EP1158174A2 - Centrifugal pump with magnetic coupling - Google Patents

Centrifugal pump with magnetic coupling Download PDF

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Publication number
EP1158174A2
EP1158174A2 EP01108334A EP01108334A EP1158174A2 EP 1158174 A2 EP1158174 A2 EP 1158174A2 EP 01108334 A EP01108334 A EP 01108334A EP 01108334 A EP01108334 A EP 01108334A EP 1158174 A2 EP1158174 A2 EP 1158174A2
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EP
European Patent Office
Prior art keywords
shaft
bearing housing
magnet rotor
pump
rotor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP01108334A
Other languages
German (de)
French (fr)
Other versions
EP1158174B1 (en
EP1158174A3 (en
Inventor
Ulrich Rennett
Manfred Sett
Alfred Mersch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ITT Manufacturing Enterprises LLC
Original Assignee
Richter Chemie Technik GmbH
ITT Manufacturing Enterprises LLC
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Richter Chemie Technik GmbH, ITT Manufacturing Enterprises LLC filed Critical Richter Chemie Technik GmbH
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
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • 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 between the pump shaft and Drive shaft arranged magnetic coupling and with a containment shell in the Magnetic gap between the inner magnet rotor of the pump and the outer one Magnet rotor of the drive shaft, being inside of the fluid flowed through the containment shell of the inner magnet rotor on a tubular Bearing housing is mounted, which surrounds the pump impeller shaft, which on the Fastener for the inner side facing away from the pump impeller Has a magnetic rotor between the bearing housing and the containment shell is arranged.
  • Magnetic coupling rotors with radial rear blades are known.
  • the Blades are used to generate a flushing or cooling medium flow.
  • This radial blades are arranged on the face of the magnetic coupling rotor and generate a flow in the radial direction by passing the medium through Centrifugal force accelerated towards the outside diameter of the rotor and through the Gap between rotor circumference and containment shell is promoted.
  • This direction of funding to the outside diameter is contrary to the required flow direction in order the flushing medium flow directly into that positioned in the center of the rotor To initiate rotor bearings.
  • Radial blades generally only generate smaller mass flows higher pressures, so that only very small amounts of flushing or cooling medium Are available and the production due to cavitation are interrupted can. When the radial blades are enlarged, more medium becomes available promoted, but the tendency to cavitation also increases. Beyond condition larger radial blades also have higher hydraulic power than Coupling power loss rating and is therefore undesirable.
  • the object of the invention is a centrifugal pump of the type mentioned above to improve that with low hydraulic power loss a high Rinsing, cooling and lubricating performance and a high leak-proofness is achieved.
  • this object is achieved in that the annular gap between the bearing area of the inner magnetic 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 will ensures that the surfaces of the Gaps in the storage area come to lie on top of each other first and thus Form emergency slide bearings before the surfaces in the area of the annular gap between The containment shell and the outside of the inner magnetic rotor lie on top of each other. In order to there can be no destruction of the containment shell and a leak.
  • annular gap between the bearing area of the inner magnetic 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.
  • a current consumption sensor in the supply line to detect an emergency operation of the driving electric motor is arranged.
  • the helical groove creates a sufficiently large flow through the Radial and axial bearings through with little design effort. It is preferably proposed that a helical groove on each Ends of the bearing housing is arranged in the respective gap.
  • the centrifugal pump 1 with magnetic coupling has one in a pump chamber rotating impeller 2, which is fixed on one end of a shaft 3.
  • the Shaft 3 carries a shaft sleeve 12, which by two ceramic radial bearings 4, 5 and two ceramic thrust bearings 6, 7 is mounted on the inner wall of a tubular bearing housing 8 are attached.
  • the bearing housing 8 is on the Wall 11 attached to the pump chamber 9 from the interior of a Separates can 10, which is attached to the partition 11.
  • At that End of the pump impeller 2 facing away from the shaft 3 carries an inner Pot-shaped magnetic rotor 14.
  • the fastening means 15 on the shaft 3 a circular base 16 is formed, on the outer edge of a tubular cylindrical coaxial magnetic carrier 17 is formed on the outside of which the output magnets 18 are attached.
  • the bearing housing 8 thus extends coaxially in the magnet rotor 14, wherein an annular space 19 and between the magnetic carrier 17 and the bearing housing 8 there is an annular gap 20 between the magnet carrier 17 and the containment shell 10.
  • the containment shell 10 is surrounded by a drive pot, not shown, which carries the drive magnets inside and via a coaxial shaft from one Electric motor is driven.
  • a ring-shaped coaxial Flow channel (annular space) 21 is introduced, which is at the level of the annular space 19 and is crossed by two to four radial axial blades 22 which the Hold magnet carrier 17 on floor 16.
  • the blades are regular Distances (angles) formed on the floor and magnetic carrier and have one Angle of attack from 5 to 15 degrees.
  • the preferably three blades 22 promote through the inlet channels 23 in the Liquid entering the interior of the canned tube from the annular gap 20 into the Gap 24 between the bearing housing 8 and shaft sleeve 12, so that the fluid conveyed thereby through the radial and axial bearings 4 to 7 flows through and then flows back to the pump chamber.
  • the tubular bearing housing 8 forms on the side facing away from the impeller 2 end face an annular gap 25 with an inner region of the inner Magnet rotor or the fastener 15.
  • an annular gap 25 with an inner region of the inner Magnet rotor or the fastener 15.
  • the outside of the ring 26 forms with the inside of the Bearing housing 8 the annular gap 25, the radial width B1 is less than that radial width B2 of the annular gap 20.
  • a helical coaxial groove 27 which in the gap 25 promotes the liquid to room 24.
  • the groove 27 can also be arranged in the outer wall of the magnetic rotor or the ring 26.

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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 between the pump shaft and Drive shaft arranged magnetic coupling and with a containment shell in the Magnetic gap between the inner magnet rotor of the pump and the outer one Magnet rotor of the drive shaft, being inside of the fluid flowed through the containment shell of the inner magnet rotor on a tubular Bearing housing is mounted, which surrounds the pump impeller shaft, which on the Fastener for the inner side facing away from the pump impeller Has a magnetic rotor between the bearing housing and the containment shell is arranged.

Bekannt sind Magnetkupplungsrotoren mit radialen Rückschaufeln. 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. Magnetic coupling rotors with radial rear blades are known. The Blades are used to generate a flushing or cooling medium flow. This radial blades are arranged on the face of the magnetic coupling rotor and generate a flow in the radial direction by passing the medium through Centrifugal force accelerated towards the outside diameter of the rotor and through the Gap between rotor circumference and containment shell is promoted. This direction of funding to the outside diameter is contrary to the required flow direction in order the flushing medium flow directly into that positioned in the center of the rotor To initiate rotor bearings.

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 only generate smaller mass flows higher pressures, so that only very small amounts of flushing or cooling medium Are available and the production due to cavitation are interrupted can. When the radial blades are enlarged, more medium becomes available promoted, but the tendency to cavitation also increases. Beyond condition larger radial blades also have higher hydraulic power than Coupling power loss rating and is 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 a centrifugal pump of the type mentioned above to improve that with low hydraulic power loss a high Rinsing, cooling and lubricating performance and a high leak-proofness is achieved.

Diese Aufgabe wird erfindungsgemäß dadurch gelöast, 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.According to the invention, this object is achieved in that the annular gap between the bearing area of the inner magnetic 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 will ensures that the surfaces of the Gaps in the storage area come to lie on top of each other first and thus Form emergency slide bearings before the surfaces in the area of the annular gap between The containment shell and the outside of the inner magnetic rotor lie on top of each other. In order to there can be no destruction of the containment shell and a leak.

Hierbei ist von Vorteil, wenn 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. Alternativ oder zusätzlich wird vorgesch lagen, dass zum Erkennen eines Notlaufs ein Stromaufnahmesensor in der Zuleitung des antreibenden Elektromotors angeordnet ist.It is advantageous here if the annular gap between the bearing area of the inner magnetic 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. Alternatively or additionally, it is suggested that a current consumption sensor in the supply line to detect an emergency operation of the driving electric motor is arranged.

Besonders vorteilhaft ist es, wenn im Ringspalt zwischen dem Lagerbereich des inneren Magnetrotors und der Innenwand des rohrförmigen Lagergehäuses eine schraubenförmige Nut in der Innenwand des rohrförmigen Lagergehäuses und/oder in der Außenwand des Magnetrotorlagers angeordnet ist, die die Flüssigkeit durch die Lager fördert, die zwischen dem Lagergehäuse und der Welle oder der Wellenhülse angeordnet sind.It when the in the annular gap between the storage area of the inner magnetic rotor and the inner wall of the tubular bearing housing a helical groove in the inner wall of the tubular bearing housing and / or is arranged in the outer wall of the magnetic rotor bearing, which the Promotes liquid through the bearing that is between the bearing housing and the Shaft or the shaft sleeve are arranged.

Die schraubenförmige Nut erzeugt eine ausreichend große Strömung durch die Radial- und Axiallager hindurch bei geringem konstruktiven Aufwand. Vorzugsweise wird vorgeschlagen, dass je eine schraubenförmige Nut an beiden Enden des Lagergehäuses im jeweiligen Spalt angeordnet ist.The helical groove creates a sufficiently large flow through the Radial and axial bearings through with little design effort. It is preferably proposed that a helical groove on each Ends of the bearing housing is arranged 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 shown in the drawing and are described in more detail below. Show it
Fig. 1
an axial section through the inner region of a magnetic coupling centrifugal pump,
Fig. 2
2 shows an enlarged detail from 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 one in a pump chamber rotating impeller 2, which is fixed on one end of a shaft 3. The Shaft 3 carries a shaft sleeve 12, which by two ceramic radial bearings 4, 5 and two ceramic thrust bearings 6, 7 is mounted on the inner wall of a tubular bearing housing 8 are attached. The bearing housing 8 is on the Wall 11 attached to the pump chamber 9 from the interior of a Separates can 10, which is attached to the partition 11. At that End of the pump impeller 2 facing away from the shaft 3 carries an inner Pot-shaped magnetic rotor 14. For this purpose, the fastening means 15 on the shaft 3 a circular base 16 is formed, on the outer edge of a tubular cylindrical coaxial magnetic carrier 17 is formed on the outside of which 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 an annular space 19 and between the magnetic carrier 17 and the bearing housing 8 there is an annular gap 20 between the magnet carrier 17 and the containment shell 10. On the outside, the containment shell 10 is surrounded by a drive pot, not shown, which carries the drive magnets inside and via a coaxial shaft from one Electric motor is driven.

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.Inside the tubular magnet carrier 17 is in the bottom 16 of the inner Magnetic rotor 14 on the end face, in particular a ring-shaped coaxial Flow channel (annular space) 21 is introduced, which is at the level of the annular space 19 and is crossed by two to four radial axial blades 22 which the Hold magnet carrier 17 on floor 16. The blades are regular Distances (angles) formed on the floor and magnetic carrier and have one Angle of attack from 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 promote through the inlet channels 23 in the Liquid entering the interior of the canned tube from the annular gap 20 into the Gap 24 between the bearing housing 8 and shaft sleeve 12, so that the fluid conveyed thereby through the radial and axial bearings 4 to 7 flows through and then flows back to the pump chamber.

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 on the side facing away from the impeller 2 end face an annular gap 25 with an inner region of the inner Magnet rotor or the fastener 15. Here is on the shaft 3 or the shaft sleeve 12 is attached to a coaxial ring 26 in which the outer axial bearing 7 lies. The outside of the ring 26 forms with the inside of the Bearing housing 8 the annular gap 25, the radial width B1 is less than that 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 inside or inside wall of the bearing housing 8 is in the range of Gap 25 introduced a helical coaxial groove 27 which in the gap 25 promotes the liquid to room 24. Alternatively or additionally, the groove 27 can also be arranged in the outer wall of the magnetic rotor or 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 especially on the outside of the tubular Bearing housing 8 is preferred at both ends of the bearing housing 8 at least at the end of the bearing housing 8 facing away from the impeller Temperature sensor 28 attached, which indicates early when a radial bearing is defective and rub the surfaces of the gap 25 together. Instead, or In addition, a bearing defect can be indicated by a current consumption sensor 29 be in or on the lead 31 of the electric motor. These sensors are equipped with a warning device (horn light, connection to the Plant monitoring) 30 connected.

Claims (5)

Kreiselpumpe mit einer zwischen Pumpenwelle und Antriebswelle angeordneten Magnetkupplung und mit einem Spalttopf (10) im Magnetspalt zwischen dem inneren Magnetrotor (14) der Pumpe und dem äußeren Magnetrotor der Antriebswelle, wobei im Inneren des von der Förderflüssigkeit durchflossenen Spalttopfes (10) der innere Magnetrotor (14) an einem rohrförmigen Lagergehäuse (8) gelagert ist, das die Pumpenlaufradwelle (3) umgibt, die auf der dem Pumpenlaufrad (2) abgewandten Seite Befestigungsmittel (15) für den inneren Magnetrotor (14) besitzt, der zwischen dem Lagergehäuse (8) und dem Spalttopf (10) angeordnet ist, dadurch gekennzeichnet,dass der Ringspalt (25) zwischen dem Lagerbereich des inneren Magnetrotors (14) und der Innenwand des rohrförmigen Lagergehäuses (8) in seiner radialen Breite (B1) kleiner ist als der Ringspalt (20) zwischen dem inneren Magnetrotor (14) und dem Spaltrohr (10).Centrifugal pump with a magnetic coupling arranged between the pump shaft and the drive shaft and with a containment shell (10) in the magnetic gap between the inner magnet rotor (14) of the pump and the outer magnet rotor of the drive shaft, the inner magnet rotor (10) 14) is mounted 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 magnet rotor (14) which is located between the bearing housing (8) and the containment shell (10), characterized 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 magnet rotor (14) and the can (10). Kreiselpumpe nach Anspruch 1,dadurch gekennzeichnet, dass zum Erkennen eines Notlaufs nahe der Lager (4 - 7) des inneren Magnetrotors (14) mindestens ein Temperatursensor (28) angeordnet ist.Centrifugal pump according to claim 1, characterized in that at least one temperature sensor (28) is arranged to detect an emergency operation near the bearings (4-7) of the inner magnet rotor (14). Kreiselpumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass zum Erkennen eines Notlaufs ein Stromaufnahmesensor (29) in der Zuleitung (30) des antreibenden Elektromotors angeordnet ist.Centrifugal pump according to claim 1 or 2, characterized in that a current consumption sensor (29) is arranged in the feed line (30) of the driving electric motor to detect an emergency operation. Kreiselpumpe mit einer zwischen Pumpenwelle und Antriebswelle angeordneten Magnetkupplung und mit einem Spalttopf (10) im Magnetspalt zwischen dem inneren Magnetrotor (14) der Pumpe und dem äußeren Magnetrotor der Antriebswelle, wobei im Inneren des von der Förderflüssigkeit durchflossenen Spalttopfes (10) der innere Magnetrotor (14) an einem rohrförmigen Lagergehäuse (8) gelagert ist, das die Pumpenlaufradwelle (3) umgibt, die auf der dem Pumpenlaufrad (2) abgewandten Seite Befestigungsmittel (15) für den inneren Magnetrotor (14) besitzt, der zwischen dem Lagergehäuse (8) und dem Spalttopf (10) angeordnet ist insbesondere nach Anspruch 1, 2 oder 3, dadurch gekennzeichnet, dass im Ringspalt (25) zwischen dem Lagerbereich des inneren Magnetrotors und der Innenwand des rohrförmigen Lagergehäuses (8) eine schraubenförmige Nut (27) in der Innenwand des rohrförmigen Lagergehäuses (8) und/oder in der Außenwand des Magnetrotorlagers (26) angeordnet ist, die die Flüssigkeit durch die Lager (4 - 7) fördert, die zwischen dem Lagergehäuse (8) und der Welle (3) oder der Wellenhülse (12) angeordnet sind.Centrifugal pump with a magnetic coupling arranged between the pump shaft and the drive shaft and with a containment shell (10) in the magnetic gap between the inner magnet rotor (14) of the pump and the outer magnet rotor of the drive shaft, the inner magnet rotor (10) 14) is mounted 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 magnet rotor (14) which is located between the bearing housing (8) and the containment shell (10) is arranged in particular according to claim 1, 2 or 3, characterized in that in the annular gap (25) between the bearing area of the inner magnet rotor and the inner wall of the tubular bearing housing (8) a helical groove (27) in the inner wall of the tubular bearing housing (8) and / or in the outer wall of the magnetic rotor bearing (26), which the liquid durc h promotes the bearings (4 - 7), which are arranged between the bearing housing (8) and the shaft (3) or the shaft sleeve (12). Kreiselpumpe nach Anspruch 4, dadurch gekennzeichnet, dass je eine schraubenförmige Nut an beiden Enden des Lagergehäuses (8) im jeweiligen Spalt (25) angeordnet ist.Centrifugal pump according to claim 4, characterized in that a helical groove is arranged at both ends of the bearing housing (8) in the respective gap (25).
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)

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DE10024953 2000-05-22
DE10024953A DE10024953A1 (en) 2000-05-22 2000-05-22 Centrifugal pump with magnetic coupling

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

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Also Published As

Publication number Publication date
DE50112181D1 (en) 2007-04-26
ATE356937T1 (en) 2007-04-15
EP1719914A3 (en) 2006-11-15
US20010043865A1 (en) 2001-11-22
DE50115684D1 (en) 2010-12-09
EP1719914A2 (en) 2006-11-08
ATE486219T1 (en) 2010-11-15
DE10024953A1 (en) 2001-11-29
EP1158174B1 (en) 2007-03-14
EP1158174A3 (en) 2005-09-07
US6554576B2 (en) 2003-04-29
EP1719914B1 (en) 2010-10-27

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