EP1584820A1 - Mixed flow pump - Google Patents

Mixed flow pump Download PDF

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Publication number
EP1584820A1
EP1584820A1 EP04405214A EP04405214A EP1584820A1 EP 1584820 A1 EP1584820 A1 EP 1584820A1 EP 04405214 A EP04405214 A EP 04405214A EP 04405214 A EP04405214 A EP 04405214A EP 1584820 A1 EP1584820 A1 EP 1584820A1
Authority
EP
European Patent Office
Prior art keywords
vane
edge
inlet
impeller
pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP04405214A
Other languages
German (de)
French (fr)
Other versions
EP1584820B1 (en
Inventor
Martin Stähle
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Frideco AG
Original Assignee
Frideco AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to DE502004000769T priority Critical patent/DE502004000769D1/en
Application filed by Frideco AG filed Critical Frideco AG
Priority to EP04405214A priority patent/EP1584820B1/en
Priority to AT04405214T priority patent/ATE330126T1/en
Priority to DK04405214T priority patent/DK1584820T3/en
Priority to CNB2004800426761A priority patent/CN100419271C/en
Priority to JP2007506630A priority patent/JP5070039B2/en
Priority to PCT/CH2004/000664 priority patent/WO2005098237A1/en
Priority to US10/588,736 priority patent/US7510368B2/en
Priority to RU2006139075/06A priority patent/RU2358159C2/en
Publication of EP1584820A1 publication Critical patent/EP1584820A1/en
Application granted granted Critical
Publication of EP1584820B1 publication Critical patent/EP1584820B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/04—Helico-centrifugal pumps

Definitions

  • the invention relates to a fferenzentrifugalradpumpe according The preamble of claim 1.
  • the invention further relates to a Method for conveying a medium with a Screw centrifugal pump according to the preamble of Claim 9.
  • centrifugal pump comprises a single, helical extending blade, which rotatably in a pump housing is arranged.
  • This pump is particularly suitable for pumping with solid admixtures permeated liquids, in particular for the promotion of waste water with long-fiber Ingredients.
  • the invention is based on the object To provide screw Centrifugalradpumpe which when conveying with solid admixtures interspersed liquids more advantageous Features.
  • Screw centrifugal pump comprising a pump housing with an inlet opening and a within the pump housing arranged impeller, which has a spiral running Having inlet blade edge, wherein in the region of Inlet opening projecting into the interior of the impeller Guide vane is arranged.
  • the guide vane the screw centrifugal wheel pump on a vane edge which in the direction of rotation of the impeller increasingly in Flow direction in the interior against the center of the Impeller protrudes.
  • the screw centrifugal pump according to the invention is especially advantageous in promoting higher concentration of fibrous solids prone to plait. Will the fibrous Stranded solids concentration is always higher, this leads to the suction line to a bale formation and increased friction in the impeller channel. If it reaches a certain limit, so The hydraulic forces alone are no longer sufficient for the material which has the consequence that the Screw centrifugal pump clogged and blocked.
  • the Screw centrifugal pump according to the invention prevents this Block by the spiral entry edge of the blade Schneckenradterrorisms against the fixed, protruding vane rotates, wherein the inlet blade edge and the vane cooperate in such a way that the Intermediate solid masses through the rotating Entry blade edge are detected and along the flow direction the inlet blade edge are loosened and / or pressed.
  • vane and Screw centrifugal wheel is added to the pumped medium to the hydraulic forces still a mechanical, im essentially acting in the direction of conveying force, what a Accumulation of solid components prevented in the conveying path.
  • these two Space curves preferably so mutually adapted running are designed that this when rotating the impeller under mutually short distance or touching each other move past each other.
  • Which is between the two Space curves located solids are mechanically in Course of the space curves, and thus essentially in Flow direction moves, and thereby loosened or in Flow direction pressed.
  • the Guide vane edge and / or the inlet blade edge at least partially on a cutting edge, so that the solids between the also mechanically moving space curves be crushed.
  • This is a crushing or dicing of the braids or fibers, which is a Attachment of the braids prevented in the conveyor and thus one continuous, reliable operation of the Screw centrifugal pump guaranteed without interruption.
  • the mutual shear, separation or clamping effect of the two Space curves also allow, depending on the design of the Guide vane edge and / or the inlet vane edge, a Cutting, crushing or weakening fibrous Solids like paper, strings, wood or solids like Plastic, rubber, metal or glass.
  • the screw centrifugal pump 1 comprises a fferenzentrifugalrad 2, which about a rotational axis 2d in Direction of rotation 4a is rotatably disposed in a pump housing 3.
  • the fferenzentrifugalrad 2 has a spiral running Entry blade edge 2a and 2c on an outer contour.
  • the fferenzentrifugalrad 2 is fixed to a pump shaft 4 connected.
  • the pump housing 3 comprises a Saugkonusgepuruseteil 3a, a spiral housing part 3b, a Inlet opening 3c and an outlet opening 3d. In the field of Inlet opening 3 c is a in the interior of the pump housing 3rd and in the interior of the lusterenzentrifugalrades.
  • FIG. 2 shows a direction designated by A in FIG Front view of the inlet opening 3 c, wherein in the interior of the pump. 1 the impeller 2 and the vane 5 can be seen. At the impeller 2 is the spiraling inlet blade edge 2a visible, which falls off against the axis of rotation 2d and axially into this grows. The foremost portion of the entrance blade edge 2a is not directly visible because of the vane 5 and therefore shown in dashed lines.
  • the guide vane 5 is designed in such a way that the vane edge 5a in the direction of rotation 4a increasingly in the direction the axis of rotation 2d, both in the radial and in the axial direction, in the interior of the impeller 2 protrudes.
  • the vane edge 5a forms a solid space curve, whereas the inlet blade edge 2a forms a rotatable about the wheel axis 2d space curve.
  • These two Room curves 2a, 5a are in the illustrated embodiment such mutually adapted designed that the Vane edge 5a a vane edge portion 5b and the Entry blade edge 2a a blade edge portion 2b within which the vane edge 5a and the Inlet blade edge 2a depending on the respective position of the Impeller 2 have a mutually small distance or yourself touching each other.
  • the mutually small distance can for example, have a value between 0.1 and 30 mm.
  • Position with mutually least distance is the point P1 on the blade edge portion 2b and the P2 on the Guide vane edge portion 5b shown.
  • the vane 5 can in many different ways such Pump housing 3 are arranged and configured that the fixed vane edge 5a and the rotating Ingress blade edge 2a cooperate such that solids by the mutual cooperation of the edges 2a, 5a mechanically conveyed, in particular in the flow direction S.
  • the blade edge section 2b in FIG Point P1 has a tangent T1 and the vane edge portion 5b at point P2 has a tangent T2, these two tangents T1, T2 as viewed from the inlet opening 3c of a viewed Have cut angle ⁇ .
  • This angle ⁇ is at least 10 Degrees, and is preferably between 30 degrees and 150 degrees, in particular between 60 degrees and 120 degrees.
  • the angle ⁇ is preferably never smaller than the angle at which sliding the solid on the inlet blade edge 2a or between Entry blade edge 2a and vane edge 5a no longer is guaranteed.
  • Figures 3 and 4 show in two detail views, analogous to Representation according to Figure 2, two different running Space curves or inlet blade edge 2a and vane edge 5a, wherein the enclosed angle ⁇ of the tangents T1, T2 of the Points P1, P2 in Figure 3 about 110 degrees and in Figure 4 about 90 degrees is.
  • This angle ⁇ is determined by the course of the space curves 2a, 5a determined, and thus in the construction of the fferenzentrifugalradpumpe 1 are selected accordingly.
  • the Course of the space curves 2a, 5a can be chosen such that the Angle ⁇ during movement of points P1, P2 in direction Q2 remains substantially constant.
  • Space curves 2a, 5a By running accordingly Space curves 2a, 5a, the angle ⁇ during the movement of the Points P1, P2 also increase and / or decrease in direction Q2.
  • At least part of the Blade edge portion 2b and / or the Leitschaufelkantenabiteses 5b as edge, cutting edge or Blade designed to a solid, which is located between the Sections 2b, 5b is to weaken or sever.
  • the screw centrifugal pump corresponding to those expected solids and admixtures thereby optimized be that the edge portions 2b, 5b and their angle ⁇ appropriately optimized to clog the pump to prevent and, for example, a good To achieve pump efficiency.
  • FIG. 5 shows a further exemplary embodiment of a fferenzentrifugalradpumpe 1, in whose inlet opening 3c a wear-resistant sleeve 7 is arranged, which with the guide vane. 5 is firmly connected. With a fastening means, not shown the sleeve 7 can be firmly connected to the pump housing 3.
  • the sleeve 7 and thus the Guide vane 5 in the direction of R movable has the particular advantage that the distance between inlet blade edge 2a and vane edge 5a, in particular the distance of the points P1, P2 in the direction of R or Q1 is adjustable.
  • the inlet blade edge 2a and / or the Vane edge 5a wears off during operation of the pump, so that the distance of points P1, P2 during operation with increased in time.
  • the sleeve 7 thus enables the position of Guide vane 5 in the direction of displacement R or Q 1 after certain To reset time intervals again.
  • the sleeve 7 can also be like this be configured that this also in the inlet opening 3c rotatable, i. with respect to the wheel axle 2d is rotatable about the sleeve 7 to rotate in the dissolved state, and thus the position of the To rotate the vane 5.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Centrifugal Separators (AREA)

Abstract

Screw centrifuge wheel pump (1) comprises a guide blade (5) arranged in the region of an inlet opening (3c) and protruding into the inner chamber of the running wheel (2). The guide blade has an edge (5a) which protrudes into the inner chamber of the running wheel in the rotary direction (4a) increasing in the direction of the axis of rotation. The running wheel and the guide blade are structured so that a part of the solid mixture flows along an inlet blade edge (2a). An independent claim is also included for a process for conveying a liquid with solid additives. Preferred Features: The guide blade slides in the direction of the axis of rotation.

Description

Die Erfindung betrifft eine Schraubenzentrifugalradpumpe gemäss dem Oberbegriff von Anspruch 1. Die Erfindung betrifft weiter ein Verfahren zum Fördern eines Mediums mit einer Schraubenzentrifugalradpumpe gemäss dem Oberbegriff von Anspruch 9.The invention relates to a Schraubenzentrifugalradpumpe according The preamble of claim 1. The invention further relates to a Method for conveying a medium with a Screw centrifugal pump according to the preamble of Claim 9.

Aus der Druckschrift CH 394814 ist eine Schraubenzentrifugalradpumpe, auch als Schneckenradpumpe bezeichnet, bekannt. Eine derartige Kreiselpumpe umfasst eine einzige, schraubenförmig verlaufende Schaufel, welche drehbar in einem Pumpengehäuse angeordnet ist. Diese Pumpe ist insbesondere zur Förderung von mit festen Beimengungen durchsetzten Flüssigkeiten geeignet, insbesondere zur Förderung von Schmutzwasser mit langfaserigen Bestandteilen.From the document CH 394814 is a screw centrifugal, Also known as worm gear known. A such centrifugal pump comprises a single, helical extending blade, which rotatably in a pump housing is arranged. This pump is particularly suitable for pumping with solid admixtures permeated liquids, in particular for the promotion of waste water with long-fiber Ingredients.

Die Fördermöglichkeit von Flüssigkeiten mit hoher Konzentration an faserigen, beispielsweise zur Zopfbildung neigenden Feststoffen ist begrenzt. Dies kann Anlagerungen fester Bestandteile im Förderweg oder eine dadurch hervorgerufene Verstopfung bis hin zum Pumpenstillstand zur Folge haben. The possibility of conveying liquids with high concentration fibrous, for example, prone to plait solids limited. This can accumulate solid constituents in the conveying path or a constipation caused thereby up to Pump standstill result.

Der Erfindung liegt die Aufgabe zugrunde, eine Schraubenzentrifugalradpumpe zu schaffen, die beim Fördern von mit festen Beimengungen durchsetzten Flüssigkeiten vorteilhaftere Eigenschaften aufweist.The invention is based on the object To provide screw Centrifugalradpumpe which when conveying with solid admixtures interspersed liquids more advantageous Features.

Diese Aufgabe wird gelöst mit einer Schraubenzentrifugalradpumpe aufweisend die Merkmale von Anspruch 1. Die Unteransprüche 2 bis 8 betreffen weitere, vorteilhafte Ausgestaltungen. Die Aufgabe wird weiter gelöst mit einem Verfahren aufweisend die Merkmale von Anspruch 9.This problem is solved with a screw centrifugal pump having the features of claim 1. The dependent claims 2 to 8 relate to further advantageous embodiments. The task becomes further solved with a method comprising the features of Claim 9.

Die Aufgabe wird insbesondere gelöst mit einer Schraubenzentrifugalradpumpe umfassend ein Pumpengehäuse mit einer Eintrittsöffnung sowie ein innerhalb des Pumpengehäuses angeordnetes Laufrad, welches eine spiralförmig verlaufende Eintrittsschaufelkante aufweist, wobei im Bereich der Eintrittsöffnung eine in den Innenraum des Laufrades vorstehende Leitschaufel angeordnet ist.The problem is solved in particular with a Screw centrifugal pump comprising a pump housing with an inlet opening and a within the pump housing arranged impeller, which has a spiral running Having inlet blade edge, wherein in the region of Inlet opening projecting into the interior of the impeller Guide vane is arranged.

In einer besonders vorteilhaften Ausgestaltung weist die Leitschaufel der Schraubenzentrifugalradpumpe eine Leitschaufelkante auf, welche in Drehrichtung des Laufrades zunehmend in Strömungsrichtung in den Innenraum gegen das Zentrum des Laufrades vorsteht.In a particularly advantageous embodiment, the guide vane the screw centrifugal wheel pump on a vane edge, which in the direction of rotation of the impeller increasingly in Flow direction in the interior against the center of the Impeller protrudes.

Die erfindungsgemässe Schraubenzentrifugalradpumpe ist insbesondere vorteilhaft beim Fördern höherer Konzentration von faserigen zu Zopfbildung neigenden Feststoffen. Wird die faserige angeschwemmte Feststoffkonzentration immer höher, so führt dies in der Saugleitung zu einer Ballenbildung und einer erhöhten Reibung im Laufradkanal. Wird dabei ein gewisser Grenzwert erreicht, so genügen die hydraulischen Kräfte alleine nicht mehr um das Material zu fördern, was zur Folge hat, dass die Schraubenzentrifugalradpumpe verstopft und blockiert. Die erfindungsgemässe Schraubenzentrifugalradpumpe verhindert dieses Blockieren indem sich die spiralförmige Eintrittsschaufelkante des Schneckenradanfangs gegenüber der fest angeordneten, vorstehenden Leitschaufel dreht, wobei die Eintrittsschaufelkante und die Leitschaufel derart zusammenwirken, dass die sich dazwischen befindlichen Feststoffmassen durch die rotierende Eintrittsschaufelkante erfasst werden und in Flussrichtung entlang der Eintrittsschaufelkante aufgelockert und/oder gepresst werden. Durch dieses Zusammenwirken von Leitschaufel und Schraubenzentrifugalrad wird auf das geförderte Medium zusätzlich zu den hydraulischen Kräften noch eine mechanische, im wesentlichen in Förderrichtung wirkende Kraft ausgeübt, was eine Anlagerung fester Bestandteile im Förderweg verhindert.The screw centrifugal pump according to the invention is especially advantageous in promoting higher concentration of fibrous solids prone to plait. Will the fibrous Stranded solids concentration is always higher, this leads to the suction line to a bale formation and increased friction in the impeller channel. If it reaches a certain limit, so The hydraulic forces alone are no longer sufficient for the material which has the consequence that the Screw centrifugal pump clogged and blocked. The Screw centrifugal pump according to the invention prevents this Block by the spiral entry edge of the blade Schneckenradanfangs against the fixed, protruding vane rotates, wherein the inlet blade edge and the vane cooperate in such a way that the Intermediate solid masses through the rotating Entry blade edge are detected and along the flow direction the inlet blade edge are loosened and / or pressed. Through this interaction of vane and Screw centrifugal wheel is added to the pumped medium to the hydraulic forces still a mechanical, im essentially acting in the direction of conveying force, what a Accumulation of solid components prevented in the conveying path.

In einer weiteren vorteilhaften Ausgestaltung bildet die Leitschaufelkante eine feste Raumkurve und die Eintrittsschaufelkante eine auf Grund des rotierbaren Schraubenzentrifugalrades rotierbare Raumkurve, wobei diese beiden Raumkurven vorzugsweise derart gegenseitig angepasst verlaufend ausgestaltet sind, dass sich diese beim Rotieren des Laufrades unter gegenseitig geringem Abstand oder sich gegenseitig berührend aneinander vorbei bewegen. Die sich zwischen den beiden Raumkurven befindlichen Feststoffe werden dabei mechanisch in Verlaufsrichtung der Raumkurven, und dadurch im wesentlichen in Strömungsrichtung bewegt, und dabei aufgelockert oder in Strömungsrichtung gepresst. In a further advantageous embodiment forms the Vane edge a solid space curve and the Entrance blade edge one due to the rotatable Screw centrifugal wheel rotatable space curve, these two Space curves preferably so mutually adapted running are designed that this when rotating the impeller under mutually short distance or touching each other move past each other. Which is between the two Space curves located solids are mechanically in Course of the space curves, and thus essentially in Flow direction moves, and thereby loosened or in Flow direction pressed.

In einer weiteren vorteilhaften Ausgestaltung weisen die Leitschaufelkante und/oder die Eintrittsschaufelkante zumindest teilweise eine Schneidkante auf, sodass die Feststoffe zwischen den sich gegenseitig bewegenden Raumkurven zudem noch mechanisch zerkleinert werden. Bei zu Zopfbildung neigenden Feststoffen bewirkt dies ein Zerkleinern oder Zertrennen der Zöpfe bzw. Fasern, was eine Anlagerung der Zöpfe im Förderweg verhindert und somit einen kontinuierlichen, zuverlässigen Betrieb der Schraubenzentrifugalradpumpe ohne Unterbruch gewährleistet.In a further advantageous embodiment, the Guide vane edge and / or the inlet blade edge at least partially on a cutting edge, so that the solids between the also mechanically moving space curves be crushed. In case of tendency to plait solids causes This is a crushing or dicing of the braids or fibers, which is a Attachment of the braids prevented in the conveyor and thus one continuous, reliable operation of the Screw centrifugal pump guaranteed without interruption.

Die gegenseitige Scher-, Trenn- oder Klemmwirkung der beiden Raumkurven ermöglich auch, abhängig von der Ausgestaltung der Leitschaufelkante und/oder der Eintrittsschaufelkante, ein Durchtrennen, Zerkleinern oder Schwächen von faserförmigen Feststoffen wie Papier, Schnüren, Holz oder Feststoffen wie Kunststoff, Gummi, Metall oder Glas.The mutual shear, separation or clamping effect of the two Space curves also allow, depending on the design of the Guide vane edge and / or the inlet vane edge, a Cutting, crushing or weakening fibrous Solids like paper, strings, wood or solids like Plastic, rubber, metal or glass.

Die Erfindung wird nachfolgend an Hand von Ausführungsbeispielen im Detail beschrieben. Es zeigen:

Figur 1
einen Axialschnitt durch eine Schraubenzentrifugalradpumpe;
Figur 2
eine Frontansicht der Eintrittsöffnung der Schraubenzentrifugalradpumpe;
Figur 3 und 4
zwei unterschiedliche Gesamtwinkel von Eintrittsschaufelkante und Leitschaufelkante;
Figur 5
eine verschiebbar angeordnete Leitschaufel.
The invention will be described below with reference to exemplary embodiments in detail. Show it:
FIG. 1
an axial section through a Schraubenzentrifugalradpumpe;
FIG. 2
a front view of the inlet opening of the Schraubenzentrifugalradpumpe;
FIGS. 3 and 4
two different total angles of entrance blade edge and vane edge;
FIG. 5
a slidably disposed vane.

Die Schraubenzentrifugalradpumpe 1 gemäss Figur 1 umfasst ein Schraubenzentrifugalrad 2, welches um eine Drehachse 2d in Drehrichtung 4a drehbar in einem Pumpengehäuse 3 angeordnet ist. Das Schraubenzentrifugalrad 2 weist eine spiralförmig verlaufende Eintrittsschaufelkante 2a sowie eine Aussenkontur 2c auf. Das Schraubenzentrifugalrad 2 ist mit einer Pumpenwelle 4 fest verbunden. Das Pumpengehäuse 3 umfasst ein Saugkonusgehäuseteil 3a, ein Spiralgehäuseteil 3b, eine Eintrittsöffnung 3c sowie eine Austrittsöffnung 3d. Im Bereich der Eintrittsöffnung 3c ist eine in den Innenraum des Pumpengehäuses 3 sowie in den Innenraum des Schraubenzentrifugalrades 2 vorstehende Leitschaufel 5 mit Leitschaufelkante 5a fest angeordnet. Unter "Innenraum des Laufrades 2" wird im vorliegenden Dokument der Innenraum verstanden, welcher bei rotierendem Schraubenzentrifugalrad 2 von der Aussenkontur 2c umgrenzt wird, sodass sich die Leitschaufel 5 zumindest teilweise in diesen Innenraum erstreckt, und das Schraubenzentrifugalrad 2, wie in Figur 1 dargestellt, im Bereich von dessen Spitze bzw. maximal innerhalb des Schraubenradanteils 6a die Leitschaufel 5 aussen umkreist. Die Schraubenzentrifugalradpumpe 1 umfasst zudem einen Schraubenradanteil 6a sowie einen Zentrifugalradanteil 6b. Das mit der Pumpe 1 geförderte Medium strömt in Strömungsrichtung S.The screw centrifugal pump 1 according to FIG. 1 comprises a Schraubenzentrifugalrad 2, which about a rotational axis 2d in Direction of rotation 4a is rotatably disposed in a pump housing 3. The Schraubenzentrifugalrad 2 has a spiral running Entry blade edge 2a and 2c on an outer contour. The Schraubenzentrifugalrad 2 is fixed to a pump shaft 4 connected. The pump housing 3 comprises a Saugkonusgehäuseteil 3a, a spiral housing part 3b, a Inlet opening 3c and an outlet opening 3d. In the field of Inlet opening 3 c is a in the interior of the pump housing 3rd and in the interior of the Schraubenzentrifugalrades. 2 projecting vane 5 with vane edge 5a fixed. Under "Interior of the impeller 2" is in the present document the interior understood, which in rotating Schraubenzentrifugalrad 2 is bounded by the outer contour 2c, so that the vane 5 at least partially in this Inner space extends, and the Schraubenzentrifugalrad 2, as in Figure 1 shown, in the region of the peak or maximum within the helical gear portion 6a, the vane 5 outside orbits. The Schraubenzentrifugalradpumpe 1 also includes a Schraubradanteil 6a and a Zentrifugalradanteil 6b. The pumped with the pump 1 medium flows in Flow direction S.

Figur 2 zeigt aus der in Figur 1 mit A bezeichneten Richtung eine Frontansicht der Eintrittsöffnung 3c, wobei im Innern der Pumpe 1 das Laufrad 2 sowie die Leitschaufel 5 erkennbar ist. Beim Laufrad 2 ist die spiralförmig verlaufende Eintrittsschaufelkante 2a ersichtlich, welche gegen die Drehachse 2d hin abfällt und axial in diese hineinwächst. Der vorderste Abschnitt der Eintrittsschaufelkante 2a ist wegen der Leitschaufel 5 nicht direkt sichtbar und deshalb strichliert dargestellt.FIG. 2 shows a direction designated by A in FIG Front view of the inlet opening 3 c, wherein in the interior of the pump. 1 the impeller 2 and the vane 5 can be seen. At the impeller 2 is the spiraling inlet blade edge 2a visible, which falls off against the axis of rotation 2d and axially into this grows. The foremost portion of the entrance blade edge 2a is not directly visible because of the vane 5 and therefore shown in dashed lines.

In den Figuren 1 und 2 ist die Leitschaufel 5 derart ausgestaltet, dass die Leitschaufelkante 5a in Drehrichtung 4a zunehmend in Richtung der Drehachse 2d, sowohl in radialer als auch in axialer Richtung, in den Innenraum des Laufrades 2 vorsteht. Die Leitschaufelkante 5a bildet eine feste Raumkurve, wogegen die Eintrittsschaufelkante 2a eine um die Radachse 2d rotierbare Raumkurve bildet. Diese beiden Raumkurven 2a,5a sind im dargestellten Ausführungsbeispiel derart gegenseitig angepasst verlaufend ausgestaltet, dass die Leitschaufelkante 5a einen Leitschaufelkantenabschnitt 5b und die Eintrittsschaufelkante 2a einen Schaufelkantenabschnitt 2b aufweist, innerhalb welchen die Leitschaufelkante 5a und die Eintrittsschaufelkante 2a abhängig von der jeweiligen Stellung des Laufrades 2 einen gegenseitig geringen Abstand aufweisen oder sich gegenseitig berühren. Der gegenseitig geringe Abstand kann beispielsweise einen Wert zwischen 0,1 und 30 mm aufweisen. Diese Stellung mit gegenseitig geringstem Abstand ist mit dem Punkt P1 auf dem Schaufelkantenabschnitt 2b sowie dem P2 auf den Leitschaufelkantenabschnitt 5b dargestellt. Auf Grund der Rotation des Laufrades 2 in Drehrichtung 4a bewegen sich die Punkt P1, P2 in der in Figur 1 dargestellten Ansicht im wesentlichen in Richtung Q1 der Drehachse 2d, und in der in Figur 2 dargestellten Ansicht im wesentlichen in Richtung Q2, welche dem Verlauf der Leitschaufelkante 5a entspricht. Dadurch wird ein sich zwischen dem Schaufelkantenabschnitt 2b und dem Leitschaufelkantenabschnitt 5b befindlicher Feststoff mechanisch im wesentlichen in Richtung Q1 beziehungsweise in Strömungsrichtung S gefördert.In FIGS. 1 and 2, the guide vane 5 is designed in such a way that the vane edge 5a in the direction of rotation 4a increasingly in the direction the axis of rotation 2d, both in the radial and in the axial direction, in the interior of the impeller 2 protrudes. The vane edge 5a forms a solid space curve, whereas the inlet blade edge 2a forms a rotatable about the wheel axis 2d space curve. These two Room curves 2a, 5a are in the illustrated embodiment such mutually adapted designed that the Vane edge 5a a vane edge portion 5b and the Entry blade edge 2a a blade edge portion 2b within which the vane edge 5a and the Inlet blade edge 2a depending on the respective position of the Impeller 2 have a mutually small distance or yourself touching each other. The mutually small distance can for example, have a value between 0.1 and 30 mm. These Position with mutually least distance is the point P1 on the blade edge portion 2b and the P2 on the Guide vane edge portion 5b shown. Due to the rotation of the impeller 2 in the direction of rotation 4a move the point P1, P2 in the view shown in Figure 1 substantially in the direction Q1 the rotation axis 2d, and in the view shown in Figure 2 in the essential in the direction of Q2, which the course of Guide blade edge 5a corresponds. This will be a between the Blade edge portion 2b and the vane edge portion 5b is located substantially mechanically in the direction Q1 or conveyed in the flow direction S.

Die Leitschaufel 5 kann auf unterschiedlichste Weise derart im Pumpengehäuse 3 angeordnet und ausgestaltet sein, dass die feststehende Leitschaufelkante 5a und die rotierende Eintrittsschaufelkante 2a derart zusammenwirken, dass Feststoffe durch das gegenseitige Zusammenwirken der Kanten 2a, 5a mechanisch gefördert werden, insbesondere in Strömungsrichtung S.The vane 5 can in many different ways such Pump housing 3 are arranged and configured that the fixed vane edge 5a and the rotating Ingress blade edge 2a cooperate such that solids by the mutual cooperation of the edges 2a, 5a mechanically conveyed, in particular in the flow direction S.

Wie aus Figur 2 ersichtlich weist der Schaufelkantenabschnitt 2b im Punkt P1 eine Tangente T1 auf und der Leitschaufelkantenabschnitt 5b im Punkt P2 eine Tangente T2 auf, wobei diese beiden Tangenten T1,T2 wie dargestellt von der Eintrittsöffnung 3c aus betrachtet einen Schnittwinkel α aufweisen. Dieser Winkel α beträgt zumindest 10 Grad, und liegt vorzugsweise zwischen 30 Grad und 150 Grad, insbesondere zwischen 60 Grad und 120 Grad. Der Winkel α ist vorzugweise nie kleiner als derjenige Winkel, bei welchem ein Gleiten des Feststoffes auf der Eintrittsschaufelkante 2a bzw. zwischen Eintrittsschaufelkante 2a und Leitschaufelkante 5a nicht mehr gewährleistet ist.As can be seen from FIG. 2, the blade edge section 2b in FIG Point P1 has a tangent T1 and the vane edge portion 5b at point P2 has a tangent T2, these two tangents T1, T2 as viewed from the inlet opening 3c of a viewed Have cut angle α. This angle α is at least 10 Degrees, and is preferably between 30 degrees and 150 degrees, in particular between 60 degrees and 120 degrees. The angle α is preferably never smaller than the angle at which sliding the solid on the inlet blade edge 2a or between Entry blade edge 2a and vane edge 5a no longer is guaranteed.

Die Figuren 3 und 4 zeigen in zwei Detailansichten, analog zur Darstellung gemäss Figur 2, zwei unterschiedlich verlaufende Raumkurven bzw. Eintrittsschaufelkante 2a und Leitschaufelkante 5a, wobei der umschlossene Winkel α der TangentenT1, T2 der Punkte P1,P2 in Figur 3 etwa 110 Grad und in Figur 4 etwa 90 Grad beträgt. Dieser Winkel α ist durch den Verlauf der Raumkurven 2a, 5a bestimmt, und kann somit bei der Konstruktion der Schraubenzentrifugalradpumpe 1 entsprechend gewählt werden. Der Verlauf der Raumkurven 2a,5a kann derart gewählt werden, dass der Winkel α während der Bewegung der Punkte P1,P2 in Richtung Q2 im wesentlichen konstant bleibt. Durch entsprechend verlaufende Raumkurven 2a,5a kann der Winkel α während der Bewegung der Punkte P1, P2 in Richtung Q2 auch zu- und/oder abnehmen.Figures 3 and 4 show in two detail views, analogous to Representation according to Figure 2, two different running Space curves or inlet blade edge 2a and vane edge 5a, wherein the enclosed angle α of the tangents T1, T2 of the Points P1, P2 in Figure 3 about 110 degrees and in Figure 4 about 90 degrees is. This angle α is determined by the course of the space curves 2a, 5a determined, and thus in the construction of the Schraubenzentrifugalradpumpe 1 are selected accordingly. The Course of the space curves 2a, 5a can be chosen such that the Angle α during movement of points P1, P2 in direction Q2 remains substantially constant. By running accordingly Space curves 2a, 5a, the angle α during the movement of the Points P1, P2 also increase and / or decrease in direction Q2.

In einer vorteilhaften Ausgestaltung ist zumindest ein Teil des Schaufelkantenabschnittes 2b und/oder des Leitschaufelkantenabschnittes 5b als Kante, Schneidkante oder Klinge ausgestaltet, um einen Feststoff, welcher sich zwischen den Abschnitten 2b,5b befindet, zu schwächen oder zu durchtrennen.In an advantageous embodiment, at least part of the Blade edge portion 2b and / or the Leitschaufelkantenabschnittes 5b as edge, cutting edge or Blade designed to a solid, which is located between the Sections 2b, 5b is to weaken or sever.

Generell gilt, je grösser der Winkel α gewählt ist, desto mehr wird ein Feststoff entlang der Kantenabschnitte 2b,5b geschoben, beziehungsweise je kleiner der Winkel α gewählt wird, desto eher wird ein Feststoff durch die Kantenabschnitte 2b, 5b zertrennt. Zusätzlich kann durch eine entsprechende Formgebung auch die Länge der wirksamen Kantenabschnitte 2b, 5b bestimmt werden. Somit kann die Schraubenzentrifugalradpumpe entsprechend den zu erwartenden Feststoffen und Beimengungen dadurch optimiert werden, dass die Kantenabschnitte 2b, 5b und deren Winkel α entsprechend optimiert gewählt wird, um ein Verstopfen der Pumpe zu verhindern und beispielsweise zudem einen guten Pumpenwirkungsgrad zu erzielen.In general, the greater the angle α is chosen, the more one becomes Solid pushed along the edge portions 2b, 5b, or the smaller the angle α is chosen, the sooner it will be a solid by the edge portions 2b, 5b divided. additionally can by appropriate shaping also the length of the effective edge portions 2b, 5b are determined. Thus, can the screw centrifugal pump corresponding to those expected solids and admixtures thereby optimized be that the edge portions 2b, 5b and their angle α appropriately optimized to clog the pump to prevent and, for example, a good To achieve pump efficiency.

Figur 5 zeigt ein weiteres Ausführungbeispiel einer Schraubenzentrifugalradpumpe 1, in deren Eintrittsöffnung 3c eine verschleissfeste Hülse 7 angeordnet ist, welche mit der Leitschaufel 5 fest verbunden ist. Mit einem nicht dargestellten Befestigungsmittel kann die Hülse 7 fest mit dem Pumpengehäuse 3 verbunden werden. FIG. 5 shows a further exemplary embodiment of a Schraubenzentrifugalradpumpe 1, in whose inlet opening 3c a wear-resistant sleeve 7 is arranged, which with the guide vane. 5 is firmly connected. With a fastening means, not shown the sleeve 7 can be firmly connected to the pump housing 3.

Bei gelöstem Befestigungsmittel ist die Hülse 7 und damit auch die Leitschaufel 5 in Bewegungsrichtung R verschiebbar. Diese Anordnung weist insbesondere den Vorteil auf, dass die Distanz zwischen Eintrittsschaufelkante 2a und Leitschaufelkante 5a, insbesondere der Abstand der Punkte P1,P2 in Richtung R bzw. Q1 einstellbar ist. Die Eintrittsschaufelkante 2a und/oder die Leitschaufelkante 5a nutzt sich während dem Betrieb der Pumpe ab, sodass sich der Abstand der Punkte P1,P2 während dem Betrieb mit der Zeit vergrössert. Die Hülse 7 ermöglicht somit die Lage der Leitschaufel 5 in Verschiebungsrichtung R bzw. Q 1 nach gewissen Zeitabständen wieder neu einzustellen. Die Hülse 7 kann auch derart ausgestaltet sein, dass diese zudem in der Eintrittsöffnung 3c rotierbar, d.h. bezüglich der Radachse 2d rotierbar ist, um die Hülse 7 im gelösten Zustand zu rotieren, und damit auch die Lage der Leitschaufel 5 zu rotieren.When dissolved fastener, the sleeve 7 and thus the Guide vane 5 in the direction of R movable. These Arrangement has the particular advantage that the distance between inlet blade edge 2a and vane edge 5a, in particular the distance of the points P1, P2 in the direction of R or Q1 is adjustable. The inlet blade edge 2a and / or the Vane edge 5a wears off during operation of the pump, so that the distance of points P1, P2 during operation with increased in time. The sleeve 7 thus enables the position of Guide vane 5 in the direction of displacement R or Q 1 after certain To reset time intervals again. The sleeve 7 can also be like this be configured that this also in the inlet opening 3c rotatable, i. with respect to the wheel axle 2d is rotatable about the sleeve 7 to rotate in the dissolved state, and thus the position of the To rotate the vane 5.

Claims (10)

Schraubenzentrifugalradpumpe (1) umfassend ein Pumpengehäuse (3) mit einer Eintrittsöffnung (3c) sowie ein innerhalb des Pumpengehäuses (3) um eine Drehachse (2d) in Drehrichtung (4a) drehbar angeordnetes Laufrad (2), welches eine spiralförmig verlaufende Eintrittsschaufelkante (2a) aufweist, dadurch gekennzeichnet, dass im Bereich der Eintrittsöffnung (3c) eine in den Innenraum des Laufrades (2) vorstehende Leitschaufel (5) angeordnet ist.Screw centrifugal wheel pump (1) comprising a pump housing (3) with an inlet opening (3c) and an impeller (2) rotatably arranged within the pump housing (3) about a rotation axis (2d) in the direction of rotation (4a) and having a spiral inlet blade edge (2a). characterized in that in the region of the inlet opening (3c) in the interior of the impeller (2) projecting vane (5) is arranged. Schraubenzentrifugalradpumpe (1) nach Anspruch 1, dadurch gekennzeichnet, dass die Leitschaufel (5) in Richtung der Drehachse (2d) verschiebbar und fixierbar gelagert ist.Schraubenzentrifugalradpumpe (1) according to claim 1, characterized in that the guide vane (5) is mounted displaceably and fixable in the direction of the axis of rotation (2d). Schraubenzentrifugalradpumpe (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Leitschaufel (5) eine Leitschaufelkante (5a) aufweist, welche in Drehrichtung (4a) zunehmend in Richtung der Drehachse (2d) in den Innenraum des Laufrades (2) vorsteht.Screw centrifugal wheel pump (1) according to one of the preceding claims, characterized in that the guide vane (5) has a vane edge (5a) which projects in the direction of rotation (4a) increasingly in the direction of the axis of rotation (2d) in the interior of the impeller (2). Schraubenzentrifugalradpumpe (1) nach Anspruch 3, dadurch gekennzeichnet, dass die Leitschaufelkante (5a) eine feste Raumkurve bildet, dass die Eintrittsschaufelkante (2a) eine rotierbare Raumkurve bildet, und dass diese beiden Raumkurven derart gegenseitig angepasst verlaufend ausgestaltet sind, dass die Leitschaufelkante (5a) einen Leitschaufelkantenabschnitt (5b) und die Eintrittsschaufelkante (2a) einen Schaufelkantenabschnitt (2b) aufweist, innerhalb welchen die Leitschaufelkante (5a) und die Eintrittsschaufelkante (2a) abhängig von der Lage des Laufrades (2) einen gegenseitig geringen Abstand aufweisen oder sich gegenseitig berühren.Screw centrifugal wheel pump (1) according to claim 3, characterized in that the vane edge (5a) forms a solid space curve, that the inlet vane edge (2a) forms a rotatable space curve, and that these two space curves are designed to be mutually adapted such that the vane edge (5a ) has a vane edge portion (5b) and the entry vane edge (2a) has a vane edge portion (2b) within which the vane edge (5a) and the entry vane edge (2a) are mutually spaced or in contact with each other depending on the position of the impeller (2) , Schraubenzentrifugalradpumpe (1) nach Anspruch 4, dadurch gekennzeichnet, dass sich sowohl innerhalb des Schaufelkantenabschnittes (2b) als auch innerhalb des Leitschaufelkantenabschnittes (5b) je ein Punkt (P1, P2) ergibt, welche den geringsten gegenseitigen Abstand zwischen Schaufelkantenabschnitt (2b) und Leitschaufelkantenabschnitt (5b) aufweisen, wobei sich diese Punkte (P1,P2) beim Drehen des Laufrades (2) in Strömungsrichtung (S) bewegen.Screw centrifugal pump (1) according to claim 4, characterized in that both within the blade edge portion (2b) and within the vane edge portion (5b) each result in a point (P1, P2) having the smallest mutual distance between blade edge portion (2b) and vane edge portion (5b), wherein these points (P1, P2) move during rotation of the impeller (2) in the flow direction (S). Schraubenzentrifugalradpumpe (1) nach Anspruch 5, dadurch gekennzeichnet, dass der Schaufelkantenabschnitt (2b) im Punkt (P1) eine Tangente (T1) aufweist, dass der Leitschaufelkantenabschnitt (5b) im Punkt (P2) eine Tangente (T2) aufweist, und dass diese beiden Tangenten (T1,T2) von der Eintrittsöffnung (3c) aus betrachtet einen Schnittwinkel (α) von zumindest 10 Grad bilden.Screw centrifugal pump (1) according to claim 5, characterized in that the blade edge portion (2b) at the point (P1) has a tangent (T1), that the Leitschaufelkantenabschnitt (5b) at the point (P2) has a tangent (T2), and that both tangents (T1, T2) viewed from the inlet opening (3c) form a cutting angle (α) of at least 10 degrees. Schraubenzentrifugalradpumpe (1) nach Anspruch 6, dadurch gekennzeichnet, dass der Schnittwinkel (α) zwischen 30 Grad und weniger als 180 Grad liegt, insbesondere zwischen 60 Grad und 120 Grad. Schraubenzentrifugalradpumpe (1) according to claim 6, characterized in that the intersection angle (α) is between 30 degrees and less than 180 degrees, in particular between 60 degrees and 120 degrees. Schraubenzentrifugalradpumpe (1) nach einem der Ansprüche 4 bis 7, dadurch gekennzeichnet, dass der Schaufelkantenabschnitt (2b) und/oder der Leitschaufelkantenabschnitt (5b) zumindest teilweise als Schneidkante ausgebildet ist.Schraubenzentrifugalradpumpe (1) according to one of claims 4 to 7, characterized in that the blade edge portion (2b) and / or the Leitschaufelkantenabschnitt (5b) is at least partially formed as a cutting edge. Verfahren zum Fördern einer mit festen Beimengungen durchsetzten Flüssigkeit mittels einer Schraubenzentrifugalradpumpe (1), dadurch gekennzeichnet, dass die Flüssigkeit mit Hilfe einer Leitschaufel (5) derart der Eintrittsschaufelkante (2a) eines sich drehenden Laufrades (2) zugeleitet wird, dass zumindest ein Teil der festen Beimengungen der Eintrittsschaufelkante (2a) entlang gleitet.Method for conveying a liquid infiltrated by solid admixtures by means of a screw-centrifugal centrifugal pump (1), characterized in that the liquid is fed by means of a guide vane (5) to the inlet vane edge (2a) of a rotating impeller (2) such that at least a part of the slides along the inlet blade edge (2a). Verfahren nach Anspruch 9, dadurch gekennzeichnet, dass eine Leitschaufelkante (5a) der Leitschaufel (5) und die Eintrittsschaufelkante (2a) bei sich drehendem Laufrad (2) derart gegenseitig zusammenwirken, dass die sich zwischen Eintrittsschaufelkante (2a) und Leitschaufelkante (5a) befindliche feste Beimengung durch die Schaufelkanten (2a,5a) mechanisch zerkleinert und/oder in Strömungsrichtung (S) geschoben wird.A method according to claim 9, characterized in that a vane edge (5a) of the vane (5) and the inlet vane edge (2a) cooperate with each other as the impeller (2) rotates so that located between the inlet vane edge (2a) and vane edge (5a) solid admixture by the blade edges (2a, 5a) mechanically comminuted and / or pushed in the flow direction (S).
EP04405214A 2004-04-07 2004-04-07 Mixed flow pump Expired - Lifetime EP1584820B1 (en)

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Application Number Priority Date Filing Date Title
EP04405214A EP1584820B1 (en) 2004-04-07 2004-04-07 Mixed flow pump
AT04405214T ATE330126T1 (en) 2004-04-07 2004-04-07 SCREW CENTRIFUGAL WHEEL PUMP
DK04405214T DK1584820T3 (en) 2004-04-07 2004-04-07 screw-centrifugal pump
DE502004000769T DE502004000769D1 (en) 2004-04-07 2004-04-07 Screw-centrifugal pump
CNB2004800426761A CN100419271C (en) 2004-04-07 2004-11-02 Screw-centrifugal pump
JP2007506630A JP5070039B2 (en) 2004-04-07 2004-11-02 Screw centrifugal pump and method for transporting liquid filled with solid additives using screw centrifugal pump
PCT/CH2004/000664 WO2005098237A1 (en) 2004-04-07 2004-11-02 Screw-centrifugal pump
US10/588,736 US7510368B2 (en) 2004-04-07 2004-11-02 Screw-centrifugal pump
RU2006139075/06A RU2358159C2 (en) 2004-04-07 2004-11-02 Screw centrifugal pump

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JP (1) JP5070039B2 (en)
CN (1) CN100419271C (en)
AT (1) ATE330126T1 (en)
DE (1) DE502004000769D1 (en)
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Publication number Priority date Publication date Assignee Title
EP2169234A2 (en) * 2007-07-17 2010-03-31 Gerardus Augustinus Maria Manshanden Sinking pump safe for fish
EP2908012A3 (en) * 2014-01-24 2015-12-30 McFinn Technologies Radial impeller and casing for centrifugal pump
US10094384B2 (en) 2014-01-24 2018-10-09 Mcfinn Technologies, Llc Radial impeller and casing for centrifugal pump

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ATE330126T1 (en) 2006-07-15
JP2007532812A (en) 2007-11-15
WO2005098237A1 (en) 2005-10-20
EP1584820B1 (en) 2006-06-14
JP5070039B2 (en) 2012-11-07
CN100419271C (en) 2008-09-17
DK1584820T3 (en) 2006-07-31
RU2358159C2 (en) 2009-06-10
RU2006139075A (en) 2008-05-20
US20070172345A1 (en) 2007-07-26
US7510368B2 (en) 2009-03-31
CN1926338A (en) 2007-03-07
DE502004000769D1 (en) 2006-07-27

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