EP0617201B1 - Filling, fluid-transporting and pumping device - Google Patents

Abstract

The pump has, in a bearing and sealing housing (21), an inlet space (28) and a driveshaft (23) which drives the rotor (55) and the two eccentric guide discs (40.2) connected to it. Slide rings (45.1, 45.2) are mounted in annular grooves in said eccentric guide discs. Said slide rings bear the arresting slides (46.1, 46.2) which penetrate, via abutment sealing surfaces, into slide receiving spaces or are drawn out therefrom. The pump is suitable for applications requiring a high degree of hygiene, for example foodstuffs, medicaments and cosmetics, and can also deliver sensitive constituents, such as fruits or other foodstuff constituents, in a gentle manner. <IMAGE>

Description

The invention relates to a filling, fluid transport and pumping device.

There are many pumps, pumping devices, feeding and guiding devices, fluid transport devices and the like. These include vane pumps, eccentric vane pumps and gate valve pumps as well as rotary vane pumps and other pumps with eccentrically moving elements. Many pumps are designed for special applications. Many of these pumps compress the pumped medium for the purpose of transportation. In particular, when conveying food and other sensitive goods, components of the medium to be conveyed and pumped can suffer. Many pumps also cause a discontinuous or pulsating flow. Gentle conveyance is particularly important for sensitive goods. With many pumps, such as. B. gear pumps or the like., Residual quantities remain in partial areas of the transport elements when the seal occurs. This often results in strong impacts. The pumps must therefore run correspondingly slowly or be equipped with additional relief openings and relief channels.

The rotary piston machine with fixed abutments and vibrating piston wings according to DE 648 719 has the features b), g), h) and i). It has swinging piston wings that are mounted in the outer hollow cylinder. This solution is not comparable to gate valves.

The rotary lobe pump or the rotary lobe motor with outer rotor according to DE 37 24 077 has the features a), b), d), g) to i), 1) and m). It has roller-shaped sealing elements in the outer housing, which perform torsional vibrations around their axis and seal with an edge on the cylindrical stator. Radially moving slides that are pushed in and out according to the eccentricity are not provided. Details about the supply and discharge of the medium have not been dealt with. The same applies to the associated documents DE-OS 37 24 076 and 36 38 022.

The rotary pump according to DE-OS 15 53 083 = US 3,303,790 has the features b), c), e) and g) to i). It has a stator with rubber-elastic blades that perform tilting and oscillating movements in accordance with the elliptical rotor. Radial insertion and removal of sealing slides is not intended. Otherwise, the structure corresponds to the usual rotary pumps. However, the medium is guided radially and axially over the rotor.

The pump according to US 1,963,350 has the features b) to i) and l). It has an eccentrically rotating rotor with a smooth outer wall of cylindrical shape and partially cylindrical oscillating sealing elements in the walls of the stator, which are rotatably mounted on axially parallel axes arranged in partially cylindrical seal receiving spaces of the stator in the stator. Radially sliding sealing slides moving in and out are not provided. There are no sealing elements on the rotor attached. The medium is fed and removed axially. Arched guide surfaces inside the rotor ensure the deflection and control of the inlet and outlet. The pump medium emerging axially towards the cover is deflected in this and supplied to the outlet formed on the pump stator housing via guide openings and openings. This pump, which is technologically interesting from the basic concept, chooses sealing elements that are not suitable, in particular, for pumping media that carry sensitive components, such as beverages and foods that contain raw fruits such as strawberries. The many small rooms and corners are also difficult to clean. This is mainly due to the bearings designed with relatively small dimensions, the springs required for the sealing vibrators and the like.

The invention has for its object to propose a pump or other pumping and conveying device of the type mentioned above, which is constructed with extremely gentle pumping from easy to assemble and disassemble and also simple and inexpensive to manufacture components, which are easily available in different series few modifications of the same or different types of pumps and types of pumps allows production and assembly to be designed and used in a manner that is favorable for production.

• a) die Sperrschiebereinrichtung ist exzentrisch geführt;
• b) umlaufende Dichtbereiche in einem zylindrisch begrenzten Pumpenraum des Gehäuses und die Sperrschieberanordnung bewirken die Abdichtung zwischen Saugseite und Druckseite;
• c) es sind wenigstens zwei bewegliche Sperrschieber und die mit einem Antriebs- und Führungskörper bzw. Rotor gebildete mitlaufende Zuführ- und Abführanordnung für die axiale Zuführung von der Saugseite und die axiale Abführung zur Druckseite vorgesehen;
• d) der Rotor ist um die zentrale Pumpenachse des Hauptraumes bzw. Pumpenraumes umlaufend, bezüglich dieser Pumpenachse jedoch exzentrisch derart ausgebildet, daß er mit einer Dichtanlage bzw. Dichtungsmantelfläche an der Mantelinnenfläche bzw. Pumpraumwand des Pumpenraumes entlanglaufen kann;
• e) der Rotor weist axiale und radiale Eintritts- und Austrittsöffnungen auf, die mit Fluidführungskanälen versehen sind;
• f) die Fluidführungskanäle sind durch eine wendelförmige Trennwand voneinander getrennt;
• g) die Pumpraumwand ist von Schieberöffnungen von Schieberaufnahmeräumen unterbrochen;
• h) die Anzahl der Schieberöffnungen entspricht der Anzahl der Sperrschieber;
• i) die Schieberöffnungen sind unter etwa gleichen Winkeln um den Pumpenraum herum angeordnet und liegen bei zwei Sperrschiebern einander gegenüber;
• k) die bezüglich des Rotors drehbeweglich gelagerten Sperrschieber tauchen mit ihrem radial nach außen weisendem Teil jewells in den zugehörigen Schieberaufnahmeraum abgedichtet ein;
• l) es sind Sperrschieber-Halte- und -Führungs-Mittel vorgesehen, an denen die Sperrschieber geführt sind;
• m) die Sperrschieber-Halte- und -Führungs-Mittel laufen exzentrisch in Synchronisation mit dem Rotor um, wenn er sicht dreht, wobei dadurch Sperrschieber-Schwingungen bewirkt werden.

According to the invention, the filling, fluid transport and pump device has a housing, inlet and outlet openings, a feed and discharge device and a gate valve device and the following features, some of which are known individually from the prior art:

• a) the gate valve device is guided eccentrically;
• b) circumferential sealing areas in a cylindrically limited pump chamber of the housing and the locking slide arrangement effect the seal between the suction side and the pressure side;
• c) there are at least two movable locking slides and the in-line feed and discharge arrangement formed with a drive and guide body or rotor for the axial feed from the suction side and the axial discharge to the pressure side;
• d) the rotor is circumferential around the central pump axis of the main space or pump space, but is formed eccentrically with respect to this pump axis in such a way that it can run along the inner surface or pump chamber wall of the pump space with a sealing system or sealing surface;
• e) the rotor has axial and radial inlet and outlet openings which are provided with fluid guide channels;
• f) the fluid guide channels are separated from one another by a helical partition;
• g) the pump chamber wall is interrupted by slide openings of slide receiving spaces;
• h) the number of slide openings corresponds to the number of locking slides;
• i) the slide openings are arranged at approximately equal angles around the pump chamber and are opposite one another in the case of two locking slides;
• k) the locking slide rotatably mounted with respect to the rotor plunges with its radially outward-pointing part into the associated slide receiving space in a sealed manner;
• l) there are locking slide holding and guiding means on which the locking slides are guided;
• m) the locking slide holding and guiding means rotate eccentrically in synchronization with the rotor when it rotates, thereby causing locking slide vibrations.

The gate valve pump has great advantages with regard to the seal, because on the one hand a sealing body running around a cylinder wall results in a seal with a relatively large area and little damage to the pump medium, and on the other hand the gate valve can be sealed over a relatively large area and accordingly very well. A slide-in gate valve pump with a oscillating piston would lead to a very uneven flow and therefore cannot be used for food, pharmaceuticals and other high-quality goods. As a result of the arrangement of two locking slides and their sensible configuration in accordance with an important feature of the invention, the respective suction and pressure spaces and transport spaces located in between can be designed more cheaply and by the parallel arrangement of guide elements for the medium the various rooms can be opened and closed at suitable times in such a way that no disturbing pressure surges occur. With a suitable choice of the design details, it can even be achieved that the conveyed medium can relax between the suction and the pushing out. This is of great importance, in particular for fruits and fruit components in foods. The device excellently fulfills the requirements of the task and results in an unexpectedly quiet, pressure surge-free or at least extremely low pressure fluctuation flow even at high speeds. High pressure build-up is possible.

Such a filling, fluid transport and pumping device is expediently designed with a cylindrical main space, in or on which jointly driven eccentric guide disks circulate in the region of both ends, and wherein the eccentric guide disks have cylindrical annular guide grooves, also known as ring grooves, in which Guide rings or slide rings are rotatable, from which the locking slides protrude outward into the respective sliding receiving spaces.

Due to the elimination of gear wheels and complex shaft bearings and the use of simple turned parts with only a few milling jobs or other machining operations, the pump can be manufactured inexpensively. Housing and cohesive components of the pump can be designed so that all parts subject to abrasion wear - rotor, gate valve, pump housing - are easily interchangeable and can also be replaced from a line system without removing the pump. The pump is suitable for left-hand or right-hand flow. As a result of the narrow or small gaps between the moving parts that separate the suction and pressure chambers, the pump is able to build up a suitable vacuum for suction under conditions that occur in practice.

Pump media are not compressed in the crescent-shaped pump delivery chamber during the delivery process. Due to the system-related design of the pump inlet on rotating parts, lumpy parts of the medium are not squeezed in the dividing line between the suction part and the rotor, but are cut off sharply. This is particularly important when pumping sauerkraut and spaghetti and similar products.

In previously known pumps with eccentrically arranged rotors and spaces, which have recesses for sealing slides in the pump chamber wall, these are arranged in the housing so as to be pivotable about axes parallel to the pump axis, such as according to US-A-1,963,350 and DE-A-37 24 077. Das requires appropriate housing storage. Bearing journals and the like must be accommodated and sealed. The cleaning of such rooms is usually very difficult and residues from the last pumped goods, impurities, bacteria and the like can accumulate. In the pump according to the invention, the slide receiving spaces are completely smooth, and the slide, which is always radially or in some other way always at the same angle, is supported by large rotary rings which run in corresponding grooves. These are located in the parts assigned to the rotor and can therefore be removed for cleaning or at least better washed around. In addition, they have larger bearing surfaces, which may be better sealed and less worn, thus avoiding flaps or slides pivotally mounted on the rotor circumference. The locking slides extend radially with respect to the drive and axis of rotation of the pump, but swing in the process about a plane through the pump axis and the inlet openings of the slide receiving spaces.

There are many other eccentric pumps with sealing aids, such as. B. Peristaltic pumps and combined pumps with gate valves. These introduce the medium tangentially from the outside into the pump chamber and accordingly. Crescent-shaped pump rooms are also formed. Most such pumps can only work intermittently. Through the axial supply and discharge of the medium and the diversion over inclined surfaces and the formation of the inlet openings with control edges in the pump according to the invention, it is possible to achieve a very low-shock or practically shock-free pumping operation; especially since the two or more gate valves enable a division into several pumping spaces, the entry and exit of which can be controlled gently. In addition, it is possible to carry sensitive media components, such as, in particular, very fresh fruit, with the pump according to the invention, but not with many other pumps, especially those that appear similar.

The device or pump can be designed in a variety of important details. Above all, it can be provided that the locking slides are guided and supported, at least in the entrance area of the slider openings, with curved sealing and support surfaces corresponding to their shape or in slots of rotatable slide guide elements. Furthermore, the transitions from the pump chamber wall into the slide receiving spaces Arched contact sealing surfaces take place, in which the distance between the tips in the area of a slide opening is slightly larger than the thickness of the locking slide.

Furthermore, it can be provided that the pump chamber wall including the system sealing surfaces is formed by a pump housing made of rubber or coated with rubber. This brings advantages, not only for the running properties and the sealing, but also in terms of wear and costs, and allows inexpensive, quickly replaceable spare parts to be created.

Furthermore, with the same basic concept of the facility, diverse variations of individual design features can be used alone or with others. Accordingly, the slide guide elements can be cylinder bodies made of plain bearing material, the diameter of which is greater than the immersion depth of the ends of the locking slide and which have a supporting cross connection in the area beyond the slide movement and in which relief channels are possibly formed. The pump chamber wall, rotor and slide can be made of corrosion-resistant steel or other metal, and the slide guide elements can be made of a plastic that may be equipped with sliding aids. This is particularly important for pumps that, because of the media to be pumped, are to be made from certain steel materials, at least in most areas, and still have good sliding and running properties.

Furthermore, it can be provided that the slide receiving spaces are approximately triangular in cross section corresponding to the pivoting angle of the respective slide and / or that three locking slides are designed with associated slide receiving spaces and, if appropriate, guide and sealing elements. Above all, it can be provided that the locking slides are designed as flat disks, the curved, inner end sealing surfaces of which are designed to lie on one another with the same radius on guide surfaces of the drive and guide body working as a rotor.

Furthermore, it can advantageously be provided that a sealing strip is arranged in the inner face sealing surface of each locking slide which vibrates on the outer wall of the rotor. For this purpose, it can be provided that a sealing groove is incorporated in the metal gate valve, in which a sealing strip consisting of a plastic suitable for the material of the rotor and the medium to be pumped is arranged.

Furthermore, it can be provided that the rotor carries the eccentric guide disks and the locking slide sealing surfaces of the locking slides, which run normally to the pump axis, are displaceably and sealingly guided between the flat inwardly facing disk sealing surfaces of the eccentric guide disks.

A particularly expedient and advantageous variant of the invention provides that the locking slides are rotatably supported by means of slide rings or slide partial rings firmly connected to them, and the slide rings or slide partial rings are rotatably guided in annular grooves which are arranged in the end face of the cylindrical pump chamber eccentric guide disks rotating around the rotor, also forming wall parts, belonging to the locking slide holding and guiding means. In the first-mentioned embodiment, there are no loss spaces filled by the medium in the annular groove. In the second version, there are small loss spaces. For this purpose, the locking slides are suspended on both sides and can be better supported symmetrically even with large loads due to high pressures, so that lower bending and torsional forces occur. The sealing surfaces and friction surfaces are not subjected to an unfavorable load and a smoother pump run can be achieved. The two variants are to be selected individually depending on the intended use of the pump and the pumps are to be designed accordingly in terms of construction and assembly technology. The locking slides, which are only attached to a slide ring on one side, are easier to install. In the case of the locking slides fastened to partial rings on both sides, care must be taken that suitable dimensions are chosen for the nested mounting due to the sizes of the pumping chamber, the locking slide receiving spaces, the transition openings and the like will. In designs with slide partial rings, these should have the same inner and outer radii and the respective angular length must then be dimensioned such that it is shortened by at least the pivoting angle of the respective locking slide. Furthermore, it can be provided in all versions that the locking slides are formed or fastened on slide rings lying outside the sealing surfaces perpendicular to the pump axis.

Another advantageous variant provides that two rings of different sizes are arranged on one side of the rotor in matching ring grooves. This allows the pump to be designed more freely on the other hand, or better supports can be achieved.

Furthermore, it can be provided that the locking slide with their slide rings are designed as one-piece, identical components.

Furthermore, it can be provided that the eccentric guide disks with their outer disk sealing surfaces run in a sealed manner on large-volume O-ring seals which are inserted into the end walls of the pump chamber housing.

Furthermore, it can be provided that the fluid guide channels are formed with a rotor inlet channel and a rotor outlet channel, each of which has an inlet opening or outlet opening pointing in different directions and a pump chamber inlet opening or pump chamber outlet opening open to the outer circumference of the rotor.

Furthermore, it can be provided that the rotor in the area of its circumferential sealing surface on the pump chamber wall deviates from the outer basic shape of the rotor in such a way that it is designed with a radius equal to the radius of the pump chamber wall.

To increase the delivery head and / or other advantages, two pump units can be arranged one behind the other on the same axis such that the pump closest to the inlet contains the low-pressure part and the pump closest to the outlet contains the high-pressure part and the media guide channels in the rotors of both pumps are designed to merge. So the outlet of one pump becomes the medium pressure transition into the inlet of the high pressure pump part. The design according to the invention with the media guidance via a rotating central body with corresponding outlet and inlet openings as well as inclined surfaces and control edges is particularly suitable for this.

It can further be provided that the drive shaft is guided through an inlet space for the pump medium and the pump medium inlet is either ring-shaped or through a lateral inlet connection, while an outlet space is arranged under the vertical drive shaft of the pump.

Devices that contain all or part of the above features make it possible to design devices that are particularly easy to assemble. The pump can be designed to be self-cleaning. It then does not need to be disassembled for cleaning and still meets high hygienic requirements and allows many disassemblies to be dispensed with for cleaning purposes in most food processing plants.

The pump parameters are far more favorable than those of a rotary lobe pump because the flow is not divided and, in addition, much larger volume portions per delivery section are pushed onto the pressure side. The pump system contains a rotating eccentric hollow body with wipers or locking slides supported and sealed on the end faces, which move and rotate in a housing during the rotation of the rotating parts in accordance with the eccentric turning, pivoting and sliding movements are supported in the housing preferably on two supports offset by 180 ° for the wipers or gate valves.

Fig. 1

Einen Vertikalschnitt durch eine Pumpe mit Lager- und Dichtungsgehäuse sowie Ein- und Austrittsanschluß;

Fig. 2

eine mehrgliedrige, z. T. explosionsartige Darstellung des Zentrums und eigentlichen Pumpenbereiches mit den Elementen für Ansaugen, Weiterbefördern mit Entspannen und Ausstoßen des Pumpmediums, wobei
Fig. 2.1  ein explosionsartiges Schrägbild von Pumpengehäuse, in der Mitte Rotor mit Exzenterführungsscheibe und eingesetztem Schieberring mit Sperrschieber der Ansaugseite und vorn Exzenterführungsscheibe der Druckseite mit eingesetztem Schieberring mit Sperrschieber;
Fig. 2.2  ein Schrägbild der zusammengesteckten Elemente: Rotor, Exzenterführungsscheiben und Schieberringe mit Sperrschiebern;
Fig. 2.3  einen zur Pumpenachse normal verlaufenden Schnitt zur Verdeutlichung der Einbauverhältnisse;
Fig. 2.4  ein Ausschnitt aus Fig. 2.3 in Schnittdarstellung mit Rotor, beiden Sperrschiebern, einem hinten liegenden Schieberring und einem Anschnitt des Pumpengehäuses;

Fig. 3

ein Schrägbild der beiden Einsetzteile, welche jeweils als einstückiges Bauteil den Sperrschieber und den Schieberring in Explosionsdarstellung ihrer räumlichen Zuordnung zeigen;

Fig. 4

einen Horizontalschnitt durch das Zentrum der beiden Schieberringe mit den beiden Sperrschiebern im eingesetzten Zustand links in der Exzenterführungsscheibe und rechts in der Einheit aus Rotor und Exzenterführungsscheibe;

Fig. 5

ein Schrägbild des Rotors mit der angesetzten, zum Eintrittsraum weisenden Exzenterführungsscheibe ohne sonstige An- und Einbauteile;

Fig. 6

ein teilweise aufgebrochenes Schrägbild der eigentlichen Pumpe, bei der die Teile, denen der vorhergehenden Figuren entsprechen, jedoch die Gehäusedarstellung gegenüber der Fig. 1 teilweise mehr vereinfacht und schematisiert ist;

Fig. 7

vier gleichartige Darstellungen eines teilweise schematisierten Querschnittes durch den eigentlichen Pumpenbereich mit seinen wesentlichen Elementen in vier verschiedenen Drehstellungsphasen;

Fig. 8

eine mehrgliedrige, stark schematisierte Schrägbild-Darstellung, die die in der mehrgliedrigen Darstellung der Fig. 7 in einer Ebene dargestellten Gegebenheiten in räumlich anschaulicherer Form beim Umlauf des Rotors mit seinen Öffnungen und schrägen inneren Umlenkflächen verdeutlicht;

Fig. 8.2

eine der Zeichnung 7.2 in der Position entsprechende Schrägbild-Darstellung, bei der der Übersichtlichkeit halber die Stirnwände des Pumpraums weggelassen und nur die Umrisse vom Pumpenraum und von den Schieberaufnahmeräumen dargestellt sind;
Fig.8.2.1  eine der Fig. 8.2 entsprechende Darstellung mit den Pumpenraum und die angrenzenden Bereiche abdeckenden Wandscheibe in Schemadarstellung, wobei Rotor und Sperrschieber eine geringfügig weiter in die Positon 50° zur oberen Senkrechten gedrehte Stellung einnehmen;
Fig. 8.3  eine der Fig. 8.2 entsprechende Darstellung in der der Fig. 7.3 entsprechenden Position von Rotor und Sperrschiebern;
Fig. 8.4  eine den vorstehend genannten Schrägbild-Darstellungen entsprechende Darstellung in der Position von Rotor und Sperrschiebern gemäß Fig. 7.4;

Fig. 9

eine mehrgliedrige Schrägbild-Darstellung einer ersten Variante mit zwei Sperrschiebern, die an auf der gleichen Seiten der beiden Sperrschieber liegenden, ineinander steckbaren Schieberringen angebracht sind, wobei weitere Pumpenteile nicht dargestellt sind; hier zeigen die
Fig. 9.1  eine Explosionsdarstellung und die
Fig. 9.2  ein Schrägbild in der Montageanordnung;

Fig. 10

eine mehrgliedrige Schrägbild-Darstellung einer weiteren Variante von wichtigen Pumpenteilen, wobei die Sperrschieber an Schieber-Teilringen befestigt sind und diese auf beiden Seiten jedes Sperrschiebers vorgesehen sind und so gestaltet sind, daß sie in derselben Schiebernut einer Führungsscheibe laufen können und wobei die
Fig. 10.1  eine Explosionsdarstellung der Teile, die
Fig. 10.2  eine Teildarstellung von zwei Sperrschiebern mit ihren vier Schieber-Teilringen in der Montagestellung und
Fig. 10.3  eine Schrägdarstellung, bei der die hinten liegenden Schieber-Teilringe in der Ringnut der einen Exzenterführungsscheibe angeordnet sind, während der Übersichtlichkeit halber die vordere Exzenterführungsscheibe weggelassen ist;

Fig. 11

eine schematische Schnittdarstellung durch die Pumpenteile einer weiteren Variante mit einer Andeutung eines Pumpenraumes, in dem der Rotor mit seinen zwei Sperrschiebern dargestellt ist und in den Schieberaufnahmeräumen Schieber-Führungs-Elemente dargestellt sind, in deren Schlitzen die Sperrschieber geführt sind - weitere Pumpenteile sind weggelassen;

Fig. 12

ein Schrägbild eines einzelnen Schieber-Führungs-Elementes;

Fig. 13

eine Schema-Querschnitts-Darstellung einer weiteren Variante einer Pumpe mit drei Sperrschiebern und etwa dreieckförmigen Schieberaufnahmeräumen;

Fig. 14

eine der Fig. 7.1 entsprechende Darstellung einer weiteren Variante einer Pumpe, bei der Dichtleisten in die Sperrschieber eingesetzt sind;

Fig. 15

ein Schrägbild einer einzelnen Dichtleiste;

Fig. 16

eine der Fig. 7.2 entsprechende Darstellung, bei der jedoch der Rotor nicht überall zylindrisch begrenzt, also sein Querschnitt nicht kreisrund ist, sondern im Bereich der Dichtanlage mit dem Radius der Pumpraumwand dargestellt ist, wobei in den Sperrschieber-Aufnahmeräumen der übliche Freiraum herrrscht;

Fig. 17

eine stark schematisierte Darstellung einer Anordnung, die zur weiteren Erläuterung der Pumpenvariante nach Fig.16 dient, wobei in den Schieber-Aufnahmeräumen Schieber-Führungs-Elemente dargestellt sind und der Rotor eine Dichtanlagefläche mit dem Radius der Pumpraumwand zeigt;

Fig. 18

eine Schemadarstellung einer weiteren Variante mit den wesentlichen Teilen von zwei Pumpen, die hintereinander angeordnet auf einer gemeinsamen Welle angetrieben werden können und mit Hilfe eines Verbindungsringes miteinander zusammenzubauen sind.

Embodiments of the invention are described below with reference to the drawings.
Show it:

Fig. 1

A vertical section through a pump with bearing and seal housing as well as inlet and outlet connection;

Fig. 2

a multi-unit, e.g. T. explosive representation of the center and actual pump area with the elements for suction, onward transport with relaxation and ejection of the pump medium, whereby
2.1 shows an exploded oblique view of the pump housing, in the middle rotor with eccentric guide disk and inserted slide ring with locking slide on the suction side and front eccentric guide disk on the pressure side with inserted slide ring with locking slide;
2.2 is an oblique view of the assembled elements: rotor, eccentric guide disks and slide rings with locking slides;
2.3 shows a section running normal to the pump axis to clarify the installation conditions;
2.4 shows a detail from FIG. 2.3 in a sectional view with a rotor, two locking slides, a slide ring at the rear and a cut of the pump housing;

Fig. 3

an oblique view of the two insert parts, each showing the locking slide and the slide ring in an exploded view of their spatial assignment as a one-piece component;

Fig. 4

a horizontal section through the center of the two slide rings with the two locking slides in the inserted state on the left in the eccentric guide disk and on the right in the unit consisting of rotor and eccentric guide disk;

Fig. 5

an oblique view of the rotor with the attached, facing the entrance eccentric guide plate without other attachments;

Fig. 6

a partially broken oblique view of the actual pump, in which the parts, which correspond to those of the previous figures, but the housing representation compared to Figure 1 is partially more simplified and schematic;

Fig. 7

four similar representations of a partially schematic cross section through the actual pump area with its essential elements in four different rotational position phases;

Fig. 8

a multi-part, highly schematic oblique image representation, which illustrates the conditions shown in the multi-part representation of FIG. 7 in one plane in a spatially clearer form when rotating the rotor with its openings and inclined inner deflection surfaces;

Fig. 8.2

an oblique image representation corresponding to the drawing 7.2 in the position, in which the end walls of the pump chamber have been omitted for the sake of clarity and only the outlines of the pump chamber and of the slide receiving chambers are shown;
8.2.1 shows a representation corresponding to FIG. 8.2 with the wall disk covering the pump chamber and the adjoining areas in a schematic representation, the rotor and locking slide taking up a position slightly further turned 50 ° to the upper vertical;
8.3 shows a representation corresponding to FIG. 8.2 in the position of the rotor and locking slide corresponding to FIG. 7.3;
8.4 shows a representation corresponding to the above-mentioned oblique image representations in the position of the rotor and locking slide according to FIG. 7.4;

Fig. 9

a multi-part oblique view of a first variant with two locking slides, which are attached to one another on the same side of the two locking slides, insertable slide rings, further pump parts are not shown; here they show
Fig. 9.1 is an exploded view and
9.2 an oblique image in the assembly arrangement;

Fig. 10

a multi-part oblique view of a further variant of important pump parts, the locking slide are attached to slide partial rings and these are provided on both sides of each locking slide and are designed so that they can run in the same slide groove of a guide disc and wherein the
10.1 is an exploded view of the parts that
10.2 is a partial view of two locking slides with their four slider partial rings in the assembly position and
10.3 is an oblique view in which the rear slide partial rings are arranged in the annular groove of the one eccentric guide disk, while the front eccentric guide disk is omitted for the sake of clarity;

Fig. 11

is a schematic sectional view through the pump parts of a further variant with a hint of a pump chamber in which the rotor is shown with its two locking slides and in the slide receiving spaces slide-guide elements are shown, in the slots of which the locking slides are guided - further pump parts are omitted;

Fig. 12

an oblique image of a single slide-guide element;

Fig. 13

a schematic cross-sectional representation of a further variant of a pump with three gate valves and approximately triangular slide receiving spaces;

Fig. 14

a representation corresponding to FIG. 7.1 of a further variant of a pump, in which sealing strips are inserted into the locking slide;

Fig. 15

an oblique image of a single sealing strip;

Fig. 16

a representation corresponding to FIG. 7.2, in which, however, the rotor is not cylindrically delimited everywhere, that is to say its cross section is not circular, but is shown in the area of the sealing system with the radius of the pump chamber wall, the usual free space prevailing in the locking slide receiving spaces;

Fig. 17

a highly schematic representation of an arrangement which serves to further explain the pump variant according to Figure 16, wherein slide-guide elements are shown in the slide receiving spaces and the rotor shows a sealing contact surface with the radius of the pump chamber wall;

Fig. 18

a schematic representation of a further variant with the essential parts of two pumps, which are arranged one behind the other on a common shaft and can be assembled with the help of a connecting ring.

The pump 20 according to FIG. 1 has a bearing and seal housing 21 which is equipped with holders 22.1 and 22.2. With these, it can be attached to an entire device or a support device. A drive shaft 23 has a connecting stub 24 with a spring groove 24.1 for the rotatable drive by a motor. Two roller bearings 26.1 and 26.2 support the drive shaft 23 radially and axially in the bearing and seal housing 21. An inlet connector 27 with screw thread 27.1 leads into the inlet space 28 in the bearing and seal housing 21, which is sealed with the help of the sealing rings 25 against the outside environment and is penetrated by the drive shaft 23. It belongs to the suction side. The actual pump 20.1 is arranged in the area under the entry space 28. It is described in more detail above all with reference to the other figures. Because of the complexity of the individual designs and arrangements, only outlines of individual components are shown in one plane in FIG. 1. The outlet port 29.1 is used to connect the pressure side with the delivery lines to the other facilities in the system.

The pump 20.1 has a housing cover 90 at the bottom, which is screwed onto the flange 92 of the bearing and seal housing 21 with screws 91 penetrating the pump housing 31. O-ring seals 93.1 and 93.2 are provided in associated grooves 94.1 and 94.2. The eccentric guide disks 40.1 and 40.2 run on these sealed around. The eccentric guide disks 40.1 and 40.2 are rotatably driven together with the aid of the drive shaft 23 via the toothing in the drive opening 56 and circulate in the pump housing 31 in the control part grooves 38.1 and 38.2. The pump housing 31, which can be seen more clearly from FIGS. 2.1 and 2.3 and further figures, is here made from an elastic material, such as rubber on a natural and / or synthetic basis, or from a suitable plastic with other basic materials. However, it can also be made from other suitable material, for example different steels, metals and / or alloys, if appropriately paired with the circulating parts. A nut 95 is used to hold the pump parts on the drive shaft 23 and to easily loosen and remove and reinstall and secure them.

The actual pumping area according to the exemplary embodiment of a pump 20.1 is first described on the basis of the multi-sectioned FIG. 2 in the structure and operating principle with reference to the details shown in the following figures. An assembled overall pump results from FIG. 1. From this, different variants and installation applications of the new pump can be derived.

The multi-part FIG. 2 has figures 2.1 marked with decimal digits, which serve to explain them jointly; 2.2 and 2.3. 2.3 and 3, 4 and 5 show details of the components more precisely and with more recognizable reference numerals.

The pump 20.1 is a blocking slide pump equipped with two blocking slides and an eccentric guide, in which the pumping medium to be pumped is fed and discharged in a new manner via moving guide elements. The pump 20.1 has a pump housing 31, which can also be referred to as a stator, with a cylindrical pump chamber 30 (FIG. 1; FIG. 2.1), the pump chamber wall 32 of which is designed with slide openings 33.1 and 33.2 (FIG. 2.1). As a result, there are two cylinder parts of the pump chamber wall 32 which are separated from one another by the two slide openings 33.1 and 33.2. The length 35 and the diameter 36 of the cylindrical pump chamber 30 together with further parts and structures determine the volume of the pump. The pump chamber wall 32 ends on both sides at a likewise cylindrical control part groove 38.1 and 38.2. The eccentric guide disks 40.1 and 40.2 lie in these shoulder-like control part grooves 38.1 and 38.2. They are designed as flat cylindrical disks and each have their individual, described in more detail below, because of the difficult description of such shapes clearly z. T. also from the drawings resulting multi-surface structured limited entry and exit openings openings 83.1 and 83.2; some with shaped outlet surfaces 41. On the side facing the inside of the pump, a cylindrical annular groove 44 is arranged eccentrically to the pump axis 43 for the respective slide ring 45.1 and 45.2. On each slide ring 45.1 and 45.2, the locking slide 46.1 or 46.2 projects radially to the center 47 of the control part grooves 38.1 and 38.2, projecting outwards. In this exemplary embodiment, two identical slide rings 45.1 and 45.2 designed with the same dimensions lie on both sides of the pump chamber 30 and each carry one of the two locking slides 46.1 and 46.2 working in the pump chamber 30. The center point 47 or the associated axis 47 are eccentric to the pump axis 43.

Each gate valve 46.1 or 46.2 has a length 48 which is equal to the length 35 of the pump chamber wall 32. Each locking slide has a depth 49 which is dimensioned such that it can engage sufficiently deep into the respective slide receiving space 50.1 or 50.2 through the slide opening 33.1 or 33.2. In a two-slide design - as in this exemplary embodiment - the slide receiving spaces 50.1 and 50.2 are arranged exactly diametrically opposite to the pump axis 43. The locking slide 46.1 and 46.2 are equipped with flat, rectangular locking slide sealing surfaces 51.1, 51.2, 51.3, 51.4, which form sliding sealing surfaces for eccentrically caused relative sliding movements compared to the eccentric guide disks 40.1 and 40.2.

A multi-unit profiled rotor 55 serves for the pump medium guide and the rotary drive. The rotor 55 has a drive opening 56 which is equipped with multi-spline internal teeth or can have a differently profiled configuration of the engagement opening around the central pump axis 43. The drive shaft 23 is inserted with an external spline or the like. This drive opening 56 is introduced with its axis 43 about the eccentricity 57 (FIG. 4, right) to the eccentric axis 47 into the rotor 55, which serves for the drive and the media guidance, as illustrated in particular in FIG. 2.3.

The rotor 55 is cylindrical in its basic structure and has several spatially structured openings. The parts of its outer wall 59 which slide on the neighboring parts and do not fall as a result of perforations or depressions lie on a cylindrical surface with a diameter 58 (FIG. 4). The axis of this cylinder surface is the eccentric axis 47. The guide surfaces 59.1 and 59.2 can be seen, which are lateral surfaces. The sealing system 76 separating between the suction area and the pressure area of the pump chamber is the part of the outer wall of the rotor 55 which is the most outer with respect to the pump axis 43 and runs in a circle along the pump chamber wall 32 with a small radius difference and a double wedge sealing gap. The basic structure of the rotor 55, which appears to be complicated, is shown in FIGS Drawings clearly recognizable. He has another one outer, lying on cylinder jacket surface parts with a somewhat smaller diameter, and occupying a larger angular range, serving for the positioning centering.There is a thin-walled rotating guide collar 39 between the centering surface 60 serving for the fixed positioning and the cylindrical annular groove 44.1 in the eccentric guide disk 40.1 Slider ring 45.1 executes its torsional vibrations.

This cylindrical rotor 55 is integrally formed on the eccentric guide disk 40.2 or otherwise connected to it in a rotationally and motionally fixed manner. It is inserted with the aid of dowel pins 61 and dowel pin receiving holes 62 in the eccentric guide disk 40.1 located at the front in FIG. 2, the centering surface 60 entering the guide groove 63 which is designed as a shoulder and is open on both sides.

The slide rings 45.1 and 45.2 are rotatably inserted in the ring grooves 44.1 and 44.2 with a smooth sliding fit. When the rotor 55 rotates with its two eccentric guide disks 40.1 and 40.2, they only oscillate back and forth because - as can be seen in FIG. 2.3 - the locking slides 46.1 and 46.2 are held in the slide openings 33.1 and 33.2 and only execute rocker arms and axially in and out can emerge as the eccentric rotary movements require. The ends 65.1 and 65.2 enter or exit the slide receiving spaces 50.1 and 50.2 corresponding to the eccentricity 57.

The locking slides 46.1 and 46.2 and formed as approximately square or rectangular disks delimited by parallel sealing surfaces 66.1 to 66.4, the end faces 67.1 and 67.2 of which can be shaped in any way, while the inner end sealing surfaces 68.1 and 68.2 are concavely partially cylindrical and limited by the radius 69, which corresponds to the outer diameter of the cylinder jacket partial surfaces serving for guiding and sealing, namely the guide surfaces 59.1 and 59.2, so that the respective locking slide when the rotor 55 rotates on the guide surfaces 59.1 and 59.2 of the rotor 55 and between the inner surfaces 52.2 and 52.4 of the two Eccentric guide plates 40.1 and 40.2 can swing back and forth sealed. The remaining gate valve sealing surfaces 51.1 to 51.4 have already been dealt with at the front.

The contact sealing surfaces 70.1 to 70.4 between the two parts of the pump chamber wall 32 and the slide receiving spaces 50.1 and 50.2 are - as can be seen from FIG. 2.3 - designed as partial cylinder surfaces with a radius 71. The distance 72 between their tips is greater than the thickness 74 (FIG. 2.4) of the locking slides 46.1 and 46.2, so that they have sufficient play to move them. The contact sealing surfaces 70.1 to 70.4 can also have a shape corresponding to the precise movement shape of the locking slides 46.1 and 46.2 and their sealing surfaces, or the surfaces involved in the sealing can be formed with other surfaces which are shaped to match the movements and shape-generating lines. In the distance very exact sealing on both sides of the locking slides 46.1 and 46.2 is not necessary because the wing-like locking slides 46.1 and 46.2 can move freely with their freely rotatable slide rings 45.1 and 45.2 and move completely freely due to the higher pressure on one side or the other be pressed tightly. Accordingly, the receiving space 50.1 or 50.2 is at the respective pressure level, which corresponds to the free sealing side. Since the gaps formed here are narrow, larger components of the pump medium do not get into the slide receiving spaces 50.1 and 50.2. Larger components are only in the crescent-shaped media shift rooms. One can have two parts. The spatial areas of the pump chamber 30 are divided by the sealing system 76.

The rotor 55, which also serves to guide the pumping medium in the space, has a diagonally guided or approximately helical, running between the rotor inlet channel 80.1 and the rotor outlet channel 80.2, which spatially profiled partition wall 81 separates these two from one another and seals with the surrounding wall surfaces 82.1 and 82.2 the rotor wall parts surrounding the drive spline provided with internal splines and the wall parts of the rotor 55 forming the guide surfaces 59.1 and 59.2 are integrally formed.

The two rotor channels, namely the rotor inlet channel 80.1 and the rotor outlet channel 80.2, each form an inlet opening 83.1 or outlet opening 83.2 which opens axially in opposite directions and at least partially in the form of a profile, and each have a large area radially into the pump chamber 30 opening pump chamber inlet opening 84.1 or pump chamber outlet opening 84.2. From FIGS. 2.2 and 2.3 it can be seen how the rotor inlet duct 80.1 opens into the pump chamber part 75.3, which is located at the top right here, while it cannot be seen in detail that the rotor outlet duct 80.2 opens into the pump chamber part 75.2. Depending on the rotor position and - as can be seen from FIGS. 7.1 to 7.4 - these media displacement or pumping spaces are semi-crescent or partly crescent-shaped due to the positions of the locking slides 46.1 and 46.2, with either one or both tips missing. This changes continuously during the circulation and leads in the largest part of the pump chamber 30 lying between the two gate valves 46.1 and 46.2, which is just shut off from the inlet and outlet, to the relaxation and thus great smoothness of the entire pump, which is particularly advantageous for fruit components of the delivery medium all connected parts of the system in which it is installed.

The pair of parallel lines shown in FIG. 4, designated "81", is an indication of the partition 81 which is concealed here. Compared to the usual relative position of various sectional views, in particular with respect to the oblique images, FIG. 4 is rotated by 90 °. The different inclined images in other figures clearly show the position of the partition 81.

The pump core parts shown are located between housing connection parts, each of which has an inlet space 28 and outlet space 29 which are open to the pump parts and which have an end face surface with an inserted O-ring seal 93.1 and 93.2 (FIG. 1). The end faces of the eccentric guide disks 40.1 and 40.2 run around this large-volume O-ring seal.

It is a pump that is similar in some structural parts to the vane pump, but with the difference that the vanes do not run around the outer surface of the pump chamber, but enter the receiving rooms and seal with their flat sealing surfaces 66.1 to 66.4 on the system sealing surfaces 70.1 up to 70.4 of the stator to seal it back and forth, press it on under the pressure of the medium and swing it up and down over the tips of the system sealing surfaces. Otherwise, the medium enters axially via the rotor inlet channel and becomes from the inclined and / or helical surface of the partition 81 diverted to the radial outlet or it enters radially into the rotor outlet duct, which has an inclined and / or helical surface, and then exits again axially.

Because of the wide opening to the inlet and outlet space for large circulation times, no compression of the medium takes place in the sickle spaces, but rather medium portions are taken up in portions, separated between the various sealing surfaces and conveyed to the outlet, so that sensitive medium portions such as fruit or the like. , not be compressed. The partially cylindrical sealing system 76 running along the pump chamber wall 32 also contributes to this.

Function description:

The pump 20 / 20.1 shown is suitable for a wide variety of pumping media or can be suitably designed by means of suitable materials and material combinations or special configurations. It is particularly intended for food and especially designed for high hygiene requirements. The pumping media can also contain sensitive components such as fruit or other food components. They can also consist of or contain chemically aggressive substances. The pump can also be used for dairy products, beverages, cosmetics, pharmaceuticals and many other liquid and viscous substances.

The pumped medium to be pumped enters the inlet space 28 through the inlet nozzle 27 and exits through the outlet space 29 in the outlet nozzle 29.1. The pump medium can be sucked in by the pump 20 / 20.1 or can be supplied in free fall or under natural liquid pressure from a funnel or reservoir. It can leave the outlet port 29.1 under pressure. This pressure is determined according to the usual design rules for pumps and the sealing conditions, in particular the sealing gaps and the flow conditions in them. They are particularly cheap in the construction and the execution options explained. Therefore, relatively high pressures can be achieved in comparison to other pumps and unusually even and low-pressure flow rates.

You can visualize the function beforehand using the following brief description:

Starting from the position shown in Fig. 7.1, the medium enters the room areas 97.1 and 97.2. When the rotor moves from the position shown in Fig. 7.1 to the position shown in Fig. 7.2; 8.2 is shown, rotates and then continues over the position of Fig. 7.3; 8.3 in the position of Fig. 7.4; 8.4, the medium sucked in is housed partly inside the rotor and partly in the area above the rotor and the blocking slide 46. Then the sucked-in medium Medium also divided into two parts, namely the part within the room areas 97.1 and 97.2 under the locking slide 46.2 and a completely separate part in the area 98.1.

From the position according to Fig. 7.4; 8.4 moving further, the outlet side of the rotor comes when the leading control edge 88.1 of the outlet opening 83.2 of the rotor outlet duct 80.2 is exceeded via the upper edge 66.8 of the right-hand slide valve 46.1 in the drawings in connection with the medium previously captured in the upper chamber area 98.1 of the pump chamber 30. As the rotor continues to rotate, this part of the medium is forced to leave the rotor outlet channel 80.2 of the rotor and is driven out through the outlet opening 83.2 until the rotor has again reached the position shown in FIG. 7.1.

The function is described in more detail below: The path of the pump medium can only be seen schematically in FIG. 1. The details of the path in the actual pump part 20.1 cannot be seen from FIG. 1 and can best be seen in FIG. 6. In order to examine the route in detail, however, it is necessary to look at various drawings alternately, on the basis of which it is explained below with reference to it. The representations in the multiform FIG. 8 show different phases during the rotation of the rotor in oblique images. These correspond essentially to the positions shown in the partial figures in FIG. 7.

The pump medium is present in the inlet chamber 28 and passes through the inlet opening 83.1 into the rotor inlet channel 80.1 and is helically deflected therein by the inclined partition 81 and approximately radially through the pump chamber inlet opening 84.1 of the rotor inlet channel 80.1 into the pump chamber 30 the rotor 55 is led outwards as a central region, depending on the position of the rotor 55 and the locking slide 46.1 and 46.2. In the explanation it is assumed that the pump is filled. The various rotational position states of the rotor 55 with the two locking slides 46.1 and 46.2 in the pump chamber 30 and the adjoining slide receiving chambers are shown in the four representations of the same basic structural structures of the main pump parts in FIGS 50.1 and 50.2 are shown.

The parts of the pump chamber 30 designated 97 or 97 and the decimal digit are always at the pressure level of the inlet chamber 28 and thus in the light suction area, that is to say under a pressure which is lower than atmospheric pressure. The parts of the room designated 98.1 and 98.2 are separated from the inlet and from the outlet in the illustrated state of the pump and therefore allow the pumping medium to relax, because they enlarge slightly in some areas during a short circulating partial path until the pumping medium of the room area 98.1 as a result of the further movement of the rotor 55 with the rotor outlet channel 80.2 and the associated pivoting movement of the blocking slides 46.1 and 46.2 through the outlet opening 83.2 is in fluid communication with the outlet and that is behind that on the trailing side and from the trailing blocking slide ejected pump medium is now pressurized and reaches the outlet chamber 29 and thus the area of the outlet port 29.1 via the rotor outlet channel 80.2, through the outlet opening 83.2 and thus the pump under the desired pressure caused by the pump through the outlet line or other connected devices leaves. Even with this route out of the pump chamber 30, the pump medium moves in the radial direction from the pump chamber through the pump chamber outlet opening 84.2 into the rotor outlet channel 80.2, is deflected in the axial direction on the spiral or inclined partition 81 and leaves through the Outlet opening 83.2 and outlet chamber 29 the actual pumping area in the direction of outlet port 29.1.

The decimal digits used below clearly show which structurally different parts of the room are at the same pressure level.

As shown in FIGS. 7.1 to 7.4 and in particular also in FIG. 5, the rotor inlet duct 80.1 is the first area that is at the suction level and is therefore designated 97.1. Otherwise, in this rotary position in the pump chamber 30 there is only the room area 97.2 in the small crescent-shaped gusset area on the right in FIG. 7.1 at the suction level, because the suction slide and the slight overpressure in the relaxation area 98 cause the blocking slide 46.2 - in FIG. 7.1 right - pressed against the system sealing surface 70.3 above and closes the room on this side. Otherwise, the space through the sealing area 76 of the rotor 55, which bears against the cylindrical pump chamber wall 32, and with its mutual outer disk sealing surfaces 52.1 and 52.3 running normal to the pump axis 43 through the two inwardly facing, flat disk sealing surfaces 52.2 and 52.4 Eccentric guide washers 40.1 and 40.2 sealed. The flat rectangular locking slide sealing surfaces 51.1, 51.2, 51.3, 51.4, which are normal to the two axes 43 and 47 and lie between the locking slides 46.1 and 46.2 and the disk sealing surfaces 52.2 and 52.4, are sliding sealing surfaces between components subject to eccentric relative sliding movements.

The space 99.1 in the rotor outlet duct 80.2 is in fluid communication with the outlet space 29 in the outlet port 29.1 at the pressure level. Furthermore, the gusset space 99.2 - on the left in Fig. 7.1 - is at the same pressure level as the slide receiving space 50.2, because due to the greatest pressure prevailing here, the locking slide 46.2 is pressed against the system sealing surface 70.2, so that there is a small gap opposite it, which forms the pressure connection to the slide receiving space 50.2. At the same time, the room 98.1 is set in this rotational position and, by the position of the blocking slide 46.1, the slide receiving space 50.1 is set to the relaxation pressure level.

If the rotor 55 continues to rotate, as shown in Fig. 7.2, the gusset space 99.2 is reduced and the rotor outlet channel 80.2 comes with the space part 98.1 between the two slide valves 46.1 and 46.2 in fluid and pressure-carrying connection, so that this total area leads to the escape of medium from the outlet port 29.1 due to the now occurring pushing and overpressure effect. The locking slides 46.1 and 46.2 tilt into the intermediate position shown in FIG. 7.2 and upon further rotation into the position shown in FIG. 7.3, namely the extended position in which the inlet and outlet are connected to sub-spaces of the same size in the pump chamber area. When turning further, the Elements rotor 55, slide valve 46.1 and 46.2 as well as the spatial components are a mirror image of the arrangement according to FIG. 7.1, as shown in FIG. 7.4. Accordingly, the pressures and movements occur. In accordance with the pressures, the blocking slides are also sucked or pressed onto the contact sealing surfaces and the sealing is effected accordingly and the slider receiving spaces are connected to the corresponding liquid and pressure areas by slight tilting movements. This benefits the advantageously elastic design of the pump housing 31, because at least the surface and areas close to the surface are to be produced from a suitable rubber, natural or synthetic rubber. These sub-housing areas or coatings are formed in a metal, usually rust-free carrier housing part.

8.2 to 8.4 are schematic skewed representations of the previously treated pump. The numbers following the point in the figure designations correspond to those in FIG. 7, so that the same angular positions of the rotor are designated with the same decimal digits. In addition, the angular positions are added to the designations. A representation corresponding to FIG. 7.1 is not shown. The illustrations contain part of the However, reference numerals, such as those used previously, are used primarily to represent the inlet and outlet openings of the rotor inlet duct and the rotor outlet duct. Only the edges of these two openings are additionally marked. From the positions shown in FIGS. 7.4 and 8.4, the rotor 55 and the locking slides 46.1 and 46.2 initially move in a further rotation according to the direction of rotation indicated by the arrow 85 via a position "235 °", not shown, to one of FIGS. 7.3 and 8.3 mirror-image position "270 °" and a mirror-image position "315 °" to FIGS. 7.2 and 8.2 at the end of a cycle according to FIG. 7.1.

The pump chamber inlet opening 84.1 has boundary edges 86.1 and 86.2 running on the outer surface 59 of the rotor 55, as well as the leading control edge 87.1 and the trailing control edge 87.2, which are drawn here as axially parallel lines. They can also be rounded or otherwise profiled to improve the transition conditions in the corner areas. 8.2, 8.2.1 and 8.3, the trailing control edge 88.2 of the pump chamber outlet opening 84.2 is not visible, and consequently its corner 88.21 is shown. The leading control edge 88.1 is visible here. 8.4 only the trailing control edge 88.2 is visible, whereas the corner 88.11 is shown instead of the leading control edge.

The axially parallel control edges 87.1 and 87.2 as well as 88.1 and 88.2 of the pump chamber inlet opening 84.1 and the pump outlet opening 84.2 have a controlling function and behave like the control edges of slides in hydraulic valves or in two-stroke internal combustion engines.

From the outlet opening 83.2, one can see the edge boundaries 89.1 and 89.2 concentric with the outer wall 59 of the rotor 55, as well as the edge 89.3 opposite the partition and the boundary line 89.4 around the drive opening 56. These are not shown in all figures.

Variants for individual configuration parts of the pump shown above are shown in the figures discussed below.

All variants can be sensibly applied to the original pump by varying the corresponding components, but also to pumps with a different design with different housings, different inlets, different drives, but with the same basic principle of designing the pump chamber, rotor, gate valves, pump wall openings and the like.

The embodiment variant according to FIGS. 9.1 and 9.2 differs from the previously treated one in that the blocking slides 146.1 and 146.2 of a single pump are now not held on two slide rings lying on both sides of the pump housing. Instead, a slide ring 145.1 of approximately the size and relative assignment is provided for the one slide 146.1 as in the first exemplary embodiment. For the other slide 146.2, however, a larger slide ring 145.2 is provided, which is now on the same side of the pump housing as the slide ring 145.1 of the blocking slide 146.1. Due to its larger inner diameter 144, the slide ring 145.1 can be arranged inside the slide ring 145.2, as shown in FIG. 9.1, so that both locking slides 146.1 and 146.2 work independently of one another and in opposite directions with respect to the direction of rotation. The corresponding ring grooves in the now only one eccentric guide disk are designed with suitable dimensions and preferably with a separating collar between the two.

While Fig. 9.1 shows the two slide rings 145.1 and 145.2 with their locking slides 146.1 and 146.2 projecting from them individually and separately from one another, Fig. 9.2 shows how they are relative to each other in the installed state.

This training may make assembly and disassembly cheaper for certain pump designs. In return, the symmetry of the components is lost to a small extent. However, this can be offset by manufacturing and assembly advantages.

The embodiment variant according to FIG. 10 differs from the above in that the locking slides 246.1 and 246.2 on each of their locking slide sealing surfaces 251.1 to 251.4 each have a slide partial ring 245.1 and 245.2 on the locking slide 246.1 and with the slide partial rings 245.3 and 245.4 on the locking slide 246.2 are attached. Locking slides supported on both sides can be arranged in ring grooves 244 in eccentric guide disks 240 in the same manner as in the first exemplary embodiment. As the partial assembly drawing in Fig. 10.3 shows, between the ends 220.1 and 220.2 of the slide partial rings in the respective annular groove there is a partial space 230 which is filled with medium and which corresponds to the oscillation process of the blocking slides 246.1 and 246.2 during the pumping process enlarged and reduced. However, this fact has fewer disadvantages for most media than it has advantages for the entire pump to support the locking slide 246 on both sides and thus to avoid bending loads on the locking slide and thus uneven wear on the sliding, sealing and bearing surfaces, and accordingly thinner or more stable To be able to design gate valves with their slide rings and guides. Of the eccentric guide disks, only the one in the drawing, labeled "240", is shown, the rest of the pump has been left out for the sake of clarity.

11 and 12 show an embodiment variant in which the locking slides 246.1 and 246.2 are not freely guided between the contact sealing surfaces 70 as in the first exemplary embodiment, but rather slide guide elements 370.1 and 370.2 are arranged in the slide receiving spaces 350.1 and 350.2. As illustrated in FIG. 12, the slide guide elements are cylindrical elements with an outer diameter that corresponds to the inner diameter of the slide receiving spaces 350.1 and 350.2. Otherwise, these cylinder bodies have a diameter which is greater than the immersion depth of the ends of the locking slides 246.1 and 246.2. A connection part 373 supporting the two cylinder sections 372.1 and 372.2 is provided in the area beyond the slide movement. Relief channels are also useful. A relief channel 374 is indicated on the left in FIG. 12. It can also be formed in the sliding surfaces. The locking slides fit in the slots 375.

The system sealing faces 70 of the first exemplary embodiment with the inlet constrictions are omitted in this variant. The slide guide elements take on their function, to which sufficiently large inlet openings 372 of the slide receiving spaces 350.1 and 350.2 are assigned for the pivoting and oblique movements of the blocking slides 346.1 and 346.2.

Such a pump design with slide guide elements is particularly useful if the pump housing 331 and the locking slide 46.1 and 46.2 are all made of stainless chromium-nickel steel and therefore cannot run in the long term without the provision of sliding materials. The slide guide elements 370.1 and 370.2 consist of a suitable material that is neutral with regard to the medium to be pumped and has good sliding properties, for example a plastic such as PEEK (polyether ether ketone), possibly with embedded carbon or other Materials that improve cohesion and / or sliding properties, also in fiber form. This material is referred to in the claims as "plain bearing material".

13 shows a further variant. In this example, three locking slides 446.1, 446.2 and 446.3 are provided. The entire pump must be designed accordingly. Another special feature here is that the slide receiving spaces 450.1, 450.2 and 450.3 are not cylindrical, but have an approximately triangular cross-section in accordance with the pivoting angles of the locking slides 446.1 to 446.3. They are designed in such a way that the locking slides rest on the essentially straight inner surfaces 447 in the end positions of their pivoting movements. Other slider receiving space shapes can also be selected based on the pump construction, the medium, possibly vibration processes and the like. However, you must always ensure the free movement of the locking slide to the extent dependent on the eccentricity. Housing with pump chamber wall 432, slide openings and rotor 455 are designed in accordance with the three locking slides 446.1 to 446.3.

The embodiment variant according to FIGS. 14 and 15 shows how the locking slides 546.1 and 546.2 sealing strips 570 are inserted into the inner end sealing surfaces 568.1 and 568.2. The sealing strips 570 are designed here, for example, in the actual sealing part with a slightly concave partial cylinder surface 571, which is formed on a dovetail body part 572, which is inserted in a corresponding groove in the locking slide 546.1 or 546.2. For this purpose, it has a partially cylindrical retaining bead 573 and a parallel-walled transition part 574. Such sealing strips 570 suitably consist of an elastic material which has the material properties of those previously treated Slider-guide elements can be the same or similar and, despite good or even improved sealing, prevents direct sliding of the same stainless steel materials onto one another. It should be noted that the locking slides only perform pivoting movements, but must perform a turning movement at the end of their swinging movement and the sealing strips 570 can also perform small tilting movements due to the elasticity with regard to the support, which must be compensated for by suitably designed sealing strips and their materials.

16 and 17 show that the sealing system 676 can be enlarged if necessary by not giving the rotor 655 a precisely cylindrical shape as in the first exemplary embodiment and the previously discussed design variants, but rather a longer sealing surface in the area of the sealing system 676 677 gives, which has exactly the radius as the pump chamber wall 32. 15 and 16 differ in that the slide receiving spaces 50.1 and 50.2 in the embodiment variant according to FIG. 15 are designed without any internals and the locking slides 46.1 and 46.2 are supported on the contact sealing surfaces 70 ..., while in the embodiment variant according to FIG 17 are arranged in the slide receiving spaces 350.1 and 350.2 slide guide elements 370.1 and 370.2.

Together with this variant, other design variants with more than two locking slides or with differently designed slider receiving spaces, e.g. 13, can be implemented on a pump or other device.

18 shows an embodiment variant in which not the entire pump is shown, but only the inner pump housing with its installation parts. It is provided that two completely identical pumps according to the first embodiment are mounted on a single shaft and only one connecting ring 710 is arranged between the pumps, in the guide grooves 711 and 712 of which the two shoulders 715 and 716 of the pump housings 731.1 and 731.2 are aligned to align them right-hand pump 720.1 and left-hand pump 720.2 are used. Then, for example, the liquid initially compressed in the right-hand pump 720.1 passes from the outlet opening 783.2 through the through-opening 785 in the right-hand eccentric guide disk 740.1 directly through the corresponding through-hole in the left-hand eccentric guide disk 740.2 into the inlet opening 783.1 of the left-hand pump 720.2, so that the pump on the right 720.1 works as a low pressure pump and the pump on the left 720.2 as a high pressure pump. As a result, the head of a pump can be significantly improved with small dimensions and favorable construction conditions.

If two or more pumps are angularly offset from one another on a shaft and the flow rates are combined in a sensible manner, you can achieve both a higher delivery head and much less fluctuating flow rate as well as a larger and quieter flow rate.

The subject of this treatise, especially with a view to possible improvements in the form of the claim, can also be summarized in the following manner:

• und enthaltend eine Mehrzahl von grundsätzlich radialen Dichtungsflügeln bzw. Sperrschiebern die über den Rotor verteilt sind, wobei jeder ein inneres Ende in dichtender Beziehung mit der Außenwandfläche des Rotorkörpers hat und ein äußeres Ende, welches gleitfähig und hin- und herbewegungsfähig sich erstreckt in den jeweiligen Aufnahmeraum, welcher in der Pumpenwand vorgesehen ist;
• und enthaltend Flügelführungsmittel, welche gekuppelt sind mit dem entsprechenden Flügel und montiert, um exzentrisch in Synchronisation oder Übereinstimmung mit dem Rotor zu rotieren, wenn der Rotor sich dreht, um so bei Drehung des Rotors oszillierende Gleit- und Hin- und Herbewegungen der Flügel zu bewirken,
• wobei Dichtungsflügel, Trennwand und Dichtungsoberfläche zusammenwirken, um zu pumpendes Medium von der Einlaßöffnung über das einlaßseitige Innere des Rotorkörpers, einen Teilbereich des Pumpenraumes und das auslaßseitige Innere des Rotorkörpers zur Austrittsöffnung zu übermitteln.

Liquid transport device comprising: a pump chamber of circular cross section with inlet and outlet openings on opposite sides; a rotor in the pump chamber which has a hollow rotor body which is eccentric to but rotatable with respect to and about the axis of the pump chamber, the rotor body having an elongated outer surface to form a seal with the circulating surface of the pump chamber and one to the sealing surface has an adjacent partition which separates the rotor body into an inlet side and an outlet side, the inlet side having an axial inlet opening at one end which communicates with the pump chamber inlet opening of the pump chamber, which is a radial opening for communication with the interior of the pump chamber, and wherein the outlet side has a radial opening for communication with the inside of the Has pump chamber and an axial outlet opening formed at the end opposite the inlet opening, which communicates with the outlet opening of the pump chamber;

• and including a plurality of generally radial sealing vanes which are distributed across the rotor, each having an inner end in sealing relationship with the outer wall surface of the rotor body and an outer end which slidably and reciprocally extends into the respective receiving space , which is provided in the pump wall;
• and including vane guide means coupled to the respective vane and mounted to rotate eccentrically in synchronization with the rotor as the rotor rotates so as to cause oscillating sliding and reciprocating movements of the vanes as the rotor rotates ,
• wherein the sealing wing, partition and sealing surface cooperate in order to transmit medium to be pumped from the inlet opening via the inlet-side interior of the rotor body, a partial region of the pump chamber and the outlet-side interior of the rotor body to the outlet opening.

• eine exzentrisch geführte Sperrschiebereinrichtung,
• umlaufende Dichtbereiche in einem zylindrisch begrenzten Pumpenraum (30) und die Sperrschieberanordnung bewirken die Abdichtung zwischen Saugseite und Druckseite,
• wenigstens zwei bewegliche Sperrschieber (46.1, 46.2),
• eine mitlaufende Zuführ- und Abführanordnung für die axiale Zuführung von der Saugseite und die axiale Abführung zur Druckseite,
• die Pumpraumwand (32) ist von Schieberöffnungen (33.1; 33.2) unterbrochen,
• die Schieberöffnungen (33.1; 33.2) sind unter Winkeln zueinander ausgebildet, welche der Zahl der Sperrschieber (46.1, 46.2) entsprechen und bei zwei Sperrschiebern etwa einander gegenüberliegen,
• die bezüglich des Rotors drehbeweglich gelagerten Sperrschieber (46.1, 46.2) tauchen mit ihrem nach außen weisenden Ende in den jeweiligen, Schieberaufnahmeraum (50.1; 50.2) ein,
• die Sperrschieber sind an mit dem Rotor exzentrisch umlaufenden, die Sperrschieber-Schwingungen zulassenden Sperrschieber-Halte- und Führungs-Mitteln geführt.

Filling, fluid transport and pumping device with the following features:

• an eccentrically guided gate valve device,
• circumferential sealing areas in a cylindrically delimited pump chamber (30) and the locking slide arrangement effect the sealing between the suction side and the pressure side,
• at least two movable locking slides (46.1, 46.2),
• a moving feed and discharge arrangement for the axial feed from the suction side and the axial discharge to the pressure side,
• the pump chamber wall (32) is interrupted by slide openings (33.1; 33.2),
• the slide openings (33.1; 33.2) are formed at angles to one another which correspond to the number of locking slides (46.1, 46.2) and are approximately opposite one another in the case of two locking slides,
• the locking slides (46.1, 46.2), which are rotatably mounted with respect to the rotor, dip with their outward-pointing end into the respective slider receiving space (50.1; 50.2),
• the locking slides are guided on locking slide holding and guiding means which rotate eccentrically with the rotor and permit the locking slide vibrations.

The pump has an inlet space (28) and a drive shaft (23) in a bearing and seal housing (21), which drives the rotor (55) and the two eccentric guide disks (40.2) connected to it. Slide rings (45.1, 45.2) are stored in these in ring grooves. These carry the locking slides (46.1, 46.2), which plunge into slide receiving spaces via system sealing surfaces or are pulled out of these. The pump is suitable for high hygienic requirements, such as for food, medication and cosmetics, and can also gently convey sensitive components such as fruit or other food components.

Reference symbol list:

20th

pump

20.1

pump

21

Bearing and seal housing

22.1

holder

22.2

"

23

drive shaft

24th

Connecting stub

24.1

Tongue groove

25th

Sealing ring

26.1

Roller bearings

26.2

"

27

Inlet connector

27.1

Screw thread

28

Entry space

29

Exit space

29.1

Outlet connection

29.2

thread

30th

Pump room

31

Pump housing

32

Pump room wall

33.1

Slide opening

33.2

Slide opening

35

Length of 30

36

Diameter of 30

38

Control unit groove

38.1

Control unit groove

38.2

"

39

Rotating guide collar

40.1

Eccentric guide washer

40.2

"

41

Outlet area

43

Pump axis

44

cylindrical ring groove

44.1

Ring groove

44.2

"

45.1

Slide ring

45.2

"

46.1

Gate valve

46.2

"

47

Center / eccentric axis

48

Length of 46.1 / 2

49

Depth of 46.1 / 2

50.1

Slider receiving space

50.2

"

51.1

Gate valve sealing surface

51.2

"

51.3

"

51.4

"

52.1

Washer sealing surface v.40.1

52.2

Washer sealing surface v.40.1

52.3

Washer sealing surface v.40.2

52.4

Washer sealing surface v.40.2

55

rotor

56

Drive opening

57

eccentricity

58

Diameter of 55

59

Outer wall

59.1

Leadership area

59.2

"

60

Centering surface

61

Dowel pin

62

Dowel pin hole

63

Guide groove

65.1

The End

65.2

"

66.1

Sealing surface

66.2

"

66.3

"

66.4

"

66.8

upper edge

67-1

Face

67.2

"

68.1

inner face sealing surface

68.2

"

69

radius

70.1

System sealing surface

70.2

"

70.3

"

70.4

"

71

radius

72

distance

74

Thickness of 46.1 / 2

75.1

Pump room part

75.2

"

75.3

"

76

Sealing system / area

80.1

Rotor inlet duct

80.2

Rotor outlet channel

81

partition wall

82.1

Surrounding wall surface

82.2

"

83.1

Entry opening from 80.1

83.2

Outlet opening from 80.2

84.1

Pump room inlet opening of 80.1

84.2

Pump chamber outlet n.80.2

85

Direction of rotation / arrow

86.1

Boundary edge

86.2

Boundary edge

87.1

Control edge

87.2

"

88.1

Control edge

88.2

Control edge

88.11

corner

88.21

corner

89.1

Edge limitation

89.2

"

89.3

Edge

89.4

Boundary line

90

Housing cover

91

screw

92

flange

93.1

O-ring seal

93.2

"

94.1

Groove

94.2

"

95

mother

97

Room part (with suction pressure)

97.1

Room area

97.2

Room area

98

Relaxation area (room area with relaxation pressure)

98.1

Room / area / part

98.2

"

99.1

Room in 80.2 (room area with delivery pressure to the outlet room

99.2

Gusset room

144

Inside diameter

145.1

Slide ring

145.2

"

146.1

Gate valve

146.2

"

220.1

End of 245

220.2

"

230

Subspace

240

Eccentric guide washer

244

Ring groove

245.1

Slider partial ring

245.2

"

245.3

"

245.4

"

246.1

Gate valve

246.2

"

251.1

Gate valve sealing surface

251.2

"

251.3

"

251.4

"

331

Pump housing

346.1

Gate valve

346.2

"

350.1

Slider receiving space

350.2

"

370.1

Slider guide elements

370.2

"

372

Entrance opening

372.1

Cylinder section

372.2

Cylinder section

373

Connecting part

374

Relief channel

375

slot

432

Pump room wall

446.1

Gate valve

446.2

"

446.3

"

447

Inner surface

450.1

Slider receiving space

450.2

"

450.3

"

455

rotor

546.1

Gate valve

546.2

"

568.1

inner face sealing surface

568.2

"

570

Sealing strips

571

Partial cylinder surface

572

Swallowtail body part

573

Retaining bead

574

Transition part

655

rotor

676

Sealing system

677

Sealing surface

710

Connecting ring

711

Guide groove

712

Guide groove

715

shoulder

716

shoulder

720.1

pump

720.2

"

731.1

Pump housing

731.2

"

740.1

Eccentric guide washer

740.2

"

783.1

Entry opening from 80.1

783.2

Outlet opening from 80.2

785

Passage opening

Claims (24)

1. Filling, fluid-transporting and pumping device, having a housing, inlet and outlet openings, supplying and discharging arrangement and gate valve device, having the following features:

   a) the gate valve device is guided eccentrically;

   b) peripheral sealing regions in a cylindrically delimited pumping space (30) of the housing and the gate valve arrangement effect the sealing between suction side and pressure side;

   c) at least two movable gate valves (46.1; 46.2) and the associated supplying and discharging arrangement, formed with a rotor (55) for supplying axially from the suction side and discharging axially to the pressure side, are provided;

   d) the rotor (55) is constructed rotating about the central pump axis (43) of the pumping space (30), but with respect to this pump axis (43) is constructed eccentrically such that it can run along the pumping space wall (32) of the pumping space (30) by means of a curved sealing surface (76);

   e) the rotor (55) has axial and radial inlet and outlet openings which are provided with fluid-guiding channels;

   f) the fluid-guiding channels are separated from one another by a helical separating wall (81);

   g) the pumping space wall (32) is interrupted by gate valve openings (33.1, 33.2) of gate valve receiving spaces (50.1; 50.2);

   h) the number of gate valve openings (33.1; 33.2) corresponds to the number of gate valves (46.1; 46.2);

   j) the gate valve openings (33.1; 33.2) are arranged at approximately the same angle around the pumping space (30) and lie opposite one another, in the case of two gate valves (46.1; 46.2);

   k) the gate valves (46.1; 46.2) which are mounted rotatably with respect to the rotor (55) penetrate in sealed manner into the associated gate valve receiving space (50.1; 50.2) by means of their in each case radially outwardly pointing part;

   l) gate valve holding and guiding means are provided, on which the gate valves (46.1; 46.2) are guided;

   m) the gate valve holding and guiding means rotate eccentrically in synchronism with the rotor (55) when the latter rotates, gate valve oscillations thereby being . produced.
2. Filling, fluid-transporting and pumping device according to Claim 1, having a cylindrical main space in or on which collectively driven eccentric guide plates rotate in the region of both ends and in which the eccentric guide plates have cylindrical ring-shaped guide grooves (44.1; 44.2) in which guide rings (45.1; 45.2) can be rotated, from which the gate valves (46.1; 46.2) project outwards into the respective gate valve receiving spaces (50.1; 50.2).
3. Device according to at least one of the preceding claims, characterized in that the gate valves (46.1, 46.2) are, at least in the inlet region of the gate valve openings (33.1; 33.2),

   - guided and supported on curved sealing and supporting surfaces which correspond to their shape

   - or guided and supported in slots of rotatable gate valve guiding elements.
4. Device according to Claim 3, characterized in that the transitions from the pumping space wall (32) to the gate valve receiving spaces (50.1; 50.2) are effected by curved bearing sealing surfaces (70.1 to 70.4), in which the spacing between the sphere caps in the region of a gate valve opening (33.1; 33.2) is slightly larger than the thickness (74) of the gate valves (46.1, 46.2).
5. Device according to at least one of the other claims, characterized in that the pumping space wall (37), together with bearing sealing surfaces (70.1 to 70.4), is formed by a pump housing (21) which is of rubber or is coated with rubber.
6. Device according to Claim 3, characterized in that the gate valve guiding elements are cylindrical bodies of sliding bearing material whereof the diameter is larger than the depth of penetration of the ends of the gate valves and which have a supporting transverse connection in the region lying beyond the gate valve movement, and in which where appropriate relief channels are constructed.
7. Device according to Claim 6, characterized in that pumping space wall, rotor and gate valve are of corrosion-resistant steel or other metal and the gate valve guiding elements are of a synthetic material provided with means to aid sliding.
8. Device according to one of Claims 1 to 5, characterized in that the gate valve receiving spaces are formed to correspond in cross-section approximately triangularly to the pivot angle of the respective gate valve. (Fig. 13)
9. Device according to at least one of the other claims, characterized in that three gate valves with associated gate valve receiving spaces and where appropriate guiding and sealing elements are provided.
10. Device according to at least one of the other claims, characterized in that the gate valves (46.1; 46.2) are constructed as flat plates whereof the curved, inner end sealing surfaces (68.1; 68.2) are constructed such that they bear against one another on guide surfaces (59.1, 59.2) of the driving and guiding body operating as the rotor (55) and having the same radius.
11. Device according to at least one of the other claims, characterized in that a sealing strip (570) is arranged in the inner end sealing surface (568.1; 568.2) of each gate valve (546.1; 546.2), this inner end sealing surface (568.1; 568.2) oscillating on the outer wall (59) of the rotor (55).
12. Device according to Claim 11, characterized in that a sealing groove is made in the metal gate valve and there is arranged therein a sealing strip (570) which is of a synthetic material suitable for the material of the rotor (55) and the medium to be pumped.
13. Device according to at least one of the other claims, characterized in that the rotor and the eccentric guide plates (40.1; 40.2) rotate together, and the gate valve sealing surfaces (51.1 to 51.4) of the gate valves running perpendicularly with respect to the pump axis (43) are guided in displaceably sealing manner between the planar, inwardly facing plate sealing surfaces (52.2; 52.4) of the eccentric guide plates (40.1; 40.2).
14. Device according to at least one of the other claims, characterized in that the gate valves (46.1; 46.2) are mounted rotatably by means of slider rings (45.1; 45.2) connected fixedly thereto or slider part rings (245.1, 245.2) and the slider rings (45.1; 45.2) or slider part rings (245.1; 245.2) are guided rotatably in annular grooves (44.1; 44.2; 244) which are constructed in eccentric guide plates (40.1; 40.2; 240; 740.1; 740.2) arranged at the end face with respect to the cylindrical pumping space (30), rotating eccentrically with the rotor, additionally forming wall parts and being associated with the gate valve holding and guiding means.
15. Device according to at least one of the other claims, characterized in that the gate valves (46.1; 46.2) are constructed or secured on slider rings (45.1; 45.2) located outside the sealing surfaces which are perpendicular with respect to the pump axis (43).
16. Device according to at least one of the other claims, characterized in that two slider rings (145.1, 145.2) of different sizes are arranged on one side of the rotor in fitting annular grooves. (Fig. 9)
17. Device according to at least one of the other claims, characterized in that the slider part rings (245.1 to 245.4) have the same internal and external radii and the respective angular length is dimensioned such that it is shortened at least by the pivot angle of the respective gate valve. (Fig. 10)
18. Device according to at least one of the other claims, characterized in that the slider ring parts (245.1 to 245.4) are fixedly mounted, on either side of the gate valve (246.1; 246.2), to the latter and are shaped in accordance with the openings for installation and removal. (Fig. 10)
19. Device according to at least one of the other claims, characterized in that the gate valves (46.1, 46.2; 146.1, 146.2; 246.1, 246.2), with their slider rings (45.1, 45.2; 145.1, 145.2; 245.1; 245.2), are formed as identical or largely similar or symmetrical components constructed in one piece.
20. Device according to at least one of the other claims, characterized in that the eccentric guide plates (40.1, 40.2) rotate in sealed manner by means of their outer plate sealing surfaces (52.1, 52.3) on large-volume O-ring seals (93.1, 93.2) which are inserted in the end walls of the pumping space housing.
21. Device according to at least one of the other claims, characterized in that the fluid-guiding channels are formed with a rotor inlet channel (80.1) and a rotor outlet channel (80.2) which each have an inlet opening (83.1) or outlet opening (83.2) respectively, which point in different directions, and a pumping space inlet opening (84.1) or pumping space outlet opening (84.2) respectively, which are open towards the external periphery of the rotor (55).
22. Device according to Claim 1, characterized in that the rotor, in the region of its sealing surface (677) running around the pumping space wall (32), differs from the external basic shape of the rotor (655) such that it is formed with a radius the same as the radius of the pumping space wall (Figs. 16 + 17).
23. Device according to at least one of the other claims, characterized in that two pumping units are arranged one behind the other on the same axis such that the pump (720.1) closest to the inlet contains the low-pressure part and the pump (720.2) closest to the outlet contains the high-pressure part, and the medium guiding channels (783.2; 783.1; 785) in the rotors of both pumps are formed merging into one another. (Fig. 18)
24. Device according to at least one of the other claims, characterized in that the drive shaft (23) is guided through an inlet space (28) for the pumping medium and the admission of pumping medium is effected either in annular manner or through a lateral inlet connection piece (27), while an outlet space (29) is arranged below the perpendicular drive shaft (23) of the pump (20, 20.1). (Fig. 1)

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