EP0237868A2 - Radial or axial flow centrifugal pump - Google Patents

Radial or axial flow centrifugal pump Download PDF

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Publication number
EP0237868A2
EP0237868A2 EP87103057A EP87103057A EP0237868A2 EP 0237868 A2 EP0237868 A2 EP 0237868A2 EP 87103057 A EP87103057 A EP 87103057A EP 87103057 A EP87103057 A EP 87103057A EP 0237868 A2 EP0237868 A2 EP 0237868A2
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EP
European Patent Office
Prior art keywords
impeller
pump
centrifugal pump
auxiliary
pump according
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Granted
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EP87103057A
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German (de)
French (fr)
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EP0237868A3 (en
EP0237868B1 (en
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Ernst Hauenstein
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Individual
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Priority to AT87103057T priority Critical patent/ATE60411T1/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
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
    • F04D13/027—Details of the magnetic circuit
    • 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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • F04D29/0416—Axial thrust balancing balancing pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/40—Transmission of power
    • F05B2260/404—Transmission of power through magnetic drive coupling
    • F05B2260/4041—Transmission of power through magnetic drive coupling the driven magnets encircling the driver magnets

Definitions

  • the present invention relates to a radial centrifugal pump, the working side of which is completely tightly separated from the drive side by a canned pot, in which, in addition, the pump impeller, which is mounted on a shaft between two axial end stops, is driven via a magnetic coupling acting through the wall of the canned pot and is in operation the impeller act axial thrust, caused by different pressure ratios on the impeller front and impeller rear, means being provided to compensate for these thrust forces.
  • Centrifugal pumps of this type are generally known. Their field of application is very wide, but due to the lack of seals, it is mainly in the field of chemistry, where particularly toxic or otherwise aggressive liquids have to be pumped.
  • centrifugal pumps in the form of so-called canned motor pumps or magnetic coupling pumps was the collection and balancing of the hydraulic forces inside the pump, in particular the thrust forces acting on the pump wheel.
  • the previously known solutions were unsatisfactory in the sense that complex constructions were required, which were also associated with relatively high energy losses (friction losses, efficiency reductions). This is all the more regrettable, since today's materials have made it possible to build the actual drive system more compactly and thus to keep the outer dimensions small.
  • the purpose of the present invention was to find in radial or axial centrifugal pumps of the type described at the outset a structurally simple solution for compensating for the axial thrust acting on the impeller, which further simplifies the actual pump construction and helps to reduce the internal forces that previously occurred that in particular the canned tube can be made with a further reduced wall thickness, which in turn can improve the overall efficiency.
  • the solution to this problem is characterized according to the invention in that the actual pump impeller, on its front side, i.e. on the side facing the suction, the delivery channels are provided, an auxiliary delivery wheel is assigned, which serves to reduce the pressure in the room or the rooms on the rear of the impeller.
  • the spaces on the rear of the impeller usually consist of a so-called hub space and an inner and outer drive space.
  • the latter two spaces are separated from one another by the flange of the carrier of one magnetic coupling part, which flange-like protrudes from the rear of the impeller.
  • control means preferably in the form of control slots or channels, are preferably provided on the pump housing, specifically in relation to the periphery of the delivery channels of the auxiliary delivery wheel, so that the medium conveyed by the auxiliary delivery wheel from the space behind the impeller as a function of the to promote the pressure conditions prevailing on the front or rear of the impeller into the pressure chamber of the pump.
  • the auxiliary conveyor wheel is preferably arranged or formed on the rear side of the actual pump impeller, for example directly on the rear wall of the pump impeller.
  • the conveying channels of the auxiliary conveying wheel are preferably designed such that they communicate with one or more of the spaces on the rear of the impeller. For example, a number of separate conveying channels of the auxiliary conveying wheel can be assigned to each of the spaces to be relieved. Depending on the magnitude of the thrust forces that arise in each case, the output of the delivery channels of the auxiliary feed wheel is more or less covered by the control means, caused by an oscillating axial displacement of the pump impeller, which ensures permanent automatic thrust compensation.
  • thrust compensation enables impellers with open or closed blading to be used as desired.
  • the bearing journal or the support shaft for the impeller can e.g. be integrated into the end face of the containment shell, or, in the case of larger embodiments, be supported in a suitable manner in the intake manifold.
  • pumps of any desired type can be built without complex control channels.
  • the rooms on the rear of the impeller can also be rinsed with cleaning fluid with little effort.
  • only a supply line for cleaning fluid into the rear hub space is required, from which certain delivery channels of the auxiliary feed wheel lead the rinsing fluid into the outer drive space.
  • the flushing liquid could also be supplied directly to the outer drive compartment.
  • the construction according to the invention is particularly suitable for pumps in which the driven part is designed as an external rotor, since on the one hand modern materials allow the construction of rotors with a low mass and on the other hand practically no friction losses occur. Nevertheless, the inevitable gaps can be made very narrow, since the risk of clogging is greatly reduced in the construction according to the invention.
  • Fig. L of the drawing shows purely schematically a radial centrifugal pump with magnetic coupling in section, wherein in the lower half of the picture a variant of the upper half of the picture is shown both with respect to the canned pot and the impeller. However, the variants have no influence on the basic structure of the pump.
  • the pump essentially consists of a housing 1 with intake port 2, a bearing pin 3 arranged in the example shown in the intake port 2 (which in the lower variant is also formed in one piece with the canned pot bottom) for a pump impeller 4 and one for the working side (pump side) completely sealed from the drive side (motor side) separating canned pot 5. Also shown is internal magnetic rotor 6 of a drive motor, not shown, the housing of which is flanged to the pump housing 1.
  • the bearing journal 3 for the pump impeller 4 is seated in a hub cover 3 ⁇ , which is supported and fastened in the intake flange 2 via supports 7, 8.
  • the medium to be conveyed reaches the pressure chamber 8 via the suction port 2 and the pump impeller 4 (in the example shown a closed impeller) and from there into the pressure line (not shown).
  • the impeller 4 with closed blades 4 ⁇ is overhung on the bearing journal 3, it being able to move freely between the stops 9 and 10 under the axial thrust forces that occur. As will be shown, the impeller does not come to rest against the stops 9, 10, which essentially serve to position the wheel.
  • This ring flange l2 divides the pump-side drive space l3, which is located on the rear side of the impeller 4, into an outer and an inner space A or B. Also on the impeller rear side is a so-called hub space C.
  • the core of the present invention now lies in this pressure or thrust compensation:
  • the pressure acting on the impeller from rooms A, B and C is greater than the pressure on the suction or front side of the impeller 4, so that the impeller would be pressed in the suction direction without special precautions. However, this should be avoided.
  • auxiliary conveyor wheel 4 which usually consists of one piece with the actual pump impeller 4, the pressure on the back of the impeller is now reduced and the axial movement of the impeller 4 in the direction of the intake is thereby stopped. So that there is no opposite movement of the impeller 4, i.e. a shift in the direction of the drive side, the delivery rate of the auxiliary conveyor wheel 4 ⁇ is controlled:
  • one or more bores 17 are preferably provided between the pressure space 8 of the pump and the drive space A.
  • the auxiliary conveyor wheel 4 ⁇ can be designed such that from the different rooms A, B and C inlet openings 18, l9 and 20, respectively, to the individual delivery channels l6 of the auxiliary conveyor wheel 4 ⁇ are provided, with a different design that for each room A, B and C a number of separate delivery channels (e.g. 2l for room C in the lower variant) are provided.
  • a mixed construction is also conceivable.
  • a rinsing liquid can be conveyed into the space C via a line 22 and a bore 23 in the journal 3 in order to from there to be promoted via the delivery channels 2l of the auxiliary feed wheel 4 ⁇ not in the pressure chamber 8 of the pump, but in room A (and from here in room B). Excellent cleaning of the pump can thus be carried out in a simple manner.
  • a rinsing or cleaning liquid could, however, also be introduced directly into space A, for example via an inlet 24.
  • FIGS. 2 and 3 show purely schematically how the control of the delivery rate of the auxiliary feed wheel 4 ⁇ via control slots on the housing, relative to the feed channels of the auxiliary feed wheel.
  • the delivery channels are covered and the pressure in room A will increase
  • Fig. 3 shows the situation with delivery channels open via the control slots, in which the pressure in room A decreases.
  • Fig. 4 finally shows a purely schematic plan view of the rear of the impeller, i.e. on the auxiliary feed wheel, with different inlet openings in the feed channels.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
  • Cyclones (AREA)
  • Non-Positive Displacement Air Blowers (AREA)

Abstract

A centrifugal pump of the magneto coupling type in which an isolation shell separates the pump side from the driver side includes an auxiliary impeller arranged additionally to the pump impeller proper. This allows a decreasing of the pressure in the spaces at the reverse side of the pump impeller and thus a balancing of the thrust forces. This effect can be controlled by control means located in the casing at the outer end of the feeding channels of the auxiliary impeller. This allows the provision of a pump of a simple design in which e.g. the isolation shell can be made with an extremely small wall thickness and in which an open or closed pump impeller can be supported without any thrust generated difficulties.

Description

Die vorliegende Erfindung betrifft eine Radialkreiselpumpe, deren Arbeitsseite von der Antriebs­seite durch einen Spaltrohrtopf vollständig dicht getrennt ist, bei welcher zudem der Antrieb des zwischen zwei axialen Endanschlägen fliegend auf einer Welle gelagerten Pumpenlaufrades über eine durch die Wand des Spaltrohr­topfes wirkende Magnetkupplung erfolgt und im Betrieb auf das Laufrad axiale Schubkräfte einwirken, hervorgeru­fen durch unterschiedliche Druckverhältnisse auf der Laufradvorderseite und Laufradrückseite, wobei Mittel vorgesehen sind, um diese Schubkräfte auszugleichen.The present invention relates to a radial centrifugal pump, the working side of which is completely tightly separated from the drive side by a canned pot, in which, in addition, the pump impeller, which is mounted on a shaft between two axial end stops, is driven via a magnetic coupling acting through the wall of the canned pot and is in operation the impeller act axial thrust, caused by different pressure ratios on the impeller front and impeller rear, means being provided to compensate for these thrust forces.

Derartige Kreiselpumpen sind allgemein bekannt. Ihr Anwendungsgebiet ist sehr breit, liegt jedoch wegen des Fehlens von Dichtungen hauptsächlich auf dem Gebiet der Chemie, wo besonders giftige bzw. anderweitig ag­gressive Flüssigkeit zu fördern sind.Centrifugal pumps of this type are generally known. Their field of application is very wide, but due to the lack of seals, it is mainly in the field of chemistry, where particularly toxic or otherwise aggressive liquids have to be pumped.

Das Problem bei den bekannten Kreiselpumpen in Form von sog. Spaltrohrmotor-Pumpen oder Magnetkupp­lungspumpen bestand im Auffangen und Ausgleichen der hydraulischen Kräfte im Pumpeninnern, insbesondere der auf das Pumpenrad wirkenden Schubkräfte. Die bisher bekannten Lösungen waren in dem Sinne unbefriedigend, als aufwendige Konstruktionen erforderlich waren, welche zudem mit relativ hohen Energieverlusten behaftet waren (Reibungsverluste, Wirkungsgradminderungen). Dies ist umso bedauerlicher, als es mit den heutigen Materialien möglich geworden ist, das eigentliche Antriebssystem immer gedrungener zu bauen und damit die äusseren Abmessun­gen gering zu halten.The problem with the known centrifugal pumps in the form of so-called canned motor pumps or magnetic coupling pumps was the collection and balancing of the hydraulic forces inside the pump, in particular the thrust forces acting on the pump wheel. The previously known solutions were unsatisfactory in the sense that complex constructions were required, which were also associated with relatively high energy losses (friction losses, efficiency reductions). This is all the more regrettable, since today's materials have made it possible to build the actual drive system more compactly and thus to keep the outer dimensions small.

Zweck der vorliegenden Erfindung war es nun, bei Radial- oder Axialkreiselpumpen der eingangs be­schriebenen Art eine konstruktiv einfache Lösung für den Ausgleich des auf das Laufrad einwirkenden Axialschubes zu finden, welche eine weitere Vereinfachung der eigent­lichen Pumpenkonstruktion ermöglicht und die früher auftretenden inneren Kräfte soweit verringern hilft, dass insbesondere das Spaltrohr mit noch weiter reduzierter Wandstärke ausgeführt werden kann, womit wiederum der Gesamtwirkungsgrad verbessert werden kann.The purpose of the present invention was to find in radial or axial centrifugal pumps of the type described at the outset a structurally simple solution for compensating for the axial thrust acting on the impeller, which further simplifies the actual pump construction and helps to reduce the internal forces that previously occurred that in particular the canned tube can be made with a further reduced wall thickness, which in turn can improve the overall efficiency.

Die Lösung dieser Aufgabe zeichnet sich erfin­dungsgemäss dadurch aus, dass dem eigentlichen Pumpenlauf­rad, auf dessen Vorderseite, d.h. der dem Ansaug zuge­wandten Seite die Förderkanäle vorgesehen sind, ein Hilfsförderrad zugeordnet ist, welches dem Druckabbau im Raum bzw. den Räumen auf der Laufradrückseite dient.The solution to this problem is characterized according to the invention in that the actual pump impeller, on its front side, i.e. on the side facing the suction, the delivery channels are provided, an auxiliary delivery wheel is assigned, which serves to reduce the pressure in the room or the rooms on the rear of the impeller.

Die laufradrückseitigen Räume bestehen üblicher­weise aus einem sog. Nabenraum und einem inneren und äusseren Antriebsraum. Die letztgenannten beiden Räume werden von dem von der Laufradrückseite flanschförmig wegragenden Träger des einen Magnetkupplungsteils vonein­ander getrennt. Zwischen dem Spalttopf und den rotierenden Teilen des Laufrades sind Spalte vorhanden, über welche die genannten Räume miteinander in Verbindung stehen.The spaces on the rear of the impeller usually consist of a so-called hub space and an inner and outer drive space. The latter two spaces are separated from one another by the flange of the carrier of one magnetic coupling part, which flange-like protrudes from the rear of the impeller. There are gaps between the containment shell and the rotating parts of the impeller, via which the spaces mentioned are connected to one another.

Damit der Schubausgleich optimal erfolgen kann, sind vorzugsweise am Pumpengehäuse, und zwar gegenüber der Peripherie der Förderkanäle des Hilfsförder­rades Steuermittel, vorzugsweise in Form von Steuer­schlitzen bzw. -kanälen vorgesehen, um das vom Hilfsförder­rad aus dem Raum hinter dem Laufrad geförderten Medium in Abhängigkeit der auf der Laufradvorderseite bzw. -rückseite herrschenden Druckverhältnisse in den Druckraum der Pumpe zu fördern.So that the thrust compensation can take place optimally, control means, preferably in the form of control slots or channels, are preferably provided on the pump housing, specifically in relation to the periphery of the delivery channels of the auxiliary delivery wheel, so that the medium conveyed by the auxiliary delivery wheel from the space behind the impeller as a function of the to promote the pressure conditions prevailing on the front or rear of the impeller into the pressure chamber of the pump.

Vorzugsweise ist das Hilfsförderrad auf der Rückseite des eigentlichen Pumpenlaufrades, und zwar beispielsweise direkt auf der Rückwand des Pumpenlaufrades angeordnet bzw. ausgebildet.The auxiliary conveyor wheel is preferably arranged or formed on the rear side of the actual pump impeller, for example directly on the rear wall of the pump impeller.

Die Förderkanäle des Hilfsförderrades sind vorzugsweise derart ausgebildet, dass diese mit einem oder mehreren der Räume auf der Laufradrückseite kommuni­zieren. Beispielsweise können jedem der zu entlastenden Räume eine Anzahl eigene Förderkanäle des Hilfsförderrades zugeordnet sein. Je nach Grösse der sich jeweils einstel­lenden Schubkräfte ist der Ausgang der Förderkanäle des Hilfsförderrades durch die Steuermittel mehr oder weniger abgedeckt, hervorgerufen durch eine pendelnde axiale Verschiebung des Pumpenlaufrades, was einen dauernden automatischen Schubausgleich gewährleistet.The conveying channels of the auxiliary conveying wheel are preferably designed such that they communicate with one or more of the spaces on the rear of the impeller. For example, a number of separate conveying channels of the auxiliary conveying wheel can be assigned to each of the spaces to be relieved. Depending on the magnitude of the thrust forces that arise in each case, the output of the delivery channels of the auxiliary feed wheel is more or less covered by the control means, caused by an oscillating axial displacement of the pump impeller, which ensures permanent automatic thrust compensation.

Die erfindungsgemässe Ausgestaltung des sog. Schubausgleiches ermöglicht nach Wahl Laufräder mit offener oder geschlossener Beschaufelung einzusetzen.The design according to the invention of the so-called thrust compensation enables impellers with open or closed blading to be used as desired.

Der Lagerzapfen bzw. die Tragwelle für das Laufrad kann z.B. in die Stirnseite des Spalttopfes integriert sein, oder bei grösseren Ausführungsformen, im Ansaugstutzen auf geeignete Weise abgestützt sein.The bearing journal or the support shaft for the impeller can e.g. be integrated into the end face of the containment shell, or, in the case of larger embodiments, be supported in a suitable manner in the intake manifold.

Mit der erfindungsgemässen Lösung können Pumpen jeder gewünschten Bauart ohne aufwendige Steuerka­näle gebaut werden. Mit geringem Aufwand können zudem die Räume auf der Laufradrückseite mit Reinigungsflüssig­keit gespült werden. Zu diesem Zweck ist lediglich eine Zuleitung für Reinigungsflüssigkeit in den rückseiti­gen Nabenraum erforderlich, aus welchem gewisse Förder­kanäle des Hilfsförderrades die Spülflüssigkeit in den äusseren Antriebsraum leiten. Selbstverständlich könnte die Spülflüssigkeit auch direkt dem äusseren Antriebsraum zugeführt werden.With the solution according to the invention, pumps of any desired type can be built without complex control channels. The rooms on the rear of the impeller can also be rinsed with cleaning fluid with little effort. For this purpose, only a supply line for cleaning fluid into the rear hub space is required, from which certain delivery channels of the auxiliary feed wheel lead the rinsing fluid into the outer drive space. Of course, the flushing liquid could also be supplied directly to the outer drive compartment.

Die erfindungsgemässe Konstruktion eignet sich besonders für Pumpen, bei denen der getriebene Teil als Aussenrotor ausgebildet ist, da einerseits moderne Materialien den Bau von Rotoren mit geringer Masse zulassen und andererseits praktisch keine Reibver­luste auftreten. Trotzdem können die unvermeidlichen Spalten sehr eng gestaltet werden, da bei der erfindungs­gemässen Konstruktion die Verstopfungsgefahr stark reduziert ist.The construction according to the invention is particularly suitable for pumps in which the driven part is designed as an external rotor, since on the one hand modern materials allow the construction of rotors with a low mass and on the other hand practically no friction losses occur. Nevertheless, the inevitable gaps can be made very narrow, since the risk of clogging is greatly reduced in the construction according to the invention.

Die Erfindung wird nachstehend anhand von in der Zeichnung dargestellten Ausführungsbeispielen noch etwas näher erläutert. Es zeigt:

  • Fig. l einen rein schematischen Schnitt durch eine Radialkreiselpumpe nach der Erfindung, wobei oberhalb und unterhalb der Längsachse zwei verschiedene Varianten gezeigt sind;
  • Fig. 2 und 3 rein schematisch die Steuerung der Fördermenge des Hilfsförderrades, und
  • Fig. 4 eine schematische Draufsicht auf das Hilfsförderrad.
The invention is explained in more detail below with reference to exemplary embodiments shown in the drawing. It shows:
  • 1 shows a purely schematic section through a radial centrifugal pump according to the invention, two different variants being shown above and below the longitudinal axis;
  • 2 and 3 purely schematically the control of the delivery rate of the auxiliary feed wheel, and
  • Fig. 4 is a schematic plan view of the auxiliary feed wheel.

Fig. l der Zeichnung zeigt rein schematisch eine Radialkreiselpumpe mit Magnetkupplung im Schnitt, wobei in der unteren Bildhälfte eine Variante zur oberen Bildhälfte sowohl bezüglich des Spaltrohrtopfes wie auch des Laufrades gezeigt ist. Die Varianten haben jedoch keinen Einfluss auf den grundsätzlichen Aufbau der Pumpe.Fig. L of the drawing shows purely schematically a radial centrifugal pump with magnetic coupling in section, wherein in the lower half of the picture a variant of the upper half of the picture is shown both with respect to the canned pot and the impeller. However, the variants have no influence on the basic structure of the pump.

Die Pumpe besteht im wesentlichen aus einem Gehäuse l mit Ansaugstutzen 2, einem beim gezeigten Beispiel im Ansaugstutzen 2 angeordneten Lagerzapfen 3 (welcher bei der unteren Variante zudem mit dem Spalt­rohrtopfboden einstückig ausgebildet ist) für ein Pumpen­laufrad 4 und einem die Arbeitsseite (Pumpenseite) vollständig dicht von der Antriebsseite (Motorseite) trennenden Spaltrohrtopf 5. Gezeigt ist ferner der innenliegende Magnetrotor 6 eines nicht dargestellten Antriebsmotors, dessen Gehäuse an das Pumpengehäuse l angeflanscht wird.The pump essentially consists of a housing 1 with intake port 2, a bearing pin 3 arranged in the example shown in the intake port 2 (which in the lower variant is also formed in one piece with the canned pot bottom) for a pump impeller 4 and one for the working side (pump side) completely sealed from the drive side (motor side) separating canned pot 5. Also shown is internal magnetic rotor 6 of a drive motor, not shown, the housing of which is flanged to the pump housing 1.

Der Lagerzapfen 3 für das Pumpenlaufrad 4 sitzt in einer Nabenverkleidung 3ʹ, welche über Träger 7,8 im Ansaugflansch 2 abgestützt und befestigt ist. Das zu fördernde Medium gelangt über den Ansaugstutzen 2 und das Pumpenlaufrad 4 (beim gezeigten Beispiel ein geschlossenes Laufrad) in den Druckraum 8 und von dort in die Druckleitung (nicht dargestellt).The bearing journal 3 for the pump impeller 4 is seated in a hub cover 3ʹ, which is supported and fastened in the intake flange 2 via supports 7, 8. The medium to be conveyed reaches the pressure chamber 8 via the suction port 2 and the pump impeller 4 (in the example shown a closed impeller) and from there into the pressure line (not shown).

Das Laufrad 4 mit geschlossener Beschaufelung 4ʹ ist fliegend auf dem Lagerzapfen 3 gelagert, wobei es sich unter den auftretenden Axialschubkräften axial zwischen den Anschlägen 9 und l0 frei bewegen kann. Wie noch gezeigt wird, kommt das Laufrad allerdings nicht zur Anlage an den Anschlägen 9,l0, welche im wesentlichen der Positionierung des Rades dienen.The impeller 4 with closed blades 4ʹ is overhung on the bearing journal 3, it being able to move freely between the stops 9 and 10 under the axial thrust forces that occur. As will be shown, the impeller does not come to rest against the stops 9, 10, which essentially serve to position the wheel.

Ein hier aussenliegender Magnetrotor ll, welcher Teil der Magnetkupplung bildet und unter dem Einfluss des motorisch angetriebenen inneren Rotors 6 ebenfalls in Drehung versetzt wird und dem Antrieb des Pumpenrades 4 dient, ist in einem auf der Rückseite des Laufrades angeordneten, axial abstehenden Ringflansch l2 untergebracht.A magnetic rotor 11 located here, which forms part of the magnetic coupling and is also set in rotation under the influence of the motor-driven inner rotor 6 and serves to drive the pump wheel 4, is accommodated in an axially projecting ring flange 12 arranged on the rear of the impeller.

Dieser Ringflansch l2 unterteilt dabei den pumpenseitigen Antriebsraum l3, welcher auf der Rückseite des Laufrades 4 liegt, in einen äusseren und einen inneren Raum A bzw. B. Ebenfalls auf der Laufradrückseite befindet sich noch ein sog. Nabenraum C.This ring flange l2 divides the pump-side drive space l3, which is located on the rear side of the impeller 4, into an outer and an inner space A or B. Also on the impeller rear side is a so-called hub space C.

Da derartige Radialkkreiselpumpen nach Möglich­keit ohne Reibungsverluste erzeugende Dichtungen ausge­führt werden, gelangt automatisch ein Teil der geförderten Flüssigkeit über die vorhandenen Spalten in die Räume A, B und C auf der Rückseite des Laufrades 4, wobei ein Druck aufgebaut wird. Dieser Druck soll nun so gering wie möglich gehalten werden, damit einerseits die Wandstärke des Spaltrohrtopfes 5 so gering wie möglich gehalten werden kann (Verbesserung des Wirkungs­grades der Magnetkupplung) und andererseits die in Richtung der Ansaugöffnung auf das Laufrad 4 wirkende Schubkraft klein bzw. ausgeglichen gehalten werden kann.Since radial centrifugal pumps of this type are, if possible, designed without generating frictional losses, part of the liquid conveyed automatically passes through the existing gaps into spaces A, B and C on the rear of the impeller 4, whereby a pressure is built up. This pressure should now be kept as low as possible so that on the one hand the wall thickness of the canned pot 5 can be kept as low as possible (improvement in the efficiency of the magnetic coupling) and on the other hand the thrust force acting on the impeller 4 in the direction of the suction opening is kept small or balanced can be.

In diesem Druck- bzw. Schubausgleich liegt nun der Kern der vorliegenden Erfindung:The core of the present invention now lies in this pressure or thrust compensation:

Es wurde gefunden, dass durch die Anordnung eines sog. Hilfsförderrades 4ʺ auf der Rückseite des eientlichen Pumpenlaufrades 4 der Druck in den Räumen A, B und C abgebaut werden kann, wobei dies durch An­bringen von Steuermitteln direkt ausserhalb der Peripherie l4 dieses Hilfsförderrades 4ʺ in gesteuerter Weise erfolgen kann.It was found that the arrangement of a so-called auxiliary conveyor wheel 4ʺ on the back of the actual pump impeller 4 can reduce the pressure in rooms A, B and C, this being done by attaching control means directly outside the periphery l4 of this auxiliary conveyor wheel 4ʺ in a controlled manner Way can be done.

Ueblicherweise ist der aus den Räumen A, B und C auf das Laufrad wirkende Druck grösser als der Druck auf der Ansaug- bzw. Vorderseite des Laufrades 4, so dass ohne besondere Vorkehren das Laufrad in Ansaugrichtung gedrückt würde. Dies sollte aber vermieden werden.Usually, the pressure acting on the impeller from rooms A, B and C is greater than the pressure on the suction or front side of the impeller 4, so that the impeller would be pressed in the suction direction without special precautions. However, this should be avoided.

Durch das Hilfsförderrad 4ʺ, welches üblicher­weise mit dem eigentlichen Pumpenlaufrad 4 aus einem Stück besteht, wird nun aber der Druck auf der Laufradrück­seite abgebaut und dadurch die Axialbewegung des Laufrades 4 in Richtung Ansaug aufgehalten. Damit nun aber keine entgegengesetzte Bewegung des Laufrades 4 erfolgt, d.h. eine Verschiebung in Richtung der Antriebsseite, wird die Fördermenge des Hilfsförderrades 4ʺ gesteuert:By means of the auxiliary conveyor wheel 4 üblicherweise, which usually consists of one piece with the actual pump impeller 4, the pressure on the back of the impeller is now reduced and the axial movement of the impeller 4 in the direction of the intake is thereby stopped. So that there is no opposite movement of the impeller 4, i.e. a shift in the direction of the drive side, the delivery rate of the auxiliary conveyor wheel 4ʺ is controlled:

Dies kann in einfacher Weise über Steuerschlitz l5 im Gehäuse l direkt gegenüber den Auslassöffnungen der Förderkanäle l6 des Hilfsförderrades 4ʺ erfolgen, indem diese Schlitze l5 die Auslassöffnungen offen lassen (mehr oder weniger stark), was z.B. bei nach links, d.h. zur Ansaugseite verschobenem Laufrad 4 der Fall ist, bzw. geschlossen halten (mehr oder weniger stark), was z.B. bis nach rechts, d.h. zur Antriebsseite verschobenem Laufrad 4 der Fall ist. Damit wird durch den sich in den Räumen A, B und C ab- bzw. aufbauenden Druck das Laufrad zwischen den Endanschlägen 9,l0 zum Pendeln gebracht (ohne die Anschläge zu berühren).This can be done in a simple manner via control slot l5 in the housing l directly opposite the outlet openings of the delivery channels l6 of the auxiliary conveyor wheel 4ʺ are made by these slots l5 leaving the outlet openings open (more or less strong), which is the case, for example, with the impeller 4 shifted to the left, ie towards the suction side, or keeping it closed (more or less strong), which is the case, for example, to the right, ie to the drive side of the impeller 4. This causes the impeller between the end stops 9, 10 to oscillate (without touching the stops) due to the pressure which builds up or builds up in rooms A, B and C.

Damit ein Druckaufbau in den Räumen auf der Laufradrückseite gewährleistet ist, sind zwischen dem Druckraum 8 der Pumpe und dem Antriebsraum A vorzugsweise eine oder mehrere Bohrungen l7 vorgesehen.In order to ensure pressure build-up in the spaces on the rear of the impeller, one or more bores 17 are preferably provided between the pressure space 8 of the pump and the drive space A.

Das Hilfsförderrad 4ʺ kann so ausgebildet sein, dass aus den verschiedenen Räumen A, B und C jeweils Einlassöffnungen l8, l9 bzw. 20 zu den einzelnen Förderkanälen l6 des Hilfsförderrades 4ʺ vorgesehen werden, ober bei einer anderen Bauweise, dass für jeden Raum A, B und C eine Anzahl eigene Förderkanäle (z.B. 2l für Raum C bei der unteren Variante) vorgesehen werden. Es ist auch eine gemischte Bauweise denkbar.The auxiliary conveyor wheel 4ʺ can be designed such that from the different rooms A, B and C inlet openings 18, l9 and 20, respectively, to the individual delivery channels l6 of the auxiliary conveyor wheel 4ʺ are provided, with a different design that for each room A, B and C a number of separate delivery channels (e.g. 2l for room C in the lower variant) are provided. A mixed construction is also conceivable.

Bei der Bauweise nach der unteren Variante von Fig. l, d.h. wenn z.B. der innere, d.h. der Nabenraum C eigene Förderkanäle 2l aufweist, kann z.B. eine Spül­flüssigkeit über eine Leitung 22 und eine Bohrung 23 im Lagerzapfen 3 in den Raum C gefördert werden, um von dort über die Förderkanäle 2l des Hilfsförderrades 4ʺ nicht in den Druckraum 8 der Pumpe, sondern in den Raum A (und von hier in den Raum B) gefördert zu werden. Damit kann auf einfache Weise eine ausgezeichnete Reini­gung der Pumpe erfolgen. Eine Spül- oder Reinigungsflüssig­keit könnte allerdings auch direkt, z.B. über einen Einlass 24, in den Raum A eingebracht werden.In the construction according to the lower variant of FIG. 1, ie if, for example, the inner, ie the hub space C has its own conveying channels 2l, for example a rinsing liquid can be conveyed into the space C via a line 22 and a bore 23 in the journal 3 in order to from there to be promoted via the delivery channels 2l of the auxiliary feed wheel 4ʺ not in the pressure chamber 8 of the pump, but in room A (and from here in room B). Excellent cleaning of the pump can thus be carried out in a simple manner. A rinsing or cleaning liquid could, however, also be introduced directly into space A, for example via an inlet 24.

Die Fig. 2 und 3 zeigen rein schematisch, wie die Steuerung der Förderleistung des Hilfsförderrades 4ʺ über Steuerschlitze am Gehäuse, gegenüber den Förder­kanälen des Hilfsförderrades erfolgt. In Fig. 2 sind die Förderkanäle abgedeckt und der Druck im Raum A wird ansteigen, während Fig. 3 die Situation bei über die Steuerschlitze offenen Förderkanälen zeigt, in welcher der Druck im Raum A sinkt.2 and 3 show purely schematically how the control of the delivery rate of the auxiliary feed wheel 4ʺ via control slots on the housing, relative to the feed channels of the auxiliary feed wheel. In Fig. 2, the delivery channels are covered and the pressure in room A will increase, while Fig. 3 shows the situation with delivery channels open via the control slots, in which the pressure in room A decreases.

Fig. 4 schliesslich zeigt rein schematisch eine Draufsicht auf die Laufradrückseite, d.h. auf das Hilfsförderrad, mit verschiedenen Einlassöffnungen in die Förderkanäle.Fig. 4 finally shows a purely schematic plan view of the rear of the impeller, i.e. on the auxiliary feed wheel, with different inlet openings in the feed channels.

Claims (12)

1. Radial- oder Axialkreiselpumpe, deren Arbeitsseite durch einen Spaltrohrtopf vollständig dicht getrennt ist, bei welcher Pumpe der Antrieb des zwischen zwei axialen Endanschlägen fliegend auf einer Welle gelagerten Pumpenlaufrades über eine durch die Wand des Spaltrohrtopfes wirkende Magnetkupplung erfolgt und im Betrieb auf das Laufrad axiale Schubkräfte ein­wirken, hervorgerufen durch unterschiedliche Druck­verhältnisse auf der Laufradvorderseite und Laufrad­rückseite, wobei Mittel vorgesehen sind, um diese Schub­kräfte auszugleichen, dadurch gekennzeichnet, dass dem eigentlichen Pumpenlaufrad, auf dessen Vorderseite die Förderkanäle vorgesehen sind, ein Hilfsförderrad zugeordnet ist, welches dem Druckabbau im Raum bzw. den Räumen auf der Laufradrückseite dient.1.Radial or axial centrifugal pump, the working side of which is completely sealed off by a canned pot, in which pump the pump impeller, which is mounted on a shaft between two axial end stops, is driven via a magnetic coupling acting through the wall of the canned pot, and in operation on the impeller Shear forces act, caused by different pressure ratios on the impeller front and impeller rear, means being provided to compensate for these thrust forces, characterized in that an auxiliary conveying wheel is assigned to the actual pump impeller, on the front of which the delivery channels are provided, which is used to reduce the pressure in the room or serves the spaces on the rear of the impeller. 2. Kreiselpumpe nach Anspruch l, dadurch gekennzeichnet, dass am Pumpengehäuse, radial gegenüber dem äusseren Ende der Förderkanäle des Hilfsförderrades Steuermittel vorgesehen sind, um das vom Hilfsförderrad aus dem Raum hinter dem Laufrad geförderte Medium in Abhängigkeit der auf der Laufradvorder- bzw. -rückseite herrschenden Druckverhältnisse in den Druckraum der Pumpe zu fördern.2. Centrifugal pump according to claim l, characterized in that on the pump housing, radially opposite the outer end of the delivery channels of the auxiliary feed wheel control means are provided to the medium conveyed by the auxiliary feed wheel from the space behind the impeller in dependence on the impeller front or back to promote prevailing pressure conditions in the pressure chamber of the pump. 3. Kreiselpumpe nach einem der Ansprüche l oder 2, dadurch gekennzeichnet, dass das Hilfsförderrad auf der Rückseite des eigentlichen Pumpenlaufrades angeordnet ist.3. Centrifugal pump according to one of claims l or 2, characterized in that the auxiliary feed wheel is arranged on the back of the actual pump impeller. 4. Kreiselpumpe nach einem der Ansprüche l bis 3, dadurch gekennzeichnet, dass das Hilfsförderrad direkt auf der Rückwand des Pumpenlaufrades angeordnet bzw. ausgebildet ist.4. Centrifugal pump according to one of claims l to 3, characterized in that the auxiliary feed wheel is arranged or formed directly on the rear wall of the pump impeller. 5. Kreiselpumpe, bei welcher auf der Laufradrück­seite bzw. der Antriebsseite mehrere in verschiedenen radialen Abständen liegende, vom Druck zu entlastende Räume vorhanden sind, dadurch gekennzeichnet, dass jeder dieser Räume mit wenigstens einem Teil der Förder­kanäle des Hilfsförderrades kommuniziert.5. Centrifugal pump, in which on the impeller rear or the drive side there are several spaces located at different radial distances to be relieved of pressure, characterized in that each of these spaces communicates with at least some of the delivery channels of the auxiliary delivery wheel. 6. Kreiselpumpe nach Anspruch 5, dadurch gekennzeichnet, dass jedem der zu entlastenden Räume eine Anzahl eigene Förderkanäle des Hilfsförderrades zugeordnet sind.6. Centrifugal pump according to claim 5, characterized in that each of the spaces to be relieved are assigned a number of their own delivery channels of the auxiliary delivery wheel. 7. Kreiselpumpe nach Anspruch 2, dadurch gekennzeichnet, dass die Steuermittel den Ausgang der Förderkanäle des Hilfsförderrades je nach Grösse der sich einstellenden Schubkräfte mehr oder weniger abdecken.7. Centrifugal pump according to claim 2, characterized in that the control means more or less cover the output of the delivery channels of the auxiliary feed wheel depending on the size of the thrust forces that arise. 8. Kreiselpumpe nach Anspruch 2 oder 7, dadurch gekennzeichnet, dass die Steuermittel im Gehäuse vorge­sehene Steuerschlitze mit entsprechend ausgebildeten Steuerkanten sind.8. Centrifugal pump according to claim 2 or 7, characterized in that the control means are provided in the housing control slots with appropriately designed control edges. 9. Kreiselpumpe nach einem der Ansprüche l-8, dadurch gekennzeichnet, dass zwischen dem Druckraum und dem Antriebsraum der Pumpe wenigstens ein die beiden Räume verbindender Durchgang vorgesehen ist.9. Centrifugal pump according to one of claims l-8, characterized in that at least one passage connecting the two spaces is provided between the pressure chamber and the drive chamber of the pump. l0. Kreiselpumpe nach Anspruch 6, dadurch gekennzeichnet, dass wenigstens einige der vom rückseiti­gen Nabenraum nach aussen führenden Förderkanäle in gewissen Betriebsstellungen des Pumpenlaufrades in den äusseren Antriebsraum münden und dass der Nabenraum an eine Flüssigkeitszuleitung angeschlossen ist.l0. Centrifugal pump according to claim 6, characterized in that at least some of the delivery channels leading outwards from the rear hub space into certain operating positions of the pump impeller open into the outer drive space and that the hub space is connected to a liquid supply line. 11. Kreiselpumpe nach einem der Ansprüche l-l0, dadurch gekennzeichnet, dass der Lagerzapfen des Pumpenlaufrades und Hilfsförderrades am Spaltrohrtopf angeordnet ist, z.B. mit letzterem einstückig ausgebildet.11. Centrifugal pump according to one of claims l-l0, characterized in that the bearing journal of the pump impeller and auxiliary feed wheel is arranged on the canned pot, e.g. integrally formed with the latter. 12. Kreiselpumpe nach einem der Ansprüche l-ll, dadurch gekennzeichnet, dass eine Zuleitung für Spülflüssigkeit in den Nabenraum durch den Lagerzapfen geführt ist.12. Centrifugal pump according to one of claims l-ll, characterized in that a feed line for flushing liquid is guided into the hub space through the bearing journal.
EP87103057A 1986-03-21 1987-03-04 Radial or axial flow centrifugal pump Expired - Lifetime EP0237868B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87103057T ATE60411T1 (en) 1986-03-21 1987-03-04 RADIAL OR AXIAL CENTRIFUGAL PUMP.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1160/86A CH672820A5 (en) 1986-03-21 1986-03-21
CH1160/86 1986-03-21

Publications (3)

Publication Number Publication Date
EP0237868A2 true EP0237868A2 (en) 1987-09-23
EP0237868A3 EP0237868A3 (en) 1988-01-20
EP0237868B1 EP0237868B1 (en) 1991-01-23

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ID=4203879

Family Applications (1)

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EP87103057A Expired - Lifetime EP0237868B1 (en) 1986-03-21 1987-03-04 Radial or axial flow centrifugal pump

Country Status (7)

Country Link
US (1) US4793777A (en)
EP (1) EP0237868B1 (en)
JP (1) JP2535004B2 (en)
AT (1) ATE60411T1 (en)
CH (1) CH672820A5 (en)
DE (1) DE3767517D1 (en)
ES (1) ES2020520B3 (en)

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WO1996032592A1 (en) * 1995-04-14 1996-10-17 Ceramiques & Composites S.A. Magnetic drive centrifugal pump
EP0982499A1 (en) * 1998-08-21 2000-03-01 CP Pumpen AG Magnetically coupled centrifugal pump
DE202016105312U1 (en) * 2016-09-23 2018-01-09 Speck Pumpen Verkaufsgesellschaft Gmbh feed pump

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JP2519466Y2 (en) * 1990-10-12 1996-12-04 株式会社帝国電機製作所 Gas seal type motor pump
FR2698667B1 (en) * 1992-11-30 1995-02-17 Europ Propulsion Centrifugal pump with open impeller.
FR2715442B1 (en) * 1994-01-26 1996-03-01 Lorraine Carbone Centrifugal pump with magnetic drive.
US6135728A (en) * 1998-10-29 2000-10-24 Innovative Mag-Drive, L.L.C. Centrifugal pump having an axial thrust balancing system
US6234748B1 (en) 1998-10-29 2001-05-22 Innovative Mag-Drive, L.L.C. Wear ring assembly for a centrifugal pump
US6293772B1 (en) 1998-10-29 2001-09-25 Innovative Mag-Drive, Llc Containment member for a magnetic-drive centrifugal pump
US6123507A (en) * 1998-11-30 2000-09-26 Smith & Loveless, Inc. Single port impeller
KR20030023720A (en) * 2001-06-05 2003-03-19 가부시키가이샤 이와키 Magnet pump
US7101158B2 (en) 2003-12-30 2006-09-05 Wanner Engineering, Inc. Hydraulic balancing magnetically driven centrifugal pump
JP4959424B2 (en) * 2007-05-31 2012-06-20 勇 青谷 Pump device
US8506259B2 (en) 2009-12-23 2013-08-13 Solar Turbines Inc. Fluid compression system
US8905728B2 (en) 2011-12-30 2014-12-09 Peopleflo Manufacturing, Inc. Rotodynamic pump with permanent magnet coupling inside the impeller
US8905729B2 (en) 2011-12-30 2014-12-09 Peopleflo Manufacturing, Inc. Rotodynamic pump with electro-magnet coupling inside the impeller
US9488184B2 (en) 2012-05-02 2016-11-08 King Abdulaziz City For Science And Technology Method and system of increasing wear resistance of a part of a rotating mechanism exposed to fluid flow therethrough
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DE102014006568A1 (en) * 2013-05-08 2014-11-13 Ksb Aktiengesellschaft Pump arrangement and method for producing a split pot of the pump assembly
US9771938B2 (en) * 2014-03-11 2017-09-26 Peopleflo Manufacturing, Inc. Rotary device having a radial magnetic coupling
JP6671048B2 (en) * 2015-11-12 2020-03-25 パナソニックＩｐマネジメント株式会社 pump
AU2016367178B2 (en) * 2015-12-07 2019-12-12 Fluid Handling Llc Opposed impeller wear ring undercut to offset generated axial thrust in multi-stage pump
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EP0982499A1 (en) * 1998-08-21 2000-03-01 CP Pumpen AG Magnetically coupled centrifugal pump
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Also Published As

Publication number Publication date
ES2020520B3 (en) 1991-08-16
US4793777A (en) 1988-12-27
JPS62233493A (en) 1987-10-13
EP0237868A3 (en) 1988-01-20
EP0237868B1 (en) 1991-01-23
CH672820A5 (en) 1989-12-29
DE3767517D1 (en) 1991-02-28
ATE60411T1 (en) 1991-02-15
JP2535004B2 (en) 1996-09-18

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