjacent fiber layers always lie one above the other and are glued. Layers 816 to 819 show the bond between the fibers, the total adhesive mass, for example the epoxy resin, forms a one-piece solid plastic after cooling, which then contains the strong and strong carbon fibers.

Figure 85 illustrates the formation of the bevels on the noses. According to FIGS. 33 to 37, the nose would go from diameter "d1" to diameter "d3". In FIG. 85 of the invention, however, it has the conical bevels 794 and 795 from “d1” to “d2”, so that the flat support only goes from the diameter “d2” to the diameter “d3”. As a result of this shortening of the support in the radial direction, the opening width of the conical gap at "d3" is smaller than in FIGS. 33 to '37. This makes sealing easier. In the figure, the cylindrical gap 820 between the outer diameter of the elements and the inner diameter of the chamber 35 in the housing 91 is so narrow that the outer surfaces of the elements are compressed Condition of the elements almost touch the wall of housing 91 to avoid any dead space. Therefore, FIG. 86 can still be read together with FIG. 85, FIG. 86 showing a cross section through the housing 91 of FIG. 85. The diameter D = 821 of the housing 91 can be seen in FIG. 86 and by comparing the figures it can be seen that according to the invention the longitudinal grooves 822 of small cross section are machined radially from the inside into the housing 91 in order to axially flow the fluid along the elements in the outer chamber 35 to realize with the smallest dead space in the outer chamber 35.

FIG. 88 shows that the beveled metallic support ring 838 should have a conical bevel 841 at the axial end in order to seal with the edge between the conical surfaces 840 and 841 on a radial flat surface when the flat surface is subjected to a deflection during compression and expansion, whereby the cylindrical surface 839 lies on an adjacent cylindrical surface, but is also conical if the adjacent surface of the adjacent part underlies corresponding deformations during operation of the system.

FIG. 87 shows a plate spring as an element, the axial axis of the plate spring 830 in question being ground flat to form the radially flat contact surface 831. In the case of two adjacent elements of this type, which are particularly simple and inexpensive to manufacture, at approximately the same pressure in the outer chamber 35 and the inner chamber 37, which according to the corresponding exemplary embodiment of the invention differ only by a few bar, even at high pressures in both chambers several thousand bars, the ring 832 with radial flat surfaces or conical surfaces placed on the flat surfaces 831 of the elements. Then the beveled metallic rings, for example of FIG. 39, must be inserted, one in each of the four radial axial edges between the ring 832 and the elements 830, as shown in the figure. Radially inside and outside, the sealing ring seats 839 then form and 845 for inserting the plastic sealing rings, which then the bevelled support rings 833,834 and 843,844 against the ring 832 and the relevant element 8 ₃₀ respectively. press its flat surface 831 and so that the Kompri-. Seal and expand the opening of the conical ring gaps axially of the ring 832 in the radial direction.

Figure 89 shows how the arrangement for rusting liquid in the inner chamber 37 can be made operationally safe. For this purpose, the element 830 made of disc spring steel is placed under (above) another, for example thin element 846 or 847, made of material that cannot be attacked by the liquid or the gas in the inner chamber 37. For example, it may consist of the Japanese stainless steel SUS 630 or VEW stainless steel or some other suitable material. The element 842 should extend radially up to the ring 832 and the conically bevelled support rings 843, 844 should then rest on the relevant element 842 and seal the known opening and closing conical gap together with the plastic sealing rings.

Figure 90 shows a longitudinal section through an alternative embodiment to Figure 89. The protective elements 848 and 847 on the plate spring elements 830 with their flat surfaces 831 extend radially so far here that they replace the noses of the 33 to 37 figures and lie directly against one another. As a result, they form the sealing ring chamber 839, into which the support ring 690 with the plastic sealing ring 691 can be inserted, as also in the right alternative part of FIG. 89. The radial inner seal is made by interposing the ring 849 between flat surfaces of adjacent elements 830. A support ring 851 made of metal encompasses the ring 849 and part of the cylindrical inner surfaces 855 of the adjacent elements 830 radially from the inside. The radial flat surfaces of the adjacent elements on their radially inner ones End pieces are shown at 850. The protective elements 847, 846 encompass part of the cylindrical or slightly conical inner surfaces 855 of the elements 830 in the form of cylindrical parts 848. The ends 848 are axially flanged by the ends 864 of the inner encompassing ring 853, that is to say clamped together in the axial direction. This forms between the parts 830, 848, 851 and 853 the sealing ring chamber 852, into which a plastic straightening ring is inserted or clamped. The two lower elements 830, which can therefore be made of steel plate springs, are in this way related to a V-element of the invention. 33 to 37, the protective elements 847, 846 firmly against attacking substances from the inner chamber 37 the resulting V-element of the present invention are included.

Figure 91 shows an arrangement of the invention with disc spring elements with radially ground axial end faces of the elements. These parts, which are installed here, are essentially all already described in the previous figures. This figure therefore shows the entire assembly of adjacent elements. The flat surfaces 831 and 876 are formed, the rings 832 and 849 are placed between them and so the chambers 860,861,862 and 863 are formed for inserting or installing the sealing arrangement. The encircling rings 784 with their bores 796 and 875 and with their encirclements 785 and 874 are arranged encompassing the element ends. In order to achieve the desired effect of the invention, namely to make the system reliable for 4000 bar with sufficient efficiency, attention must be paid to the dimensions of the encapsulation and the foot rings according to this figure. The encapsulations therefore receive the cylindrical end faces 869 and 872, while the filler rings 865 and 904 receive the cylindrical radial ends, for example 871, so that the radial ends just fit into the cleat ends 870, 872 when the elements are pressed together without any significant between them harmful dead space remains. The thickness of the filling blocks 865 and 905 corresponds in principle to the thickness of the rings 832 and 849, so that there is no dead space between the filling rings and the elements when the elements are pressed together. The filler rings 865,904 are conical, however, if the elements are not fully compressed due to their internal tension due to their service life. See the Europe OS mentioned above or the GDR patent mentioned for the tensions. The space 820 must be kept narrow, as described earlier, and the longitudinal grooves 822 are expediently machined into the housing 91.

In FIG. 92, the conical ring elements are replaced by axially displaceable, radially nested, in principle cylindrical tubes 1882,883,884,885,886 and 887. This is known per se, but the known designs are not reliable because they fall apart. Therefore, according to the invention, the upper ring element 1882 is recessed with a radial flange 880 mung 881 clamped between the head cover 1001 and the housing 91. All other ring elements have a head 894, preferably with a sealing ring chamber with a sealing ring, 895 therein. In addition, all elements have an outer recess 892 and an inner recess 889 with stroke limiting rings 893 and 890 therein. The heads and the limiting rings limit the axial stroke of the elements relative to each other and prevent the elements from falling apart axially. In addition, additional guides 900 can be arranged in order to obtain good guidance of adjacent ring elements through the heads 894 on the inner surfaces 882 and through the inner surfaces 901 of the additional guide 900 on the cylindrical outer surfaces 899. The limiting rings can be round or radially flat. This unit according to FIG. 43 is also suitable for lower and medium pressures with large amounts of material in the inner chamber 37. According to the invention, it is driven either by reciprocating pistons acting on the lower element 887 or by pressurizing the outer chamber 35 with pressurized fluid. A withdrawal arrangement 902, 656, 657 and reciprocating piston 52 may be arranged within the scope of the invention. A filling block 903 or several filling blocks can be installed in the system for dead space filling. Since the inner chamber 37 can be reduced to practically zero here, such filling blocks are useful for the chamber 35 if they permit an arrangement.

In the figures 74 to 76 it should also be noted that the elements must remain compressed at all times. This can be achieved by all times higher pressure in the outer chamber 35 or by the prestressing of the elements.

In FIG. 72, as in the other relevant figures, it is important that the lower sealing cover of the pillar elements or of the inner chamber 37 must be separated from the reciprocating piston in the axial direction, since the speeds run at different axes. The fluid is forced out of the spaces outside between the elements radially outside around the elements into the space part below the elements when the elements are compressed.

The elements, for example also those of FIGS. 82 to 86, are to be radially rolled in the hot state and the surface parts facing the inner chamber 37 are to be provided with a protective layer against attacking fluid in the inner chamber. The elements should be shot-peened in order to be durable.

Figure 93 shows the element made from the plate spring or like the plate spring in a separate representation. It has the sealing ring recess 503 and the radially flat contact surfaces 831 and 850 on the element 830.

FIG. 94 shows an element likewise produced from the plate spring or like the plate spring with a design of the holder for the encircling rings in such a way that the encircling ring comes axially outside the element axially to the support of the element on the adjacent element for engaging the element. This arrangement can also be carried out on other of the elements and has the purpose of preventing the axial loosening of the encircling ring. In the figures described above, the wrap-around rings can be pulled apart axially, because when the elements are pressed together, the conical angles arise which also axially press the element against the part of the wrap-around ring and push away the part where the wrap-around ring engages the element. This is prevented by the design according to FIG. 45. The element 947 therefore receives the recess 926 and or 26 at such a point that an elevation 929 or 927 forms exactly axially beyond the support of the element on the neighboring element.

In FIG. 95, several of the elements 947 are assembled and encompassed by the relevant inner and outer wrap-around rings 936 and 937. These now touch the elements in the elevations 927 and 929 of FIG. 94. Since these elevations in the axial direction are exactly above the call position of the one element on the other, the elevations 927 and 927 only move in the radial direction during the compression and expansion of the elements, while they keep practically the same height in the axial direction, so that the elevations 927,929 only on the facing inner surfaces of the encircling rings 936 and 937 glide, but do not press or deform the encircling parts of the encircling rings axially.

An alternative valve for FIG. 77 is shown in FIG. 96. It serves to keep the pressure in the inner chamber low 37 relative to the outer chamber 35. Two bores, for example of different diameters, 938 and 938 are closed by valves 941 and 942, which are loaded by the springs 942, 943. A pressure body 944 is assigned to the springs and can be moved towards and away from the valves by a piston 945 which is slidable in the cylinder 946. One of the pressures is passed into the cylinder 946 in order to pressurize the piston 945 accordingly. One of the bores 938, 939 is connected to the inner chamber 37 and the other to the outer chamber 35. Due to the different diameters of the bores 938,939, the valve for the inner chamber opens at a lower pressure than that of the outer chamber. Instead of using different bore diameters, springs or valves of different strengths can be used, or other means can be used to ensure that the valve of the inner chamber opens at a lower pressure than the valve of the outer chamber.

FIG. 97 shows that the problem of the losses of the pressure translators of FIG. 54 which have been in use up to now can be overcome by the present invention. The reversing of the reciprocating piston 605 is now carried out by the reversing valve 918. The pump 921 now delivers in only one direction. According to the invention. the return line 922 is connected from the cylinder spaces (via the reversing valve) to the feed line to the pump. However, a check valve (one-way valve) 919 is installed before connecting the return line to the inlet line to the pump, i.e. between this connection and the tank 920. It is thereby achieved that the highly compressed fluid with its high internal compression cannot escape into the tank, but is forced to press into the inlet side of the pump 921, so that its rotor as a hydraulic motor is driven by the compressed fluid from the pressure chamber 604, until this fluid is fully released.

In order to partially obtain the energy of the highly compressed fluid from chamber 604 or from outer chamber 35 of the invention for driving the pump as a hydraulic motor and thus to increase the efficiency of the unit, long-stroke drives are useful because short-stroke arrangements consume too much friction.

FIG. 98 therefore shows a long-stroke unit. The long-stroke unit of the radial piston design was already shown in FIG. 6t. In FIG. 98 the long stroke is built into the housing 91 of the invention, but the principle of FIG. 98 can also be used in the pump 921 of FIG. 97. According to this invention, the driving pistons 949 are not provided with piston shoes, but rather with connecting rods 904, which are supported in a non-rotating swash plate 907. Such connecting rods and the inclined position of the pans in a disc or a drive flange set at an angle are known from the inclined axis units of the axial piston machines. According to the invention, however, the swash plate 907 does not rotate, but is prevented from circulating by a holder 914, 915, 916, the barrel body 916 or 915 of which is movable in a groove 917 in the housing 91. When the shaft 910 of the unit rotates, the inclined adjusting part 908 of the shaft 910 presses the inclined plate upwards and thus lets it run downwards at the opposite angle. When the shaft rotates once, the holder 915, 916 in the holding groove 917 moves once up and once down. In this way, the driving pistons 949 are periodically pressed upwards once per revolution of the shaft and left once downwards once. The swash plate 907 with the holding disc 913 does not therefore rotate, but rather swings around its center 925. The pistons 949 run in the cylinders 905. Pressure fluid lines and hydrostatic pressure fluid pockets (bearing pockets) 908, 912 can be arranged. As a result of the large angle of attack of the lifting part 909 to the axis of the shaft 910, the long piston stroke of the piston 949 arises. This is important because the highly compressed fluid from the outer chamber 35 or from the chamber 604 of FIG. 97 only occurs during part of the rotation of the shaft 910 works. Would the piston travel be very short with this rotating part. Then the pistons are almost perpendicular to the piston stroke guide, the friction is high and the internal energy of the high-tension fluid is largely consumed by friction, as is the case with short-stroke units of the radial piston units and the swash plate axial piston units, which are commercially available on the market. In contrast, Figures 61 and 98 of this invention achieve better utilization of the internal energy of the high tension fluid with better efficiency due to their long piston stroke.

The support rings 616, 617, that is to say the alternative designs, are not hatched in FIG. 58, so that they can be better recognized.

In FIG. 90 and the corresponding figures or designs, it is important that three support rings are inserted into the sealing ring seat, because three opening and closing conical ring gaps are created. However, these support rings 690, 833 and 834 have already been described, so that you now know how to arrange them. Here, e.g. the outer support rings 833, 834 are shaped so that they touch or overlap the middle support ring 690.

The filling rings are partially cast precisely because the radii and the bevels of the V-elements or other elements of the invention must also be filled in in order to achieve high efficiency at the high pressures. Machining this shape mechanically is often difficult or too expensive. The protective layers against attack by fluid in the inner chamber 37 should only be applied where the fluid can destroy the element.

If one compares the exemplary embodiments or these with the known technology, one can easily see that a high-pressure pump for non-lubricating liquids for several thousand bars cannot be realized with a single subject of the invention, but rather a number of new or known features in a specific one , the object of the invention solving combination must be applied. This combination (these combinations), which is the object of the invention to create a simple, reliable, high pressure pump for several thousand bars, cannot be found in the known technology and this is the reason why a pump such as the object of the invention it creates, so far not available on the market, so there has been a lack of invention and knowledge of the right combinations, so that the current invention was very necessary for the progress of technology.

Pumps with action on the outer chamber and with disc springs cannot achieve the object of the invention if the outer chamber is not free of harmful dead space and if the housing wall is not thicker than the radius of the outer chamber. is not sufficiently thick compared to the radius of the outer chamber. Low pressure elements cannot empty the outer chamber of the pressure fluid quickly enough to allow the next pressure stroke to follow if no retraction device is attached. Elements glued in parallel break under the extremely high internal pressure. The axial boosters of Figure 54 have inevitable losses that can only be overcome by the current invention. The invention also has the advantage that residual energy, tensioned fluids not conveyed from dead spaces in the inner chamber, presses on the elements and this energy is transferred to the fluid of the outer chamber, from where the inner energy together with the outer chamber according to the invention is at least partially used for the Motor drive of the pump can be recovered. According to the invention not only promote the conical parts of the elements, but also the chamber part formation radially inside the elements. In the invention, however, this subspace is practically dead space-free, that is, it can be used without remaining internal compression energy in the fluid. The amount of space in the outer chamber is therefore, according to the invention, smaller than the amount of space in the inner chamber, which increases the efficiency and performance accordingly. The large inner diameter of the elements increases the efficiency. Accordingly, the radial cross section of the elements is kept small in order to achieve high efficiency. None of these agents can be found in the known technology. Filling blocks can be poured into the compressed element columns hot, for example made of aluminum, zinc, tin, etc., if the steel-hardened elements are cooled immediately afterwards or from the other sewite, for example by means of water. Glued or welded or soldered elements break when safety valves fail and even at medium pressure. The compression of the plastic sealing rings is not taken into account in the known technology and there are no teachings for their use. The opening and closing conical sealing gaps were not recognized by previous technology and were not closed. The low pressure systems, many of which have diaphragms or weak disc springs, often only compress air and only for low pressures. They do not teach the recovery of internal energies, which is important at high pressures if the dead space is not completely eliminated. The plate springs or element design according to FIGS. 85, 86 can have no dead space Fuellkloetze (slices) get along between the elements, because the elements after their axial compression leave no dead spaces between the elements. This arrangement can only work through the current invention, because only this, for example also through the formation of the support differences "Delta A" and "Delta B" or the diameter difference "d3 minus d2", the elements lying together and thus the sealing guarantee the inner chamber 37 from the outer chamber 35. Compared to the known technology, the units of the invention bring lighter and cheaper units, which are easier to manufacture and which can offer higher efficiency.

The version with higher pressure in the outer chamber is the cheapest version with the smallest outside dimensions.

It is also able to achieve higher efficiency than the known axial boosters of FIG. 54 used today.

If you pass half pressure into the outer chamber and use the W elements or the elements of the U figures, you can achieve even higher levels of efficiency. If you use the unit of Figures 65 to 67 without pressure in the outer chamber, you get the highest efficiency for the pressure range up to at least 1500 bar, but you have to pay for it with construction costs, weight, size and construction costs. The same can be achieved through the elements of the V-figures.

Further details of the invention emerge from the patent claims, which are therefore part of the description of the invention.

FIG. 99 creates further operational safety for the elements 1 of FIGS. 8 and 11. Here, the flat surfaces 952 on the ring lugs 12 are clearly shown, which merge into the arches 954 before the initially radially plane surface merges with the conically running inner surface 4. It is also clearly shown that the centering ring (usually made of hard stainless steel) 20 is closely fitted into the cylindrical partial surface 952, with its partial partial surface 953 cylindrical in this area, as a result of which it also closes the support 23 of the two elements 1 and 11. So that the centering ring 20 cannot abut anywhere, in particular cannot abut the curved surfaces 954, it preferably has a 45 chamfering chamfer surface 955. In order that the plastic sealing ring cannot be damaged when very narrow conical gaps are removed, there are radially inside the centering ring 20 double conical support rings 959 with their conical surfaces 958 and 960, which correspond in their basic form to that of FIG. 88. Radially inside this and the centering ring 20 is the plastic sealing ring 26 and presses the support rings, following the movement of the parts of the element 1, 11 tightly against the centering ring 26 and against the inner walls 4 of the elements 1 and 11. By this pressure under fluid pressure from the inside all gaps are closed at all times and the arrangement is tight for the required high pressures. As an alternative, a centering ring 961 with spring-based sealing lips is drawn in the right half of the figure, which, in addition to the 45 grave chamfer on the side back, should also have the more pointed chamfer 963, so that the tip, as a pressed-on line seal with surface support, is so tight on the inner walls 4 of the elements can be pressed so that no plastic sealing ring parts can be squeezed into the gaps.

FIG. 100 shows a strongly resilient U element with a high resilient clamping force, which only requires a single seal to the adjacent U element. Its resilient resilience is achieved in that the neck 12 of the U-element 111 is strengthened by the fact that its outer surface is not formed with a radius around the same center as the inner radius “Ri” but with the outer radius “Ro” around a circle , the center line of which is displaced radially outwards by the radius difference "Delta R" so that it is at a distance R2 from the axis, while the inner radius circle is at a distance R1 from the axis of the element. Radially inwardly tapering ring parts 966 are produced between the surfaces 964 and 965, which bring about the shape that springs well, has the same loads at all points and is simple to manufacture, with small deviations from the best elastic line Takes price reasons into account. For the purpose of sealing against the adjacent element, the U-element receives the recesses 967 with the cylindrical surfaces 970 and the flat surfaces 969 on its radially inner outer edges.

FIG. 101 shows several of these elements put together to form an element column and provided with the support rings 790 and the plastic sealing rings 791. Here you can see a very simple design of a double element that can be produced on automatic turning racks with the simplest seats for the seal. It should be noted that the interior 50 must be partially filled, as was described in FIG. 30. This set of elements is one of the simplest and most reliable, once you look at the way of sealing, unscrewing the interior of ^. inside and accustomed to the methodology of bringing in the dead space filler block.

FIG. 102 shows that this U-element can also be easily sealed against the outer chamber if the means of the invention are used, namely the sealing means 616,617,690,691. Most of the time, however, this element will be used for units with a purely inner chamber conveyor, so that the outer seal according to Figure 102 is then not required.

FIG. 103 shows the structurally simple, but nevertheless highly resilient V-element with a large 'tensioning force in line with the elastic line with the same tension in all parts. Therefore, the V-element of this figure has the inner radius 976 around the ring line 975 at a distance R1 from the axis of the element, while the neck of the element forms its outer surface with the larger radius 978 around the circular line 977 with a smaller distance R1 from the axis of the element . This strengthens the neck 972 and increases the elasticity of the element. On the right you can see the inside and outside radii "Ri" and "Ro" and the radial distance "Delta R" can be found between the radii R1 and R2. For the rest, the element is known from the figures described above. It should also be noted that when compressing axially, the outer diameter increases from 981 by the difference 983 to 982. The element must be calculated so that with this change in diameter it does not stick to the wall of the hole in which it is installed. As a result of the radius formation of the neck 529, a special filling block must be inserted between two adjacent V-elements of this figure.

Figure 104 with 10.5 shows this formation of the assembly of two V-elements to form an element column. The filler block here receives the thickening with the radii 985 around the circular lines 986 for perfect dead space filling radially on the inside of the part 740. For precise dead space filling, the outer filler block 1530 with its walls 987,988 along the flat surface 991 (FIG. 105) may be divided in a radial plane. It may be put together and held by means of the holder 989. For perfect dead space filling, the filler block 1530 is given the outer diameter 983 of FIG. 104, so that when the element is unstressed it projects radially beyond the diameter of the element by the radial distance 990.

FIG. 106 shows in principle a repetition of FIGS. 12 and 63, but this figure is intended to show that, for the high pressures of the invention, this system can only fully achieve the aim of the invention if it fulfills the following condition,
characterized,
that the oil volume is limited to a fraction of the displacement volume of the piston 15, that if a separating block is arranged between the water and the oil, the material of the separating piston is limited to approximately three times the specific weight of the water in its specific weight, that the valves 38, 39 have conical seats of oppositely directed cones relative to the axis of the piston 15 and their end faces are in the closed state in the bottom plane of the cylinder 11;
that the heavier liquid lies vertically below the lighter liquid and fluid in the lines between the piston 15 and the valves 38, 39, which causes bends, bevels or acceleration losses, is avoided,
and the wall thickness of the housing 11 thickens than the diameter of the piston 11;
it is furthermore desired that the lines 709 and 795, for example of FIG. 72, with the valve means assigned to these lines are arranged precisely at the lower level of the oil in the uncompressed state.

FIG. 107 shows a further alternative for a valve for checking the ventilation and filling of the outer chamber 35. It is arranged in the cylinder 993, designated 994 and axially movable in the cylinder, whereby it is pressed by the spring 701 into the right end position shown. In this position, fluid flows from the outer chamber 35 through bore 795 via the control groove 796 of the piston 994 into the outflow line 1020 with the flow restrictor 704.

If the pressure in chamber 35 increases, then the pressure pushes through bore 992 on the right-hand piston end and thereby the control piston 994 against the spring 701 until the control groove 796 has overflowed the outlet control groove 1020 and the piston 994 has flowed through the bore 795 to Shuts off outlet 704 and closes the chamber 35.

FIG. 108 shows that in some places in units of the invention the spacer ring 832 may not be completely flat, but instead conical bevels 1022 and 1023 adjacent to the flat end surfaces 1024 are useful in order to reduce the openings of conical ring gaps. The taper direction is reversed when installed elsewhere in the invention.

Figures 109 and 110 show partially flat plate springs in the open and in the tensioned state. You can clearly see the opening conical ring gaps, because the angles of attack are drawn exaggeratedly enlarged. It can also be seen that the slants 1025 are created, which must be taken into account when preventing dead space.

FIG. 110 shows the design of the surfaces 1026 that are flat in the untensioned state and the sealing ring seats 613.

FIG. 112 shows the position of these parts after the elements have been pressed together. The sealing ring seats - are now characterized by the positions of the surfaces 1027 and 1028. This forms the axially outer tips 129, which are now well suited to being gripped by a retaining ring 1030.

FIG. 113 shows this retaining ring 1030, which can be easily produced on the lathe (also automatically), the figure showing that it is either split radially flat along the line 1033 or divided radially through the slot 1034, so that it radially from the outside around the edges 1029 112 and placed with its NSussameter on the wall of the hole in which the arrangement is installed, that is held on the wall of the outer chamber 35 and can slide on it.

In FIG. 114, such a wrap-around ring is not divided radially flat, but remains round, receives a thread and the other end part 1036 is screwed into it.

FIG. 115 shows a set of elements made of disc springs in the tensioned state with outer seals to the outer chamber ₃₅ and with inner seals to the inner chamber 37. These disc springs of this example of the invention have no sealing ring seat recesses, but the seals are built around the normal disc spring. Accordingly, the support rings 690 and 1043, 1044 according to the invention, the plastic sealing rings 691 and 1040, and the spacer ring 849 with the sealing ring (plastic) 861 and dead space filler block 865 can be seen again. It should be noted here that two support rings must be provided radially on the inside, namely the Support rings 1043 and 1044. The inner retaining ring is easy to manufacture because it does not encompass any elements. The sealing and support rings 1040, 1042 and 1043 are only inserted from the outside into the groove between the rims 1041, 1046 of the inner retaining ring 1045. One of the designs described so far can be arranged as the outer retaining ring or can be arranged in FIG. This has a thick part 1037 under the encompassing flange, which is used to hold the sealing arrangement at the top. The lower limiting ring 1038 is inserted from below into the ring 1037, has a backward slope and is flanged over there by the lower end 1039 of the ring 1037.

FIG. 116 shows the pressure curve of the unit with exposure to the outer chamber 35 and the inner chamber 37 over time "t". The pressure is labeled "P". One sees the first delivery course G, the pressure drop F, the filling of the outer chamber 35 by the described valves, which also includes their emptying of air, as described, and the pressure rise to the next stroke G, the pressure rise H being in the outer chamber and K which is in the inner chamber. M is the closure of the safety valve 795 with accessories according to FIGS. 72, 107 etc. The angle difference between H and K results from the automatic control valve of FIGS. 77, 96 or the like.

Figure 117 shows the volumetric efficiency of aggregates with the U elements, W elements or those of Figures 8, 11, etc., as measured in the tests.

Line D shows the measured volumetric efficiency over the pressure. The dashed line E shows the efficiency, not measured but expected, if the E elements and other arrangements were designed for 2000 bar instead of 1500 bar.

FIG. 118 shows the volumetric efficiency of units with delta pressure in the outer chamber 35 for compressing the elements and conveying water from the inner chamber. Curve "C" shows the measured results, which correspond approximately to the state of the art, because the experimental unit had only part of the knowledge of the invention available. Curve "B" shows the best measured volumetric efficiencies so far with units built according to this invention. Curve "A" is the expected curve if the aggregate was further perfected or built 100 percent exactly according to the teachings of this invention.

FIG. 119 is a longitudinal section through part of the housing tube 6, in which a set of elements from FIGS. 8, 11 is installed axially one above the other. The parts of this figure are not described here, because an exact description in Baelde from the Japanese. Patent office is published, in which you can read the parts and because it is already known from the Europe-OS mentioned at the beginning that the elements are pressed together by pressure oil to produce a pressure stroke. Therefore, it should only be mentioned here that the units built so far, with the internal chamber and elements 1, 11 placed on the reciprocating piston 1051 with a base block, which is pressed against the elements in the lifting cylinder 1050, when pressure oil is pressed into the cylinder by the supply line 1052 becomes. If the supply line is released, the elements push the Del out of the X cylinder and the piston back to the starting position. The upper element is fastened under the head cover (not shown) of the housing 6. The remaining parts within the housing 6 show tried or planned control means.

FIGS. 120 and 121 show views, partly in sections, of transmitter units for driving the controls in housing 6 of FIG. 119. However, due to the present invention, these are partly outdated and only brought to indicate the development work to some extent completely.

• dass die konischen Spalte zwischen Elementen in Richtung zur Aussenkammer oeffnen, aber gegen die Innenkammer 37 eine Auflage zur Begrenzung der Radialabmessung der Innenkammer mit dem radialem Differenzabstand "Delta A" vom Aussende des betreffenden konischen Spaltes bildet und die an den radial plan geschliffenen achsialen Aussenflaechen der radial inneren Enden der Tellerfedern Elemente eine benachbarte radial plane Flaeche (eines Ringes, einer Wand) beruehren, sodass dort beim Komprimieren der Tellerfeder (des Elements) eine Auflagenlinie "B" zur radialen Begrenzung der Aussenkammer besteht und die sich dabei oeffnenden konischen Spalte zwischen dem Element und der benachbarten Planflaeche der Innenkammer zu oeffnen;
  und/oder dadurch gekennzeichnet,
• dass die konischen Spalte durch Stuetzringe (bevorzugterweise metallischer Stuetzringe) ueberdeckt und mit plastischen Dichtringen jenseits der Stuetzringe abgedichtet sind,
  und/oder
• ein Koerper (Rohr) mit Dichtringnuten und plastischen Dichtringen radial innerhalb der Innendurchmesser der Elemente angeordnet sind.

If you look back at the described invention, the following features are essential for the invention:

• that the conical gaps between elements open towards the outer chamber, but forms a support against the inner chamber 37 to limit the radial dimension of the inner chamber with the radial difference distance "Delta A" from the outside of the conical gap in question and that on the radially ground axial outer surfaces of the the radially inner ends of the disc springs contact an adjacent, radially flat surface (a ring, a wall), so that when the disc spring (the element) is compressed there is a support line "B" for the radial delimitation of the outer chamber and the conical gaps that open between it To open the element and the adjacent plane surface of the inner chamber;
  and / or characterized by
• that the conical gaps are covered by support rings (preferably metallic support rings) and sealed with plastic sealing rings on the other side of the support rings,
  and or
• a body (tube) with sealing ring grooves and plastic sealing rings are arranged radially within the inner diameter of the elements.

• dadurch geklennzeichnet,
• dass die Innenkammer zur Aussenkammer und die Aussenkammer zur Innenkammer relativ zu den Radialdurchmesser Begrenzungen, den Stuetzrngen, den Dichtringen wird, wenn Einlass und Auslass Ventile der Aussenkammer verbunden sind. und dadurch gekennzeichnet,
• dass das Volumen der Aussenkammer im unkomprimiertem Zustande kleiner, als das der Innenkammer ist.

Further;

• characterized by
• that the inner chamber becomes the outer chamber and the outer chamber becomes the inner chamber relative to the radial diameter limits, the support rings, the sealing rings when the inlet and outlet valves of the outer chamber are connected. and characterized by
• that the volume of the outer chamber in the uncompressed state is smaller than that of the inner chamber.

In an essential part of the invention, it is still essential that the relevant unit of the invention is space-saving and inexpensive. For example, consider Figures 69, 35 and so on. Because it is not enough to be able to make 4000 bar, because with the Axial Boosters this can also be done with considerable effort. The principle of Figures 12, 63, 106 runs too slowly if it does not have light, durable separating pistons. The weak elements of the well-known technology cannot push the pistons back fast enough. The elements with arches inside and outside can often not allow rapid stroke sequences without breaking. The correct elements disclosed within the scope of the invention can be used at 400 to 1200 rpm. depending on the case, run. This is very important to get small, cheap units. The units are said to be able to withstand around 30 million strokes today and work with at least 400 strokes per minute in order to be small and light enough in terms of size and weight and to reduce the costs of production sufficiently.

Since the parts of the exemplary embodiments are also at least partially extensively described in the claims, the claims should also be considered part of the disclosure and description of the invention.

Claims (151)

1.) Aggregate that can be flowed through by fluid with at least one working chamber that increases and reduces its volume periodically with inlet and outlet means, in particular also for high pressures and possibly non-lubricating fluid,
characterized,
that means are arranged to increase performance, efficiency, operational safety, weight reduction, space requirements, cost reduction or service life. 2,) unit according to claim 1 and characterized,
that conical ring elements are used to seal said chamber, which serve to seal the inner chamber 37, which is partially arranged radially inside the ring elements, and said elements, 1 etc., with ring lugs 12, radially resilient cleat ring parts 32, 29, sealing lips 22 on the inner surfaces 60, centering rings 20 and sealing ring arrangements 49, 26 or support rings 616, etc. or their equivalents are provided or are arranged. 3.) unit according to claim 2,
and characterized by
that the element is designed as a U element 1, 11, 11, 12, 1111, etc. with an inner space 550 and axial supports 3, or is configured or arranged as a W element 642. 4.) Unit according to claim 2 or 3,
and characterized by
that several of the elements are assembled axially one above the other to form an element column and that two neighboring elements each have common, intermittent gaps Rigid, flexible, resilient support rings made of solid materials for high pressures in the adjacent fluid or plastic sealing ring are assigned or arranged. 5.) Unit according to claim 1,
and characterized by
that conical ring parts 1,526,527,830 etc. are arranged in a bore and are inserted into the separation of the bore into an inner chamber 37 and an outer chamber 35, the chamber called the inner chamber touches the inlet and outlet means 37, 38 and the outer chamber connects to one in a cylinder (a chamber ) Reciprocable piston is communicated and the pressure in the outer chamber together with the tension of the conical ring parts are stronger than the counter pressure from the inner chamber, so that the ring parts are arranged to act as separators of the chambers. 6.) Unit according to claim 5,
and characterized by
that the conical ring part or element or U-element in question is assigned at least one support on a neighboring surface, which forms a radially inner and a radially outer-sealing boundary and thereby at the same pressure in the inner and outer chamber through the support using the area difference caused, pressing at least one of the elements or rings onto another or against a surface and the support being designed to be closed. 7.) Unit according to claim 5
and characterized by
that the volume of the outer chamber is made smaller than the maximum change in volume of the inner chamber and the piston mentioned is switched on to limit the volume of the outer chamber. 8.) Unit according to claim 1,
and characterized by
that means for the partial recovery of the energies of relaxing, compressed, liquid fluid have been used in the unit of claim 1 or in related units, for example axial boosters. 9.) Unit according to claim 1 or at least one of the claims
and characterized by
that means are arranged, which are shown in the figures, described in the description, or goals are achieved, which are described in the objects or solutions to the objects of the invention. 10.) Unit according to claim 1 or at least one of the claims
and characterized by
that at least one of the following 141 versions is arranged or several of the mentioned versions are or are arranged together in an assembly or in an assembly according to at least one of the claims. 1.) Axially resilient conical ring, which forms a hollow conical space underneath, (like a plate spring), characterized in that
that at least one of the radial ends 3, 13, 33 is associated with an essentially cylindrical ring part 2, 12, 32, 42 that extends from the ring 1, 11 in the essentially axial direction and is partially radially resilient. 2.) Ring after execution 1, thereby recognizable,
that the ring part 12 is in one piece with the conical ring 1.11. 3.) Ring after execution 1, thereby recognizable,
that said cylindrical ring part 12 is formed in one piece with the conical ring at the radially outer end (wiusu 13, 33) of the conical ring 1, 11 and extends essentially axially directed from the hollow-conical axial end 4 of the conical ring. 4.) Ring after execution 1 and thereby recognizable,
that a conical pair of rings 1 and 11 is formed from two conical rings, 1, 11, the hollow-conical axial ends 4 of which face each other. 5.) Ring pair according to versions 3 and 4, thereby recognizable,
that a centering cylinder 20 touching the inner surfaces of both cylindrical ring parts 12 is arranged radially inside the cylindrical ring parts 12 of the pair of rings, the cylindrical ring parts 12 of which lie axially and coaxially with their outer axial ends 13. 6.) Ring pair according to version 5, thereby recognizable,
that the pair of rings is surrounded and held together by tension rings 27, 28, 80, which engage around the axially and radially ae, outer ends 13 of the conical rings 1, 11 of the pair of rings 1, 11 with the radially inner parts 32, the rings 1, 11 of the Clamp the pair of rings together and the clamping rings in particular = the axial and radial ends of the conical rings partially radially resilient, in essence: chem cylindrical ring parts 32, 42 included. 7.) Pair of rings according to version 6, thereby recognizable,
that the clamping rings 27, 28 are screwed together and a pump or motor chamber is formed in the hollow conical chamber 4, 4, 50 between the conical rings 1, 11 of the ring pair, the cylindrical ring parts 12 with positions or Parts of the said cylindrical ring parts 12 follow the radial = movement of the radially outer ends of the conical rings 1 and 11 during the compression and expansion of the conical rings and preferably a plastic sealing ring 26 is arranged radially inside the centro-cylinder 20. 8.) Ring after execution 1, thereby recognizable,
that the radially inner end 3 of the conical ring on the end 5 facing away from the hollow cone in the direction facing away from the hollow cone is assigned a cylindrical, partially radially resilient, essentially cylindrical ring part 2. 9.) pair of rings according to versions 6 and 7, thereby recognizable,
that between two of the ring pairs mentioned, an essentially cylindrical ring 2, which touches the radially inner ends of two of the tapered rings of the ring pair, is arranged partially radially resiliently from wall 2, which is thin compared to its diameter. 10.) Ring according to version 1, thereby recognizable,
that said ring part 2,32,22 is formed by arranging an annular groove 29,48 in a body or ring on a body 27,28,66 or rings. 11.) pair of rings after execution 7, thereby recognizable,
that the conical ring in question is provided with a cylindrical inner surface 60, a chamber cover 6, 7, 66 for the at least partial closure of said chamber 50 is arranged in it and a radially at least point = wise resilient ring piece 22 is formed on said chamber cover, which possibly seals on said inner surface 60 with the engagement of a plastic sealing ring 49 and said rin piece at least in places radially from the inside with the pressure from the fluid in said chamber, supporting the seal between said comic ring and said ring piece, is acted upon. 12.) Ring pair recognizable after execution 5,
that the pair of rings is surrounded by a snap ring 80 which holds the two conical rings of the pair of rings together and is resilient in the radial direction. 13.) Pair of rings according to version 5 but without the gene 20, dadutch recognizable,
that the two conical rings 1, 11 of the pair of rings together with their associated partially cylindrical ring parts 12, 13, 23 are formed in one piece as a single spring body, on the inner axial ends of which the cylindrical ring parts 2 are also formed in one piece with the one-piece spring body 111, the in between its conical inner surfaces 4 and its connecting part 112 which, in terms of its volume during compression and expansion of the conical parts 1, 11 of the spring body 111, forms, can be formed or can be assigned to chamber 50. 14.) Warning after execution 1 or
recognizable by
that the arrangement is used as a pump or motor. 15.) Arrangement according to version 14, thereby recognizable,
that thinner sealing ring support tubes 3 are used in the conical ring elements 1 compared to them, while the sealing ring support tubes 3 are filled with solid blocks 5, which form a narrow ring gap 4 between the inside = diameter of the sealing ring support tubes 3 and the outside diameter of the solid blocks 5, into which pressure fluid can penetrate from the working chamber in question, in order to bend the sealing carrier pipe in question radially outwards and to form a good seal with the relevant sealing ring 93, even with radial expansion of the conical ring element 1 in question, on its inside diameter. 16.) Arrangement according to version 14,
recognizable by
that the arrangement is arranged in a closed housing 6 with a strong wall 6, the housing is provided with a pressure fluid inlet 7 and the housing is temporarily filled with pressure fluid periodically. 17.) arrangement according to citation 16,
recognizable by
that the pressure fluid filling of the housing mentioned is controlled in parallel with the stroke of the working cycle of the pump or the motor is and the fluid pressure in the housing is kept at about half the level of the fluid pressure in the relevant working chamber 1, 1 of the pump or of the motor and is kept parallel to the pressure in the said chamber. 18.) Unit according to version 14, thereby recognizable, or pump or motor, characterized in that two liquids with different specific weights are arranged in a container 11 or the two liquids are otherwise kept separate and a working piston 45 without the second to touch the liquids in which one of the liquids is immersed, arranged. 19.) unit according to version 18,
recognizable by
that the first of the liquids is one with smear properties, e.g. Del, and the second. of the liquids is a non-lubricating or rust-causing liquid, for example water, and the first of the liquids has a lower specific weight than the second of the liquids. 20.) Unit according to version 19, thereby recognizable,
that said liquids are arranged in a vertical container, for example in a tube 11, and said piston is arranged from above to be immersed in said first of the liquids, its immersion in the second of the liquids being precluded by the fact that the second of the liquids, due to their higher specific weight, is always below the The first of the liquids with the lower specific weight is located and the height of the piston and its stroke are arranged accordingly. 21.) Unit according to embodiment 20, recognizable in that the piston 33, 49, 52 is arranged as a second piston of a piston drive, in that the second piston 33, 49, 52 is located in a cylinder 6, 11, 1111 and the upper cylinder part of the second cylinder containing the second calf is connected to the cylinder base of a first cylinder containing a first piston 15 by means of a line 3l. 22.) Unit according to version 21, recognizable in that the said first piston is a master piston 15 driven by a piston drive, whereby the master piston 15 presses a fluid column from the first cylinder through said line 31 into the second cylinder and said second piston thereby as Follower piston is driven parallel to the movement of the master piston 15. 23.) Unit according to version 22, recognizable by the fact that the follower piston is associated with means which push it back into its initial position and thus the fluid in the line mentioned also. Pushes the master piston back into its starting position. 24.) Unit according to version 23, recognizable by the fact that several master pistons and follower pistons are arranged sequentially operated by a common drive. 25.) Unit according to version 24, recognizable in that the means mentioned are arranged between the master piston and the follower piston means for filling the line completely with fluid and / or for draining the excess fluid contained therein. 26.) Unit according to version 25 and thereby recognizable, or according to one of the other claims and characterized,
that a transmission is arranged between the master piston and the follower piston such that the follower piston is designed with a larger diameter than the master piston. 27.) Unit according to version 26, thereby recognizable,
that a separating means following their movement, for example a separating piston 36, or a membrane 61 is arranged between the two liquids mentioned, the membrane being firmly clamped and the separating piston being provided with a sealing ring 43, 82, 83. 28.) Unit according to version 26, thereby recognizable,
that the two liquids mentioned are arranged in chamber parts or are in them, which provide one or both of them with a corresponding filler connection. 21.) .Assembly according to version 28, thereby recognizable,
that the chamber part, which contains the second of the liquids, is provided with an inlet and an outlet, wherein in each case a valve 38, 39 can be arranged in the inlet and or in the outlet. 30.) unit according to version 26, thereby recognizable,
that a working piston Ω of smaller diameter is arranged below the follower piston 49 of the larger diameter, a preferably non-pressurized space 50 is arranged between the follower piston and the working piston and said working piston 52 forms the piston immersed in said first of the liquids, so that said working piston may also coexist much higher prints immersed in said first of the liquids when said master piston supplies pressure, since said larger diameter piston (49) between the master piston and the working piston increases the force with which the working piston 52 is pressed into the liquid. 31.) unit according to version 30, thereby recognizable, or recognizable according to one of the other versions,
that the named parts of the room with the first and second liquids in them are so narrow that the volume of the liquids in them is just sufficient to fulfill the task given to them, but every other room and every other liquid are avoided in order to Reduce or avoid delivery losses of fluid in the pump due to internal compression of the fluid. 32.) unit according to version 14 or according to one of versions 15 to 31, thereby recognizable,
that the axial and radial tensions of the elements, pipes, housings, rings etc., as well as the fluid-filled chambers and line volumes when the relevant parts or fluids relax via the follower piston, the fluid column in the center channel and the master piston as a hydraulic motor on the Acting piston drive, driving the shaft of the drive, are switched on in the unit. 33.) Arrangement according to embodiment 1, or an assembly with a pump chamber arranged in a housing, which is arranged between a cover and an element (spring, membrane) which is flexible in the axial direction and with a device for periodically changing the volume of the pump chamber, according to the Main patent,
characterized,
that the element is assigned a floor support (7,8.101) and a head rest (7.8.100), the distance from each other of which is smaller than the axial deflectability of the element, between the element (7.8-61) and the floor support a first pumping chamber (7.8 .35), a second pumping chamber (7.8.37) are formed between the element and the head system, the first chamber is assigned a pumping device (7.8.52) for periodic filling and filling and the second pumping chamber has inlet and outlet means for Example valves (38,39) are assigned. 34.) Unit according to version 33,
recognizable by
that the element is clamped between the cover (1) and an attached bracket (insert, body) (91). 35.) Unit according to version 34,
recognizable by
that the floor covering is a flat surface on which the element rests in the untensioned state and the head rest is bulged inwards, for example, forming a flat hollow cone. (Figures and 2) 36.) Unit according to version 34,
recognizable by
that the clamped forms the fastening of the element and the inner diameter of the fastening forms the outer diameter of the pump chambers (35, 37). 37.) Unit according to version 36,
recognizable by
that the first pump chamber (35) is assigned a reciprocating piston (52) which is small in diameter but has a long stroke in comparison to the pump chambers (35, 37). 38.) Unit according to version 37,
recognizable by
that the reciprocating piston (52) rests on a pressure piston (124) and is driven by it, the pressure piston having a larger diameter than the reciprocating piston and the pressure piston arranged in a cylinder being designed to be operated by a pump piston of smaller diameter via an intermediate pressure fluid. 39.) Unit according to version 34,
recognizable by
that the element is a thin round disc that forms waves radially towards the center, increasing in its axial depth in both axial directions (261, 461) between oblique or almost axially directed intermediate pieces (361) and thus as an axial direction with a particularly long stroke deformable, resilient element forming ring element (61) is arranged. 40.) unit after execution 39,
recognizable by
that the floor support (111, figure) forms a waveform support adapted to the wave shape of the element (61, figure), which is designed to avoid the space in the untensioned state of the element. 41.) unit according to version 40, thereby recognizable,
that one of the wave crests of the floor support is assigned a vent hole (120) going through the floor (insert 91, figure). 42.) Unit according to version 39,
recognizable by
that the head system (110, figure) forms a wave system (312) adapted to the wave shape of the element (61, figure), the distance of the shaft system (312) in the axial direction from the element from the outside diameter of the pumping chambers (35, 37) and is thus increasingly arranged from the inside diameter of the fastening radially inwards. 43.) Unit according to version 42,
recognizable by
that the outlet valve (39) is arranged radially in the middle and thus at the deepest shaft point of the Kopaf system and the axes of the element and the pumping chambers are aligned vertically with the head system upwards, so that the outlet valve forms an automatic ventilation and the mentioned head system Stroke of said element is arranged limiting. 44.) Unit according to version 37,
recognizable by
that said reciprocating piston (52) is arranged in a reciprocating manner in a cylinder (35) communicating with said first pumping chamber (35), the first pumping chamber and said cylinder are filled with fluid and a fluid filling hole (121) is fed to the cylinder, which through the reciprocating piston in its dead center position, in which said element (61) assumes its untensioned state, opens and the chamber-cylinder unit (35) can be filled with fluid through a pressurized fluid delivery unit, as long as said reciprocating piston in said external dead center position Keep hole open. 45.) unit according to at least one of the versions,
and thereby recognizable,
that the element consists of at least two conical ring parts, which are arranged symmetrically to one another and a part of said second pumping chamber is formed, and said floor support and head rest can be omitted, because said second pumping chamber is partly formed within said element. 46.) unit according to version 45,
and thereby recognizable,
that said element (210) is clamped with its flange (284) between the head cover (201) and the housing (222) in a sealing manner and forms a bottom (218, 217, 221), so that the element (210, 250 to 254, 260 to 272, 421 to 427, etc. ) and the bottom (440,256,218, etc.) the separation of the first pumping chamber (213) from. form the second pumping chamber (212). (7.8. Figure) 47.) unit according to version 46,
and thereby recognizable,
that the bottom (eg 440) of the element (eg 210,510,610,280, 261,284) is arranged a pulling arrangement through which the element is pulled into its untensioned state, the pulling device consisting of a bolt (441). may exist with piston (443) in a cylinder (444) and the space surrounding the bolt in the cylinder can be acted upon by means of pressure oil in order to pull the piston and thus the bolt over the bottom of the element into the untensioned state of the element. 48.) unit according to version 47,
and thereby recognizable,
that the pulling arrangement is used to ingest fluid through the inlet valve (eg 202, 204) into said second pumping chamber (212) due to the expansion of the element. 49.) Unit after execution 45.
and thereby recognizable,
that the element (210, 250 etc., e.g. according to FIGS. 6 and 13) consists of several symmetrical conical ring parts (260, 266) which are connected to each other by means of inner and outer parts (263, 270) or by means of inner and outer ring arches (280, 281) Parts of the second pump chamber (212) are formed between ring parts (266, 260) of a conical ring part pair that are arranged symmetrically inward. 50.) unit according to version 49,
and thereby recognizable,
that the element is made of fiber-reinforced plastic, for example according to FIG. 7, and the parts or ring arches mentioned are replaced by flat, bonded (bonded) inner or outer plan surfaces on the conical ring parts (251, 252), so that the plane connections (253, 254) match the respective one Form connection of adjacent conical ring parts (251,252). 5 /.) Unit according to versions 49 or 50,
and thereby recognizable,
that the interior of the element is provided with a filling block (216) which fills the interior in the tensioned state of the element. 52.) unit according to version 51,
and thereby recognizable,
that the filler block is provided with one of the first pumping chambers to open space (220) (FIG. 5) into which a pumping piston (227) for conveying fluid into the first pumping chamber can temporarily and at least partially enter in order to shorten the unit. 53.) Unit after execution 45 ,.
and thereby recognizable,
that the first pumping chamber is assigned a pumping piston (227, FIG. 5), that of its small diameter and its stroke length because at its outer end in a cylinder (224) has an end piston (226) and in the middle between the bottom of the cylinder (224) and the end piston (226) has a guide ring (226) which is displaceable on the piston (227) and which is held in the respective center by means of springs (225) on both ends of the ring (226), while the reciprocating piston (227) runs sealingly in a cylinder of the same diameter in the housing (222) and the reciprocating piston (227) with a drive (e.g. '226,230,231,232 ) for its piston stroke or with a piston stroke guide. 54.) unit recognizable according to versions 33 or 45 or at least one version,
that said first pumping comb (35, 213) is assigned a reciprocating piston (227, 52) arranged in a pressure cylinder (35, 213), to which pressure fluid is periodically supplied and discharged through a feed bore (223, 121), said bore (121, 223) being at that Place in said cylinder at which the inner end of said piston reaches its outer end position so that said cylinder and said pump chamber are completely filled with fluid in this position of the piston and. the fluid pressure stroke begins after the short stroke of said piston, after the passage of which said bore is closed by said piston. 55.) unit according to version 45, or one of the versions, and thereby recognizable,
that the spaces between the adjacent conical ring parts (510, 610) are provided with filler material in order to avoid dead space, the filler material being, for example, aluminum or lead if the element (210 etc.) is made of steel or the like, or that the filler material is in the element is poured in and after heating to the kneading temperature of the filler, the element is pressed to the maximum stroke, the then kneadable excess filler being squeezed out, so that after the element (210) has been relaxed, pump chamber parts (537,637) between the filler (214) and the neighboring ones conical ring parts (510, 610) are formed, and / or there are spaces between the ring parts mentioned and the outer filler parts (215). 56.) unit according to version 45 or one of the versions and thereby recognizable,
that the element (210, etc.) is formed from disc springs (260, 266) provided with radially planar inner and outer ends, spacer rings (263.270) being arranged between the radially planar surfaces and being radially inward and radially outward of sealing rings (268, 264, 269,271) are surrounded, whereby one of the sealing rings radially surrounds the spacer ring and the ends of two plate springs and the plate springs are gripped and held together by cleat rings (265, 272). (Figure) 57.) aggregate after executions, 33,45 or one execution and thereby recognizable,
that the element (301, FIG. 10) is provided with a sealing ring carrier (381), the sealing lip (380) of which lies sealingly on the inner surface (379) of the element, and a plastic sealing ring (387) is arranged axially within the sealing lip in an annular groove of the sealing ring carrier and the sealing ring rests against the axially inner end of the inner surface of the element, the sealing lip and the sealing ring are short in the axial direction compared to the element and / or axially outside the sealing lip there is a recess (377) in the sealing ring carrier and / or a conical widening (378) are formed in the element to prevent crushing between the element and the seal carrier in the axial tension of the element. avoid and the sealing ring carrier is designed as a cylindrical part (3B1), the interior of which is provided with a filling block (383) leaving a gap (382), the axial length of the sealing ring carrier 381 being dimensioned such that its radial expansion under internal pressure in the gap 382 Follow the sealing lip for radially widening the inner surface (379) of the _' element during its tensioning and maintains the sealing effect and the contact between the sealing lip and the element at all times during the working movement of the element. 58.) unit according to version 33 or one of the versions and thereby recognizable,
that the element or elements (327,328) and its assignments (393,329,359,360,302 etc.) is assigned a reciprocating piston (Figure 9) which is designed as a differential piston in a differential cylinder with a piston rod (357) on the reciprocating piston (354), piston and piston rod are arranged so as to be axially movable in a sealing manner in cylinder parts, the annular space (356) around the piston rod (357) is relieved of pressure by means of a bore (358) and the cylinder (352) by means of a bore or fluid line (351) to the interior (350) in the housing (306) of the unit is connected so that the difference in the diameter of the piston and the piston rod determines the difference in pressure in the cylinder and the second pumping chamber (37) inside or above the element, so that the elements between the pressure differences in the first pumping chamber (352,350 ) and the second pumping chamber (37), the pressure in the second pumping chamber being able to be increased substantially above the pressure in the second pressure chamber of the Maxiaml would be permissible pressure if the space surrounding the elements were filled with atmospheric pressure, so that, for example, the pressure in the second pumping chamber is twice the pressure in the first pumping chamber and thus the pressure in the second pumping chamber is convenient and simple Can be increased to approximately twice the relevant pressure in European Patent Application 064 563 without changing the dimensions of the elements. 59.) unit according to version 33 or one of the versions and thereby recognizable,
that the cleat rings (327, 328, FIG. 6) have ring grooves (329) which form radially resilient holding parts (332) on the cleat rings for holding the elements of the pair of elements (301, 302) together. 60.) unit according to version 45 or one of the versions and thereby recognizable,
that the elements (401, FIG. 11) of a pair of elements are provided with radially flat surfaces on the axial inner walls near the radially inner end, the elements are centered on one another by the centering rings (403) and are arranged radially inside the elements sealing lip carrier (409), the sealing lip supports form sealing lips (416) with radial flat surfaces and the radial flat surfaces (415) of the sealing lips and the radial flat surfaces (416) of the elements (401) form the sealing support (408), two adjacent elements each being arranged by an arrangement (410,412,413,411) are axially coupled to one another and spacer rings (405) can be arranged between the elements, 6 /.) Unit according to version 45 or one of the versions, and thereby recognizable,
that a U-element is made of a connecting bend (423) with two radially inwardly tapered conical ring parts (421; 422) and axial end stops (424,425) made of steel or similar material and in the space between the conical ring parts (421,422) fillers ( 427) are arranged, between which and the conical ring parts pump chamber parts (426) are formed, wherein the filler can be aluminum, lead or the like and the fabrication of the element with the filler and the pump chamber parts can be produced according to the method of one of the claims. 62.) Unit according to version 33.45 or one of the versions, and thereby recognizable,
that an arrangement is designed according to a part of one of the figures or a part of the description, or that in the interior (350) of the housing surrounding the elements and / or cleat rings, (for example, 306) spaces are arranged between parts filling, reducing dead space reducing fillings (362) . 63,) Arrangement according to embodiment 1, or, unit with a fluid-containing working chamber arranged in a housing, the volume of which can be changed periodically and is provided with inlet and outlet valves and which has a first pumping chamber (working chamber) with an associated one , the shape or position of the first pump chamber of periodically changing pistons is assigned via a fluid separating surface, membrane, conical ring element, according to the main patent, characterized in that
that the first pump chamber (35) is separated from the second pump chamber (37) provided with the valves (38, 39) by a conical ring element (501) and the said ring element (501) with a bearing lug delimited by an inner diameter and an outer diameter ( 502) is provided, which can hold a sealing ring (516, 517) radially inside and radially outside of the nose and which separates the first and second chambers from one another in such a way that a cross section (520) of such a size is formed between the mentioned diameters (518, 519) that said nose (502) forms a seal with an adjacent surface of an adjacent part (1,501) under internal and external pressure on said element (501). 64.) unit according to version 63,
and thereby recognizable,
that the nose (502) delimits a sealing ring seat (503) radially outwards and delimits a sealing ring seat (504) radially inwards, the sealing ring seats being formed by radial flat surfaces which extend radially from the root of the nose. 65.) unit according to version 63,
and thereby recognizable,
that the element (501) forms an inner nose (508) with an inner diameter (521) and an outer diameter (522) on the radially inner and axially backward part of the element, the difference between the diameters forms a cross-sectional area (523) and from the root of the nose The radial inner and outer sealing seats (509 and 507) are formed from extended radial flat surfaces. 66) unit according to version 65,
and thereby recognizable,
that two of the elements (501) are aligned axially, but axially opposite, with their outer lugs (502) in (509) placed symmetrically on one another, form a pair of elements. 67) unit according to specification 66,
and thereby recognizable,
that a chamber part (537) is formed within the elements of the pair of elements. 68,) unit according to version 67,
and thereby recognizable,
that several of the element pairs, with their inner lugs (508) om (511) placed one on top of the other, form an element lifting column (526). 69.) Unit according to versions 66.69 or 68,
and thereby recognizable,
that adjacent sealing seats of two adjacent elements (501) form common sealing seats (503,504,507,509) for receiving a common sealing ring (524,525). 70,) unit according to versions 66,67,68 or 69,
and thereby recognizable,
that the relevant element (501) rests at one axial end with its nose (502) on a part (eg 1) containing the valves (38, 39) and the relevant element has an axial closure at the other axial end. (505,514) forms or carries. 7 /,) Unit according to versions 63 or one of the versions
and thereby recognizable,
that a one-piece "V element" (527) is formed, that a radially inner piece (529) replaces the inner lugs (508) of two adjacent elements (501) united in (511) and symmetrically arranged in radially conically extending ones conical ring elements (501) passes over, which form axially oppositely directed lugs (502) on their outer pieces with sealing seats (503, 504) extending from their roots. 72.) unit according to version 71,
and thereby recognizable,
that several of the U - elements (527) are placed axially coaxially behind one another, form a V - element lifting column (533). 73.) unit according to versions 71 or 72,
and thereby recognizable,
that the annular groove (528) formed radially outside of the center piece (529) between the element parts (501) of the V-element (527) is at least partially filled by means of a radially divided filler ring (530) for the purpose of reducing dead space. 74.) unit according to version 63 or at least one of the versions and thereby identifiable,
in that in the axial intermediate spaces between adjacent elements (501) or elements (501) adjacent, inner and / or outer rings (531, 5322) are assigned as filler rings which reduce dead space. 75.) unit according to version 63 or one of the versions and thereby recognizable,
that a housing (91) contains a bore (534) into which an element column (526, 533) is inserted and the inside diameter of said bore is only slightly larger than the outside diameter of the elements of the lifting column, around a first chamber (35) around the lifting column with the smallest possible volume for the purpose of reducing dead space in order to form the mentioned lifting column (526,533). 76.) unit according to version 63 or one of the versions and thereby recognizable,
that a plate (a ring) (91) forms a plurality of axially parallel bores (534) radially at equal angles around the axis (545) of the plate (91) with the same radii, so that the plate forms a plurality of first chambers (35) into which Elementensaeulen (526.533) are inserted, said plate (91), a head cover (1) to each of the holes individually Leading indviduelle inlet and outlet _- valves associated (38,39), to the head cover, the respective elements (501) with noses (502) and the valve channels radially inside the lugs (502) in the second chamber (37) within the elements (501) respectively. of the element pairs or the element columns (526, 533) must terminate, the element in question at the end facing away from the head cover forms a closure (505, 514) of the said second chamber (37) and the other axial end of the plate (91) has at least part of the drive arrangement for changing the first working chamber (s) (35). Drive housing (536) is assigned, wherein the three parts (1.91 and 533) are connected to one another by screws (539) or other means and are held together if the parts (1.91, 533) are not wholly or partly designed as one-piece arrangements . 77.) unit according to versions 63, 75, 76 or another of the executions and thereby recognizable,
that said first chamber (s) (35) is connected to form a cylinder in comparison to the diameter of the first chamber of small diameter and a master piston (535) is reciprocated in this cylinder. 78.) unit according to version 77,
and thereby recognizable,
that the master piston (535) periodically presses and receives fluid into the first chamber (35) so that the change in the volume of the first chamber with the volume of the cylinder (538) forces the second chamber (537) within the elements to parallel their volume to change the volume change of the first chamber with the cylinder and so periodically ingest fluid through the inlet valve and dispense it through the outlet valve. 79.) AggrEgat after execution 78,
and thereby recognizable,
that a plurality of first and second chambers are arranged in the plate (91), the master piston (535) of the first chambers is assigned a common piston drive (7.8. 510 ms 544) and the inlet valves and / or the outlet valves (38, 39) Form common lines or connections. 80,) unit according to version 63 or one of the versions

and thereby recognizable,
that the outer chamber 35 is assigned a master piston (535), which releases a pressure fluid filler mouth of a pressure fluid supply line (544, 566) near its outer dead center position, so that the outer chamber 35 is completely filled with pressure fluid during operation and does not lack fluid filling. 81,) unit according to version 60,
and thereby recognizable,
that the outer chamber (35) is assigned a ventilation line (550) with an openable closure (551). 82.) Unit according to version 63 or one of the versions
and thereby recognizable,
that several master pistons (535,635,735) are assigned to the outer chamber and act together to give them fluid. 83,) Unit according to version 63 or one of the versions
and thereby recognizable,
that a one-piece element column (582) is conical with outer and inner spaces around the conical ring element parts rising like a thread in the axial direction. 84.) Unit according to version 63 or one of the versions
and thereby recognizable, class
a master piston (535) directly into an outer chamber (35). is arranged. 85.) unit according to version 63 or one of the versions and thereby recognizable,
that a pulling piston (575) is assigned to a separating piston (572) and with a piston rod end (578) into one with the outer chamber. connected additional chamber (579) is arranged immersed. 86.) unit according to version 63 or one of the versions and thereby recognizable,
that a control groove (566) controlling an outer chamber (35) is arranged in a lifting surface of an eccentric lifting disc (565). 87.) Unit according to version 63 or one of the versions
and thereby recognizable,
that a type of execution, a part, an omission, a correction, an improvement or a calculation is arranged or evaluated, which was shown or described in the description or the figures. 88.) Arrangement according to embodiment 1 or an assembly through which fluid flows for pressures up to several thousand bars, also for non-lubricating fluid and with conical ring parts, axially resilient embodiment for forming the delivery chamber for the fluid to be conveyed, thereby recognizable,
that means for increasing the efficiency or for increasing the operational safety are arranged. 89.) unit according to version 88,
and thereby recognizable,
that a means (7.8.616.617.613.654 use) for closing periodically open and closing conical gaps is arranged. 90.) unit according to version 88,
and thereby recognizable,
that a plate spring is machined flat on both axial ends and contains a recess for a sealing ring at one radial end. 91.) unit according to version 90,
and thereby recognizable,
that the sealing ring recess (718, 503) has a rectangular cross section with walls (931) perpendicular and parallel to the adjacent support face (831). 92.) unit according to version 88,
and thereby recognizable,
that an outer chamber (35) surrounds the inner chamber (37) forming elements (1,527,830 USW.), whose radius is small compared to the wall thickness of the housing (91). 93.) Unit according to at least one of the versions
or recognizable by it,
that means for increasing performance, operational safety or efficiency are arranged in combination with other features or in combination with known means from the prior art. 94.) unit according to version 93,
and thereby recognizable,
that a set of conical ring / parts (1,527,830) is arranged adjacent to one another between a housing (91) and an upper and lower closure (1001, 91), said set separating an outer chamber (35) and an inner chamber (37) from one another . 95.) unit according to version 93,
and thereby recognizable,
that the inner chamber (37) inlet and outlet means (38,39) are assigned and the outer chamber is assigned a reciprocating piston (51,535 etc.) which periodically compresses and expands the fluid in the outer chamber. 96.) unit according to version 95,
and thereby recognizable,
that the reciprocating piston is assigned a driving piston (619, etc.) of larger diameter, which runs in a cylinder (663, etc.) of larger diameter. 97.) unit according to version 93,
and thereby recognizable.
that the elements (1,501, 527, 830, etc.) are provided with radially limited contact surfaces, which form a diameter difference between the adjacent parts of the inner chamber (37) and the outer chamber (35). 98.) unit according to version 93,
and thereby recognizable,
that a metallic or solid support ring (eg 616 or 617) is inserted in the sealing ring seat (eg 613 of FIGS. 9, etc.) and a plastic sealing ring (ZB687, 691) is arranged radially therefrom. 99.) unit according to version 98,
and thereby recognizable,
that the support ring (616, 617) is designed with a cylindrical inner surface or with an inner surface with the radius "R" around the root of the conical gap (612). 100.) unit according to claim 98,
and thereby recognizable,
that the support ring is formed with an outer surface with the radius "r" around its inner center. 101.) unit according to version 93,
and thereby recognizable,
that a long-stroke drive (619,622,623,624,625, 629,628,630,631 and 634) of FIG. 13 is arranged in the unit together with at least one further feature of the invention. 102.) unit according to version 93,
and thereby recognizable,
that a piston (15,639) is periodically immersed in a cylinder filled with Del and water (according to FIG. 14 or 15), the cylinder is assigned an inlet and an outlet valve (38,39) and the cylinder (16,638) in comparison to the piston mentioned has a slightly larger diameter and the amount of oil in the cylinder is such a minimum that the piston remains wetted by the oil at all times. 103.) unit according to version 93,
and thereby recognizable,
that a W-element (642) of FIG. 16 is arranged with a center piece (2,646,649) between two end parts (643,644) of a conical ring shape. 104.) Unit according to version 103,
and thereby recognizable,
that at the end parts (643,644) cylindrical ring lugs (13) are arranged axially projecting. 105.) Unit after execution 100,104, erc.
and thereby recognizable,
that two adjacent ones of the W elements are clamped together by cleat rings (27, 28), the cleat rings being arranged partially engaging in the W elements. 106.) unit according to version 105,
and thereby recognizable,
that several such W elements screwed together are arranged and the upper one of the W elements is attached to a head cover (1001) and the lower one of the W elements is attached to a reciprocating piston (652). (Figure 67). 107.) unit according to version 93,
and thereby recognizable,
that the boundary between the inner chamber (37) and the outer chamber (35), for example the elements (1,501,527,830,642), is assigned a retraction device (eg 655,656,657,658). 108.) unit according to version 107,
and thereby recognizable,
that the pull rod (662) is arranged sealed by inner bores (692, 106) of a reciprocating piston (52), a driving piston (649) or another means and / or spring means (669) or fluid pressure is arranged to act on the return piston (668) . (Figures 67, 68, 73, 92). 109.) unit according to version 93,
and thereby recognizable,
that the inner chamber. (37) a floor closure (501), possibly in association with at least one other means of the invention, and / or the floor closure with a thread (671) that is open to the center of the inner chamber and / or a sealing ring (681) for sealing a pull rod (662) is arranged. 110) unit according to version 93,
and thereby recognizable,
that V-elements (527) with ring lugs (502) lie against each other, which are sealed radially inwards and outwards by sealing ring means (503, 512) and the outer edges of the elements are arranged axially encompassing cleat rings (682). 111) unit according to version 93,
and recognizable by the fact that
a retraction device (1003, 672, 673) is arranged radially offset from installed reciprocating pistons (535 or 735, etc.) (Fig. 69). 112.) unit according to version 93,
and recognizable by the fact that
a solid, for example metallic, support ring (686,690) inserted into a sealing groove, is arranged in the axial direction and in one of the two radial directions surrounded by a plastic sealing ring (687, 688,689,691,692,693) (Fig. 70, 71 etc.) 113.) unit according to version 93,
and thereby recognizable,
that an inlet (709) for supplying pressurized fluid to the outer chamber (35) is formed and a non-return valve (706) for preventing the outflow of fluid from the outer chamber is arranged in the inlet line near the outer chamber (FIG. 72). 115.) 'unit according to version 93,
and recognizable by the fact that
the outer chamber (35) preferably has an automatic outlet valve (1006,696,699,1012,704,703,7D0,701, 702,703,704) at its upper end and empties the outer chamber of excess fluid and appropriate air and closes itself at the stroke pressure in the outer chamber is arranged. (Figure 72) 116.) unit according to version 93,
and recognizable by the fact that
a V-element (527) is arranged at one end with a flat surface and at the other end with an annular surface (719, 720, 721, 722) which is curved outwards. (Figures 74 and 75). 117.) unit according to version 93,
and thereby recognizable,
that an element with a ring formed with a radius around a circle axially outside the element (724, 725) -. groove (726) is provided and between two adjacent such elements a round ring (727), in particular a metallic version, is placed in the two ring grooves. Fig. 76) 118.) Unit after execution 93
and recognizable by the fact that
an automatically acting differential pressure valve (728 to -736, 938 to 946 or a correspondingly acting other design), for example according to FIGS. 28 or 47, is assigned to the inner chamber (37) and the outer chamber (35) and is designed so that it is a small one Pressure difference of, for example, only a few bars between the inner chamber and the outer chamber with the pressure in the inner chamber being lower than the pressure in the outer chamber at all pressure ranges which occur in the chambers, is maintained. 119.) Unit according to version 93,
and thereby recognizable,
that in a sealing ring recess of an element with approximately 45 degrees beveled, preferably metallic, support ring (653.760 etc.) with the beveling a plastic sealing ring (761.654 etc.), with one of its surfaces the neighboring element (e.g. 502.527 etc.) and with the first face is in contact with the end face of an adjacent part (for example head cover 1001, reciprocating piston 652 or the like). (Figures 79, 67, 89, 90, etc.) 120.) unit according to version 93,
and thereby recognizable,
that an approximately uniformly thick element (765) is formed and placed with an arc (766) around a round ring (763), the radial outer parts forming plate portions (768), two adjacent identical elements. are arranged symmetrically axially to each other around the round ring (763) and are arranged in contact with the radii surface parts 769 of the round ring and the plate portions 768 in the surface 770. (Figures and 81). 121) unit according to version 93,
and recognizable by the fact that
between the elements (777) spaces (779 and / or 782) are formed, the radii - ring grooves formed in the elements touching the circular ring (727) in the surfaces (780, 781) radially in places inside and outside, forming the difference in distance "Delta B" are arranged. (Figure 82). / 2 _2. ) Unit according to version 93,
and thereby recognizable,
that two adjacent elements (501, 527) are tapered radially on the outside and athsially on the outside to form the holder (783), the axial ends (785) of an encompassing ring (784) encompassing the elements in places axially and also radially encompassing the holders and entering the tapering, and / or this arrangement is arranged to prevent the projecting ring parts from projecting axially over the elements (eg FIGS. 82, 83 etc.) 123.) Unit after execution 93
and thereby recognizable,
that fiber plastic material (for example carbon fiber) layers form an element laid around a round ring or semicircular ring (801) in that the fiber layers are arranged one above the other but with the ends offset radially to one another. (Figure 84) 124.) unit according to version 93,
and thereby recognizable,
that the space (820 etc.) between the outer diameter of the element and the inner diameter of the housing (91) is very narrow (for example a few tenths of a millimeter wide) and axial fluid flow grooves (822) of narrow cross-section are arranged in the housing. (Figures 85, 86, etc.) 125.) unit according to version 93,
and thereby recognizable,
that rectangular or square rings (832,849) are inserted between axially plane-ground disc springs and radially arranged, support rings touching the flat surfaces (831,850) of the elements and part of the surfaces of the ring with these contacting plastic sealing rings. (Figs. 87 to 89) 126.) unit according to version 125,
and thereby recognizable,
that the support ring is formed with one or more conical surfaces (841, 840). (Figure 88 etc.) 127) unit according to version 93,
and thereby recognizable,
that about the element (830), the plate spring, (830) a fluid provided with the same shaped conical ring part, not destructible second element (842,847) is placed. (Figures 89.90). 128.) Unit after execution 127.
and thereby recognizable,
that the second element ends radially in front of the intermediate ring (832) and is there in contact with a support ring (eg according to FIG. 69) and with an inserted plastic sealing ring. (Figure 9 ₀ ) 123) unit according to version 127,
and thereby recognizable,
that the second elements (846,847) between two adjacent elements (830) are extended and limited radially to the extent that they are provided with plan ends, that the plan ends form the support and the sealing seat, support rings (690,833,834) are used in contact, a plastic sealing ring touches the support rings and or Umgreif sealing arrangement, (848-854), for example, arranged according to FIG 9 ₀ / radial inside of two elements. 130.) unit according to version 93,
and thereby recognizable,
that with flat ground disc springs with axially final flat surfaces (831,850) the elements are used. In principle, cylindrical end surfaces are provided, the diameter of which is precisely arranged to contact the filling rings (864,865) used, or the diameters mentioned (869,870, 871,872), as far as they are adjacent, either just touch one another when the elements (830) are compressed, or between they are arranged in very narrow spaces (preferably a few tenths or hundredths of a millimeter). (Fig. 91) 131.) unit according to version 93,
and thereby recognizable,
that the elements are formed from radially nested rings (882 to 887), which are axially displaceable relative to one another and are provided with axial movement limiters (889,890,893,897 etc.) and / or double guides and limits (894,890,899, etc.) and / or Seals (895) and / or fastenings (880,881,657) are formed on end parts of the outer chamber (35) and the elements form the inner chamber (37) provided radially on the inside with the inlet and outlet valves (38, 39). (Fig. 92) 132.) unit according to version 131,
and thereby recognizable
that a retraction device (902, 656, 657 or the like) is arranged in association with the elements (1882, 882. to 887) or a part of these elements. (Figure 92.) 132) Unit according to version 93
and thereby recognizable,
that the element (830) with the flat surfaces (850, 831) is formed parallel to one another and the sealing ring seat (503), for example according to FIG. 93, is arranged on the element. 133.) unit according to version 93,
and thereby recognizable,
that recesses (926 or 928 or both) are formed in the element (947) for the purpose of forming attack heights (927,929) and are arranged axially of the support surface parts (531,850) on the opposite side at the same radial height. (Figures 94.95) 134.) unit according to version 133,
and thereby recognizable,
that in the case of elements (947) placed axially next to one another, encompassing rings (936,937) with their axial encircling parts are arranged so as to touch (in 934,935), for example, according to FIG. / 35) unit according to version 93,
and thereby recognizable.
that in the case of an axial piston unit (booster according to the figure) the return line (922) is connected to the feed line to the pump (921) and a check valve (919) preventing any outflow from these lines is arranged between the connection of the lines mentioned and the fluid tank, to conduct the tension energy of the compressed fluid of one of the chambers (604) into the pump, in order to exert an effect in it of a hydraulic motor driving the rotor of the pump, until the compressed return fluid is relaxed and / or this or a similar arrangement has been made, in order to increase the efficiency of axial boosters by using the compressed fluid. 136) unit according to version 93,
and thereby recognizable,
that a swashplate arrangement (904 to 910) with a turn prevention (914 to 917) is arranged for example according to Figure 98. 137.) unit according to version 93,
and thereby recognizable,
that a means, which is shown in the figures or described in the text of this patent application, is arranged. 138.) Arrangement, for example according to one of the designs
recognizable by
that the oil volume is limited to a fraction of the displacement volume of the piston 15, that if a separating block is arranged between the water and the del, the material of the separating piston is limited to approximately three times the specific weight of the water in its specific weight,
that the valves 38, 39 have conical seats of oppositely directed cones relative to the axis of the piston 15 and their end faces are in the closed state in the bottom plane of the cylinder 11;
that the heavier liquid lies vertically below the lighter liquid and fluid in the lines between the piston 15 and the valves 38, 39, which causes bends, bevels or acceleration losses, is avoided,
and the thickness of the housing 11 thickens than the diameter of the piston 11;
it is furthermore desired that the lines 709 and 795, for example in FIG. 72, with the valve means assigned to these lines are arranged precisely at the lower level of the oil in the uncompressed state. 139.) Unit according to one of the versions and thereby recognizable that the conical gaps between elements open in the direction of the outer chamber, but against the inner chamber 37 a support for limiting the radial dimension of the inner chamber with the radial difference distance "Delta A" from the end of the conical in question Gap forms and the radially ground axially outer surfaces of the radially inner ends of the plate springs elements touch an adjacent radially flat surface (a ring, a wall), so that when compressing the plate spring (the element) there is a contact line "B" for radial limitation the outer chamber exists and the conical gaps that open in the process between the element and the adjacent plane surface of the inner chamber are opened;
and / or thereby recognizable,
that the conical gaps are covered by support rings (preferably metallic support rings) and sealed with plastic sealing rings on the other side of the support rings,
and or
a body (tube) with sealing ring grooves and plastic sealing rings are arranged radially within the inner diameter of the elements. 140) Unit according to one of the designs and
recognizable by
that the inner chamber becomes the outer chamber and the outer chamber becomes the inner chamber relative to the radial diameter limits, the support rings, the sealing rings when the inlet and outlet valves of the outer chamber are connected. 141.) Unit according to one of the versions
and thereby recognizable,
that the volume of the outer chamber in the uncompressed state is smaller than that of the inner chamber.

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