EP1158173B1 - Centrifugal pump with magnetic coupling - Google Patents

Centrifugal pump with magnetic coupling Download PDF

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Publication number
EP1158173B1
EP1158173B1 EP01100290A EP01100290A EP1158173B1 EP 1158173 B1 EP1158173 B1 EP 1158173B1 EP 01100290 A EP01100290 A EP 01100290A EP 01100290 A EP01100290 A EP 01100290A EP 1158173 B1 EP1158173 B1 EP 1158173B1
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EP
European Patent Office
Prior art keywords
shaft
rotor
blades
pump
magnetic 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.)
Expired - Lifetime
Application number
EP01100290A
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German (de)
French (fr)
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EP1158173A3 (en
EP1158173A2 (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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Filing date
Publication date
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Publication of EP1158173A2 publication Critical patent/EP1158173A2/en
Publication of EP1158173A3 publication Critical patent/EP1158173A3/en
Application granted granted Critical
Publication of EP1158173B1 publication Critical patent/EP1158173B1/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
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
    • F04D13/027—Details of the magnetic circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • 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

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.
  • Magnetic clutch 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 towards the outer diameter is contrary to the required flow direction 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 is achieved.
  • the fastening means of the inner magnet rotor on the shaft or on the shaft sleeve has at least one flow channel for the pumped liquid, are arranged in or on the blades for the axial conveying of the liquid wherein the funded by the axial blades from the liquid Is sucked gap between the output magnet and the split pot and pressed by the bearings, which are arranged between the bearing housing and the shaft or the shaft sleeve.
  • Axial blades are positioned in the inner diameter of a magnetic coupling rotor, which is designed as a rotationally symmetrical hollow body.
  • the blades are connected to the rotationally symmetrical hollow body and the magnetic coupling shaft.
  • Such a magnetic coupling rotor designed with axial blades eliminates the mentioned disadvantages.
  • the rotor consists of a cylindrical body, in the inner diameter of a plurality of blades - preferably three pieces - are positioned.
  • the blades may be planar or spatially curved and have a defined angle of attack - preferably 5 to 15 °.
  • the axial blades promote a larger liquid flow at low pressure differences. Thus, a lot of cooling or rinsing medium is available and cavitation is reliably avoided.
  • the medium is conveyed by means of axial blades into the inner diameter of the cylindrical body and flows through the rotor bearing positioned in the rotor center.
  • the axial blades connect the rotationally symmetrical hollow body with the shaft of the rotor and serve in addition to the axial medium promotion and the transmission of the rotor torque. Since the front side of the rotor, in contrast to known rotors with radial blades is not full circle, but due to the blading has a reduced surface, the fluid friction of the rotor end face is reduced. As a result, compared to radial blade designs already low hydraulic power consumption of the rotor is further reduced.
  • the flow channel is formed by a coaxial ring opening in which two or more blades are fastened.
  • 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 (with radial bearing sleeve and radial bearing bushing) 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 formed on the shaft 3 as a fastening means 15, on the outer Edge of a tube-shaped cylindrical coaxial magnetic body 17 is formed, on the outside of the output magnets 18 are attached.
  • the bearing housing 8 thus extends coaxially into the magnet rotor 14, wherein an annular space 19 exists between the magnet carrier 17 and the bearing housing 8 and an annular gap 20 exists between the magnet carrier 17 and the gap pot 10.
  • 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 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 promote the entering through the inlet channels 23 into the crevice interior liquid from the annular gap 20 in the intermediate space 24 between the bearing housing 8 and shaft sleeve 12, so that the fluid thereby conveyed through the radial and thrust bearings 4 to 7 flows thereafter to Flow back to the pump chamber.

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

Abstract

A pump has a housing plate, a housing can fixed to the plate and defining a chamber on a back face thereof, 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. Bearings support the rotor shaft in the sleeve and an impeller is carried on the rotor-shaft front end. A rotor body fixed to the shaft rear end extends axially forward in the can around the bearing sleeve. The rotor body defines an annular space around the bearing sleeve and is formed with at least one axially throughgoing passage open axially forward into the space and axially rearward into the can. A vane in the passage is angled for pumping liquid from inside the can axially forward into the space on rotation of the rotor about the axis.

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.

Aus der US-A 4,080,112 ist eine derartige Kreiselpumpe bekannt, bei der die Befestigungsmittel schräg angeordnete Kanäle aufweisen.From US-A 4,080,112 such a centrifugal pump is known, in which the fastening means have obliquely arranged channels.

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 clutch 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 towards the outer diameter is contrary to the required flow direction 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 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 is achieved.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, dass die Befestigungsmittel des inneren Magnetrotors an der Welle oder an der Wellenhülse mindestens einen Durchflusskanal für die Förderflüssigkeit aufweist, in oder an dem Schaufeln zur axialen Förderung der Flüssigkeit angeordnet sind wobei die von den axialen Schaufeln geförderte Flüssigkeit aus dem Spalt zwischen den Abtriebsmagneten und dem Spalttopf gesogen und durch die Lager gedrückt wird, die zwischen dem Lagergehäuse und der Welle oder der Wellenhülse angeordnet sind.This object is achieved in that the fastening means of the inner magnet rotor on the shaft or on the shaft sleeve has at least one flow channel for the pumped liquid, are arranged in or on the blades for the axial conveying of the liquid wherein the funded by the axial blades from the liquid Is sucked gap between the output magnet and the split pot and pressed by the bearings, which are arranged between the bearing housing and the shaft or the shaft sleeve.

Axiale Schaufeln sind im Innendurchmesser eines Magnetkupplungsrotors positioniert, der als rotationssymmetrischer Hohlkörper gestaltet ist. Die Schaufeln sind mit dem rotationssymmetrischen Hohlkörper und der Magnetkupplungswelle verbunden. Ein solcher mit Axialschaufeln ausgeführter Magnetkupplungsrotor eliminiert die genannten Nachteile. Der Rotor besteht aus einem zylindrischen Körper, in dessen Innendurchmesser mehrere Schaufeln - vorzugsweise drei Stück - positioniert sind. Die Schaufeln können planar oder räumlich gekrümmt sein und weisen einen definierten Anstellwinkel auf - vorzugsweise 5 bis 15 °. Die Axialschaufeln fördern einen größeren Flüssigkeitsstrom bei niedrigen Druckdifferenzen. Somit steht viel Kühl- bzw. Spülmedium zur Verfügung und Kavitation wird zuverlässig vermieden. Das Medium wird mittels Axialschaufeln in den Innendurchmesser des zylindrischen Körpers gefördert und durchströmt die im Rotorzentrum positonierte Rotorlagerung. Die Axialschaufeln verbinden den rotationssymmetrischen Hohlkörper mit der Welle des Rotors und dienen neben der axialen Mediumförderung auch der Übertragung des Rotordrehmomentes. Da die Stirnseite des Rotors im Gegensatz zu bekannten Rotoren mit radialen Schaufeln nicht vollkreisflächig ist, sondern bedingt durch die Beschaufelung eine verminderte Oberfläche aufweist, wird die Flüssigkeitsreibung der Rotor-Stirnfläche reduziert. Dadurch wird die im Vergleich zu radialen Schaufelkonstruktionen ohnehin schon geringe hydraulische Leistungsaufnahme des Rotors noch weiter vermindert.Axial blades are positioned in the inner diameter of a magnetic coupling rotor, which is designed as a rotationally symmetrical hollow body. The blades are connected to the rotationally symmetrical hollow body and the magnetic coupling shaft. Such a magnetic coupling rotor designed with axial blades eliminates the mentioned disadvantages. The rotor consists of a cylindrical body, in the inner diameter of a plurality of blades - preferably three pieces - are positioned. The blades may be planar or spatially curved and have a defined angle of attack - preferably 5 to 15 °. The axial blades promote a larger liquid flow at low pressure differences. Thus, a lot of cooling or rinsing medium is available and cavitation is reliably avoided. The medium is conveyed by means of axial blades into the inner diameter of the cylindrical body and flows through the rotor bearing positioned in the rotor center. The axial blades connect the rotationally symmetrical hollow body with the shaft of the rotor and serve in addition to the axial medium promotion and the transmission of the rotor torque. Since the front side of the rotor, in contrast to known rotors with radial blades is not full circle, but due to the blading has a reduced surface, the fluid friction of the rotor end face is reduced. As a result, compared to radial blade designs already low hydraulic power consumption of the rotor is further reduced.

Besonders vorteilhaft ist es, wenn der Durchflusskanal von einer koaxialen Ringöffnung gebildet ist, in dem zwei oder mehr Schaufeln befestigt sind.It is particularly advantageous if the flow channel is formed by a coaxial ring opening in which two or more blades are fastened.

Eine vorteilhafte Ausgestaltung der Erfindung ist in der Zeichnung in einem axialen Schnitt durch den inneren Bereich dargestellt und wird im folgenden näher beschrieben.An advantageous embodiment of the invention is shown in the drawing in an axial section through the inner region and will be described in more detail below.

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 (mit Radiallagerhülse und Radiallagerbuchse) 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 äußerem Rand ein rohrabschnittförmiger zylindrischer koaxialer Magnetkörper 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 (with radial bearing sleeve and radial bearing bushing) 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 formed on the shaft 3 as a fastening means 15, on the outer Edge of a tube-shaped cylindrical coaxial magnetic body 17 is formed, on the outside of the output magnets 18 are attached.

Das Lagergehäuse 8 erstreckt sich somit koaxial in den 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 into the magnet rotor 14, wherein an annular space 19 exists between the magnet carrier 17 and the bearing housing 8 and an annular gap 20 exists between the magnet carrier 17 and the gap pot 10. 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 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 promote the entering through the inlet channels 23 into the crevice interior liquid from the annular gap 20 in the intermediate space 24 between the bearing housing 8 and shaft sleeve 12, so that the fluid thereby conveyed through the radial and thrust bearings 4 to 7 flows thereafter to Flow back to the pump chamber.

Claims (2)

  1. Centrifugal pump having a magnetic coupling disposed between pump shaft and drive shaft and having a split pot (10) in the magnet clearance between the inner magnetic rotor (14) of the pump and the outer magnetic rotor of the drive shaft, wherein in the interior of the split pot (10), through which the pumping liquid flows, the inner magnetic rotor (14) is supported against a tubular bearing housing (8) that surrounds the pump impeller shaft (3), which at the side remote from the pump impeller (2) has fastening means (15) for the inner magnetic rotor (14), which is disposed between the bearing housing (8) and the split pot (10), characterized in that the fastening means of the inner magnetic rotor (14) to the shaft (3) or to the shaft sleeve (12) has at least one throughflow channel (21) for the pumping liquid, in or at which throughflow channel blades (22) for axial delivery of the liquid are disposed, wherein the liquid delivered by the axial blades (22) is sucked out of the gap (20) between the output magnets (18) and the split pot (10) and pressed through the bearings (4-7) that are disposed between the bearing housing (8) and the shaft (3) or shaft sleeve (12).
  2. Centrifugal pump according to claim 1, characterized in that the throughflow channel (21) is formed by a coaxial annular opening, in which two or more blades (22) are fastened.
EP01100290A 2000-05-22 2001-01-04 Centrifugal pump with magnetic coupling Expired - Lifetime EP1158173B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10024955 2000-05-22
DE10024955A DE10024955A1 (en) 2000-05-22 2000-05-22 Centrifugal pump with magnetic coupling

Publications (3)

Publication Number Publication Date
EP1158173A2 EP1158173A2 (en) 2001-11-28
EP1158173A3 EP1158173A3 (en) 2004-03-10
EP1158173B1 true EP1158173B1 (en) 2006-07-05

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EP01100290A Expired - Lifetime EP1158173B1 (en) 2000-05-22 2001-01-04 Centrifugal pump with magnetic coupling

Country Status (4)

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US (1) US6457951B2 (en)
EP (1) EP1158173B1 (en)
AT (1) ATE332444T1 (en)
DE (2) DE10024955A1 (en)

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Publication number Priority date Publication date Assignee Title
CN102146928A (en) * 2011-06-03 2011-08-10 浙江腾宇泵阀设备有限公司 Device for preventing magnetic pump from no-load, overload, magnetic steel slipping, rotor blockage and abrasion

Also Published As

Publication number Publication date
EP1158173A3 (en) 2004-03-10
DE10024955A1 (en) 2001-11-29
EP1158173A2 (en) 2001-11-28
DE50110376D1 (en) 2006-08-17
ATE332444T1 (en) 2006-07-15
US20010043871A1 (en) 2001-11-22
US6457951B2 (en) 2002-10-01

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