EP0171515A1 - Centrifugal pump with an isolating tubular air gap cap - Google Patents
Centrifugal pump with an isolating tubular air gap cap Download PDFInfo
- Publication number
- EP0171515A1 EP0171515A1 EP85105626A EP85105626A EP0171515A1 EP 0171515 A1 EP0171515 A1 EP 0171515A1 EP 85105626 A EP85105626 A EP 85105626A EP 85105626 A EP85105626 A EP 85105626A EP 0171515 A1 EP0171515 A1 EP 0171515A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump
- pump impeller
- impeller
- centrifugal pump
- pot
- 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
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Classifications
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- 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
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- 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
- F04D13/025—Details of the can separating the pump and drive area
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- 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
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- 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
- F04D29/0416—Axial thrust balancing balancing pistons
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- 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
- F04D29/08—Sealings
- F04D29/16—Sealings between pressure and suction sides
- F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
- F04D29/167—Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2260/00—Function
- F05B2260/40—Transmission of power
- F05B2260/404—Transmission of power through magnetic drive coupling
- F05B2260/4041—Transmission of power through magnetic drive coupling the driven magnets encircling the driver magnets
Definitions
- the invention relates to a centrifugal pump according to the preamble of claim 1.
- centrifugal pumps are known from DE-OS 26 20 502, the axis being at least partially held on the canned pot bottom, which can result in undesirable mechanical stress on the canned pot and can cause difficulties in equalizing pressure differences behind and in front of the pump impeller.
- DE-OS 27 33 631 It is provided in DE-OS 27 33 631 to compensate for the fluctuating axial forces by controlling the passage of the compensating opening of the pump impeller, which can at least lead to undesired disturbances in the impeller flow and to loss of performance.
- EP-A1 0 078 345 in turn, even provides a control device for increasing the cross section of compensation openings in the pump housing, which is from the axial position of the shaft is controlled.
- CH-PS 529 929 wearable axial main bearings and axial auxiliary bearings are provided, the wear of which allows the axial displacement of the pump impeller under certain operating conditions, which should result in a reduction in axial force.
- new wear and a new "run-in" is always necessary, which must ultimately lead to total wear of the thrust bearings.
- the invention is based on the object of avoiding these disadvantages, the short stationary axis already having the advantage in comparison to the long idling shafts that one does not have to take into account the lubrication of a bearing located far away from the motor.
- the aim was to have a construction that was as simple and economical as possible and easy to maintain.
- This balancing effect is so excellent that you can do without an axial bearing of the pump impeller if you use both the space behind and in front of the pump impeller with the intake and pressure ports to conduct the medium, e.g. connects in a liquid-conducting manner, the size of the passage cross-sections being variable due to the axial position of the pump impeller and allowing the desired compensation to be achieved automatically.
- drados rings which are attached to the front and rear of the impeller and are preferably located near the axle on the front. At least on the front, a mating ring on the housing is preferable, while on the back the bottom of the pot can serve as an emergency support.
- These rings can advantageously have emergency running properties and consist, for example, of polytetrafluoroethylene, which is chemically stable and is well self-lubricating.
- the throttle rings will hardly ever come into contact in normal operation, since they are separated from each other or from the bottom of the pot by a damping medium layer and, in the event of extreme movements of the pump impeller in one direction, will intercept and immediately regulate the balancing effect.
- a canned pot 2 is inserted so tightly in the pump housing 1 that the canned pot 2 separates the pump chamber 3 from the motor chamber 4 in a sealed manner and without any movable seals.
- the pump impeller 5 is housed connected to the associated external rotor 6 equipped with permanent magnets 60.
- the electric drive motor 10 and the inner rotor 9 connected to it and equipped with permanent magnets 90 are accommodated in the engine compartment.
- the pot wall 20 has an edge 22 which is mounted sealingly in the pump housing 1 and constitutes the only sealing point of the canned pot 2 at the pump housing. 1
- the pot base 21 of the canned pot 2 is connected in one piece to the pot wall 20, with the entire canned pot 2 preferably being made of electrically non-conductive ceramic material.
- the pot base 21 is arched towards the motor 10, which allows the pump impeller 5 to be balanced with the external rotor 6 in a favorable manner.
- the pump impeller 5 is rotatably mounted on the stationary axis 7, this bearing being limited to a purely radial bearing.
- An axial bearing is not necessary and is not provided: the axis 7 is fastened in the intake manifold 8 by means of supporting ribs 80, a ceramic sliding bearing 70 serving for the radial mounting of the pump impeller 5, and an external lubrication channel 75 through a supporting rib 80 and through the axis 7 to the ceramic Slide bearing 70 is guided. If the pump medium is unfavorable for bearing lubrication, external lubrication can take place.
- the axis 7 has a generously dimensioned compensating channel 71, which has some front lateral openings 72 and a rear opening 73, so that the suction port 8 of the pump housing 1 located on the front 52 of the pump impeller 5 with that on the rear 53 of the pump impeller 5 located part of the pump chamber 3 is permeably connected by this channel 71 with low inertia for the pumped medium.
- the pump impeller 5 of the illustrated type of a radial pump has a front suction opening 50 and radial channels 51 which lead to the pressure connection 11 of the pump housing 1 are arranged to promote.
- the pump impeller 5 is otherwise free of openings.
- the pump chamber located in front of the pump impeller is connected to the suction nozzle 8 and to the pressure nozzle 11 and the rear part of the pump chamber to the pressure nozzle 11 in a medium-conducting manner.
- 5 throttle rings 520 and 530 are provided on the pump impeller 5 on the front 52 and on the rear 53 of the pump impeller, respectively, which allow a balanced axial self-adjustment of the pump impeller 5 to be optimized for the intended purpose.
- the rear throttle ring 530 is held by a retaining ring 531 and has no counterpart on the pot base 21, which does not mean, however, that a counter ring should not be attached if necessary.
- a counter ring 521 is fastened to the pump housing 1 close to the axis by means of retaining ring 522.
- the operating conditions can also be taken into account with a throttle screw 74 which is designed as a grub screw in a rib 80 and is accessible from the outside and through which the free passage in the channel 71 can be changed.
- the intended emergency running properties of the throttle rings 520/521 and 530 are used at most in exceptional cases if, due to extraordinary events, the pump impeller 5 travels a somewhat larger axial path than is planned in the axial mobility. Otherwise the pressure equalization through channel 71 acts so spontaneously that even violent pressure fluctuations can be absorbed.
- the throttle rings have an optimized, regulating effect on the desired operating center position of the pump impeller 7.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Control Of Non-Positive-Displacement Pumps (AREA)
Abstract
Description
Die Erfindung betrifft eine Kreiselpumpe nach dem Oberbegriff des Anspruch 1.The invention relates to a centrifugal pump according to the preamble of claim 1.
Derartige Kreiselpumpen sind aus der DE-OS 26 20 502 bekannt, wobei die Achse mindestens teilweise am Spaltrohrtopfboden gehaltert ist, was eine unerwünschte mechanische Beanspruchung des Spaltrohrtopfes mit sich bringen kann und Schwierigkeiten beim Ausgleich von Druckunterschieden hinter und vor dem Pumpenlaufrad mit sich bringen kann.Such centrifugal pumps are known from DE-OS 26 20 502, the axis being at least partially held on the canned pot bottom, which can result in undesirable mechanical stress on the canned pot and can cause difficulties in equalizing pressure differences behind and in front of the pump impeller.
Bei mit der Welle umlaufenden Pumpenlaufrädern einer Spaltrohrpumpe (ohne Topfboden) ist es bereits bekannt die Druckunterschiede teilweise auszugleichen, soweit sie nicht zur Förderung eines Nebenstromes zur Kühlung und zum Schmieren des hinteren Lagers benötigt werden. Dazu hat man Ausgleichsöffnungen in das Pumpenlaufrad gemacht, welche von der Pumpenlaufrad-Hinterseite in das Innere des Pumpenlaufrades hineinreichen. Dass diese mit Leistungsverlusten verbunden ist und die Aufnahme der verbleibenden Axialkräfte durch Axiallager nötig macht geht aus allen Vorveröffentlichungen hervor, vgl. z.B. DE-OS 27 33 631, CH-PS 529 929 und EP-A1 0 078 345.In the case of pump impellers rotating around the shaft of a canned pump (without a pot bottom), it is already known to partially compensate for the pressure differences insofar as they are not required to promote a secondary flow for cooling and lubricating the rear bearing. For this purpose, compensation openings have been made in the pump impeller, which extend from the rear of the pump impeller into the interior of the pump impeller. All previous publications show that this is associated with a loss of power and necessitates the absorption of the remaining axial forces by axial bearings, cf. e.g. DE-OS 27 33 631, CH-PS 529 929 and EP-A1 0 078 345.
Es ist dabei in der DE-OS 27 33 631 vorgesehen die schwankenden Axialkräfte durch Steuerung des Durchlasses der Ausgleichsöffnung des Pumpenlaufrades auszugleichen, was zumindest zu unerwünschten Störungen der Laufradströmung und zu Leistungsverlusten führen kann.It is provided in DE-OS 27 33 631 to compensate for the fluctuating axial forces by controlling the passage of the compensating opening of the pump impeller, which can at least lead to undesired disturbances in the impeller flow and to loss of performance.
In der EP-A1 0 078 345 wiederum ist sogar ein Steuerapparat zur Steigerung des Querschnittes von Ausgleichsöffnungen im Pumpengehäuse vorgesehen, welcher von der Axiallage der Welle her gesteuert wird. Bei der CH-PS 529 929 werden verachleissbare Axialhauptlager und Axielhilfalager vorgesehen, deren Verschleiss unter gewissen Betriebsbedingungen eine Axial-Lageverschiebung des Pumpenlaufrades erlauben, die eine Axialkraftminderung zu Folge haben soll. Soweit das überhaupt geht, ist bei sich ändernden Betriebsbedingungen, und das ist nicht gerade selten der Fall, immer wieder ein neuer Verschleiss und ein neues "Einlaufen" nötig, das schliesslich zum totalen Verschleiss der Axiallager führen muss.EP-A1 0 078 345, in turn, even provides a control device for increasing the cross section of compensation openings in the pump housing, which is from the axial position of the shaft is controlled. In CH-PS 529 929, wearable axial main bearings and axial auxiliary bearings are provided, the wear of which allows the axial displacement of the pump impeller under certain operating conditions, which should result in a reduction in axial force. As far as that is possible, and with changing operating conditions, and this is not infrequently the case, new wear and a new "run-in" is always necessary, which must ultimately lead to total wear of the thrust bearings.
Der Erfindung liegt die Aufgabe zugrunde diese Nachteile zu vermeiden, wobei die kurze stationäre Achse im Vergleich zu den langen mitlaufenden Wellen schon den Vorteil hat, dass man nicht die Schmierung eines weit motorseitig entfernt angeordneten Lagers berücksichtigen muss.The invention is based on the object of avoiding these disadvantages, the short stationary axis already having the advantage in comparison to the long idling shafts that one does not have to take into account the lubrication of a bearing located far away from the motor.
Ausgleichsöffnungen in das Innere des Pumpenlaufrades haben sich nicht als ausreichend vorteilhaft gezeigt und die Steuerung der Durchlässe nach Axiallage ergab dabei auch keine brauchbare Verbesserung.Compensating openings in the interior of the pump impeller have not proven to be sufficiently advantageous, and the control of the passages according to the axial position did not result in any useful improvement.
Angestrebt wurde eine möglichst einfache wirtschaftliche und wartungsfreundliche Konstruktion.The aim was to have a construction that was as simple and economical as possible and easy to maintain.
Ueberraschenderweise wurde nun gefunden, dass sich ein gut beherrschbarer, praktisch verzögerungsfreier bzw. trägheitsarmer Druckausgleich durch die hohle Achse bewirken lässt, ohne dass man Ausgleichsöffnungen am Pumpenlaufrad selbst benötigt.Surprisingly, it has now been found that a well controllable, practically instantaneous or low-inertia pressure compensation can be achieved through the hollow axis without the need for compensation openings on the pump impeller itself.
Diese Ausgleichswirkung ist so hervorragend, dass man auf eine Axiallagerung des Pumpenlaufrades ganz verzichten kann, wenn man sowohl den Raum hinter als auch vor dem Pumpenlaufrad mit dem Ansaugstutzen und mit dem Druckstutzen mediumleitend, z.B. flüssigkeitsleitend verbindet, wobei durch die Axiallage des Pumpenlaufrades die Grösse der Durchlassquerschnitte veränderlich ist und den erwünschten Ausgleich selbsttätig erreichen lässt.This balancing effect is so excellent that you can do without an axial bearing of the pump impeller if you use both the space behind and in front of the pump impeller with the intake and pressure ports to conduct the medium, e.g. connects in a liquid-conducting manner, the size of the passage cross-sections being variable due to the axial position of the pump impeller and allowing the desired compensation to be achieved automatically.
Damit dies auch bei vorübergehend ungünstigen Laufbedingungen nicht zu einem direkten Kontakt des Pumpenlaufrades mit dem Pumpengehäuse führt, ist es vorteilhaft Droaselringe vorzusehen, die vordereeitig und hinterseitig am Laufrad angebracht sind und sich vorderseitig vorzugsweise nahe der Achse befinden. Wenigstens vorderaeitig ist auch ein Gegenring am Gehäuse vorzuziehen, während rückseitig der Topfboden als Notabstützung dienen kann. Diese Ringe können vorteilhafterweise Notlaufeigenachaften haben und z.B. aus Polytetrafluoräthylen bestehen, das chemisch beständig und gut selbstschmierend ist.It is advantageous that this does not result in direct contact of the pump impeller with the pump housing even under temporarily unfavorable running conditions To provide droasel rings, which are attached to the front and rear of the impeller and are preferably located near the axle on the front. At least on the front, a mating ring on the housing is preferable, while on the back the bottom of the pot can serve as an emergency support. These rings can advantageously have emergency running properties and consist, for example, of polytetrafluoroethylene, which is chemically stable and is well self-lubricating.
Die Drosselringewerden aber kaum je im normalen Betrieb zur Anlage kommen, da sie voneinander bzw. vom Topfboden durch eine dämpfende Mediumschicht getrennt sind und bei extremen Bewegungen des Pumpenlaufradee in eine Richtung eine augenblickliche Ausgleichawirkung abfangend und rückregulierend wirken wird.However, the throttle rings will hardly ever come into contact in normal operation, since they are separated from each other or from the bottom of the pot by a damping medium layer and, in the event of extreme movements of the pump impeller in one direction, will intercept and immediately regulate the balancing effect.
Die Erfindung wird nachstehend beispielsweise anhand der rein schematischen Zeichnung näher besprochen. Es zeigen:
- Fig. 1 eine Ansicht einer erfindungsgemässen Pumpe von der Ansaugseite her, und
- Fig. 2 einen Längsschnitt durch die Pumpe.
- Fig. 1 is a view of an inventive pump from the suction side, and
- Fig. 2 shows a longitudinal section through the pump.
Im Pumpengehäuse 1 ist ein Spaltrohrtopf 2 so dicht eingesetzt, dass der Spaltrohrtopf 2 den Pumpenraum 3 vom Motorraum 4 dicht und ohne bewegliche Dichtungen trennt.A canned pot 2 is inserted so tightly in the pump housing 1 that the canned pot 2 separates the pump chamber 3 from the motor chamber 4 in a sealed manner and without any movable seals.
Im Pumpenraum 3 ist das Pumpenlaufrad 5 mit dem zugehörigen, mit Permanentmagneten 60 bestückten Aussenläufer 6 verbunden untergebracht.In the pump chamber 3, the
Im Motorraum ist der elektrische Antriebsmotor 10 und der mit ihm verbundene, mit Permanentmagneten 90 bestückte Innenläufer 9 untergebracht.The electric drive motor 10 and the inner rotor 9 connected to it and equipped with permanent magnets 90 are accommodated in the engine compartment.
Es liegt hier also eine Umkehrung der Zuordnung der mit Permanentmagneten bestückten Läufer gegenüber der üblichen Konstruktion und eine Umkehr der Anordnung des Spaltrohrtopfes 2 vor, was es ermöglicht, die das Spaltrohr bildende Topfwand 20 mindestens angenähert nur mit Druckkräften zu beaufschlagen, was sich auf die Gesamtkonstruktion vorteilhaft auswirkt, und was Gegenstand einer am gleichen Tage mit Anwaltszeichen 7074 eingereichten Patentanmeldung ist.There is therefore a reversal of the assignment of the runners equipped with permanent magnets compared to the usual construction and a reversal of the arrangement of the canned pot 2, which makes it possible to at least approximate the
Die Topfwand 20 hat einen Rand 22, welcher im Pumpenge- häuse 1 dichtend gehaltert ist und die einzige Dichtungsstelle des Spaltrohrtopfes 2 am Pumpengehäuse 1 darstellt.The
Der Topfboden 21 des Spaltrohrtopfes 2 ist einstückig mit der Topfwand 20 verbunden, wobei hier beispielsweise der ganze Spaltrohrtopf 2 bevorzugterweise aus elektrisch nicht leitendem keramischen Material besteht.The
Der Topfboden 21 ist gegen den Motor 10 hin eingewölbt, was eine günstige Ausbalancierung des Pumpenlaufrades 5 mit dem Aussenläufer 6 gestattet.The
Dabei ist das Pumpenlaufrad 5 auf der stationären Achse 7 drehbar gelagert, wobei sich diese Lagerung auf eine reine Radiallagerung beschränkt. Eine Axiallagerung ist nicht nötig und nicht vorgesehen: Die Achse 7 ist im Ansaugstutzen 8 mittels Tragrippen 80 befestigt, wobei ein Keramikgleitlager 70 der radialen Lagerung des Pumpenlaufrades 5 dient, und wobei ein Fremdschmierkanal 75 durch eine Tragrippe 80 und durch die Achse 7 zum Keramik-Gleitlager 70 geführt ist. Bei für die Lagerschmierung ungünstigem Pumpmedium kann so eine Fremdschmierung erfolgen.The
Die Achse 7 hat einen grosszügig dimensionierten dem Ausgleich dienenden Kanal 71, welcher einige vordere seitliche Oeffnungen 72 und eine hintere Oeffnung 73 aufweist, so dass der an der Vorderseite 52 des Pumpenlaufrades 5 befindliche Ansaugstutzen 8 des Pumpengehäuses 1 mit dem an der Hinterseite 53 des Pumpenlaufrades 5 befindlichen Teil des Pumpenraumes 3 durch diesen Kanal 71 trägheitsarm für das gepumpte Medium durchlässig verbunden ist.The axis 7 has a generously dimensioned compensating
Das Pumpenlaufrad 5 der gezeichneten Bauart einer Radialpumpe hat eine vordere Ansaugöffnung 50 und Radialkanäle 51, welche zum Druckstutzen 11 des Pumpengehäuses 1 fördernd angeordnet sind. Das Pumpenlaufrad 5 ist sonst frei von Oeffnungen. Dabei ist der vor dem Pumpenlaufrad befindliche Pumpenraum mit dem Ansaugstutzen 8 und mit dem Druckstutzen 11 und der hintere Pumpenraumteil mit dem Druckstutzen 11 mediumleitend verbunden.The
Wenn die Pumpe in Betrieb ist, kann sich deshalb ein sich hinter dem Pumpenlaufrad aufbauender Druck mit einem sich vor dem Pumpenlaufrad aufbauenden unterschiedlichen Druck trägheitsarm ausgleichen, so dass das Pumpenlaufrad 5 keiner axialen Lagerung bedarf und selbstzentriert läuft.When the pump is in operation, a pressure building up behind the pump impeller can therefore compensate for low inertia with a different pressure building up in front of the pump impeller, so that the
Nun sind aber verschiedene Pumpen für ganz bestimmte Zwecke mit ganz bestimmten Eigenschaften ausgestattet, und es können auch gewisse Unterschiede in den Betriebsbedingungen auftreten.Now, however, various pumps are equipped with very specific properties for very specific purposes, and certain differences in the operating conditions can also occur.
Der Zweckbestimmung entsprechend sind an der Vorderseite 52 bzw. an der Rückseite 53 des Pumpenlaufrades 5 Drosselringe 520 bzw. 530 am Pumpenlaufrad 5 vorgesehen, welche ein ausgeglichenes axiales Selbsteinstellen des Pumpenlaufrades 5 zweckbestimmungsmässig optimieren lassen. Der rückseitige Drosselring 530 wird von einem Haltering 531 gehaltert und hat kein Gegenstück am Topfboden 21, was aber nicht heisst, dass man dort nötigenfalls keinen Gegenring anbringen dürfte. Dagegen ist am Pumpengehäuse 1 achsnah ein Gegenring 521 mittels Haltering 522 befestigt.In accordance with the intended use, 5
Den Betriebsbedingungen kann man darüberhinaus mit einer als Madenschraube in einer Rippe 80 ausgebildeten und von aussen zugänglichen Drosselschraube 74 Rechnung tragen, durch welche der freie Durchgang im Kanal 71 veränderbar ist.The operating conditions can also be taken into account with a
Höchstens ausnahmsweise kommen die vorgesehenen Notlaufeigenschaften der Drosselringe 520/521 und 530 zum Einsatz, wenn durch ausserordentliche Ereignisse das Pumpenlaufrad 5 einen etwas grösseren Axialweg zurücklegt, als dies in der Axialbeweglichkeit eingeplant ist. Sonst wirkt der Druckausgleich durch den Kanal 71 so spontan, dass selbst heftige Druckschwankungen abgefangen werden - können. Die Drosselringe wirken dabei zweckbestimmungsgemäss optimiert regulierend auf die gewünschte Betriebs-Mittellage des Pumpenlaufrades 7.The intended emergency running properties of the
Während hier eine Radialpumpe gezeichnet wurde, kann die Erfindung auch bei anderen Kreiselpumpen nutzbringend angewendet werden, so z.B. bei Radial-Axial-Pumpen.While a radial pump has been drawn here, the invention can also be used to advantage in other centrifugal pumps, e.g. with radial-axial pumps.
Claims (9)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT85105626T ATE29275T1 (en) | 1984-07-16 | 1985-05-08 | CENTRIFUGAL PUMP WITH CANNED TUBE. |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CH3451/84 | 1984-07-16 | ||
CH345184 | 1984-07-16 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0171515A1 true EP0171515A1 (en) | 1986-02-19 |
EP0171515B1 EP0171515B1 (en) | 1987-09-02 |
Family
ID=4256229
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP85105626A Expired EP0171515B1 (en) | 1984-07-16 | 1985-05-08 | Centrifugal pump with an isolating tubular air gap cap |
Country Status (5)
Country | Link |
---|---|
US (1) | US4645433A (en) |
EP (1) | EP0171515B1 (en) |
JP (1) | JPS6138192A (en) |
AT (1) | ATE29275T1 (en) |
DE (1) | DE3560533D1 (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0237868A2 (en) * | 1986-03-21 | 1987-09-23 | Ernst Hauenstein | Radial or axial flow centrifugal pump |
WO1996032592A1 (en) * | 1995-04-14 | 1996-10-17 | Ceramiques & Composites S.A. | Magnetic drive centrifugal pump |
DE4238132C2 (en) * | 1992-11-12 | 2002-10-24 | Teves Gmbh Alfred | Centrifugal pump, in particular water pump for motor vehicles |
EP1329638A1 (en) * | 2002-01-18 | 2003-07-23 | CP Pumpen AG | Magnetically coupled centrifugal pump |
WO2007112938A2 (en) * | 2006-03-31 | 2007-10-11 | H. Wernert & Co. Ohg | Rotary pump with coaxial magnetic coupling |
Families Citing this family (23)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH670286A5 (en) * | 1986-06-04 | 1989-05-31 | Sulzer Ag | |
DE3636404A1 (en) * | 1986-10-25 | 1988-04-28 | Richter Chemie Technik Gmbh | MAGNETIC CENTRIFUGAL PUMP |
DE3818832A1 (en) * | 1988-06-03 | 1989-12-07 | Uranit Gmbh | CLEANER FOR SLEEVELESS ELECTRIC OR MAGNETIC DRIVE UNITS |
US5324177A (en) * | 1989-05-08 | 1994-06-28 | The Cleveland Clinic Foundation | Sealless rotodynamic pump with radially offset rotor |
US5039061A (en) * | 1990-01-26 | 1991-08-13 | John H. Carter Co., Inc. | Magnetically actuated linear valve operator and method |
GB2263312A (en) * | 1992-01-17 | 1993-07-21 | Stork Pompen | Vertical pump with magnetic coupling. |
DE9201412U1 (en) * | 1992-02-05 | 1992-05-07 | Qvf Glastechnik Gmbh, 6200 Wiesbaden | Magnetic coupling pump, especially for pumping aggressive and environmentally harmful media |
US5269664A (en) * | 1992-09-16 | 1993-12-14 | Ingersoll-Dresser Pump Company | Magnetically coupled centrifugal pump |
WO1994009274A1 (en) * | 1992-10-19 | 1994-04-28 | The Cleveland Clinic Foundation | Sealless rotodynamic pump |
FR2715442B1 (en) * | 1994-01-26 | 1996-03-01 | Lorraine Carbone | Centrifugal pump with magnetic drive. |
US5659205A (en) * | 1996-01-11 | 1997-08-19 | Ebara International Corporation | Hydraulic turbine power generator incorporating axial thrust equalization means |
US5779456A (en) * | 1996-10-28 | 1998-07-14 | Finish Thompson Inc. | Magnetic drive |
US6293772B1 (en) | 1998-10-29 | 2001-09-25 | Innovative Mag-Drive, Llc | Containment member for a magnetic-drive centrifugal pump |
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JP2009532131A (en) | 2006-03-31 | 2009-09-10 | オーキス メディカル コーポレイション | Rotating blood pump |
WO2010079088A1 (en) * | 2009-01-09 | 2010-07-15 | Sulzer Pumpen Ag | Centrifugal pump having a device for removal of particles |
US8905729B2 (en) | 2011-12-30 | 2014-12-09 | Peopleflo Manufacturing, Inc. | Rotodynamic pump with electro-magnet coupling inside the impeller |
US8905728B2 (en) | 2011-12-30 | 2014-12-09 | Peopleflo Manufacturing, Inc. | Rotodynamic pump with permanent magnet coupling inside the impeller |
CN102966557A (en) * | 2012-11-07 | 2013-03-13 | 无锡惠山泵业有限公司 | Clean water pump |
US9771938B2 (en) * | 2014-03-11 | 2017-09-26 | Peopleflo Manufacturing, Inc. | Rotary device having a radial magnetic coupling |
CA3041837C (en) | 2016-11-01 | 2021-08-10 | Psg Worldwide, Inc. | Magnetically coupled sealless centrifugal pump |
CN107313974A (en) * | 2017-07-04 | 2017-11-03 | 安徽腾龙泵阀制造有限公司 | A kind of separation sleeve for improving magnetic drive pump stability |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB888514A (en) * | 1958-06-28 | 1962-01-31 | Pumpindustri Ab | Magnetically driven fluid pump |
FR1432982A (en) * | 1965-04-21 | 1966-03-25 | Klausmaschinen Und Appbau F | Air gap tube pump with axial thrust compensation |
DE1453760A1 (en) * | 1962-01-08 | 1969-01-09 | Fuss Und Stahl Veredlung Gmbh | Pump with a rapidly rotating impeller, in particular a centrifugal pump |
DE1943124A1 (en) * | 1969-08-25 | 1971-03-04 | Elektrotechnik Maschb A Loell | Fluid pump, especially circulation pump for hot water heating systems |
US4047847A (en) * | 1975-03-26 | 1977-09-13 | Iwaki Co., Ltd. | Magnetically driven centrifugal pump |
GB1496035A (en) * | 1974-07-18 | 1977-12-21 | Iwaki Co Ltd | Magnetically driven centrifugal pump |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2970548A (en) * | 1958-06-23 | 1961-02-07 | Pumpindustri Ab | Magnetically driven pump |
SU144401A1 (en) * | 1961-05-11 | 1961-11-30 | В.В. Иванов | Hermetic drive centrifugal pump |
US3373927A (en) * | 1966-06-01 | 1968-03-19 | Carrier Corp | Fluid compressor |
US3597117A (en) * | 1969-01-10 | 1971-08-03 | Rotorn Inc | Fan for narrow environments |
US3825366A (en) * | 1972-07-31 | 1974-07-23 | Dresser Ind | Assembly for centrifugal blowers and the like |
DE2254265C3 (en) * | 1972-11-06 | 1980-06-12 | Franz 4630 Bochum Klaus | Chemical centrifugal pump without stuffing box |
FR2311201A1 (en) * | 1975-05-12 | 1976-12-10 | Siebec Filtres | Rotor support stub in magnetic pump - is retainable allowing stable seal fitment between stub and dividing wall |
US4304532A (en) * | 1979-12-17 | 1981-12-08 | Mccoy Lee A | Pump having magnetic drive |
-
1985
- 1985-05-08 DE DE8585105626T patent/DE3560533D1/en not_active Expired
- 1985-05-08 AT AT85105626T patent/ATE29275T1/en active
- 1985-05-08 EP EP85105626A patent/EP0171515B1/en not_active Expired
- 1985-07-09 US US06/753,140 patent/US4645433A/en not_active Expired - Lifetime
- 1985-07-16 JP JP15531785A patent/JPS6138192A/en active Granted
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB888514A (en) * | 1958-06-28 | 1962-01-31 | Pumpindustri Ab | Magnetically driven fluid pump |
DE1453760A1 (en) * | 1962-01-08 | 1969-01-09 | Fuss Und Stahl Veredlung Gmbh | Pump with a rapidly rotating impeller, in particular a centrifugal pump |
FR1432982A (en) * | 1965-04-21 | 1966-03-25 | Klausmaschinen Und Appbau F | Air gap tube pump with axial thrust compensation |
DE1943124A1 (en) * | 1969-08-25 | 1971-03-04 | Elektrotechnik Maschb A Loell | Fluid pump, especially circulation pump for hot water heating systems |
GB1496035A (en) * | 1974-07-18 | 1977-12-21 | Iwaki Co Ltd | Magnetically driven centrifugal pump |
US4047847A (en) * | 1975-03-26 | 1977-09-13 | Iwaki Co., Ltd. | Magnetically driven centrifugal pump |
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0237868A2 (en) * | 1986-03-21 | 1987-09-23 | Ernst Hauenstein | Radial or axial flow centrifugal pump |
EP0237868A3 (en) * | 1986-03-21 | 1988-01-20 | Ernst Hauenstein | Radial or axial flow centrifugal pump |
DE4238132C2 (en) * | 1992-11-12 | 2002-10-24 | Teves Gmbh Alfred | Centrifugal pump, in particular water pump for motor vehicles |
WO1996032592A1 (en) * | 1995-04-14 | 1996-10-17 | Ceramiques & Composites S.A. | Magnetic drive centrifugal pump |
FR2733010A1 (en) * | 1995-04-14 | 1996-10-18 | Ceramiques Et Composites Sa | MAGNETICALLY DRIVEN CENTRIFUGAL PUMP |
EP1329638A1 (en) * | 2002-01-18 | 2003-07-23 | CP Pumpen AG | Magnetically coupled centrifugal pump |
WO2007112938A2 (en) * | 2006-03-31 | 2007-10-11 | H. Wernert & Co. Ohg | Rotary pump with coaxial magnetic coupling |
WO2007112938A3 (en) * | 2006-03-31 | 2008-04-10 | Wernert & Co Ohg H | Rotary pump with coaxial magnetic coupling |
KR101410628B1 (en) * | 2006-03-31 | 2014-06-20 | 하. 베르너트 운트 코. 오하게 | Rotary pump with coaxial magnetic coupling |
Also Published As
Publication number | Publication date |
---|---|
DE3560533D1 (en) | 1987-10-08 |
JPH0562240B2 (en) | 1993-09-08 |
EP0171515B1 (en) | 1987-09-02 |
JPS6138192A (en) | 1986-02-24 |
US4645433A (en) | 1987-02-24 |
ATE29275T1 (en) | 1987-09-15 |
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