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EP0221300B1 - Centrifugal pump unit - Google Patents

Centrifugal pump unit Download PDF

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Publication number
EP0221300B1
EP0221300B1 EP86112695A EP86112695A EP0221300B1 EP 0221300 B1 EP0221300 B1 EP 0221300B1 EP 86112695 A EP86112695 A EP 86112695A EP 86112695 A EP86112695 A EP 86112695A EP 0221300 B1 EP0221300 B1 EP 0221300B1
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EP
European Patent Office
Prior art keywords
centrifugal pump
axial
angular
impeller
pump unit
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.)
Expired - Lifetime
Application number
EP86112695A
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German (de)
French (fr)
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EP0221300A1 (en
Inventor
Adolf Kratzer
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KSB AG
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KSB AG
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Publication date
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Publication of EP0221300A1 publication Critical patent/EP0221300A1/en
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Publication of EP0221300B1 publication Critical patent/EP0221300B1/en
Anticipated expiration legal-status Critical
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/08Sealings
    • F04D29/16Sealings between pressure and suction sides
    • F04D29/165Sealings between pressure and suction sides especially adapted for liquid pumps
    • F04D29/167Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00Pumping installations or systems
    • F04D13/02Units comprising pumps and their driving means
    • F04D13/021Units comprising pumps and their driving means containing a coupling
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/04Shafts or bearings, or assemblies thereof
    • F04D29/041Axial thrust balancing
    • F04D29/0416Axial thrust balancing balancing pistons

Definitions

  • the invention relates to a centrifugal pump unit consisting of a centrifugal pump and a drive motor, the centrifugal pump of which has a radial impeller with relief bores, on the two sides of which angular sealing gaps designed as a fluid bearing are arranged, the diameters of which are coordinated with one another for the purpose of axial thrust compensation, the connection between the centrifugal pump and the drive motor via a coupling which permits the axial displacements of the pump impeller necessary for axial thrust compensation.
  • an axial thrust compensation which acts by means of a partial flow diverted from one point of increased pressure, which is returned to a point of lower pressure.
  • the partial flow is conducted via at least one slip ring, an axial thrust compensation end face on an axially displaceable rotor and a return bore cooperating with a throttle valve, the throttle valve responding to an axial displacement of the rotor.
  • the slip rings arranged in the housing interact with angular inner rings on the impeller side, resulting in angular sealing gaps.
  • Axial stops provided on the slip rings are intended to accommodate a restaxial thrust. However, they can endanger the partners involved in the radial bearing. If an inner ring comes into contact with an axial stop, the partial flow becomes so throttled that the flow required for bearing lubrication goes to zero and the radial pressure in the radial bearing practically prevails. A hydrodynamic bearing lubrication can then no longer be used. Especially with materials that are sensitive to dry running, such as ceramics or PTFE, this can lead to destruction of the bearing caused by overheating and thermal stresses.
  • the invention has for its object to provide an axial thrust compensation which, while avoiding an additional radial or axial bearing, offers a high level of security against endangering the parts serving for axial thrust compensation and the bearing.
  • this object is achieved in that the angular sealing gaps are formed by housing-fixed angle split rings, which act both as axial and radial bearings, with the parts of the angle split rings acting as axial bearings on the low pressure side of the Radial bearing acting parts are arranged.
  • the invention is explained in more detail using an exemplary embodiment.
  • the drawing shows the centrifugal pump and the coupling of a centrifugal pump unit according to the invention connecting this with a drive motor, not shown, in a sectional view.
  • a radial impeller (3) equipped with a relief bore (2) is arranged in a centrifugal pump housing (1).
  • the radial impeller (3) is driven by a drive shaft (4) of a drive motor (not shown), an elastic coupling (5) and a stub shaft (6) firmly connected to the radial impeller (3).
  • the coupling (5) is designed and arranged in such a way that neither longitudinal nor transverse forces act on the stub shaft (6) and the radial impeller (3); a magnetic coupling could be used here.
  • the radial impeller (3) is supported by a suction-side angle split ring (7) and a pressure-side angle split ring (8), which are arranged in the centrifugal pump housing (1) or the rear wall of the housing (9) and which, together with the radial impeller (3), form an inlet-side angular sealing gap ( 10) and form an angular sealing gap (11) on the pressure side.
  • a mechanical seal (12) serves to seal the centrifugal pump housing (1) to the outside.
  • the housing-fixed angle split rings are advantageously made of ceramic and their diameters are graduated so that the larger pressure-side angle split ring corresponds in its dimensions to the suction-side dimensions of a centrifugal pump of the next largest nominal size.

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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)

Description

Die Erfindung betrifft ein aus einer Kreiselpumpe und einem Antriebsmotor bestehendes Kreiselpumpenaggregat, dessen Kreiselpumpe ein Radiallaufrad mit Entlastungsbohrungen besitzt, auf dessen beiden Seiten als Unterflüssigkeitslager ausgebildete winkelförmig verlaufende Dichtspalte angeordnet sind, deren Durchmesser zum Zwecke des Axialschubausgleichs aufeinander abgestimmt sind, wobei die Verbindung zwischen der Kreiselpumpe und dem Antriebsmotor über eine die für den Axialschubausgleich notwendigen axialen Verschiebungen des Pumpenlaufrades zulassende Kupplung erfolgt.The invention relates to a centrifugal pump unit consisting of a centrifugal pump and a drive motor, the centrifugal pump of which has a radial impeller with relief bores, on the two sides of which angular sealing gaps designed as a fluid bearing are arranged, the diameters of which are coordinated with one another for the purpose of axial thrust compensation, the connection between the centrifugal pump and the drive motor via a coupling which permits the axial displacements of the pump impeller necessary for axial thrust compensation.

Durch die DE-A 1 811 430 ist es für hydraulische Strömungsmaschinen bekannt, die beidseitig eines Laufrades angeordneten Dichtspalte als Unterflüssigkeitslager auszubilden. Bei der in der Fig. 2 dieser Schrift gezeigten Francis-Turbinen werden hierfür gummielastische Lager verwendet, die beide von einem Leckstrom durchströmt werden. Ein gewisser axialer Druckausgleich soll dadurch erzielt werden, daß die beiden Lager gleiche Abmessungen besitzen. Außerdem ist das Laufrad mit einer Ausgleichsbohrung versehen, die Druckgleichheit zwischen beiden Seiten des Laufrades herbeiführen soll. Da aber noch ein Axiallager für die Pumpenwelle notwendig ist, wird die für einen selbsttätigen Axialschubausgleich erforderliche Beweglichkeit des Laufrades in axialer Richtung behindert.From DE-A 1 811 430 it is known for hydraulic fluid-flow machines to design the sealing gaps arranged on both sides of an impeller as a sub-fluid bearing. In the Francis turbines shown in FIG. 2 of this document, rubber-elastic bearings are used for this, both of which a leakage current flows through. A certain axial pressure compensation should be achieved in that the two bearings have the same dimensions. In addition, the impeller is provided with a compensating hole, which should bring about pressure equality between the two sides of the impeller. However, since an axial bearing is still required for the pump shaft, the mobility of the impeller required for automatic axial thrust compensation is hindered in the axial direction.

Aus der DE-A 3 242 931 und der mit dieser weitgehend übereinstimmenden DE-A 3 305 174 ist eine Kreiselpumpe mit Spaltrohr-Magnetkupplungs-Antrieb bekannt, die im wesentlichen wälz- und gleitlagerfrei ausgebildet ist. Durch mindestens einen Schleifring soll hier die Funktion einer hydrodynamischen Lagerung übernommen werden.From DE-A 3 242 931 and DE-A 3 305 174, which largely corresponds to this, a centrifugal pump with a canned magnetic coupling drive is known, which is essentially free of rolling and plain bearings. The function of a hydrodynamic bearing is to be taken over here by at least one slip ring.

In der älteren der beiden Schriften wird auf die Möglichkeit eines Axialschubausgleichs hingewiesen, der bei Anordnung mehrerer Schleifringe dadurch erreicht werden soll, daß wenigstens ein antriebsseitiger Schleifring einen größeren Außendurchmesser aufweist als der bzw. die axial weiter pumpenseitig angeordneten Schleifringe. In der jüngeren Schrift wird dagegen ein Axialschubausgleich gelehrt, der mittels eines von einer Stelle erhöhten Druckes abgezweigten Teilstromes wirkt, der zu einer Stelle niederen Druckes zurückgeführt wird. Der Teilstrom wird über mindestens einen Schleifring, eine Axialschubausgleich-Stirnseite an einem axial verschiebbaren Läufer und eine mit einem Drosselventil zusammenarbeitende Rücklaufbohrung geleitet, wobei das Drosselventil auf eine Axialverschiebung des Läufers anspricht.In the older of the two documents, reference is made to the possibility of axial thrust compensation, which is to be achieved when several slip rings are arranged in that at least one slip ring on the drive side has a larger outer diameter than the slip ring or axially further arranged on the pump side. In the more recent writing, on the other hand, an axial thrust compensation is taught, which acts by means of a partial flow diverted from one point of increased pressure, which is returned to a point of lower pressure. The partial flow is conducted via at least one slip ring, an axial thrust compensation end face on an axially displaceable rotor and a return bore cooperating with a throttle valve, the throttle valve responding to an axial displacement of the rotor.

In beiden zitierten Schriften wirken die im Gehäuse angeordneten Schleifringe mit laufradseitigen winkelförmigen Innenringen zusammen, wodurch winkelförmige Dichtspalte entstehen. An den Schleifringen vorgesehene Axialanschläge sollen zur Aufnahme eines Restaxialschubes dienen. Durch sie kann aber eine Gefährdung der an der Radiallagerung beteiligten Partner entstehen. Gelangt nämlich ein Innenring zum Anlauf an einen Axialanschlag, so wird der Teilstrom so stark gedrosseit, daß der zur Lagerschmierung erforderliche Durchfluß gegen Null geht und im Radiallager praktisch der Eintrittsdruck herrscht. Von einer hydrodynamischen Lagerschmierung kann dann nicht mehr die Rede sein. Vor allem bei trockenlaufempfindlichen Werkstoffen, wie Keramik oder PTFE, kann dies zu einer durch Überhitzung und Wärmespannungen verursachten Zerstörung der Lagerung führen.In both of the cited documents, the slip rings arranged in the housing interact with angular inner rings on the impeller side, resulting in angular sealing gaps. Axial stops provided on the slip rings are intended to accommodate a restaxial thrust. However, they can endanger the partners involved in the radial bearing. If an inner ring comes into contact with an axial stop, the partial flow becomes so throttled that the flow required for bearing lubrication goes to zero and the radial pressure in the radial bearing practically prevails. A hydrodynamic bearing lubrication can then no longer be used. Especially with materials that are sensitive to dry running, such as ceramics or PTFE, this can lead to destruction of the bearing caused by overheating and thermal stresses.

Der Erfindung liegt die Aufgabe zugrunde, einen Axialschubausgleich zu schaffen, der bei Vermeidung eines zusätzlichen Radial- oder Axiallagers eine hohe Sicherheit gegen eine Gefährdung der dem Axialschubausgleich und der Lagerung dienenden Teile bietet.The invention has for its object to provide an axial thrust compensation which, while avoiding an additional radial or axial bearing, offers a high level of security against endangering the parts serving for axial thrust compensation and the bearing.

Ausgehend von einem Kreiselpumpenaggregat der eingangs genannten Art, wird diese Aufgabe dadurch gelöst, daß die winkelförmig verlaufenden Dichtspalte durch gehäusefeste Winkelspaltringe gebildet werden, die sowohl als Axial- als auch als Radiallager wirken, wobei die als Axiallager wirkenden Teile der Winkelspaltringe an der Niederdruckseite der als Radiallager wirkenden Teile angeordnet sind.Starting from a centrifugal pump unit of the type mentioned, this object is achieved in that the angular sealing gaps are formed by housing-fixed angle split rings, which act both as axial and radial bearings, with the parts of the angle split rings acting as axial bearings on the low pressure side of the Radial bearing acting parts are arranged.

Die Unteransprüche nennen zweckmäßige Ausgestaltungen der Erfindung.The subclaims name expedient embodiments of the invention.

Anhand eines Ausführungsbeispiels wird die Erfindung näher erläutert. Die Zeichnung zeigt die Kreiselpumpe und die diese mit einem nicht dargestellten Antriesmotor verbindende Kupplung eines erfindungsgemäßen Kreiselpumpenaggregates in Schnittdarstellung.The invention is explained in more detail using an exemplary embodiment. The drawing shows the centrifugal pump and the coupling of a centrifugal pump unit according to the invention connecting this with a drive motor, not shown, in a sectional view.

In einem Kreiselpumpengehäuse (1) ist ein mit einer Entlastungsbohrung (2) ausgestattetes Radiallaufrad (3) angeordnet. Der Antrieb des Radiallaufrades (3) erfolgt über eine Antriebswelle (4) eines nicht dargestellten Antriebsmotors, eine elastische Kupplung (5) und einen mit dem Radiallaufrad (3) fest verbundenen Wellenstumpf (6). Die Kupplung (5) ist so ausgelegt und angeordnet, daß sie weder Längs- noch Querkräfte auf den Wellenstumpf (6) und das Radiallaufrad (3) wirken läßt; es könnte hier eine Magnetkupplung verwendet werden.A radial impeller (3) equipped with a relief bore (2) is arranged in a centrifugal pump housing (1). The radial impeller (3) is driven by a drive shaft (4) of a drive motor (not shown), an elastic coupling (5) and a stub shaft (6) firmly connected to the radial impeller (3). The coupling (5) is designed and arranged in such a way that neither longitudinal nor transverse forces act on the stub shaft (6) and the radial impeller (3); a magnetic coupling could be used here.

Der Lagerung des Radiallaufrades (3) dienen ein saugseitiger Winkelspaltring (7) und ein druckseitiger Winkelspaltring (8), die im Kreiselpumpengehäuse (1) bzw. der Gehäuserückwand (9) angeordnet sind und die mit dem Radiallaufrad (3) einen zulaufseitigen winkelförmigen Dichtspalt (10) und einen druckseitigen winkelförmigen Dichtspalt (11) bilden. Der Abdichtung des Kreiselpumpengehäuses (1) nach außen dient eine Gleitringdichtung (12).The radial impeller (3) is supported by a suction-side angle split ring (7) and a pressure-side angle split ring (8), which are arranged in the centrifugal pump housing (1) or the rear wall of the housing (9) and which, together with the radial impeller (3), form an inlet-side angular sealing gap ( 10) and form an angular sealing gap (11) on the pressure side. A mechanical seal (12) serves to seal the centrifugal pump housing (1) to the outside.

Der Axialschubausgleich des erfindungsgemäßen Kreiselpumpenaggregates wirkt folgendermaßen:

  • Durch den im allgemeinen zur Zulaufseite wirkenden Axialschub verschiebt sich das Radiallaufrad (3) so weit zur Zulaufseite, bis die Drosselwirkung des axial durchströmten zulaufseitigen winkeIförmigen Dichtspaltes (10) so groß wird, daß bei stark reduziertem Durchfluß sich im zulaufseitigen Laufradseitenraum ein höherer Mitteldruck einstellt als im druckseitigen Laufradseitenraum, in welchem der analog vergrößerte axial durchströmte winkelförmige Dichtspalt (11) eine entsprechend geringere Drosselwirkung ausübt. Das Radiallaufrad (3) wird sich daher in eine stabile axialkraftfreie Stellung einpendeln.
The axial thrust compensation of the centrifugal pump unit according to the invention works as follows:
  • Due to the axial thrust, which generally acts on the inlet side, the radial impeller (3) moves to the inlet side until the throttling effect of the axially flowed angular sealing gap (10) on the inlet side becomes so large that, with greatly reduced flow, a higher mean pressure is established in the inlet side impeller side space than in the pressure-side impeller side space, in which the angular sealing gap (11), which is enlarged axially and flows analogously, has a correspondingly smaller one Throttling effect. The radial impeller (3) will therefore level off in a stable position free of axial force.

Da der von den beiden Lagerstellen symmetrisch aufgenommene Radialschub erheblich größer ist als das Gewicht des Wellenstumpfes (6), der Gleitringdichtung (12) und des mit dem Wellenstumpf (6) verbundenen Teiles der Kupplung (5), wird ein Verkanten des Radiallaufrades (3) innerhalb der Winkelspaltringe (7) und (8) vermieden.Since the radial thrust absorbed symmetrically by the two bearing points is considerably greater than the weight of the stub shaft (6), the mechanical seal (12) and the part of the coupling (5) connected to the stub shaft (6), the radial impeller (3) will tilt. avoided within the angle split rings (7) and (8).

Die gehäusefesten Winkelspaltringe sind vorteilhafterweise aus Keramik und deren Durchmesser sind so abgestuft, daß der größere druckseitige Winkelspaltring in seinen Abmessungen den saugseitigen Abmessungen einer Kreiselpumpe der nächstgrößeren Nennweite entspricht.The housing-fixed angle split rings are advantageously made of ceramic and their diameters are graduated so that the larger pressure-side angle split ring corresponds in its dimensions to the suction-side dimensions of a centrifugal pump of the next largest nominal size.

Claims (4)

1. A centrifugal pump unit consisting of a centrifugal pump and a prime mover, whose centrifugal pump possesses a radial impeller with balance holes and on whose two sides clearance gap seals are arranged which are in the form of subliquid bearings with an angular configuration and whose diameters are matched in order to balance axial thrust, the connection between the centrifugal pump and the prime mover being by way of a coupling which allows axial displacements of the pump impeller as needed for balancing the axial thrus, characterized in that clearance gaps (10 and 11), which have an angular configuration, are defined by angular gap rings (7 -and 8) fixed in relation to the housing, which act both as an axial and as a radial bearing means, the parts, acting as axial bearing means, of the angular gap rings (7 and 8) being arranged on the low pressure side of the parts acting as radial bearing means.
2. The centrifugal pump unit as claimed in claim 1, characterized in that the impeller hub of the centrifugal pump terminates in a stub shaft (6), via which the pump is connected with the shaft (4) of the prime mover by way of an elastic coupling (5).
3. The centrifugal pump unit as claimed in claim 1, characterized in that the centrifugal pump is connected with the prime mover via a magnetic coupling.
4. The centrifugal pump unit as claimed in claim 1, characterized in that the angular gap rings (7 and 8), which are fixed in relation to the housing consist of a ceramic material and are so graded in their diameter that the larger angular gap ring (8), which is on the pressure side, has dimensions with are equal to the angular gap ring (7) of a centrifugal pump of the next larger rated width.
EP86112695A 1985-10-10 1986-09-13 Centrifugal pump unit Expired - Lifetime EP0221300B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853536140 DE3536140A1 (en) 1985-10-10 1985-10-10 CENTRIFUGAL PUMP UNIT
DE3536140 1985-10-10

Publications (2)

Publication Number Publication Date
EP0221300A1 EP0221300A1 (en) 1987-05-13
EP0221300B1 true EP0221300B1 (en) 1990-09-19

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP86112695A Expired - Lifetime EP0221300B1 (en) 1985-10-10 1986-09-13 Centrifugal pump unit

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EP (1) EP0221300B1 (en)
DE (2) DE3536140A1 (en)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3940670C1 (en) * 1989-12-08 1990-07-26 Waeschle Maschinenfabrik Gmbh, 7980 Ravensburg, De
WO1991015680A1 (en) * 1990-04-03 1991-10-17 Osoboe Konstruktorskoe Bjuro Po Konstruirovaniju, Issledovaniju I Vnedreniju Glubinnykh Besshtangovykh Nasosov Vortex-type rotor machine
US5263816A (en) * 1991-09-03 1993-11-23 General Motors Corporation Turbomachine with active tip clearance control
US7146822B2 (en) * 2002-12-30 2006-12-12 Intel Corporation Centrifugal liquid pump with perimeter magnetic drive
DE102009027645B4 (en) 2009-07-13 2018-08-02 BSH Hausgeräte GmbH Dishwasher with a circulation pump
CN104214128B (en) * 2013-05-30 2017-05-17 高涵文 Magnetic drive pump with improved structure
CN104454628B (en) * 2014-12-10 2017-01-11 襄阳五二五泵业有限公司 Seal pressure-relief device for pump in coal chemical industry
DE102016003180A1 (en) * 2016-03-16 2017-09-21 Ksb Aktiengesellschaft Centrifugal pump with an arrangement for reducing a backflow
DE102019122042A1 (en) * 2019-08-16 2021-02-18 HELLA GmbH & Co. KGaA Pumping device

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3305174A1 (en) * 1983-02-15 1984-09-06 Hermann 7800 Freiburg Krämer Centrifugal pump with canned magnetic clutch drive

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Publication number Priority date Publication date Assignee Title
US2625883A (en) * 1951-01-25 1953-01-20 Julia M Howser Centrifugal pump drive and seal means
DE902942C (en) * 1951-10-02 1954-01-28 Bruno C Grosskopf Multi-stage impeller machine
DE1653670A1 (en) * 1967-01-20 1971-08-19 Bosch Gmbh Robert Radial pump with self-adjusting hydraulic force compensation
DE1811430A1 (en) * 1968-11-25 1970-06-11 Gummi Jaeger Kg Gmbh & Cie Hydraulic flow machine
DE2460095B2 (en) * 1974-12-19 1980-01-17 Messerschmitt-Boelkow-Blohm Gmbh, 8000 Muenchen Centrifugal pump with axial thrust compensation
DE8115273U1 (en) * 1981-05-22 1981-08-13 Hermetic-Pumpen Gmbh, 7803 Gundelfingen "CENTRIFUGAL PUMP WITH CLEAR TUBE MAGNETIC CLUTCH DRIVE"
DE3242931A1 (en) * 1981-05-22 1984-05-24 Hermetic Pumpen Gmbh Centrifugal pump with canned magnetic clutch drive
DE3307726C2 (en) * 1983-03-04 1986-04-24 Franz Klaus Union Armaturen, Pumpen Gmbh & Co, 4630 Bochum Runner and bearing of a pump

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3305174A1 (en) * 1983-02-15 1984-09-06 Hermann 7800 Freiburg Krämer Centrifugal pump with canned magnetic clutch drive

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Publication number Publication date
EP0221300A1 (en) 1987-05-13
DE3536140A1 (en) 1987-04-16
DE3674331D1 (en) 1990-10-25

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