EP2322803B1 - Pump with a magnetic coupling - Google Patents

Pump with a magnetic coupling Download PDF

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Publication number
EP2322803B1
EP2322803B1 EP10190314.4A EP10190314A EP2322803B1 EP 2322803 B1 EP2322803 B1 EP 2322803B1 EP 10190314 A EP10190314 A EP 10190314A EP 2322803 B1 EP2322803 B1 EP 2322803B1
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EP
European Patent Office
Prior art keywords
fluid
rotor
pump
cover
containment
Prior art date
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Active
Application number
EP10190314.4A
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German (de)
French (fr)
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EP2322803A2 (en
EP2322803A3 (en
Inventor
Frank Holz
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Leistritz Pumpen GmbH
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Leistritz Pumpen GmbH
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Publication of EP2322803A2 publication Critical patent/EP2322803A2/en
Publication of EP2322803A3 publication Critical patent/EP2322803A3/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C15/0069—Magnetic couplings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0096—Heating; Cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/16—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/588—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps cooling or heating the machine

Definitions

  • the invention relates to a pump with a magnetic coupling, comprising a rotor shaft rotatably mounted in a pump housing, which carries an impeller or a spindle for conveying a fluid from a suction chamber into a pressure chamber as well as a rotor with an internal magnet arranged in a can through which the fluid flows. which can be set in rotation via the magnetic field of an external magnet.
  • a generic pump is from the patent US 5 165 868 discloses the features of the preamble of claim 1 and is considered the closest prior art.
  • Figure 1 shows a conventional pump with a magnetic coupling, a rotor shaft 2 rotatably mounted in a pump housing 1, which has an impeller or a spindle 3 for conveying a fluid from a suction chamber 4 into a pressure chamber 5.
  • the rotor shaft 2 carries a rotor 6, which is arranged in a containment shell 7, through which the fluid flows.
  • the rotor 6 has an inner magnet 8, which is in through the magnetic field Figure 1 External magnet, not shown, can be set in rotation.
  • a leakage flow is required, which is driven by the pressure difference between the suction side and the pressure side of the pump.
  • the leakage flow which is absolutely necessary for cooling the magnetic coupling, is branched off from the pumped medium by guiding it from the pressure chamber 5 in the pump housing 1 through a gap 9 between a throttle piston formed as a component of the rotor shaft 2 and a cover 10 axially closing the pump housing 1.
  • the fluid After flowing through the gap 9, the fluid passes into the can 7, between the cover 10 and the rotor 6 of the magnetic coupling, further through a narrow gap 11 between the inside of the can 7 and the rotor 6. From there, the fluid passes through a longitudinal bore 12 of the rotor shaft 2 back into the suction chamber 4 in the pump housing 1.
  • This flow guidance results in a not negligible force in the axial direction, which acts on the rotating components and must be absorbed by appropriately solid bearings.
  • the invention is therefore based on the object of specifying a pump with a magnetic coupling in which the axial force acting on the rotor shaft is reduced.
  • the suction chamber and the containment shell are connected to one another via a line through which the fluid can flow.
  • the line provided according to the invention which connects the containment shell to the suction chamber, prevents an appreciable axial force from acting on the rotor shaft.
  • the manufacture of the pump according to the invention is facilitated since the rotor shaft can be manufactured without a longitudinal bore. Instead, the fluid flows back through the line which connects the suction chamber to the containment shell and which can be arranged inside or outside the pump housing.
  • the line leading to the containment shell opens into a cover arranged between the pump housing and the containment shell.
  • the cover is thus located between the pump housing and the containment shell, the line connecting the suction space and the containment shell can be at least partially guided in the cover.
  • the cover arranged between the pressure chamber and the containment shell preferably has an opening which can be designed as a diaphragm. Due to the higher pressure in the pressure chamber compared to the containment shell, in which the pressure of the pressure chamber essentially prevails, a fluid flow is generated from the pressure chamber into the containment shell, which cools the magnetic coupling in the containment shell and in particular its rotor.
  • the opening in the lid opens into a gap between the outside of the rotor and the inside of the containment shell.
  • the outside of the rotor is practically completely flowed around by the fluid, as a result of which the heat generated during operation of the magnetic coupling is dissipated.
  • the size and the shape of the gap are selected such that the fluid essentially exerts pressure upon flowing through the gap is relaxed in the suction chamber.
  • the rotor of the pump according to the invention has a plurality of openings which are distributed in the circumferential direction and through which the fluid can flow. After flowing through the openings, the fluid returns to the suction space through the line.
  • a sealing gap is formed between the cover and the rotor. This sealing gap prevents a significant amount of the fluid from flowing directly into the area of the rotor shaft from the opening, instead the fluid is guided past the outside of the rotor, so that the desired cooling effect of the magnetic coupling is achieved.
  • the pump according to the invention can in particular be designed as a screw pump.
  • the pump 13 shown essentially consists of a pump housing 14 in which a rotor shaft 15 is rotatably mounted.
  • the rotor shaft 15 carries an impeller or a spindle 16, which with a in Fig. 2 not shown second, counter-rotating spindle combs, the spindles being formed with a spindle profile, so that during the rotation delivery spaces for a fluid are formed, whereby the fluid is axially conveyed.
  • On the in Fig. 2 On the left side is the suction chamber 17, which is connected to an inlet, not shown, for the fluid, at the other end of the spindle 16 is the pressure chamber 18, which is connected to an outlet, not shown, for the fluid.
  • a cover 19 is placed on the pump housing 14, which is open on one side.
  • a can 20 is attached to the cover 19 and receives a magnetic coupling.
  • the magnetic coupling comprises a rotor 21 which is fixedly connected to the rotor shaft 15.
  • the rotor 21 On its outside, the rotor 21 has an inner magnet 22 which consists of a A plurality of individual magnets exist.
  • the rotor 21 can be set in rotation by a magnetic rotary field generated outside the containment shell 20, so that it sets the intermeshing profile packages of the spindles 16 in rotation via the rotor shaft 15, whereby the fluid is conveyed from the suction chamber 17 into the pressure chamber 18.
  • the cover 19 has an opening 23 in the form of an aperture, which passes through the cover 19 and is connected on the one hand to the pressure chamber 18 and on the other hand to a gap 24 which is formed between the inside of the can 20 and the outside of the rotor 21.
  • the opening 23 causes part of the fluid from the pressure chamber 18 to flow through the opening 23 and the gap 24 past the outside of the rotor 21, as a result of which it is cooled.
  • the flowing fluid dissipates the heat generated by the external rotating field acting on the rotor 21.
  • the rotor 21 After the fluid has flowed around the rotor 21, it has been approximately released to the pressure prevailing in the suction space 17.
  • the rotor 21 has a plurality of openings 25 arranged distributed in the circumferential direction, so that the rotor 21 has the fluid flowing around it on practically all sides and is cooled in this way.
  • a circumferential sealing gap 26 is formed between the stationary cover 19 and the rotatable rotor 21, which ensures that the fluid flows into the can 20 via the outside of the rotor 21.
  • the rotor shaft 15 in the area of the cover 19 has a shoulder 27 with an enlarged diameter, so that the rotor shaft 15 acts as a throttle piston at this point.
  • Part of the fluid also flows into the can 20 between the shoulder 27 and a circular opening 28 in the cover 19.
  • the fluid flows out via a line 29, which is connected on the one hand to the interior of the can 20 and on the other hand to the suction chamber 17 the can 20 back into the suction chamber 17.
  • a section of the line 29 runs in the cover 19, another section runs outside the pump housing 14.
  • the line can be arranged completely outside the pump housing and open directly into the interior of the containment can without it being arranged inside the cover.
  • the line is arranged inside the pump housing.
  • the diameter of the line 29 is selected so that the comparatively large amount of the flowing fluid, which flows on the one hand via the opening 23 and on the other hand via the opening 28 into the can 20, can be removed.
  • the opening 23 is designed as an orifice whose opening diameter can be set differently depending on the pressure difference of the pump 13.
  • the pump shown has the advantage that there is no or only a slight axial force which acts on the rotor shaft 15. An axial force that may occur is only dependent on the pressure losses in the openings of the magnetic coupling and the external or internal line 29 that leads into the suction space 17.
  • Another advantage can be seen in the fact that the amount of the fluid serving as the cooling flow is independent of the leakage through the gap at the shoulder 27 of the rotor shaft 15 acting as a throttle piston, since the partial flows of the fluid for the cooling and the leakage are separated from one another. Since the rotor shaft 15 does not require a longitudinal bore, it can be manufactured more easily in comparison to through-drilled rotor shafts.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Rotary Pumps (AREA)
  • Dynamo-Electric Clutches, Dynamo-Electric Brakes (AREA)

Description

Die Erfindung betrifft eine Pumpe mit einer Magnetkupplung, umfassend eine in einem Pumpengehäuse drehbar gelagerte Rotorwelle, die ein Laufrad oder eine Spindel zum Fördern eines Fluids von einem Saugraum in einen Druckraum sowie einen in einem von dem Fluid durchströmten Spalttopf angeordneten Rotor mit einem Innenmagnet trägt, der über das magnetische Feld eines Außenmagnets in Drehung versetzbar ist.The invention relates to a pump with a magnetic coupling, comprising a rotor shaft rotatably mounted in a pump housing, which carries an impeller or a spindle for conveying a fluid from a suction chamber into a pressure chamber as well as a rotor with an internal magnet arranged in a can through which the fluid flows. which can be set in rotation via the magnetic field of an external magnet.

Bei herkömmlichen Pumpen muss besondere Aufmerksamkeit auf die Abdichtung der Antriebswelle gelegt werden, um das Austreten des geförderten Fluids zu vermeiden oder auf ein Minimum zu begrenzen. Die zu diesem Zweck eingesetzten dynamischen Dichtungen, die beispielsweise als Gleitringdichtungen ausgebildet sein können, sind allerdings Verschleißteile, die einen Wartungsaufwand verursachen. Um diesen Nachteil zu vermeiden, werden zum Pumpen von gefährlichen oder aggressiven Fluiden, die nicht in die Umgebung gelangen dürfen, Pumpen mit Spaltrotormotor oder Pumpen mit permanentmagnetischer Zentraldrehkupplung (Magnetkupplung) verwendet. Diese Pumpen weisen den Vorteil auf, dass keine dynamische Dichtung vorhanden ist.In conventional pumps, special attention must be paid to the sealing of the drive shaft in order to avoid or to keep the pumped fluid from escaping to a minimum. The dynamic seals used for this purpose, which can be designed, for example, as mechanical seals, are, however, wear parts that cause maintenance. In order to avoid this disadvantage, pumps with a split rotor motor or pumps with a permanent magnetic central rotary coupling (magnetic coupling) are used for pumping dangerous or aggressive fluids that must not get into the environment. These pumps have the advantage that there is no dynamic seal.

Eine gattungsgemäße Pumpe ist von der Patentschrift US 5 165 868 offenbart, die die Merkmale des Oberbegriffs des Anspruchs 1 zeigt und als nächstliegender Stand der Technik angesehen wird.A generic pump is from the patent US 5 165 868 discloses the features of the preamble of claim 1 and is considered the closest prior art.

Figur 1 zeigt eine herkömmliche Pumpe mit einer Magnetkupplung, einer in einem Pumpengehäuse 1 drehbar gelagerten Rotorwelle 2, die ein Laufrad oder eine Spindel 3 zum Fördern eines Fluids von einem Saugraum 4 in einen Druckraum 5 aufweist. Die Rotorwelle 2 trägt einen Rotor 6, der in einem Spalttopf 7 angeordnet ist, der von dem Fluid durchströmt wird. Der Rotor 6 weist einen Innenmagnet 8 auf, der durch das magnetische Feld eines in Figur 1 nicht gezeigten Außenmagnets in Drehung versetzbar ist. Zur Kühlung der in dem Spalttopf 7 angeordneten Magnetkupplung wird ein Leckagestrom benötigt, der durch den Druckunterschied zwischen Saugseite und Druckseite der Pumpe getrieben ist. Der Leckagestrom, der zwingend zur Kühlung der Magnetkupplung erforderlich ist, wird von dem geförderten Medium abgezweigt, indem dieses von dem Druckraum 5 im Pumpengehäuse 1 durch einen Spalt 9 zwischen einem als Bestandteil der Rotorwelle 2 ausgebildeten Drosselkolben und einem das Pumpengehäuse 1 axial verschließenden Deckel 10 geführt wird. Nach dem Durchströmen des Spalts 9 gelangt das Fluid in den Spalttopf 7, zwischen den Deckel 10 und dem Rotor 6 der Magnetkupplung, weiter durch einen engen Spalt 11 zwischen der Innenseite des Spalttopfes 7 und dem Rotor 6. Von dort gelangt das Fluid durch eine Längsbohrung 12 der Rotorwelle 2 wieder in den Saugraum 4 in dem Pumpengehäuse 1. Bei dieser Strömungsführung ergibt sich eine nicht zu vernachlässigende Kraft in axialer Richtung, die auf die rotierenden Komponenten einwirkt und durch entsprechend massiv ausgebildete Lager aufgefangen werden muss. Die Ursache für diese axiale Kraft ist die Verteilung des statischen Drucks innerhalb des Spalttopfes 7. Man hat daher versucht, derartige Pumpen so auszulegen, dass die auf die Rotorwelle einwirkende axiale Kraft möglichst gering ist. Da die erforderliche Kühlung der Magnetkupplung durch das Fluid gewährleistet werden muss, sind diesen Bemühungen allerdings Grenzen gesetzt. Figure 1 shows a conventional pump with a magnetic coupling, a rotor shaft 2 rotatably mounted in a pump housing 1, which has an impeller or a spindle 3 for conveying a fluid from a suction chamber 4 into a pressure chamber 5. The rotor shaft 2 carries a rotor 6, which is arranged in a containment shell 7, through which the fluid flows. The rotor 6 has an inner magnet 8, which is in through the magnetic field Figure 1 External magnet, not shown, can be set in rotation. To cool the magnetic coupling arranged in the containment shell 7, a leakage flow is required, which is driven by the pressure difference between the suction side and the pressure side of the pump. The leakage flow, which is absolutely necessary for cooling the magnetic coupling, is branched off from the pumped medium by guiding it from the pressure chamber 5 in the pump housing 1 through a gap 9 between a throttle piston formed as a component of the rotor shaft 2 and a cover 10 axially closing the pump housing 1. After flowing through the gap 9, the fluid passes into the can 7, between the cover 10 and the rotor 6 of the magnetic coupling, further through a narrow gap 11 between the inside of the can 7 and the rotor 6. From there, the fluid passes through a longitudinal bore 12 of the rotor shaft 2 back into the suction chamber 4 in the pump housing 1. This flow guidance results in a not negligible force in the axial direction, which acts on the rotating components and must be absorbed by appropriately solid bearings. The reason for this axial force is the distribution of the static pressure within the containment shell 7. Attempts have therefore been made to design pumps of this type in such a way that the axial force acting on the rotor shaft is as low as possible. However, since the required cooling of the magnetic coupling has to be ensured by the fluid, there are limits to these efforts.

Der Erfindung liegt daher die Aufgabe zugrunde, eine Pumpe mit einer Magnetkupplung anzugeben, bei der die auf die Rotorwelle wirkende Axialkraft verringert ist.The invention is therefore based on the object of specifying a pump with a magnetic coupling in which the axial force acting on the rotor shaft is reduced.

Diese Aufgabe wird durch eine erfindungsgemäße Pumpe gemäß Patentanspruch 1 gelöst.This object is achieved by an inventive pump according to claim 1.

Der Saugraum und der Spalttopf sind über eine von dem Fluid durchströmbare Leitung miteinander verbunden. Durch die erfindungsgemäß vorgesehene Leitung, die den Spalttopf mit dem Saugraum verbindet, wird verhindert, dass eine nennenswerte auf die Rotorwelle einwirkende Axialkraft entsteht. Die Herstellung der erfindungsgemäßen Pumpe wird erleichtert, da die Rotorwelle ohne Längsbohrung hergestellt werden kann. Das Fluid strömt stattdessen durch die Leitung zurück, die den Saugraum mit dem Spalttopf verbindet und die innerhalb oder außerhalb des Pumpengehäuses an-geordnet sein kann.The suction chamber and the containment shell are connected to one another via a line through which the fluid can flow. The line provided according to the invention, which connects the containment shell to the suction chamber, prevents an appreciable axial force from acting on the rotor shaft. The manufacture of the pump according to the invention is facilitated since the rotor shaft can be manufactured without a longitudinal bore. Instead, the fluid flows back through the line which connects the suction chamber to the containment shell and which can be arranged inside or outside the pump housing.

Bei der erfindungsgemäßen Pumpe kann es vorgesehen sein, dass die zum Spalttopf führende Leitung in einem zwischen dem Pumpengehäuse und dem Spalttopf angeordneten Deckel mündet. Der Deckel befindet sich somit zwischen dem Pumpengehäuse und dem Spalttopf, die den Saugraum und den Spalttopf verbindende Leitung kann zumindest teilweise in dem Deckel geführt sein.In the pump according to the invention it can be provided that the line leading to the containment shell opens into a cover arranged between the pump housing and the containment shell. The cover is thus located between the pump housing and the containment shell, the line connecting the suction space and the containment shell can be at least partially guided in the cover.

Vorzugsweise weist der zwischen dem Druckraum und dem Spalttopf angeordnete Deckel bei der erfindungsgemäßen Pumpe eine Öffnung auf, die als Blende ausgebildet sein kann. Durch den höheren Druck im Druckraum im Vergleich zum Spalttopf, in dem im Wesentlichen der Druck des Druckraums herrscht, entsteht ein Fluidstrom von dem Druckraum in den Spalttopf, der die Magnetkupplung in dem Spalttopf und insbesondere deren Rotor kühlt.In the pump according to the invention, the cover arranged between the pressure chamber and the containment shell preferably has an opening which can be designed as a diaphragm. Due to the higher pressure in the pressure chamber compared to the containment shell, in which the pressure of the pressure chamber essentially prevails, a fluid flow is generated from the pressure chamber into the containment shell, which cools the magnetic coupling in the containment shell and in particular its rotor.

Gemäß der Erfindung ist es vorgesehen, dass die Öffnung in dem Deckel in einen Spalt zwischen der Außenseite des Rotors und der Innenseite des Spalttopfes mündet. Dadurch wird der Rotor an seiner Außenseite praktisch vollständig von dem Fluid umströmt, wodurch die beim Betrieb der Magnetkupplung entstehende Wärme abgeführt wird.According to the invention, it is provided that the opening in the lid opens into a gap between the outside of the rotor and the inside of the containment shell. As a result, the outside of the rotor is practically completely flowed around by the fluid, as a result of which the heat generated during operation of the magnetic coupling is dissipated.

Um den bereits erwähnten Effekt zu erzielen, dass auf die Rotorwelle nahezu keine axiale Kraft ausgeübt wird, kann es erfindungsgemäß vorgesehen sein, dass die Größe und die Form des Spalts so gewählt sind, dass das Fluid nach dem Durchströmen des Spalts im Wesentlichen auf den Druck im Saugraum entspannt ist.In order to achieve the effect already mentioned that almost no axial force is exerted on the rotor shaft, it can be provided according to the invention that the size and the shape of the gap are selected such that the fluid essentially exerts pressure upon flowing through the gap is relaxed in the suction chamber.

Eine noch bessere und besonders gleichmäßige Kühlung der Magnetkupplung ergibt sich, wenn der Rotor der erfindungsgemäßen Pumpe mehrere in Umfangsrichtung verteilt angeordnete, von dem Fluid durchströmbare Öffnungen aufweist. Nach dem Durchströmen der Öffnungen gelangt das Fluid durch die Leitung wieder zurück in den Saugraum.An even better and particularly uniform cooling of the magnetic coupling is obtained if the rotor of the pump according to the invention has a plurality of openings which are distributed in the circumferential direction and through which the fluid can flow. After flowing through the openings, the fluid returns to the suction space through the line.

Gemäß der Erfindung ist es vorgesehen, dass zwischen dem Deckel und dem Rotor ein Dichtspalt gebildet ist. Dieser Dichtspalt verhindert, dass eine nennenswerte Menge des Fluids von der Öffnung direkt in den Bereich der Rotorwelle fließt, stattdessen wird das Fluid an der Außenseite des Rotors vorbei geführt, sodass die gewünschte Kühlwirkung der Magnetkupplung erzielt wird.According to the invention, it is provided that a sealing gap is formed between the cover and the rotor. This sealing gap prevents a significant amount of the fluid from flowing directly into the area of the rotor shaft from the opening, instead the fluid is guided past the outside of the rotor, so that the desired cooling effect of the magnetic coupling is achieved.

Die erfindungsgemäße Pumpe kann insbesondere als Schraubenspindelpumpe ausgebildet sein.The pump according to the invention can in particular be designed as a screw pump.

Weitere Vorteile und Einzelheiten der Erfindung werden nachfolgend anhand eines Ausführungsbeispiels unter Bezugnahme auf die Zeichnungen erläutert. Die Zeichnungen sind schematische Darstellungen, in denen die Pfeile jeweils die Strömungsrichtung des Fluids angeben, und zeigen:

Fig. 1
einen Schnitt durch eine herkömmliche Pumpe mit einer Magnetkupplung; und
Fig. 2
einen Schnitt durch eine erfindungsgemäße Pumpe mit einer Magnetkupplung.
Further advantages and details of the invention are explained below using an exemplary embodiment with reference to the drawings. The drawings are schematic representations, in which the arrows indicate the direction of flow of the fluid, and show:
Fig. 1
a section through a conventional pump with a magnetic coupling; and
Fig. 2
a section through a pump according to the invention with a magnetic coupling.

Die in Fig. 2 gezeigte Pumpe 13 besteht im Wesentlichen aus einem Pumpengehäuse 14, in dem eine Rotorwelle 15 drehbar gelagert ist. Die Rotorwelle 15 trägt ein Laufrad bzw. eine Spindel 16, die mit einer in Fig. 2 nicht gezeigten zweiten, gegenläufigen Spindel kämmt, wobei die Spindeln mit einem Spindelprofil ausgebildet sind, sodass bei der Rotation Förderräume für ein Fluid gebildet werden, wodurch das Fluid axial gefördert wird. Auf der in Fig. 2 linken Seite befindet sich der Saugraum 17, der mit einem nicht dargestellten Einlass für das Fluid verbunden ist, am anderen Ende der Spindel 16 befindet sich der Druckraum 18, der mit einem nicht dargestellten Auslass für das Fluid verbunden ist. Auf das an einer Seite offene Pumpengehäuse 14 ist ein Deckel 19 aufgesetzt. An dem Deckel 19 ist ein Spalttopf 20 befestigt, der eine Magnetkupplung aufnimmt. Die Magnetkupplung umfasst einen Rotor 21, der fest mit der Rotorwelle 15 verbunden ist. An seiner Außenseite besitzt der Rotor 21 einen Innenmagnet 22, der aus einer Mehrzahl von Einzelmagneten besteht. Durch ein außerhalb des Spalttopfes 20 erzeugtes magnetisches Drehfeld kann der Rotor 21 in Drehung versetzt werden, sodass er über die Rotorwelle 15 die miteinander kämmenden Profilpakete der Spindeln 16 in Drehung versetzt, wodurch das Fluid von dem Saugraum 17 in den Druckraum 18 gefördert wird.In the Fig. 2 The pump 13 shown essentially consists of a pump housing 14 in which a rotor shaft 15 is rotatably mounted. The rotor shaft 15 carries an impeller or a spindle 16, which with a in Fig. 2 not shown second, counter-rotating spindle combs, the spindles being formed with a spindle profile, so that during the rotation delivery spaces for a fluid are formed, whereby the fluid is axially conveyed. On the in Fig. 2 On the left side is the suction chamber 17, which is connected to an inlet, not shown, for the fluid, at the other end of the spindle 16 is the pressure chamber 18, which is connected to an outlet, not shown, for the fluid. A cover 19 is placed on the pump housing 14, which is open on one side. A can 20 is attached to the cover 19 and receives a magnetic coupling. The magnetic coupling comprises a rotor 21 which is fixedly connected to the rotor shaft 15. On its outside, the rotor 21 has an inner magnet 22 which consists of a A plurality of individual magnets exist. The rotor 21 can be set in rotation by a magnetic rotary field generated outside the containment shell 20, so that it sets the intermeshing profile packages of the spindles 16 in rotation via the rotor shaft 15, whereby the fluid is conveyed from the suction chamber 17 into the pressure chamber 18.

Der Deckel 19 weist eine als Blende ausgebildete Öffnung 23 auf, die den Deckel 19 durchsetzt und einerseits mit dem Druckraum 18 und andererseits mit einem Spalt 24 verbunden ist, der zwischen der Innenseite des Spalttopfes 20 und der Außenseite des Rotors 21 gebildet ist. Die Öffnung 23 bewirkt, dass ein Teil des Fluids aus dem Druckraum 18 durch die Öffnung 23 und den Spalt 24 an der Außenseite des Rotors 21 vorbei strömt, wodurch dieser gekühlt wird. Das strömende Fluid führt die Wärme ab, die durch das auf den Rotor 21 einwirkende externe Drehfeld erzeugt wird.The cover 19 has an opening 23 in the form of an aperture, which passes through the cover 19 and is connected on the one hand to the pressure chamber 18 and on the other hand to a gap 24 which is formed between the inside of the can 20 and the outside of the rotor 21. The opening 23 causes part of the fluid from the pressure chamber 18 to flow through the opening 23 and the gap 24 past the outside of the rotor 21, as a result of which it is cooled. The flowing fluid dissipates the heat generated by the external rotating field acting on the rotor 21.

Nachdem das Fluid den Rotor 21 umströmt hat, ist es näherungsweise auf den in dem Saugraum 17 herrschenden Druck entspannt worden. Der Rotor 21 weist mehrere in Umfangsrichtung verteilt angeordnete Öffnungen 25 auf, sodass der Rotor 21 praktisch an allen Seiten von dem Fluid umströmt und auf diese Weise gekühlt wird. Zwischen dem ortsfesten Deckel 19 und dem drehbaren Rotor 21 ist ein in Umfangsrichtung umlaufender Dichtspalt 26 gebildet, der sicherstellt, dass das Fluid über die Außenseite des Rotors 21 in den Spalttopf 20 strömt.After the fluid has flowed around the rotor 21, it has been approximately released to the pressure prevailing in the suction space 17. The rotor 21 has a plurality of openings 25 arranged distributed in the circumferential direction, so that the rotor 21 has the fluid flowing around it on practically all sides and is cooled in this way. A circumferential sealing gap 26 is formed between the stationary cover 19 and the rotatable rotor 21, which ensures that the fluid flows into the can 20 via the outside of the rotor 21.

Wie in Fig. 2 gezeigt ist, weist die Rotorwelle 15 im Bereich des Deckels 19 einen Absatz 27 mit einem vergrößerten Durchmesser auf, sodass die Rotorwelle 15 an dieser Stelle als Drosselkolben wirkt. Zwischen dem Absatz 27 und einer kreisförmigen Öffnung 28 in dem Deckel 19 strömt ebenfalls ein Teil des Fluids in den Spalttopf 20. Über eine Leitung 29, die einerseits mit dem Innenraum des Spalttopfes 20 und andererseits mit dem Saugraum 17 verbunden ist, strömt das Fluid aus dem Spalttopf 20 zurück in den Saugraum 17. Ein Abschnitt der Leitung 29 verläuft in dem dargestellten Ausführungsbeispiel in dem Deckel 19, ein weiterer Abschnitt verläuft außerhalb des Pumpengehäuses 14. Bei anderen Ausführungen kann die Leitung vollständig außerhalb des Pumpengehäuses angeordnet sein und direkt in den Innenraum des Spalttopfes münden, ohne dass sie innerhalb des Deckels angeordnet ist. Daneben sind Anordnungen möglich, bei denen die Leitung innerhalb des Pumpengehäuses angeordnet ist. Der Durchmesser der Leitung 29 ist so gewählt, dass die vergleichsweise große Menge des strömenden Fluids, das einerseits über die Öffnung 23 und andererseits über die Öffnung 28 in den Spalttopf 20 strömt, abgeführt werden kann.As in Fig. 2 is shown, the rotor shaft 15 in the area of the cover 19 has a shoulder 27 with an enlarged diameter, so that the rotor shaft 15 acts as a throttle piston at this point. Part of the fluid also flows into the can 20 between the shoulder 27 and a circular opening 28 in the cover 19. The fluid flows out via a line 29, which is connected on the one hand to the interior of the can 20 and on the other hand to the suction chamber 17 the can 20 back into the suction chamber 17. In the exemplary embodiment shown, a section of the line 29 runs in the cover 19, another section runs outside the pump housing 14. In other embodiments, the line can be arranged completely outside the pump housing and open directly into the interior of the containment can without it being arranged inside the cover. In addition, arrangements are possible in which the line is arranged inside the pump housing. The diameter of the line 29 is selected so that the comparatively large amount of the flowing fluid, which flows on the one hand via the opening 23 and on the other hand via the opening 28 into the can 20, can be removed.

Um den Einfluss der Viskosität des geförderten Fluids auf die Kühlstrommenge auszugleichen, ist die Öffnung 23 als Blende ausgebildet, deren Öffnungsdurchmesser in Abhängigkeit von der Druckdifferenz der Pumpe 13 unterschiedlich eingestellt sein kann.In order to compensate for the influence of the viscosity of the conveyed fluid on the amount of cooling current, the opening 23 is designed as an orifice whose opening diameter can be set differently depending on the pressure difference of the pump 13.

Die in Fig. 2 gezeigte Pumpe weist den Vorteil auf, dass keine oder lediglich eine geringe axiale Kraft entsteht, die auf die Rotorwelle 15 wirkt. Eine gegebenenfalls auftretende axiale Kraft ist lediglich von den Druckverlusten in den Öffnungen der Magnetkupplung und der externen oder internen Leitung 29, die in den Saugraum 17 führt, abhängig. Ein weiterer Vorteil ist darin zu sehen, dass die Menge des als Kühlstrom dienenden Fluids unabhängig von der Leckage durch den Spalt am Absatz 27 der als Drosselkolben wirkenden Rotorwelle 15 ist, da die Teilströme des Fluids für die Kühlung und die Leckage voneinander getrennt sind. Da die Rotorwelle 15 keine Längsbohrung benötigt, kann sie im Vergleich zu durchbohrten Rotorwellen einfacher hergestellt werden.In the Fig. 2 The pump shown has the advantage that there is no or only a slight axial force which acts on the rotor shaft 15. An axial force that may occur is only dependent on the pressure losses in the openings of the magnetic coupling and the external or internal line 29 that leads into the suction space 17. Another advantage can be seen in the fact that the amount of the fluid serving as the cooling flow is independent of the leakage through the gap at the shoulder 27 of the rotor shaft 15 acting as a throttle piston, since the partial flows of the fluid for the cooling and the leakage are separated from one another. Since the rotor shaft 15 does not require a longitudinal bore, it can be manufactured more easily in comparison to through-drilled rotor shafts.

Claims (6)

  1. Pump (13) having a magnetic coupling, comprising a rotor shaft (15) which is mounted rotatably in a pump housing (14) and which bears an impeller or a spindle (16) for delivering a fluid from a suction space (17) into a pressure space (18) and bears a rotor (21) arranged in a containment can (20) through which the fluid flows, said rotor having an inner magnet and being able to be set in rotation via the magnetic field of an outer magnet, wherein the suction space (17) and the containment can (20) are connected to one another via a line (29) through which the fluid is able to flow, wherein a cover (19) having an opening (23) is arranged between the pressure space (18) and the containment can (20), characterized in that a sealing gap (26) is formed between the cover (19) and the rotor (21), and the opening (23) is connected to a gap (24) which is formed between the inner side of the containment can (20) and the outer side of the rotor (21), wherein the rotor shaft (15) has in the region of the cover (19) a shoulder (27) with an enlarged diameter, with the result that the rotor shaft (27) acts as a throttle piston at this location, wherein a ring-shaped opening (28) is formed between the cover (19) and the shoulder (27), wherein both openings (23, 28) allow the fluid to flow from the pressure space (18) into the containment can (20), and the line (29) allows the fluid to flow back into the suction space (17).
  2. Pump according to Claim 1, characterized in that the line (29) connecting the suction space (17) and the containment can (20) opens into the cover (19) arranged between the pump housing (14) and the containment can (20) .
  3. Pump according to Claim 1 or 2, characterized in that the opening (23) provided in the cover (19) has an aperture.
  4. Pump according to one of the preceding claims, characterized in that the size and the shape of the gap (24) are selected such that the fluid, after flowing through the gap (24), is expanded substantially to the pressure in the suction space (17).
  5. Pump according to one of the preceding claims, characterized in that the rotor (21) has multiple openings (25) which are arranged so as to be distributed in a circumferential direction and through which the fluid is able to flow.
  6. Pump according to one of the preceding claims, characterized in that it is designed as a screw spindle pump.
EP10190314.4A 2009-11-11 2010-11-08 Pump with a magnetic coupling Active EP2322803B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102009052856A DE102009052856B3 (en) 2009-11-11 2009-11-11 Pump i.e. screw pump, has magnetic clutch provided with rotor shaft that is rotatably supported by pump housing, and suction chamber and slit pot connected with each other over line by fluid

Publications (3)

Publication Number Publication Date
EP2322803A2 EP2322803A2 (en) 2011-05-18
EP2322803A3 EP2322803A3 (en) 2014-09-03
EP2322803B1 true EP2322803B1 (en) 2020-05-06

Family

ID=42538772

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10190314.4A Active EP2322803B1 (en) 2009-11-11 2010-11-08 Pump with a magnetic coupling

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EP (1) EP2322803B1 (en)
DE (1) DE102009052856B3 (en)
ES (1) ES2796658T3 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013206141A1 (en) 2013-04-08 2014-10-09 Schaeffler Technologies Gmbh & Co. Kg Media-lubricated rolling bearing
DE102016120579B3 (en) * 2016-10-27 2018-04-05 Klaus Union Gmbh & Co. Kg Horizontally split screw pump
EP3567333A1 (en) * 2018-05-09 2019-11-13 Linde Aktiengesellschaft Drive device for a cleaning device for a heat exchanger
DE102018113950A1 (en) 2018-06-12 2019-12-12 Geomar Helmholtz-Zentrum Für Ozeanforschung Kiel Device for non-contact transmission of rotational movements
DE102021133106A1 (en) 2021-12-14 2023-06-15 Leistritz Pumpen Gmbh screw pump
DE102023117802A1 (en) * 2023-07-06 2025-01-09 Netzsch Pumpen & Systeme Gmbh eccentric screw pump with magnetic coupling

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8906020U1 (en) * 1989-05-13 1989-06-29 Rheinhütte GmbH & Co., 6200 Wiesbaden Magnetic coupling pump
US5165868A (en) * 1991-04-29 1992-11-24 Tuthill Corporation Magnetically driven pump
JP3346698B2 (en) * 1996-03-18 2002-11-18 株式会社荏原製作所 High temperature motor pump and its operation method
US5763973A (en) * 1996-10-30 1998-06-09 Imo Industries, Inc. Composite barrier can for a magnetic coupling
DE10024953A1 (en) * 2000-05-22 2001-11-29 Richter Chemie Tech Itt Gmbh Centrifugal pump with magnetic coupling
US20040105768A1 (en) * 2002-11-27 2004-06-03 Cameron Donald B. Internal recirculation for magnetically coupled positive displacement pumps

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP2322803A2 (en) 2011-05-18
ES2796658T3 (en) 2020-11-27
DE102009052856B3 (en) 2010-09-09
EP2322803A3 (en) 2014-09-03

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