EP1719914B1 - Centrifugal pump with magnetic coupling - Google Patents

Centrifugal pump with magnetic coupling Download PDF

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Publication number
EP1719914B1
EP1719914B1 EP06015105A EP06015105A EP1719914B1 EP 1719914 B1 EP1719914 B1 EP 1719914B1 EP 06015105 A EP06015105 A EP 06015105A EP 06015105 A EP06015105 A EP 06015105A EP 1719914 B1 EP1719914 B1 EP 1719914B1
Authority
EP
European Patent Office
Prior art keywords
shaft
pump
bearing housing
rotor
gap
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
EP06015105A
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German (de)
French (fr)
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EP1719914A3 (en
EP1719914A2 (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
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Publication of EP1719914A2 publication Critical patent/EP1719914A2/en
Publication of EP1719914A3 publication Critical patent/EP1719914A3/en
Application granted granted Critical
Publication of EP1719914B1 publication Critical patent/EP1719914B1/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 arranged between a pump shaft and a drive shaft magnetic coupling 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 pump shaft has on the side facing away from the pump impeller fastening means for the inner magnet rotor.
  • a conventional magnetic pump drive is from the DE 37 15 484 known. In addition, it is from the EP 0 398 175 known to lead a small portion of the fluid to be cooled between the stator and rotor.
  • magnetic coupling 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 in the radial direction by the medium accelerated by centrifugal force to the outer diameter of the rotor and is conveyed through the gap between the rotor circumference and split pot. 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, a high leakage safety is achieved.
  • the helical groove generates a sufficiently large flow through the radial and thrust bearings through with little design effort.
  • a respective helical groove is arranged at both ends of the bearing housing in the respective gap.
  • 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 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.
  • Outside the containment shell 10 is surrounded by a drive pot, not shown, the inside carries the drive magnets and is driven by a coaxial shaft of an electric motor.
  • annular coaxial flow channel (annulus) 21 is introduced, which is equal to the annular space 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 fluid 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 region 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 conveys the liquid to the space 24 in the gap 25.
  • 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 to both ends of the bearing housing 8 preferably at least at the end remote from the impeller of the bearing housing 8, which indicates early, if 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 be located in or on the supply line 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 einer Pumpenwelle und einer Antriebswelle angeordneten Magnetkupplung und mit einem Spalttopf im Magnetspalt zwischen dem inneren Magnetrotor der Pumpe und dem äußeren Magnetrotor der Antriebswelle, wobei die Pumpenwelle auf der dem Pumpenlaufrad abgewandten Seite Befestigungsmittel für den inneren Magnetrotor besitzt.The invention relates to a centrifugal pump with a arranged between a pump shaft and a drive shaft magnetic coupling 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 pump shaft has on the side facing away from the pump impeller fastening means for the inner magnet rotor.

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 from the DE 37 15 484 known. In addition, it is from the EP 0 398 175 known to lead a small portion of the fluid to be cooled between the stator and rotor.

Auch sind Magnetkupplungsrotoren mit radialen Rückschaufeln bekannt. 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 coupling 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 in the radial direction by the medium accelerated by centrifugal force to the outer diameter of the rotor and is conveyed through the gap between the rotor circumference and split pot. 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.

Aus der Druckschrift US 4812108 die die Gattungsmerkmale des Anspruchs 1 offenbart, ist es bekannt, einen Kanal schraubenförmig auszuführen, der an der Außenseite der Welle in einem der Lagerteile entlang läuft, um Flüssigkeit zu fördern. Bei dieser bekannten Konstruktion ist auf Grund des breiten Spaltes eine effektive Förderung begrenzt, so dass nur eine geringe Kühl- und Spülleistung erreicht wird. Eine ähnliche Konstruktion ist auch aus der US 5160246 bekannt, wobei hier ein äußeres Lager nicht vorhanden ist und damit nur ein sehr enger Bereich einer Kühlung erzielt wird.From the publication US 4812108 discloses the generic features of claim 1, it is known to perform a helical channel, which runs along the outside of the shaft in one of the bearing parts to convey liquid. In this known construction effective promotion is limited due to the wide gap, so that only a small cooling and flushing performance is achieved. A similar construction is also from the US 5160246 known, in which case an outer bearing is not present and thus only a very narrow range of cooling is achieved.

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, 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, a high leakage safety is achieved.

Diese Aufgabe wird erfindungsgemäß durch die kennzeichnenden Merkmale des Anspruchs 1 gelöst.This object is achieved by the characterizing features of claim 1.

Die schraubenförmige Nut erzeugt eine ausreichend große Strömung durch die Radial- und Axiallager hindurch bei geringem konstruktiven Aufwand.The helical groove generates a sufficiently large flow through the radial and thrust bearings through with little design effort.

Vorzugsweise wird vorgeschlagen, dass je eine schraubenförmige Nut an beiden Enden des Lagergehäuses im jeweiligen Spalt angeordnet ist.It is preferably proposed that a respective helical groove is arranged at both ends of the bearing housing in the respective gap.

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 section 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 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 containment shell 10 is surrounded by a drive pot, not shown, the inside carries the drive magnets 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 equal to the annular space 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 fluid 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 region 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 conveys the liquid to the space 24 in the gap 25. 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, a temperature sensor 28 is attached to both ends of the bearing housing 8 preferably at least at the end remote from the impeller of the bearing housing 8, which indicates early, if 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 be located in or on the supply line 31 of the electric motor. These sensors are connected to a warning device (horn light, connection to the system monitoring) 30.

Claims (2)

  1. Centrifugal pump with a magnetic coupling arranged between a pump shaft (3) and a drive shaft and with a containment shell (10) in the magnetic gap between the inner magnetic rotor (14) of the pump and the outer magnetic rotor of the drive shaft, in which the pump shaft (3) has means of fastening (15) for the inner magnetic rotor (14) on the side facing away from the pump impeller (2), characterised in that two axial bearings of the pump shaft (3) and two radial bearings arranged between them are arranged between a tubular bearing housing (8) surrounding the pump shaft (3) and a shaft sleeve (12) carried by the pump shaft (3), in which inside the containment shell (10), through which a conveying liquid flows, the inner magnetic rotor (14) is supported on the tubular bearing housing (8) and arranged between the bearing housing (8) and the containment shell (10), in which a coaxial ring (26) is fastened on the shaft sleeve (12), in which an axial bearing (7) facing away from the pump impeller is enclosed, in which the outside of the ring (26) forms a ring gap (25) with the inside of the bearing housing (8) and in the ring gap (25) a helical groove (27) is arranged in the inner wall of the tubular bearing housing (8) and/or in the outer wall of the ring (26), with which conveying liquid may be conveyed through the bearings (4 - 7) of the pump shaft (3) into an intermediate area (24) between the bearing housing (8) and the shaft sleeve (12).
  2. Centrifugal pump according to claim 1, characterised in that a helical groove (27) is arranged at both ends of the bearing housing (8) in each gap (25).
EP06015105A 2000-05-22 2001-04-03 Centrifugal pump with magnetic coupling Expired - Lifetime EP1719914B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10024953A DE10024953A1 (en) 2000-05-22 2000-05-22 Centrifugal pump with magnetic coupling
EP01108334A EP1158174B1 (en) 2000-05-22 2001-04-03 Centrifugal pump with magnetic coupling

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP01108334A Division EP1158174B1 (en) 2000-05-22 2001-04-03 Centrifugal pump with magnetic coupling
EP01108334.2 Division 2001-04-03

Publications (3)

Publication Number Publication Date
EP1719914A2 EP1719914A2 (en) 2006-11-08
EP1719914A3 EP1719914A3 (en) 2006-11-15
EP1719914B1 true EP1719914B1 (en) 2010-10-27

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EP06015105A Expired - Lifetime EP1719914B1 (en) 2000-05-22 2001-04-03 Centrifugal pump with magnetic coupling
EP01108334A Expired - Lifetime EP1158174B1 (en) 2000-05-22 2001-04-03 Centrifugal pump with magnetic coupling

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EP01108334A Expired - Lifetime EP1158174B1 (en) 2000-05-22 2001-04-03 Centrifugal pump with magnetic coupling

Country Status (4)

Country Link
US (1) US6554576B2 (en)
EP (2) EP1719914B1 (en)
AT (2) ATE356937T1 (en)
DE (3) DE10024953A1 (en)

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Publication number Priority date Publication date Assignee Title
CN102465884A (en) * 2010-11-17 2012-05-23 黄佳华 Vertical magnetic drive slurry pump

Also Published As

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ATE356937T1 (en) 2007-04-15
DE10024953A1 (en) 2001-11-29
DE50112181D1 (en) 2007-04-26
EP1158174A2 (en) 2001-11-28
EP1719914A3 (en) 2006-11-15
US6554576B2 (en) 2003-04-29
EP1158174A3 (en) 2005-09-07
EP1719914A2 (en) 2006-11-08
ATE486219T1 (en) 2010-11-15
US20010043865A1 (en) 2001-11-22
EP1158174B1 (en) 2007-03-14
DE50115684D1 (en) 2010-12-09

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