EP1158174B1 - Centrifugal pump with magnetic coupling - Google Patents

Centrifugal pump with magnetic coupling Download PDF

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Publication number
EP1158174B1
EP1158174B1 EP01108334A EP01108334A EP1158174B1 EP 1158174 B1 EP1158174 B1 EP 1158174B1 EP 01108334 A EP01108334 A EP 01108334A EP 01108334 A EP01108334 A EP 01108334A EP 1158174 B1 EP1158174 B1 EP 1158174B1
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EP
European Patent Office
Prior art keywords
shaft
rotor
pump
magnetic rotor
bearing housing
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
EP01108334A
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German (de)
French (fr)
Other versions
EP1158174A2 (en
EP1158174A3 (en
Inventor
Ulrich Rennett
Manfred Sett
Alfred Mersch
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ITT Manufacturing Enterprises LLC
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ITT Manufacturing Enterprises LLC
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Publication date
Application filed by ITT Manufacturing Enterprises LLC filed Critical ITT Manufacturing Enterprises LLC
Priority to EP06015105A priority Critical patent/EP1719914B1/en
Publication of EP1158174A2 publication Critical patent/EP1158174A2/en
Publication of EP1158174A3 publication Critical patent/EP1158174A3/en
Application granted granted Critical
Publication of EP1158174B1 publication Critical patent/EP1158174B1/en
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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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/047—Bearings hydrostatic; hydrodynamic
    • 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
    • F04D13/026—Details of the bearings
    • 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
    • F04D29/0413—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
    • 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
    • F04D29/046—Bearings
    • F04D29/0465—Ceramic bearing designs

Definitions

  • the invention relates to a centrifugal pump with a magnetic coupling arranged between the pump shaft and the drive shaft and a split pot in the magnetic gap between the inner magnet rotor of the pump and the outer magnet rotor of the drive shaft, wherein the inner magnet rotor is mounted on a tubular bearing housing in the interior of the split pot through which the fluid flows surrounding the pump impeller shaft having on the side facing away from the pump impeller fastening means for the inner magnet rotor, which is arranged between the bearing housing and the containment shell.
  • a conventional magnetic pump drive is known from DE 37 15 484. Moreover, it is known from EP 0 398 175 to lead a small part of the conveying medium between the stator and the rotor for cooling.
  • magnetic return rotors with radial return vanes are known.
  • the blades serve to generate a flushing or cooling medium flow.
  • These radial blades are arranged on the front side of the magnetic coupling rotor and generate a flow rate in the radial direction by the medium accelerates by centrifugal force to the outer diameter of the rotor and through the Gap between rotor circumference and split pot is promoted. This conveying direction to the outer diameter is contrary to the required flow direction in order to be able to initiate the flushing medium flow directly into the rotor bearing positioned in the center of the rotor.
  • Radial blades generally produce only smaller mass flows at higher pressures, so that only very small amounts of flushing or cooling medium are available and the promotion can be interrupted due to cavitation. When enlarging the radial blades, although more medium is promoted, but the tendency to cavitation also increases. In addition, larger radial blades also require a higher hydraulic power, which is to be classified as a coupling power loss and therefore undesirable.
  • the object of the invention is to improve a centrifugal pump of the type mentioned so that at low hydraulic power loss high rinsing, cooling and lubricating performance and high leakage safety is achieved.
  • annular gap between the bearing portion of the inner magnet rotor and the inner wall of the tubular bearing housing in its radial width is smaller than the annular gap between the inner magnet rotor and the can. This ensures that at a fraction of the plain bearing of the shaft surfaces of the gap in the storage area first come to rest on each other and thus form a Notgleitlager before the surfaces in the region of the annular gap between the containment shell and the outside of the inner magnet rotor are superimposed. This can not lead to a destruction of the split pot and a leak.
  • At least one temperature sensor is arranged to detect an emergency run close to the bearing of the inner magnet rotor.
  • a current consumption sensor is arranged in the supply line of the driving electric motor.
  • the centrifugal pump 1 with magnetic coupling has a rotating in a pump chamber impeller 2, which is fixed to one end of a shaft 3.
  • the shaft 3 carries a shaft sleeve 12, which is supported by two ceramic radial bearings 4, 5 and two ceramic thrust bearings 6, 7, which are fixed to the inner wall of a tubular bearing housing 8.
  • the bearing housing 8 is fixed to the wall 11, which separates the pump chamber 9 from the interior of a split pot 10, which is fixed to the partition wall 11.
  • the shaft 3 carries an inner pot-shaped magnet rotor 14.
  • a circular bottom 16 is integrally formed on the shaft 3 as a fastening means 15, on the outer edge of a tubular coaxial magnetic carrier 17 is formed on the outer edge, on the outside of the output magnets 18 are attached.
  • the bearing housing 8 thus extends coaxially in the magnet rotor 14, wherein between the magnet carrier 17 and the bearing housing 8, an annular space 19 and between the magnet carrier 17 and the gap pot 10 is an annular gap 20.
  • the split pot 10 is surrounded by a drive pot, not shown, which carries the drive magnets inside and is driven by a coaxial shaft of an electric motor.
  • annular coaxial flow channel (annulus) 21 is introduced, which is in the amount of the annulus 19 and is traversed by two to four radial axial blades 22, the magnetic carrier 17 at the bottom of the 16th hold.
  • the blades are formed at regular intervals (angles) on the bottom and magnetic carrier and have an angle of attack of 5 to 15 degrees.
  • the preferably three blades 22 convey the liquid entering through the inlet channels 23 into the crevice interior space from the annular gap 20 into the intermediate space 24 between the bearing housing 8 and the shaft sleeve 12, so that the liquid conveyed through it flows through the radial and axial bearings 4 to 7 to the pumping chamber flow back.
  • the tubular bearing housing 8 forms at the end facing away from the impeller 2 an annular gap 25 with an inner portion of the inner magnet rotor or the fastening means 15.
  • a coaxial ring 26 is fixed, in which the outer thrust bearing 7 is present.
  • the outer side of the ring 26 forms, with the inside of the bearing housing 8, the annular gap 25 whose radial width B1 is less than the radial width B2 of the annular gap 20.
  • a helical coaxial groove 27 is introduced in the region of the gap 25, which in the gap 25 the fluid promotes the space 24.
  • the groove 27 may also be arranged in the outer wall of the magnet rotor or of the ring 26.
  • a temperature sensor 28 is attached, indicating early, when a radial bearing is defective and the surfaces of the Rub gap 25 together.
  • a bearing defect may be indicated by a current sensing sensor 29 located in or on the lead 31 of the electric motor. These sensors are connected to a warning device (horn light, connection to the system monitoring) 30.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Ceramic Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

The pump has a housing plate having a front face and a back face, a housing can fixed to the plate and defining a chamber on the back face, a bearing sleeve in the can fixed to the plate and extending rearward from the back face along an axis, and a rotor shaft extending axially through the sleeve and having a front end and a rear end. Bearings support the rotor shaft in the sleeve for rotation about the axis. The shaft has an outer surface spaced a predetermined inner radial distance from an inside surface of the bearing sleeve. An impeller is carried on the rotor-shaft front end in a pump chamber at the front face of the housing plate. A rotor body fixed to the shaft rear end extends axially forward in the can around the bearing sleeve. The rotor body has an outer surface spaced a predetermined outer radial distance from an inside surface of the can. The inner radial dimension is smaller than the outer radial dimension.

Description

Die Erfindung betrifft eine Kreiselpumpe mit einer zwischen Pumpenwelle und Antriebswelle angeordneten Magnetkupplung und mit einem Spalttopf im Magnetspalt zwischen dem inneren Magnetrotor der Pumpe und dem äußeren Magnetrotor der Antriebswelle, wobei im Inneren des von der Förderflüssigkeit durchflossenen Spalttopfes der innere Magnetrotor an einem rohrförmigen Lagergehäuse gelagert ist, das die Pumpenlaufradwelle umgibt, die auf der dem Pumpenlaufrad abgewandten Seite Befestigungsmittel für den inneren Magnetrotor besitzt, der zwischen dem Lagergehäuse und dem Spalttopf angeordnet ist.The invention relates to a centrifugal pump with a magnetic coupling arranged between the pump shaft and the drive shaft and a split pot in the magnetic gap between the inner magnet rotor of the pump and the outer magnet rotor of the drive shaft, wherein the inner magnet rotor is mounted on a tubular bearing housing in the interior of the split pot through which the fluid flows surrounding the pump impeller shaft having on the side facing away from the pump impeller fastening means for the inner magnet rotor, which is arranged between the bearing housing and the containment shell.

Ein üblicher magnetischer Pumpenantrieb ist aus der DE 37 15 484 bekannt. Darüber hinaus ist es aus der EP 0 398 175 bekannt, zwischen Stator und Rotor einen geringen Teil des Fördermediums zur Kühlung zu führen.A conventional magnetic pump drive is known from DE 37 15 484. Moreover, it is known from EP 0 398 175 to lead a small part of the conveying medium between the stator and the rotor for cooling.

Auch sind Magnetkupplungsrotoren mit radialen Rückschaufelnbekannt. Die Schaufeln dienen der Generierung eines Spül- bzw. Kühlmediumstromes. Diese radialen Schaufeln sind stirnseitig am Magnetkupplungsrotor angeordnet und erzeugen einen Förderstrom in radialer Richtung, indem das Medium durch Fliehkraft zum Außendurchmesser des Rotors hin beschleunigt und durch den Spalt zwischen Rotorumfang und Spalttopf gefördert wird. Diese Förderrichtung zum Außendurchmesser hin ist konträr zu der erforderlichen Fließrichtung, um den Spülmediumstrom unmittelbar in die im Zentrum des Rotors positionierte Rotorlagerung einleiten zu können.Also, magnetic return rotors with radial return vanes are known. The blades serve to generate a flushing or cooling medium flow. These radial blades are arranged on the front side of the magnetic coupling rotor and generate a flow rate in the radial direction by the medium accelerates by centrifugal force to the outer diameter of the rotor and through the Gap between rotor circumference and split pot is promoted. This conveying direction to the outer diameter is contrary to the required flow direction in order to be able to initiate the flushing medium flow directly into the rotor bearing positioned in the center of the rotor.

Radiale Schaufeln erzeugen im allgemeinen nur kleinere Massenströme bei höheren Drücken, so dass nur recht geringe Mengen Spül- bzw. Kühlmedium zur Verfügung stehen und die Förderung infolge Kavitation unterbrochen werden kann. Bei Vergrößerung der radialen Schaufeln wird zwar mehr Medium gefördert, aber die Kavitationsneigung nimmt auch zu. Darüber hinaus bedingen größere Radialschaufeln auch eine höhere hydraulische Leistung, die als Kupplungsverlustleistung einzustufen und daher unerwünscht ist.Radial blades generally produce only smaller mass flows at higher pressures, so that only very small amounts of flushing or cooling medium are available and the promotion can be interrupted due to cavitation. When enlarging the radial blades, although more medium is promoted, but the tendency to cavitation also increases. In addition, larger radial blades also require a higher hydraulic power, which is to be classified as a coupling power loss and therefore undesirable.

Aufgabe der Erfindung ist es eine Kreiselpumpe der eingangs genannten Art so zu verbessern, dass bei geringem hydraulischen Leistungsverlust eine hohe Spül-, Kühl- und Schmierleistung und eine hohe Auslaufsicherheit erzielt wird.The object of the invention is to improve a centrifugal pump of the type mentioned so that at low hydraulic power loss high rinsing, cooling and lubricating performance and high leakage safety is achieved.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, dass der Ringspalt zwischen dem Lagerbereich des inneren Magnetrotors und der Innenwand des rohrförmigen Lagergehäuses in seiner radialen Breite kleiner ist als der Ringspalt zwischen dem inneren Magnetrotor und dem Spaltrohr. Hierdurch wird sichergestellt, dass bei einem Bruch des Gleitlagers der Welle die Flächen des Spaltes im Lagerbereich zuerst aufeinander zu liegen kommen und damit ein Notgleitlager bilden, ehe die Flächen im Bereich des Ringspaltes zwischen Spalttopf und der Außenseite des inneren Magnetrotors aufeinanderliegen. Damit kann es nicht zu einer Zerstörung des Spalttopfes und zu einem Leck kommen.This object is achieved in that the annular gap between the bearing portion of the inner magnet rotor and the inner wall of the tubular bearing housing in its radial width is smaller than the annular gap between the inner magnet rotor and the can. This ensures that at a fraction of the plain bearing of the shaft surfaces of the gap in the storage area first come to rest on each other and thus form a Notgleitlager before the surfaces in the region of the annular gap between the containment shell and the outside of the inner magnet rotor are superimposed. This can not lead to a destruction of the split pot and a leak.

Hierbei ist von Vorteil, wenn zum Erkennen eines Notlaufs nahe der Lager des inneren Magnetrotors mindestens ein Temperatursensor angeordnet ist. Alternativ oder zusätzlich wird vorgeschlagen, dass zum Erkennen eines Notlaufs ein Stromaufnahmesensor in der Zuleitung des antreibenden Elektromotors angeordnet ist.It is advantageous if at least one temperature sensor is arranged to detect an emergency run close to the bearing of the inner magnet rotor. Alternatively or additionally, it is proposed that for detecting an emergency operation, a current consumption sensor is arranged in the supply line of the driving electric motor.

Vorteilhafte Ausgestaltungen der Erfindung sind in der Zeichnung dargestellt und werden im folgenden näher beschrieben. Es zeigen

Fig. 1
einen axialen Schnitt durch den inneren Bereich einer Magnetkupplungskreiselpumpe,
Fig. 2
einen vergrößerten Ausschnitt aus Fig. 1,
Fig. 3
ein Schaltbild der Sensoren.
Advantageous embodiments of the invention are illustrated in the drawings and will be described in more detail below. Show it
Fig. 1
an axial section through the inner region of a magnetic coupling centrifugal pump,
Fig. 2
an enlarged detail of Fig. 1,
Fig. 3
a circuit diagram of the sensors.

Die Kreiselpumpe 1 mit Magnetkupplung weist einen in einer Pumpenkammer sich drehendes Laufrad 2 auf, das auf einem Ende einer Welle 3 befestigt ist. Die Welle 3 trägt eine Wellenhülse 12, die durch zwei Keramik-Radiallager 4, 5 und zwei Keramik-Axiallager 6, 7 gelagert ist, die an der Innenwand eines rohrförmigen Lagergehäuses 8 befestigt sind. Das Lagergehäuse 8 ist an der Wand 11 befestigt, die die Pumpenkammer 9 von dem Innenraum eines Spalttopfes 10 trennt, der an der Trennwand 11 befestigt ist. An der dem Pumpenlaufrad 2 abgewandten Ende trägt die Welle 3 einen inneren topfförmigen Magnetrotor 14. Hierzu ist an der Welle 3 als Befestigungsmittel 15 ein kreisförmiger Boden 16 angeformt, an dessen äußeren Rand ein rohrabschnittförmiger zylindrischer koaxialer Magneträger 17 angeformt ist, an dessen Außenseite die Abtriebsmagnete 18 befestigt sind.The centrifugal pump 1 with magnetic coupling has a rotating in a pump chamber impeller 2, which is fixed to one end of a shaft 3. The shaft 3 carries a shaft sleeve 12, which is supported by two ceramic radial bearings 4, 5 and two ceramic thrust bearings 6, 7, which are fixed to the inner wall of a tubular bearing housing 8. The bearing housing 8 is fixed to the wall 11, which separates the pump chamber 9 from the interior of a split pot 10, which is fixed to the partition wall 11. At the end facing away from the pump impeller 2, the shaft 3 carries an inner pot-shaped magnet rotor 14. For this purpose, a circular bottom 16 is integrally formed on the shaft 3 as a fastening means 15, on the outer edge of a tubular coaxial magnetic carrier 17 is formed on the outer edge, on the outside of the output magnets 18 are attached.

Das Lagergehäuse 8 erstreckt sich somit koaxial in dem Magnetrotor 14, wobei zwischen dem Magnetträger 17 und dem Lagergehäuse 8 ein Ringraum 19 und zwischen dem Magnetträger 17 und dem Spalttopf 10 ein Ringspalt 20 besteht. Außen ist der Spalttopf 10 von einem nicht dargestellten Antriebstopf umgeben, der innen die Antriebsmagnete trägt und über eine koaxiale Welle von einem Elektromotor angetrieben ist.The bearing housing 8 thus extends coaxially in the magnet rotor 14, wherein between the magnet carrier 17 and the bearing housing 8, an annular space 19 and between the magnet carrier 17 and the gap pot 10 is an annular gap 20. Outside, the split pot 10 is surrounded by a drive pot, not shown, which carries the drive magnets inside and is driven by a coaxial shaft of an electric motor.

Innerhalb des rohrförmigen Magnetträgers 17 ist im Boden 16 des inneren Magnetrotors 14 stirnseitig ein insbesondere ringförmiger koaxialer Durchflusskanal (Ringraum) 21 eingebracht, der in Höhe des Ringraums 19 liegt und von zwei bis vier radialen Axialschaufeln 22 durchquert ist, die den Magnetträger 17 am Boden 16 halten. Die Schaufeln sind in regelmäßigen Abständen (Winkeln) am Boden und Magnetträger angeformt und weisen einen Anstellwinkel von 5 bis 15 Grad auf.Within the tubular magnet carrier 17 in the bottom 16 of the inner magnet rotor 14 frontally a particular annular coaxial flow channel (annulus) 21 is introduced, which is in the amount of the annulus 19 and is traversed by two to four radial axial blades 22, the magnetic carrier 17 at the bottom of the 16th hold. The blades are formed at regular intervals (angles) on the bottom and magnetic carrier and have an angle of attack of 5 to 15 degrees.

Die vorzugsweise drei Schaufeln 22 fördern die durch Eintrittskanäle 23 in den Spaltrohrinnenraum eintretende Flüssigkeit aus dem Ringspalt 20 in den Zwischenraum 24 zwischen Lagergehäuse 8 und Wellenhülse 12, so dass die hierdurch geförderte Flüssigkeit durch die Radial- und Axiallager 4 bis 7 hindurchfließt um danach zur Pumpenkammer zurückzufließen.The preferably three blades 22 convey the liquid entering through the inlet channels 23 into the crevice interior space from the annular gap 20 into the intermediate space 24 between the bearing housing 8 and the shaft sleeve 12, so that the liquid conveyed through it flows through the radial and axial bearings 4 to 7 to the pumping chamber flow back.

Das rohrförmige Lagergehäuse 8 bildet am vom Laufrad 2 abgewandten stirnseitigen Ende einen Ringspalt 25 mit einem inneren Bereich des inneren Magnetrotors bzw. der Befestigungsmittel 15. Hierbei ist auf der Welle 3 oder auf der Wellenhülse 12 ein koaxialer Ring 26 befestigt, in dem das äußere Axiallager 7 einliegt. Die Außenseite des Ringes 26 bildet mit der Innenseite des Lagergehäuses 8 den Ringspalt 25, dessen radiale Breite B1 geringer ist als die radiale Breite B2 des Ringspaltes 20.The tubular bearing housing 8 forms at the end facing away from the impeller 2 an annular gap 25 with an inner portion of the inner magnet rotor or the fastening means 15. Here, on the shaft 3 or on the shaft sleeve 12, a coaxial ring 26 is fixed, in which the outer thrust bearing 7 is present. The outer side of the ring 26 forms, with the inside of the bearing housing 8, the annular gap 25 whose radial width B1 is less than the radial width B2 of the annular gap 20.

In der Innenseite bzw. Innenwand des Lagergehäuses 8 ist im Bereich des Spaltes 25 eine schraubenförmige koaxiale Nut 27 eingebracht, die im Spalt 25 die Flüssigkeit zum Raum 24 fördert. Alternativ oder zusätzlich kann die Nut 27 auch in der Außenwand des Magnetrotors bzw. des Ringes 26 angeordnet sein.In the inner side or inner wall of the bearing housing 8, a helical coaxial groove 27 is introduced in the region of the gap 25, which in the gap 25 the fluid promotes the space 24. Alternatively or additionally, the groove 27 may also be arranged in the outer wall of the magnet rotor or of the ring 26.

Nahe der Lager 4 bis 7 insbesondere auf der Außenseite des rohrförmigen Lagergehäuses 8 ist zu beiden Enden des Lagergehäuses 8 vorzugsweise zumindest an dem dem Laufrad abgewandten Ende des Lagergehäuses 8 ein Temperatursensor 28 befestigt, der frühzeitig anzeigt, wenn ein Radiallager defekt ist und die Flächen des Spaltes 25 aneinander reiben. Stattdessen oder zusätzlich kann ein Lagerdefekt durch einen Stromaufnahmesensor 29 angezeigt werden, der in oder an der Zuleitung 31 des Elektromotors liegt. Diese Sensoren sind mit einer Warneinrichtung (Hupe Leuchte, Verbindung zur Anlagenüberwachung) 30 verbunden.Near the bearings 4 to 7, in particular on the outside of the tubular bearing housing 8 at both ends of the bearing housing 8 preferably at least at the end facing away from the impeller of the bearing housing 8, a temperature sensor 28 is attached, indicating early, when a radial bearing is defective and the surfaces of the Rub gap 25 together. Instead or in addition, a bearing defect may be indicated by a current sensing sensor 29 located in or on the lead 31 of the electric motor. These sensors are connected to a warning device (horn light, connection to the system monitoring) 30.

Claims (3)

  1. Centrifugal pump with a magnetic coupling arranged between the pump shaft and the drive shaft and with a can (10) in the magnetic gap between the inner magnetic rotor (14) of the pump and the outer magnetic rotor of the drive shaft, wherein inside the can (10), through which the discharge fluid flows, the inner magnetic rotor (14) is held on a tubular bearing housing (8) which surrounds the pump impeller shaft (3), which on the side facing away from the pump impeller (2) has fastening means (15) for the inner magnetic rotor (14), arranged between the bearing housing (8) and the can (10), characterised in that the annular gap (25) between the bearing area of the inner magnetic rotor (14) and the inner wall of the tubular bearing housing (8) is smaller in its radial width (B1) than the annular gap (20) between the inner magnetic rotor (14) and the can (10).
  2. Centrifugal pump according to claim 1, characterised in that at least one temperature sensor (28) is arranged to detect an emergency run near the bearing (4-7) of the inner magnetic rotor (14).
  3. Centrifugal pump according to claim 1 or 2, characterised in that a current recording sensor (29) is arranged in the feed line (30) of the driving electric motor to detect an emergency run.
EP01108334A 2000-05-22 2001-04-03 Centrifugal pump with magnetic coupling Expired - Lifetime EP1158174B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP06015105A EP1719914B1 (en) 2000-05-22 2001-04-03 Centrifugal pump with magnetic coupling

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10024953 2000-05-22
DE10024953A DE10024953A1 (en) 2000-05-22 2000-05-22 Centrifugal pump with magnetic coupling

Related Child Applications (1)

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EP06015105A Division EP1719914B1 (en) 2000-05-22 2001-04-03 Centrifugal pump with magnetic coupling

Publications (3)

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EP1158174A2 EP1158174A2 (en) 2001-11-28
EP1158174A3 EP1158174A3 (en) 2005-09-07
EP1158174B1 true EP1158174B1 (en) 2007-03-14

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US (1) US6554576B2 (en)
EP (2) EP1158174B1 (en)
AT (2) ATE486219T1 (en)
DE (3) DE10024953A1 (en)

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8337166B2 (en) * 2001-11-26 2012-12-25 Shurflo, Llc Pump and pump control circuit apparatus and method
DE10221843B4 (en) * 2002-05-16 2004-12-30 Minebea Co., Ltd. Electric motor for use as a pump motor and pump
WO2011022557A2 (en) * 2009-08-19 2011-02-24 Aspen Motion Technologies, Inc. D/B/A Magnetic drive pump assembly with integrated motor
DE102009052856B3 (en) * 2009-11-11 2010-09-09 Leistritz Ag Pump i.e. screw pump, has magnetic clutch provided with rotor shaft that is rotatably supported by pump housing, and suction chamber and slit pot connected with each other over line by fluid
CN102844576B (en) * 2010-03-29 2015-12-02 Ntn株式会社 Fluid dynamic-pressure bearing device and assembling method thereof
CN102465884A (en) * 2010-11-17 2012-05-23 黄佳华 Vertical magnetic drive slurry pump
DE102011114191A1 (en) 2011-09-22 2013-03-28 Eagleburgmann Germany Gmbh & Co. Kg Slit pot for a magnetic coupling with improved fluid flow
TW201317459A (en) * 2011-10-26 2013-05-01 Assoma Inc Permanent magnet canned pump structure improvement
US20140271270A1 (en) * 2013-03-12 2014-09-18 Geotek Energy, Llc Magnetically coupled expander pump with axial flow path
DE102014006568A1 (en) * 2013-05-08 2014-11-13 Ksb Aktiengesellschaft Pump arrangement and method for producing a split pot of the pump assembly
DE102013007849A1 (en) * 2013-05-08 2014-11-13 Ksb Aktiengesellschaft pump assembly
CN103410739B (en) * 2013-07-24 2016-09-21 黄佳华 Vertical submerged multiple-set slag-pulp magnetic drive pump
CN104776033B (en) * 2014-01-14 2017-09-15 高涵文 A kind of magnetic drive pump of corrosion-resistant anti-dry grinding
US9771938B2 (en) 2014-03-11 2017-09-26 Peopleflo Manufacturing, Inc. Rotary device having a radial magnetic coupling
US9920764B2 (en) 2015-09-30 2018-03-20 Peopleflo Manufacturing, Inc. Pump devices
CN110873061B (en) * 2018-08-29 2023-08-01 广东德昌电机有限公司 Pump body and method for manufacturing rotor assembly for pump body
DE202019101723U1 (en) * 2019-03-26 2020-06-29 Meßner GmbH & Co. KG Pond pump
KR102484602B1 (en) * 2020-11-23 2023-01-06 주식회사 코아비스 Electric water pump
DE102020132907A1 (en) 2020-12-10 2022-06-15 Eagleburgmann Germany Gmbh & Co. Kg Magnetic clutch with improved cooling

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB922319A (en) * 1960-03-28 1963-03-27 Klaus Franz Centrifugal pump
US3420184A (en) * 1967-05-17 1969-01-07 Julius L Englesberg Pump employing magnetic drive
DE2639540A1 (en) * 1976-09-02 1978-03-09 Grundfos As Plain bearing sleeve for circulation pump shafts - has diametrically opposite overlapping grooves for access of liquid for lubricating
DE2752249B2 (en) * 1977-11-23 1979-09-27 Klein, Schanzlin & Becker Ag, 6710 Frankenthal Protective device for pumps
JPS6352992U (en) * 1986-09-25 1988-04-09
DE8717855U1 (en) * 1987-02-14 1990-09-27 Richter Chemie Technik GmbH, 47906 Kempen Leak detection device for a magnetic centrifugal pump
DE3715484A1 (en) * 1987-05-09 1988-11-17 Klaus Union Armaturen MAGNETIC PUMP DRIVE
EP0308372B1 (en) * 1987-09-15 1991-04-03 Bieri Pumpenbau Ag Circulation pump, particularly for hot water systems
DE8906020U1 (en) * 1989-05-13 1989-06-29 Rheinhütte GmbH & Co., 6200 Wiesbaden Magnetic coupling pump
EP0431332B1 (en) * 1989-11-08 1995-11-02 Sanwa Tokushu Seiko Co., Ltd. Magnetically driven pump
US5184945A (en) * 1991-12-27 1993-02-09 Assoma, Inc. Bushing structure for using in magnetically driving centrifugal pumps
DE4212982C2 (en) * 1992-04-18 1996-04-11 Lederle Pumpen & Maschf Pump for hot fluids
DE9316897U1 (en) * 1993-11-04 1994-07-28 Renner GmbH, 75433 Maulbronn Magnetic pump with overheating protection
US5944489A (en) * 1996-12-11 1999-08-31 Crane Co. Rotary fluid pump

Also Published As

Publication number Publication date
DE10024953A1 (en) 2001-11-29
EP1719914B1 (en) 2010-10-27
EP1158174A2 (en) 2001-11-28
ATE486219T1 (en) 2010-11-15
ATE356937T1 (en) 2007-04-15
EP1158174A3 (en) 2005-09-07
DE50115684D1 (en) 2010-12-09
EP1719914A2 (en) 2006-11-08
EP1719914A3 (en) 2006-11-15
US20010043865A1 (en) 2001-11-22
US6554576B2 (en) 2003-04-29
DE50112181D1 (en) 2007-04-26

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