EP1891334B9 - Centrifugal pump - Google Patents

Centrifugal pump Download PDF

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Publication number
EP1891334B9
EP1891334B9 EP05750409A EP05750409A EP1891334B9 EP 1891334 B9 EP1891334 B9 EP 1891334B9 EP 05750409 A EP05750409 A EP 05750409A EP 05750409 A EP05750409 A EP 05750409A EP 1891334 B9 EP1891334 B9 EP 1891334B9
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EP
European Patent Office
Prior art keywords
impeller
centrifugal pump
pump according
vanes
casing
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EP05750409A
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German (de)
French (fr)
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EP1891334B1 (en
EP1891334A1 (en
Inventor
Michel Grimm
Jean-Nicolas Favre
Hagen Renger
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EGGER PUMPS Tech AG
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EGGER PUMPS Tech AG
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Priority to PL05750409T priority Critical patent/PL1891334T3/en
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Publication of EP1891334B1 publication Critical patent/EP1891334B1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2288—Rotors specially for centrifugal pumps with special measures for comminuting, mixing or separating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous
    • F04D7/045—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous with means for comminuting, mixing stirring or otherwise treating

Definitions

  • the present invention relates to a centrifugal pump for conveying liquids with solids and gas admixtures, in particular a Kanalradpumpe, according preamble of claim 1.
  • the invention has for its object to provide a centrifugal pump, in which the ability to transport gas accumulations, is significantly improved.
  • a free-flow pump comprises an impeller chamber in which an impeller is arranged, and a vortex chamber extending in front of the impeller chamber, which is provided by blades is not crossed out.
  • the liquid enters the blade channels axially near the hub from the end face of the impeller, migrates outwards on a rim of approximately 180 ° and leaves the impeller in the outer region in the axial, but reverse direction, on the front side.
  • the exiting liquid causes the fluid mass in the vortex chamber by pulse exchange in rotation.
  • Single wider blades will be like in DE 34 08 810 C2 described used to improve the coupling effect on the liquid mass in the swirl chamber. Due to the way the liquid is taken through the impeller, the widening of the blades, which is anyway to be limited, also equals that of a blade extension, measured along the flow path.
  • the per se known centrifugal pump in particular channel wheel pump, an impeller chamber, in which an impeller is arranged, but have no vortex chamber in contrast to free-flow pumps.
  • the interior of the correspondingly redesigned housing of the inventive centrifugal pump now consists of a front and one of them separated by a virtual plane rear room part.
  • the front part of the blade (s) extends while the impeller plate and the rear part of the blade (s) connected thereto are accommodated in the rear space part.
  • FIG. 1 shown is an impeller 10 of a liquid inlet 2 and output 3, respectively. enclosing a suction and outlet opening housing 1.
  • the impeller 10 is mounted on a shaft 60 driven by a motor, not shown.
  • the housing 1, the impeller 10 and the shaft 60 have a common axis of symmetry 1A.
  • the inner space 6 of the housing 1 consists of a front chamber part 5A encompassing an annular space or spiral collecting chamber 4 and a rear room part 5B separated from it by a virtual plane ⁇ T ⁇ .
  • This plane ⁇ T ⁇ roughly coincides with the plane (not shown) which contains the rear (also not referenced) generatrix of the aperture 3 and which is orthogonal to the axis of symmetry 1A.
  • the impeller 10 comprises a number of preferably curved blades 15 carrying a number of preferably curved blades 15, having a front 12 and a rear surface 13, corresponding to the size of the solids.
  • the front part 15F and the rear part 15R of the blade (s) 15 extend in the front 5A respectively.
  • the front edge 16 of the blade 15 may be in the immediate vicinity of the inner surface 7 of the housing wall portion 7A extending around the entrance.
  • the peripheral edge 17 of the front part 15F of the blades 15 can move close to the liquid outlet 3.
  • a defined depending on the design of the pump, rotationally symmetrical housing surface 8, 8A of the housing 1 preferably encloses narrow (that is in the order of a few millimeters) the impeller 11, that is, the peripheral surface 14 and the example according to flush peripheral edges 17 of the blades 15 and the rear part 15R of these blades.
  • the rotation surface 8 is cylindrical around the impeller plate 11, while the rotation surface 8A, for example, cylindrical (on the FIG. 1 this contour is indicated only in a dotted line) or may be conical with a cone angle 2 ⁇ , the angle ⁇ preferably being ⁇ (less than or equal to) 20 °.
  • the choice of impeller design, in particular the peripheral edges 17 and the peripheral surface 14, is determined as known to those skilled in the art in view of the specific speed n q .
  • the impeller plate is arranged such that its front surface is at least approximately in the virtual plane ⁇ T ⁇ , while the blades extend entirely in the impeller chamber located in front of this level ⁇ T ⁇ .
  • the surface 12 of the impeller plate 11 is offset by a distance D to the rear, ie direction drive, the blades are widened by this distance (part 15R of the blades) and the original impeller chamber 5A to another impeller chamber part 5B with the distance D corresponding volume is increased.
  • the experiments have shown that the distance D in a range of 25% to 75% of Total width of the blades should be 15, preferably at about 50% of the total width.
  • the rear surface 13 of the impeller plate 11 may be located in the immediate vicinity of the surface 9 of the rear wall 9A of the housing 1. According to a variant, however, a greater distance can be provided between the surfaces 13, 9 in order to leave room for ribs 18 (on the surface 13) or 19 (on the surface 9) attached to the one and / or other of these surfaces.
  • the ribs 18 known per se may be curved radially or, for example, in a manner similar to the blades 15 (see FIG FIG. 3 , Reference numeral 23).
  • the ribs 19 which are not known, however, are preferably radial and fulfill the function of a swirl brake, avoid a centrifuge effect and thus ensure a better gas flow.
  • FIG. 2 a second embodiment is shown, which in comparison to the first or basic embodiment described above has the same housing 1, but is provided with an over the shaft 60 driven impeller 20 whose impeller plate 21 is provided with a blade system 25.
  • This blade system consists on the one hand of at least one with the blade 15 identical or at least similar wide blade 25L, the front edge 26A can move in the immediate vicinity of the inner surface 7 of the front wall portion 7A of the housing 1, and additionally on the other hand of at least one narrower, preferably curved auxiliary blade 25S extending at least partially in the rear impeller chamber 5B.
  • This means that the leading edge 26B of this auxiliary blade 25S is in the virtual plane ⁇ T ⁇ or in close proximity to that plane ⁇ T ⁇ Area can lie.
  • the latter may be flat and parallel or oblique to the plane ⁇ T ⁇ or curved.
  • the edges 26B may be orthogonal or have a different profile to the axis of symmetry 1A, for example outwardly or inwardly (for illustrative purposes, the dotted line 26C shows a possible tapered shape of the leading edge of the auxiliary blades 25S).
  • the distance D between the front surface 22 of the impeller plate 21 and the front edge 26B corresponding to the width (or average width (determined at about half radius of the impeller blade)) of the auxiliary blades 25S is to be in a range of 25% to 75% of the total width B g of the wide blades 25L, preferably at about 50% of the stated overall width, so that the blades 25S extend substantially only in the rear impeller chamber 5B.
  • the rear surface 23 of the impeller plate 21 may be in the immediate vicinity of the surface 9 of the rear wall 9A of the housing 1 or according to a variant between these surfaces 23, 9 a greater distance may be provided in order to leave enough space for the attachment of preferably radially extending ribs 28 (on the surface 23) and ribs 29 (on the surface 9) on one and / or other of these surfaces.
  • a connected to the shaft 60 impeller 30 with axis 100A of a liquid inlet 102 and exit 103 having housing 100 is enclosed.
  • the housing 100 is similar to the housing 1 and has a front chamber 105A surrounded by a collection chamber 104 similar to the collection chamber 4 and a rear chamber 105B separated by the virtual plane ⁇ T ⁇ .
  • the impeller 30 offset rearwardly by the distance D comprises a vane system 35 connected to an impeller blade 31, which consists of at least one wide vane 35L and at least one small auxiliary vane 35S, preferably three each, as mentioned in the second embodiment.
  • the auxiliary blades 35S may be shaped similar to the auxiliary blades 25S, with only one leading edge 36B shown here.
  • the auxiliary blades 35S and the impeller plate 31 are surrounded by an outer ring 34.
  • the inner surface 34B of the ring 34 can be made conical with a cone angle of 2 ⁇ (with ⁇ preferably ⁇ 20 °).
  • the impeller plate 31, the ring 34 and the associated Auxiliary vanes 35S extend in the impeller chamber 105B.
  • the peripheral edges 37L which can be moved past in relative proximity to the liquid outlet 103, can run parallel or obliquely to the axis of symmetry 100A or else be configured differently.
  • the front edges 36A of the wide blades 35L are covered by a cover plate 40.
  • the latter is rotatably mounted in a ring 110 pressed into a sealing gap 111 in the vicinity of the inlet 102 of the housing 100.
  • the front surface 41 of the cover plate 40 can move in the immediate vicinity of the surface 107 of the wall portion 107A.
  • This cover disk which is known per se, is often provided for stability reasons or for pumps with a low specific speed n q .
  • the rear surface 33 of the impeller plate 31 may be in the immediate vicinity of the surface 109 of the rear wall 109A of the housing 100 or according to a variant between these surfaces 33, 109 a greater distance may be provided to provide sufficient space for to allow the attachment of preferably radially extending ribs 38 (on the surface 33) and ribs 39 (on the surface 109) on one and / or other of these surfaces.
  • the impeller 31 may be provided with at least one hole 45.
  • three or six holes 45 with axis 45A are distributed between the blades 35L and the auxiliary blades 35S and dimensioned accordingly.
  • the axes 45A extend at a distance R parallel to the axis 100A.
  • the dimension of the radius R is preferably selected to be approximately in an interval between one half and two thirds of the peripheral radius of the Impeller plate is located. It has been found that these holes 45 markedly improve the efficiency of escape of the gas to the outside.
  • wheels 11 and 21 according to the first and second embodiment with individual or all based FIG. 4 described additional features of the impeller 30, so outer ring 34, holes 45, cover plate 40, or provided with other features known in the art.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Reciprocating Pumps (AREA)

Abstract

An impeller plate of an impeller of a centrifugal pump, particularly a channel impeller pump, for pumping liquids with solid or gaseous admixtures, is provided with at least one wide vane that is displaced toward the impeller drive by a distance D so that the impeller chamber is enlarged by a rearward portion thereof. In addition, the impeller comprises at least one auxiliary vane having a center width at between 25%-75% of the width of the wide vane. This arrangement improves particularly the gas transporting ability of the pump.

Description

Die vorliegende Erfindung betrifft eine Kreiselpumpe zum Fördern von Flüssigkeiten mit Feststoff- und Gasbeimengungen, insbesondere eine Kanalradpumpe, gemäss Präambel des Anspruchs 1.The present invention relates to a centrifugal pump for conveying liquids with solids and gas admixtures, in particular a Kanalradpumpe, according preamble of claim 1.

Bei derartigen bekannten Pumpen sind die Querschnitte der Kanäle zwischen den Schaufeln des Laufrades so gestaltet, dass relativ grosse Festkörper passieren können. Dies bedingt, dass Kanalräder in der Regel mit nur 1 bis 3 Laufschaufeln ausgeführt werden. Kanalradpumpen werden mit gutem Erfolg zur Förderung von mit Dickstoffen, Schlamm, Schlacken, usw. beladenen Flüssigkeiten eingesetzt; ihre Fähigkeit, Gas- (inklusive Luft-) ansammlungen abzutransportieren ist jedoch, wie bei anderen Kreiselpumpen auch, eingeschränkt.In such known pumps, the cross sections of the channels between the blades of the impeller are designed so that relatively large solids can happen. This requires that channel wheels are usually run with only 1 to 3 blades. Duct wheel pumps are used with great success for pumping liquids loaded with heavy materials, sludge, slag, etc.; However, their ability to transport gas (including air) collections is limited, as with other centrifugal pumps too.

Der Erfindung liegt die Aufgabe zugrunde, eine Kreiselpumpe zu schaffen, bei der die Fähigkeit, Gasansammlungen abzutransportieren, deutlich verbessert ist.The invention has for its object to provide a centrifugal pump, in which the ability to transport gas accumulations, is significantly improved.

Kreiselpumpen bzw. Kanalradpumpen mit befriedigenden spezifischen Merkmalen zur Lösung dieses Problems sind dem Erfinder nicht bekannt.Centrifugal or Kanalradpumpen with satisfactory specific features to solve this problem are not known to the inventor.

Da diese Gattung von Pumpen wegen unterschiedlicher Funktionsweise mit Freistrompumpen nicht vergleichbar ist, sind die Massnahmen zur Änderung der Eigenschaften von der einen auf die andere in der Regel nicht übertragbar.Since this type of pumps is not comparable with free-pumping because of their different modes of operation, the measures for changing the characteristics of one to the other are generally not transferable.

Eine Freistrompumpe umfasst eine Laufradkammer, in welcher ein Laufrad angeordnet ist, und eine sich vor der Laufradkammer erstreckende Wirbelkammer, die durch Schaufeln nicht durchstrichen wird. Die Flüssigkeit tritt axial in Nabennähe von der Stirnseite des Laufrades in die Schaufelkanäle ein, wandert auf einem Sogen von annähernd 180° nach aussen und verlässt das Laufrad im äusseren Bereich wieder in axialer, jedoch umgekehrter Richtung, auf der Stirnseite. Die austretende Flüssigkeit versetzt die Flüssigkeitsmasse in der Wirbelkammer durch Impulsaustausch in Rotation. Einzelne breitere Schaufeln werden wie in DE 34 08 810 C2 beschrieben eingesetzt, um die Kupplungswirkung auf die Flüssigkeitsmasse in der Wirbelkammer zu verbessern. Aufgrund des Weges, den die Flüssigkeit durch das Laufrad nimmt, kommt die jedenfalls in grenzen zu haltende Verbreiterung der Schaufeln auch einer Schaufelverlängerung, gemessen entlang der Strombahn, gleich.A free-flow pump comprises an impeller chamber in which an impeller is arranged, and a vortex chamber extending in front of the impeller chamber, which is provided by blades is not crossed out. The liquid enters the blade channels axially near the hub from the end face of the impeller, migrates outwards on a rim of approximately 180 ° and leaves the impeller in the outer region in the axial, but reverse direction, on the front side. The exiting liquid causes the fluid mass in the vortex chamber by pulse exchange in rotation. Single wider blades will be like in DE 34 08 810 C2 described used to improve the coupling effect on the liquid mass in the swirl chamber. Due to the way the liquid is taken through the impeller, the widening of the blades, which is anyway to be limited, also equals that of a blade extension, measured along the flow path.

US-2005/0095124 und US-4,347,035 offenbaren Kanalrad- bzw. Kreiselpumpen, die für die Beförderung von mit Langfasern-Feststoffen beladenen Fluiden bestimmt und deswegen mit einer Vorrichtung zur Verkleinerung derselben vesehen sind. Diese Pumpen sind für einzufriedenstellendes Abtransportieren von Fluiden, die darüber hinaus Gasbeimengungen enthalten, nicht vorgesehen und auch nicht geeignet, weil auch bei diesen Pumpen die Laufradkammer nicht die Funktion einer Wirbelkammer ausüben können. US-2005/0095124 and US 4,347,035 disclose centrifugal pumps intended for the carriage of long fiber solids laden fluids and therefore having a device for reducing them. These pumps are not designed for satisfactory transport away fluids that also contain gas additives, and also not suitable, because even with these pumps the impeller chamber can not exercise the function of a vortex chamber.

Zusammenfassend umfassen die an sich bekannten Kreiselpumpe, insbesondere Kanalradpumpe, eine Laufradkammer, in welcher ein Laufrad angeordnet ist, weisen jedoch im Unterschied zu Freistrompumpen keine Wirbelkammer auf.In summary, the per se known centrifugal pump, in particular channel wheel pump, an impeller chamber, in which an impeller is arranged, but have no vortex chamber in contrast to free-flow pumps.

Bekanntlich steigt die Fähigkeit, Gaseinschlüsse mit der Flüssigkeit abzutransportieren, mit der Strömungsgeschwindigkeit und der Strömungsturbulenz des Mediums entlang des Weges durch die Pumpe. In anderen Worten würde also eine Erhöhung dieser Geschwindigkeit für das gestellte Problem eine auf der Hand liegende mögliche Lösung bilden. In Anbetracht der Tatsache, dass mit der Flüssigkeit Feststoffe befördert werden müsse, und den damit verbundenen Konstruktionsimperativen erweist sich der Lösungsweg mit der erhöhten Strömungsgeschwindigkeit als nicht gangbar.As is well known, the ability to carry gas pockets with the liquid increases with the flow rate and flow turbulence of the medium along the way through the pump. In other words, increasing this speed would be an obvious solution to the problem posed. Considering the fact that solids have to be carried with the liquid and the associated design imperatives, the approach with the increased flow rate proves to be unworkable.

Erst anhand zahlreicher und mannigfaltiger Versuche konnte schliesslich festgestellt werden, dass das Abfördern der Gasbeimengungen in der Flüssigkeit dank der im kennzeichnenden Teil des Anspruchs 1 angegebenen Merkmale spürbar verbessert wird. Dabei ist das gesetzte Ziel erreicht ohne Reduzieren des freien Durchgangs, was eine unumgängliche Rahmenbedingung darstellt, da ja die sich in der Flüssigkeit befindenden Feststoffe gefördert werden müssen.Only on the basis of numerous and varied experiments could finally be found that the discharge of gas admixtures in the liquid is noticeably improved thanks to the features indicated in the characterizing part of claim 1. In this case, the set goal is achieved without reducing the free passage, which is an indispensable framework condition, since the solids in the liquid must be conveyed.

Die in den abhängigen Ansprüchen definierten Merkmale stellen darauf aufbauend besonders vorteilhafte Ausführungen der Erfindung dar, da dadurch hinsichtlich der problematischen Gasförderung und schliesslich des allegemeinen Wirkungsgrades noch bessere Ergebnisse registriert werden konnten.The features defined in the dependent claims make it based on particularly advantageous embodiments of the invention, since even better results could be registered with regard to the problematic gas production and finally the general efficiency.

Insbesondere in Kreiselpumpen ablaufende Strömungsphänomene sind öfters lediglich empirisch feststellbar und mathematisch und physikalisch kaum nachvollziehbar oder überschaubar. Der Innenraum des entsprechend neu gestalteten Gehäuses der erfindungsgemässen Kreiselpumpe besteht nun aus einem vorderen und aus einem davon durch eine virtuelle Ebene getrennten hinteren Raumteil. In dem die ursprüngliche Laufradkammer bildenden vorderen Raumteil erstreckt sich der vordere Teil der Schaufel(n), während der Laufradteller und der damit verbundene hintere Teil der Schaufel(n) in dem hinteren Raumteil untergebracht sind. Es darf angenommen werden, dass dank dieser neuen Anordnung des Laufrades und der daraus folgenden Kammerdifferenzierung und -erweiterung der sich in der zwischen dem Flüssigkeitseingang und - ausgang erstreckenden vorderen Kammer bildende Zentrifugaleffekt, also die Bildung eines Flüssigkeitsringes, innerhalb welchem sich Gas ansammelt, das einen weiteren kontinuierlichen Eingang der zu fördernden Flüssigkeit verhindert, zerstört wird und vielmehr eine bestimmte Wirbelung bzw. Turbulenzen auftreten. Darüber hinaus dürfte sich infolge einer langsamen Durchströmungsgeschwindigkeit die Strömung an den Schaufelsaugseiten ablösen. Schliesslich kennzeichnet noch ein höherer Wirkungsgrad die erfindungsgemässe Pumpe im Vergleich zu bekannten Pumpen für gashaltige MedienIn particular, flow phenomena occurring in centrifugal pumps are often only empirically ascertainable and mathematically and physically hardly comprehensible or manageable. The interior of the correspondingly redesigned housing of the inventive centrifugal pump now consists of a front and one of them separated by a virtual plane rear room part. In the front space part constituting the original impeller chamber, the front part of the blade (s) extends while the impeller plate and the rear part of the blade (s) connected thereto are accommodated in the rear space part. It may be assumed that thanks to this new arrangement of the impeller and the consequent chamber differentiation and enlargement, the centrifugal effect forming in the front chamber extending between the liquid inlet and outlet, ie the formation of a liquid ring within which gas accumulates, prevents a further continuous input of the liquid to be conveyed, is destroyed and rather a certain turbulence or turbulence occur. In addition, due to a slow flow rate, the flow on the blade suction sides is likely to come off. Finally, even higher efficiency characterizes the pump according to the invention in comparison to known pumps for gas-containing media

Die Ergebnisse konnten noch dadurch verbessert werden, dass das Laufrad mit den in den Ansprüchen 2 oder 3 definierten Merkmalen ausgerüstet wird. In der Tat stossen dann die Flüssigkeitsmoleküle und die Feststoffe gegen die vorderen Kanten der Hilfsschaufel(n), wobei der durch die erzielte verbesserte Gasverteilung resultierende Vorteil den durch die von den zusätzlichen Reibungsflächen der Hilfsschaufeln erzeugten Reibungskräfte entstehenden Nachteil weit übertrifft. 'The results could be further improved by equipping the impeller with the features defined in claims 2 or 3. In fact, the liquid molecules and solids then strike against the leading edges of the auxiliary blade (s), the advantage afforded by the improved gas distribution achieved far surpassing the disadvantage caused by the frictional forces generated by the additional friction surfaces of the auxiliary blades. '

Nachstehend sind drei bevorzugt Ausführungsbeispiele der Erfindung anhand der Zeichnung näher beschrieben. Es zeigt in schematischer Darstellung:

  • Figur 1 einen Schnitt einer ersten Ausführungsform der erfindungsgemässen Kanalrad- oder Kreiselpumpe,
  • Figur 2 einen Schnitt einer zweiten Ausführungsform dieser Pumpe,
  • Figur 3 eine perspektivische Ansicht einer für die zweite Ausführungsform vorgesehenen möglichen Variante eines Laufrades mit drei Hilfsschaufeln
    und
  • Figur 4 einen Schnitt einer dritten Ausführungsform der Pumpe.
Below are three preferred embodiments of the invention described with reference to the drawings. It shows in a schematic representation:
  • FIG. 1 a section of a first embodiment of the invention Kanalrad- or centrifugal pump,
  • FIG. 2 a section of a second embodiment of this pump,
  • FIG. 3 a perspective view of a proposed embodiment of the second embodiment of an impeller with three auxiliary blades
    and
  • FIG. 4 a section of a third embodiment of the pump.

Wie in Figur 1 dargestellt ist ein Laufrad 10 von einem einen Flüssigkeitseingang 2 und -ausgang 3 resp. eine Ansaug- und Auslassöffnung aufweisenden Gehäuse 1 umschlossen. Das Laufrad 10 ist auf einer von einem nicht dargestellten Motor antreibaren Welle 60 befestigt. Das Gehäuse 1, das Laufrad 10 und die Welle 60 weisen eine gemeinsam Symmetrieachse 1A auf. Der Innenraum 6 des Gehäuses 1 besteht aus einem vorderen, eine als Ringraum oder Spirale umlaufende Sammelkammer 4 umfassenden Raumteil 5A und aus einem davon durch eine virtuelle Ebene {T} getrennten hinteren Raumteil 5B. Diese Ebene {T} überfällt in etwa mit der (ohne Bezugszeichnen versehenen) Ebenes zusammen, die die hintere (ebenfalls ohne Bezugszeichen versehene) Mantellinie der Öffnung 3 beinhaltet und orthogonal zur Symmetrieachse 1A verläuft.As in FIG. 1 shown is an impeller 10 of a liquid inlet 2 and output 3, respectively. enclosing a suction and outlet opening housing 1. The impeller 10 is mounted on a shaft 60 driven by a motor, not shown. The housing 1, the impeller 10 and the shaft 60 have a common axis of symmetry 1A. The inner space 6 of the housing 1 consists of a front chamber part 5A encompassing an annular space or spiral collecting chamber 4 and a rear room part 5B separated from it by a virtual plane {T}. This plane {T} roughly coincides with the plane (not shown) which contains the rear (also not referenced) generatrix of the aperture 3 and which is orthogonal to the axis of symmetry 1A.

Das Laufrad 10 umfasst einen eine entsprechend der Grösse der Feststoffe definierte Anzahl von vorzugsweise gewölbten Schaufeln 15 tragenden, eine vordere 12 und eine hintere Fläche 13 aufweisenden Laufradteller 11. In der Regel, wie oben gesagt, sind, es eine bis drei Schaufeln (siehe auch Figur 3). Der vordere Teil 15F und der hintere Teil 15R der Schaufel(n) 15 erstrecken sich im vorderen 5A resp. hinteren Kammerteil 5B des Gehäuses 1. Die vordere Kante 16 der Schaufel 15 kann sich in unmittelbarer Nähe der inneren Fläche 7 des sich um den Eingang erstreckenden Gehäusewandteils 7A vorbeibewegen. Dank dieser Nähe wird eine gewisse Abdichtung erzielt, da der Abstand zwischen genannter Fläche und genannter vordere Kante in der Grössenordnung von Zehntelsmillimetern beträgt und in der Regel eher kleiner als 0.5 mm ist. Die Peripheriekante 17 des vorderen Teils 15F der Schaufeln 15 kann sich nahe am Flüssigkeitsausgang 3 vorbeibewegen. Eine je nach Bauart der Pumpe definierte, rotationssymmetrische Gehäusefläche 8, 8A des Gehäuses 1 umschließt vorzugsweise eng (das heisst in der Grössenordnung einiger Millimeter) den Laufradteller 11, das heisst dessen Peripheriefläche 14 und die gemäss Beispiel damit bündigen Peripheriekanten 17 der Schaufeln 15 bzw. des hinteren Teils 15R dieser Schaufeln. Gemäss in Figur 1 dargestellter Ausführungsform ist die Rotationsfläche 8 um den Laufradteller 11 herum zylindrisch, während die Rotationsfläche 8A beispielsweise zylindrisch (auf der Figur 1 ist diese Kontur lediglich in punktierter Linie angedeutet) oder konisch mit einem Kegelwinkel 2γ sein kann, wobei der Winkel γ vorzugsweise ≤ (kleiner oder gleich) 20° ist. Die Wahl der Laufradbauart, insbesondere der Peripheriekanten 17 und der Peripheriefläche 14, wird wie dem Fachmann bekannt in Anbetracht der spezifischen Drehzahl nq festgelegt.The impeller 10 comprises a number of preferably curved blades 15 carrying a number of preferably curved blades 15, having a front 12 and a rear surface 13, corresponding to the size of the solids. As a rule, as stated above, there are one to three blades (see also FIGS FIG. 3 ). The front part 15F and the rear part 15R of the blade (s) 15 extend in the front 5A respectively. Rear chamber portion 5B of the housing 1. The front edge 16 of the blade 15 may be in the immediate vicinity of the inner surface 7 of the housing wall portion 7A extending around the entrance. Thanks to this proximity, a certain degree of sealing is achieved, since the distance between said surface and said leading edge is on the order of tenths of a millimeter and in the Usually rather less than 0.5 mm. The peripheral edge 17 of the front part 15F of the blades 15 can move close to the liquid outlet 3. A defined depending on the design of the pump, rotationally symmetrical housing surface 8, 8A of the housing 1 preferably encloses narrow (that is in the order of a few millimeters) the impeller 11, that is, the peripheral surface 14 and the example according to flush peripheral edges 17 of the blades 15 and the rear part 15R of these blades. According to FIG. 1 illustrated embodiment, the rotation surface 8 is cylindrical around the impeller plate 11, while the rotation surface 8A, for example, cylindrical (on the FIG. 1 this contour is indicated only in a dotted line) or may be conical with a cone angle 2γ, the angle γ preferably being ≤ (less than or equal to) 20 °. The choice of impeller design, in particular the peripheral edges 17 and the peripheral surface 14, is determined as known to those skilled in the art in view of the specific speed n q .

Bei den konventionellen Kreisel- oder Kanalradpumpen ist der Laufradteller derart angeordnet, dass sich dessen vordere Fläche zumindest annähernd in der virtuellen Ebene {T} befindet, während sich die Schaufeln ganz in der sich vor dieser Ebene {T} befindenden Laufradkammer erstrecken. Im Vergleich zu diesen bekannten Pumpen wird also die Fläche 12 des Laufradtellers 11 um eine Distanz D nach hinten, also Richtung Antrieb, versetzt, wobei die Schaufeln um diese Distanz verbreitert werden (Teil 15R der Schaufeln) und die ursprüngliche Laufradkammer 5A um einen weiteren Laufradkammerteil 5B mit der Distanz D entsprechendem Volumen vergrössert wird. Die Versuche haben ergeben, dass die Distanz D in einem Bereich von 25 % bis 75 % der Gesamtbreite der Schaufeln 15 liegen sollte, vorzugsweise bei ca. 50% genannter Gesamtbreite.In the conventional centrifugal or Kanalradpumpen the impeller plate is arranged such that its front surface is at least approximately in the virtual plane {T}, while the blades extend entirely in the impeller chamber located in front of this level {T}. Compared to these known pumps so the surface 12 of the impeller plate 11 is offset by a distance D to the rear, ie direction drive, the blades are widened by this distance (part 15R of the blades) and the original impeller chamber 5A to another impeller chamber part 5B with the distance D corresponding volume is increased. The experiments have shown that the distance D in a range of 25% to 75% of Total width of the blades should be 15, preferably at about 50% of the total width.

Die hintere Fläche 13 des Laufradtellers 11 kann sich in unmittelbarer Nähe der Fläche 9 der hinteren Wand 9A des Gehäuses 1 befinde. Gemäss einer Variante kann jedoch zwischen den Flächen 13, 9 einen grösseren Abstand vorgesehen werden, um Platz für an der einen und / oder anderen dieser Flächen angebrachte Rippen 18 (an der Fläche 13) bzw. 19 (an der Fläche 9) zu lassen. Die an sich bekannten Rippen 18 können radial oder zum Beispiel in ähnlicher Weise wie die Schaufeln 15 gewölbt sein (siehe Figur 3, Bezugszeichen 23). Die dagegen nicht bekannten Rippen 19 verlaufen vorzugsweise radial und erfüllen die Funktion einer Drallbremse aus, vermeiden eine Zentrifugenwirkung und gewährleisten somit einen besseren Gasfluss.The rear surface 13 of the impeller plate 11 may be located in the immediate vicinity of the surface 9 of the rear wall 9A of the housing 1. According to a variant, however, a greater distance can be provided between the surfaces 13, 9 in order to leave room for ribs 18 (on the surface 13) or 19 (on the surface 9) attached to the one and / or other of these surfaces. The ribs 18 known per se may be curved radially or, for example, in a manner similar to the blades 15 (see FIG FIG. 3 , Reference numeral 23). The ribs 19 which are not known, however, are preferably radial and fulfill the function of a swirl brake, avoid a centrifuge effect and thus ensure a better gas flow.

In Figur 2 ist eine zweite Ausführungsform dargestellt, die im Vergleich zur oben beschriebenen ersten oder Grundausführungsform dasselbe Gehäuse 1 aufweist, jedoch mit einem über die Welle 60 angetriebenes Laufrad 20 versehen ist, dessen Laufradteller 21 mit einem Schaufelsystem 25 versehen ist. Dieses Schaufelsystem besteht einerseits aus wenigstens einer mit der Schaufel 15 identischen oder zumindest ähnlichen breiten Schaufel 25L, deren vordere Kante 26A sich in unmittelbarer Nähe der inneren Fläche 7 des vorderen Wandteils 7A des Gehäuses 1 vorbeibewegen kann, und zusätzlich andererseits aus wenigstens einer schmäleren, vorzugsweise gewölbten Hilfsschaufel 25S, die sich wenigstens zum Teil in der hinteren Laufradkammer 5B erstreckt. Dies bedeutet, dass die vordere Kante 26B dieser Hilfsschaufel 25S in der virtuellen Ebene {T} oder in einer sich zu dieser Ebene {T} in unmittelbarer Nähe befindenden Fläche liegen kann. Letztere kann flach und parallel oder schräg zur Ebene {T} verlaufen oder gekrümmt sein. Mit anderen Worten können die Kanten 26B zur Symmetrieachse 1A orthogonal sein oder einen anderen Verlauf aufweisen, zum Beispiel nach außen oder innen ansteigen (zur Illustration zeigt die punktierte Linie 26C einen möglichen verjüngten Verlauf der vorderen Kante der Hilfsschaufeln 25S).In FIG. 2 a second embodiment is shown, which in comparison to the first or basic embodiment described above has the same housing 1, but is provided with an over the shaft 60 driven impeller 20 whose impeller plate 21 is provided with a blade system 25. This blade system consists on the one hand of at least one with the blade 15 identical or at least similar wide blade 25L, the front edge 26A can move in the immediate vicinity of the inner surface 7 of the front wall portion 7A of the housing 1, and additionally on the other hand of at least one narrower, preferably curved auxiliary blade 25S extending at least partially in the rear impeller chamber 5B. This means that the leading edge 26B of this auxiliary blade 25S is in the virtual plane {T} or in close proximity to that plane {T} Area can lie. The latter may be flat and parallel or oblique to the plane {T} or curved. In other words, the edges 26B may be orthogonal or have a different profile to the axis of symmetry 1A, for example outwardly or inwardly (for illustrative purposes, the dotted line 26C shows a possible tapered shape of the leading edge of the auxiliary blades 25S).

Die der Breite (oder mittleren Breite (ermittelt auf etwa halbem Radius des Laufradtellers)) der Hilfsschaufeln 25S entsprechende Distanz D zwischen der vorderen Fläche 22 des Laufradtellers 21 und der vorderen Kante 26B soll in einem Bereich von 25 % bis 75 % der Gesamtbreite Bg der breiten Schaufeln 25L liegen, vorzugsweise bei ca. 50% genannter Gesamtbreite, so dass sich die Schaufeln 25S im wesentlich nur in der hinteren Laufradkammer 5B erstrecken.The distance D between the front surface 22 of the impeller plate 21 and the front edge 26B corresponding to the width (or average width (determined at about half radius of the impeller blade)) of the auxiliary blades 25S is to be in a range of 25% to 75% of the total width B g of the wide blades 25L, preferably at about 50% of the stated overall width, so that the blades 25S extend substantially only in the rear impeller chamber 5B.

Vorzugsweise kann das Laufrad 20 dieser zweiten Ausführungsform wie in Figur 3 in Perspektive dargestellt drei breite Schaufeln 25L und drei schmälere Hilfsschaufeln 25S umfassen, wobei jeweils eine Hilfsschaufel 25S zwischen zwei Schaufeln 25L angeordnet ist.Preferably, the impeller 20 of this second embodiment as in FIG. 3 in perspective, three wide vanes 25L and three narrower auxiliary vanes 25S comprise, with one auxiliary vane 25S interposed between two vanes 25L.

Die Peripheriefläche 24 des Laufradtellers 21, die Peripheriekanten 27L der breiten Schaufeln 25L und die Peripheriekanten 27S der schmäleren Hilfsschaufeln 25S liegen auf demselben nicht dargestellten zylindrischen oder kegeligen oder andersförmigen rotationssymmetrischen Mantelfläche, wobei diese von der rotationssymmetrischen Gehäusefläche 8, 8A des Gehäuses 1 in ähnlicher Weise wie in der ersten Ausführungsform beschrieben vorzugsweise eng umschlossen sind.The peripheral surface 24 of the impeller plate 21, the peripheral edges 27L of the wide blades 25L and the peripheral edges 27S of the narrower auxiliary blades 25S lie on the same cylindrical or conical or other rotationally symmetric lateral surface, not shown, from the rotationally symmetrical housing surface 8, 8A of the housing 1 in a similar manner as described in the first embodiment are preferably tightly enclosed.

Auch hier (d. h. ähnlich wie in der ersten Ausführungsform) kann die hintere Fläche 23 des Laufradtellers 21 in unmittelbarer Nähe der Fläche 9 der hinteren Wand 9A des Gehäuses 1 liegen oder es kann gemäss einer Variante zwischen diesen Flächen 23, 9 einen grösseren Abstand vorgesehen werden, um genügend Platz für das Anbringen von vorzugsweise radial verlaufenden Rippen 28 (an der Fläche 23) bzw. Rippen 29 (an der Fläche 9) an der einen und / oder anderen dieser Flächen zu lassen.Again (ie, similar to the first embodiment), the rear surface 23 of the impeller plate 21 may be in the immediate vicinity of the surface 9 of the rear wall 9A of the housing 1 or according to a variant between these surfaces 23, 9 a greater distance may be provided in order to leave enough space for the attachment of preferably radially extending ribs 28 (on the surface 23) and ribs 29 (on the surface 9) on one and / or other of these surfaces.

Gemäss der in Figur 4 dargestellten dritten Ausführungsform ist ein mit der Welle 60 verbundenes Laufrad 30 mit Achse 100A von einem einen Flüssigkeitseingang 102 und -ausgang 103 aufweisenden Gehäuse 100 umschlossen. Das Gehäuse 100 ähnelt dem Gehäuse 1 und weist eine von einer ähnlich wie die Sammelkammer 4 ausgebildeten Sammelkammer 104 umringte vordere Kammer 105A und eine davon durch die virtuelle Ebene {T} getrennte hintere Kammer 105B auf.According to the in FIG. 4 illustrated third embodiment, a connected to the shaft 60 impeller 30 with axis 100A of a liquid inlet 102 and exit 103 having housing 100 is enclosed. The housing 100 is similar to the housing 1 and has a front chamber 105A surrounded by a collection chamber 104 similar to the collection chamber 4 and a rear chamber 105B separated by the virtual plane {T}.

Das um die Distanz D nach hinten versetzte Laufrad 30 umfasst ein mit einem Laufradteller 31 verbundenes Schaufelsystem 35, welches aus wenigstens einer breiten Schaufel 35L und wenigstens einer schmalen Hilfsschaufel 35S besteht, vorzugsweise, wie anhand der zweiten Ausführungsform erwähnt, jeweils drei davon. Die Hilfsschaufeln 35S können ähnlich wie die Hilfsschaufeln 25S geformt sein, wobei hier lediglich eine vordere Kante 36B dargestellt ist.The impeller 30 offset rearwardly by the distance D comprises a vane system 35 connected to an impeller blade 31, which consists of at least one wide vane 35L and at least one small auxiliary vane 35S, preferably three each, as mentioned in the second embodiment. The auxiliary blades 35S may be shaped similar to the auxiliary blades 25S, with only one leading edge 36B shown here.

Die Hilfsschaufeln 35S und der Laufradteller 31 sind von einem Aussenring 34 umfasst. Die innere Fläche 34B des Ringes 34 kann konisch ausgeführt werden mit einem Kegelwinkel von 2γ (mit γ vorzugsweise ≤ 20°). Der Laufradteller 31, der Ring 34 und die damit verbundenen Hilfsschaufeln 35S erstrecken sich in der Laufradkammer 105B. Die in relativer Nähe am Flüssigkeitsausgang 103 vorbeibewegbaren Peripheriekanten 37L können parallel oder schräg zur Symmetrieachse 100A verlaufen oder auch anders ausgebildet sein.The auxiliary blades 35S and the impeller plate 31 are surrounded by an outer ring 34. The inner surface 34B of the ring 34 can be made conical with a cone angle of 2γ (with γ preferably ≤20 °). The impeller plate 31, the ring 34 and the associated Auxiliary vanes 35S extend in the impeller chamber 105B. The peripheral edges 37L, which can be moved past in relative proximity to the liquid outlet 103, can run parallel or obliquely to the axis of symmetry 100A or else be configured differently.

Die vorderen Kanten 36A der breiten Schaufeln 35L sind von einer Deckscheibe 40 bedeckt. Letztere ist in einem in einem Dichtspalt 111 eingepressten Ring 110 in der Nähe des Eingangs 102 des Gehäuses 100 drehbar gelagert. Die vordere Fläche 41 der Deckscheibe 40 kann sich in unmittelbarer Nähe der Fläche 107 des Wandteils 107A vorbeibewegen. Diese an sich bekannte Deckscheibe wird oft aus Stabilitätsgründen oder bei Pumpen mit kleiner spezifischer Drehzahl nq vorgesehen.The front edges 36A of the wide blades 35L are covered by a cover plate 40. The latter is rotatably mounted in a ring 110 pressed into a sealing gap 111 in the vicinity of the inlet 102 of the housing 100. The front surface 41 of the cover plate 40 can move in the immediate vicinity of the surface 107 of the wall portion 107A. This cover disk, which is known per se, is often provided for stability reasons or for pumps with a low specific speed n q .

Ähnlich wie in der ersten Ausführungsform kann die hintere Fläche 33 des Laufradtellers 31 in unmittelbarer Nähe der Fläche 109 der hinteren Wand 109A des Gehäuses 100 liegen oder es kann gemäss einer Variante zwischen diesen Flächen 33, 109 einen grösseren Abstand vorgesehen werden, um genügend Platz für das Anbringen von vorzugsweise radial verlaufenden Rippen 38 (an der Fläche 33) bzw. Rippen 39 (an der Fläche 109) an der einen und / oder anderen dieser Flächen zu lassen.Similarly as in the first embodiment, the rear surface 33 of the impeller plate 31 may be in the immediate vicinity of the surface 109 of the rear wall 109A of the housing 100 or according to a variant between these surfaces 33, 109 a greater distance may be provided to provide sufficient space for to allow the attachment of preferably radially extending ribs 38 (on the surface 33) and ribs 39 (on the surface 109) on one and / or other of these surfaces.

Darüber hinaus kann der Laufradteller 31 mit wenigstens einem Loch 45 versehen werden. Gemäss dem Beispiel sind drei oder sechs Bohrungen 45 mit Achse 45A zwischen den Schaufeln 35L und den Hilfsschaufeln 35S verteilt und entsprechend dimensioniert.-Die Achsen 45A verlaufen mit einem Abstand R parallel zur Achse 100A. Das Mass des Radius R ist vorzugsweise so gewählt, dass es in etwa in einem Intervall zwischen der Hälfte und zwei Dritteln des Umfangsradius' des Laufradtellers liegt. Es konnte festgestellt werden, dass diese Löcher 45 die Wirksamkeit des Entweichens des Gas nach aussen merklich verbessern.In addition, the impeller 31 may be provided with at least one hole 45. According to the example, three or six holes 45 with axis 45A are distributed between the blades 35L and the auxiliary blades 35S and dimensioned accordingly. The axes 45A extend at a distance R parallel to the axis 100A. The dimension of the radius R is preferably selected to be approximately in an interval between one half and two thirds of the peripheral radius of the Impeller plate is located. It has been found that these holes 45 markedly improve the efficiency of escape of the gas to the outside.

Selbstverständlich können weitere bevorzugte Ausführungsformen realisiert werden in welchen Merkmalen der beschriebenen Ausführungsformen miteinander kombiniert werden. Insbesondere besteht die Möglichkeit, die Laufräder 11 und 21 gemäss erster und zweiter Ausführungsform mit einzelnen oder auch allen anhand Figur 4 beschriebenen zusätzlichen Merkmalen des Laufrads 30, also Aussenring 34, Bohrungen 45, Deckscheibe 40, oder mit weiteren dem Fachmann bekannten Merkmalen zu versehen.Of course, further preferred embodiments can be realized in which features of the described embodiments are combined. In particular, it is possible, the wheels 11 and 21 according to the first and second embodiment with individual or all based FIG. 4 described additional features of the impeller 30, so outer ring 34, holes 45, cover plate 40, or provided with other features known in the art.

Aus der vorstehenden Beschreibung sind dem Fachmann weitere Abwandlungen und Änderungen zugänglich, ohne den Schutzbereich der Erfindung zu verlassen, der durch die Patentansprüche definiert ist.From the foregoing description, other modifications and changes will be apparent to those skilled in the art without departing from the scope of the invention, which is defined by the claims.

Claims (15)

  1. Centrifugal pump for the pumping of liquids containing solids and gases, more particularly a channel impeller pump, comprising a casing (1; 100) having a forward respectively lateral liquid entrance (2; 102) and exit (3; 103) and therebetween an impeller chamber (5A; 105A) in which a driveable impeller is arranged that comprises an impeller plate carrying at least one vane, the vanes extending in the impeller chamber of the casing, and the forward edges of these vanes, on one hand, which are directed toward the liquid entrance, being at least partly arranged to move in immediate proximity past the inner surface (7; 107) of the casing wall portion (7A; 107A) that extends around the liquid entrance, and the peripheral edges (17), on the other hand, past the liquid exit,
    characterised in that the impeller plate (11) having a peripheral surface (14) is set back by a defined distance D and the vane(s) (15; 25L; 35L) are axially enlarged by this distance, the parts of the peripheral edges (17) of the vanes (15) that extend in the rearward impeller chamber (5B) being enclosed in a rotation-symmetrical casing surface (8, 8A) of the casing (1), whereby the original forward impeller chamber (5A; 105A) is enlarged by a rearward impeller chamber (5B; 105B) that is separated from that impeller chamber by a virtual radial plane {T} and has a volume that corresponds to the distance D in order to improve the gas transport.
  2. Centrifugal pump according to claim 1, characterised in that the impeller plate (21; 31) having a peripheral surface (24) carries at least one auxiliary vane (25S; 35S) and in that the parts of peripheral edges (27L, 27S) of the vanes (25L) and of the auxiliary vane that extend in the rearward impeller chamber (105B) are enclosed in a rotation-symmetrical casing surface.
  3. Centrifugal pump according to claim 2, characterised in that the centre width of the auxiliary vanes (25S; 35S) is equal to approx. 25 % to approx. 75 %, preferably to 50 % of the centre width of the vanes (25L; 35L).
  4. Centrifugal pump according to claim 2 or 3, characterised in that the impeller (20; 30) has three vanes (25L; 35L) and three auxiliary vanes (25S; 35S).
  5. Centrifugal pump according to any one of claims 1 to 4, characterised in that the impeller plate (11; 21; 31) is provided with at least one hole (45).
  6. Centrifugal pump according to any one of claims 1 to 5, characterised in that the inner surface (9; 109) of the rearward casing wall (9A; 109A) that is turned toward the rearward surface (13; 23; 33) of the impeller plate (11; 21; 31) is provided with preferably radially extending ridges (19; 29; 39).
  7. Centrifugal pump according to any one of claims 1 to 6, characterised in that the rearward surface (13; 23; 33) of the impeller plate (11; 21; 31) is provided with preferably curved ridges (18; 28; 38).
  8. Centrifugal pump according to any one of claims 2 to 7, characterised in that the rotation-symmetrical casing surface (8A) of the casing (1) that encloses the vanes (15; 25L) and auxiliary vanes (25) extending in the rearward impeller chamber (5B) is conically shaped with a cone angle of 2γ, where γ is preferably smaller than or equal to 20°.
  9. Centrifugal pump according to any one of claims 2 to 8, characterised in that the impeller plate (31) is provided with a ring (34) that encompasses the auxiliary vanes (35S).
  10. Centrifugal pump according to claim 9, characterised in that the external surface (34A) of the ring (34) is enclosed in a rotation-symmetrical casing surface (108) of the casing (100).
  11. Centrifugal pump according to claim 9 or 10, characterised in that the internal surface (34B) of the ring (34) is conical with a cone angle 2γ, where γ is preferably smaller than or equal to 20°.
  12. Centrifugal pump according to any one of claims 1 to 11, characterised in that the impeller comprises a forward cover disk.
  13. Centrifugal pump according to any one of claims 2 to 12, characterised in that the forward edges (26B; 26C; 36B) of the auxiliary vanes (25S; 35S) are orthogonal to the symmetry axis (1A; 100A).
  14. Centrifugal pump according to any one of claims 2 to 14, characterised in that the forward edges (26B; 26C; 36B) of the auxiliary vanes (25S; 35S) are outwardly or inwardly rising with respect to the symmetry axis (1A; 100A) or have any other shape.
  15. Centrifugal pump according to any one of claims 1 to 14, characterised in that the peripheral edges (17; 27L; 37L;) of the vane system (15; 25; 35), which are movable past the liquid exit (3; 103) in relative proximity thereto, may be parallel or inclined with respect to the symmetry axis (1A; 100A) or may be differently shaped.
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Also Published As

Publication number Publication date
US20090324402A1 (en) 2009-12-31
EP1891334B1 (en) 2009-01-14
ES2318497T3 (en) 2009-05-01
CA2611141C (en) 2013-01-22
BRPI0520297B1 (en) 2018-06-26
JP2008544132A (en) 2008-12-04
CN101208521B (en) 2011-08-31
BRPI0520297A2 (en) 2009-04-28
PL1891334T3 (en) 2009-07-31
DK1891334T3 (en) 2009-05-11
US8025478B2 (en) 2011-09-27
DE502005006506D1 (en) 2009-03-05
ATE421043T1 (en) 2009-01-15
CA2611141A1 (en) 2006-12-21
EP1891334A1 (en) 2008-02-27
WO2006133577A1 (en) 2006-12-21
JP5384103B2 (en) 2014-01-08
CN101208521A (en) 2008-06-25

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