EP1979621B1 - Magnetically coupled centrifugal pump for corrosive media - Google Patents
Magnetically coupled centrifugal pump for corrosive media Download PDFInfo
- Publication number
- EP1979621B1 EP1979621B1 EP08715923A EP08715923A EP1979621B1 EP 1979621 B1 EP1979621 B1 EP 1979621B1 EP 08715923 A EP08715923 A EP 08715923A EP 08715923 A EP08715923 A EP 08715923A EP 1979621 B1 EP1979621 B1 EP 1979621B1
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- EP
- European Patent Office
- Prior art keywords
- centrifugal pump
- bearings
- hub
- pump according
- permanent magnets
- 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.)
- Revoked
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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
- F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
- F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
- F04D7/06—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being hot or corrosive, e.g. liquid metals
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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
- F04D29/046—Bearings
- F04D29/0465—Ceramic bearing designs
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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
- F04D29/046—Bearings
- F04D29/049—Roller bearings
Definitions
- a magnetically coupled centrifugal pump is known, according to which the preamble of claim 1 has been formed and which for pumping a fluid medium, a housing in which a split pot, which has a bottom, a jacket and a clamped between two parts of the housing flange, one of the Medium flowed pump chamber separated by a permanent magnet on its circumference bearing rotor, which is driven by a motor.
- a pump chamber opens a suction and for the outlet of the medium is an out of the pump room leading outlet exists.
- an impeller is arranged, which is rotatably connected to a hub which is mounted on an axle and carries permanent magnets, which are opposite to the permanent magnets of the driving rotor.
- the hub is arranged with its permanent magnets in the containment shell, which has a cylindrical or nearly cylindrical shell.
- the impeller is arranged outside the gap pot in the pump room.
- a centrifugal pump designed as a centrifugal pump, as in US-A-4,013,384 represented, by rotation of the impeller, the medium is sucked through an axially arranged suction port and out through a radially arranged outlet opening out of the pump chamber.
- the medium is sucked by rotation of the impeller through a radially disposed suction port and out through a radially arranged outlet opening out of the pump chamber.
- the inlet opening and the outlet opening are not opposite each other diagonally; A pumping channel extends beyond its larger spacing, taken in the circumferential direction of the impeller, whereas otherwise a barrier is provided between the inlet opening and the outlet opening.
- the impeller is driven indirectly by an electric motor, which is mechanically connected to the driving rotor, which at least partially surrounds the jacket of the split pot and carries the permanent magnets which transmit the rotational movement of the driving rotor to the impeller by magnetic coupling with the permanent magnets of the impeller ,
- the magnetically coupled drive makes it possible to pump corrosive and aggressive media with the centrifugal pump without endangering the drive unit because it is hermetically separated from the pump chamber by the stationary containment shell.
- the surfaces in contact with the medium in the pump room are not metallic, but are made of a plastic such as plastic.
- Polypropylene PP
- PVDF polyvinylidene fluoride
- PPS polyphenylene sulfide
- PEEK polyetheretherketone
- PTFE polytetrafluoroethylene
- bearing for the magnetically coupled centrifugal pump for aggressive and corrosive media slide bearings are used from an alumina ceramic, carbon or plastic, which are lubricated by the pumped medium itself by the medium flows on the jacket of the split pot along to the bottom, where it is deflected and then the plain bearings flows through, for which purpose gaps are provided.
- the impeller In order to make the pump suitable for short periods of dry running, the impeller has a hub with two ceramic ball bearings whose inner races are seated on a metallic axle and on whose outer races a metallic sleeve is shrunk onto which the actual impeller is welded.
- the present invention has for its object to provide a magnetically coupled centrifugal pump, which is particularly suitable for pumping corrosive and aggressive media, is highly suitable for dry running and shows a smooth running even at high pumping power.
- the jacket of the split pot is, as is known, cylindrical or almost cylindrical. Almost cylindrical means a slight, the demolding of the split pot facilitating conicity.
- the length of the split pot is to achieve a smooth running and precise alignment of the impeller of the pump and for transmitting high torques greater than the outer diameter of the shell of the split pot.
- the length of the split pot is approximately equal to the length of the hub, which is in the containment shell. It can easily be up to a multiple of the outer diameter of the shell of the split pot.
- Zirconium oxide, silicon carbide and silicon nitride are particularly suitable as material for the rolling elements and the races of the ceramic rolling bearings. They are characterized by high hardness, strength and chemical resistance and can be produced with high dimensional stability and surface quality.
- the rolling elements have an average roughness of less than 0.1 microns, more preferably less than 0.05 microns, and the running surfaces of the rolling bearing rings preferably have an average roughness of not more than 0.35 microns, in particular an average roughness of not more than 0.32 ⁇ m.
- Investigations on a centrifugal pump according to the invention with such rolling bearings have shown that even in dry running for hours and days, the temperature of the bearings only by a few degrees Celsius, so that in a pump according to the invention with such ceramic bearings is for the first time an absolute dry running safety. In this case, the additional effort required for this is insignificant in terms of the technical progress achievable thereby and the achievable high operational reliability.
- the rolling bearings can be designed as ball bearings or roller bearings. Particularly preferred is the use of radial deep groove ball bearings.
- the hub is stored on two radial bearings. If the ability of the radial bearing to absorb axial forces, should be insufficient in individual cases, one or two ceramic thrust bearings can be additionally provided or a radial ball bearing can be replaced by two designed as a radial shoulder bearing ball bearings.
- a pump according to the invention is no longer endangered by dry running, dry running can have a cause which represents a risk to the system in which the pump is operated or to the medium pumped therein.
- a sensor is preferably provided in connection with the pump, which detects a occurring during dry running of the pump or changing the measured variable. The occurrence of such a measurand or the change of such a measurand may be communicated as an indication of dry running to an operator or to a control room and cause the cause to be checked.
- an acoustic sensor is provided. It has been shown that ceramic bearings emit characteristic noise in dry running, which are not present when the ceramic bearings are surrounded by the medium to be pumped and penetrated.
- noises can be easily detected by an acoustic sensor and distinguished from other noises, the distinction being able to be improved by determining the typical frequency spectrum of the noises and narrowing the sensitivity of the acoustic sensor to a frequency range in which the characteristic dry running noise is particularly pronounced strongly occur.
- the in the FIGS. 1 to 5 The rear part 2 of the housing 1 receives a split pot 3, which has a bottom 4, a slightly conical jacket 5 and a flange 6, which between the rear part 2 of the housing and a front part. 7 is clamped in the housing and in this way a medium flowed through the pump chamber 8 separates from a rear space 9, in which a rotor 10 is mounted, which is driven by an electric motor 27 which is attached to the rear end of the housing 1.
- the rotor 10 is cup-shaped and surrounds the gap pot 3. At the inner periphery of the rotor 10 permanent magnets 11 are attached. They are opposed to permanent magnets 12, which are embedded in a sleeve 29 which is mounted on a hub 13 which is disposed in the split pot 3 and rotatably supported on an axle 14. The sleeve 29 with the permanent magnets 12 is rotatably connected to the hub 13.
- the inner race 15a of the rear ball bearing 15 abuts against a rear collar surface 17 of the axle 14.
- the inner race 16a of the front ball bearing 16 abuts against a front collar surface 18 of the axle 14.
- the outer race 15b of the rear ball bearing 15 is secured by a locking ring 19 engaging in the hub 13.
- the outer race 16a of the front ball bearing 16 is clamped between a collar surface 20 on the hub 13 and a cylindrical extension 21 of an impeller 22 which is mounted outside of the split pot 3 at the front end of the hub 13.
- the axis 14 is inserted with its rear end in a provided on the bottom 4 of the split pot 3 recess 23 and with its front end in a formed in the front housing part 7 bracket 24.
- the flattening is designated by the reference numeral 28.
- the recess 23 in the bottom 4 of the can 3 is suitably flattened to match; This results in a positive engagement, softer rotation of the axle 14 prevents.
- the races 15a, 15b, 16, a and 16b of the ball bearings and the balls 15c and 16c are made of a ceramic material, in particular of silicon nitride or zirconia.
- An unillustrated ball cage is preferably made of plastic.
- the motor 27 drives the rotor 10. This in turn drives by the magnetic coupling between the permanent magnets 11 and 12, the hub 13 and is therefore referred to as a driving rotor 10.
- the impeller 22 rotates together with the hub 13 to which it is attached sucks the medium to be pumped through an axially arranged suction port 25 and conveys it through a radially arranged outlet opening 26 out of the pump chamber 8.
- the containment shell 3 is preferably made of plastic, but may also consist of a ceramic, for example of alumina.
- the axis 14 is preferably made of alumina, but may also consist of a plastic.
- a sucked by the pump liquid medium can flow through an existing between the hub 13 and the sleeve 29 and the gap pot 3 annular gap to the bottom 4 of the split pot 3. There, the medium is deflected and flows back through an existing between the axis 14 and the impeller annular gap 22, where it penetrates the two ceramic ball bearings 15 and 16 and lubricates. If the lubrication of the ceramic ball bearings 15 and 16 is interrupted, they may dry without damage, which may be caused by e.g. on the outside of the housing 1 mounted acoustic sensor due to a characteristic of the dry running, emanating from the ceramic ball bearings 15 and 16 noise development and can be reported.
- FIG. 6 shows a longitudinally-cut hub 13 on an axis 14, which in relation to the corresponding arrangement in the FIGS. 1 to 5 is modified to the effect that instead of the front deep groove ball bearing 16, a radial roller bearing 30 is provided, which sits with its inner race 30a on the axis 14, with its outer race 30b sitting in the hub 13 and between inner race 30a and outer race 30b a wreath of preferably cylindrical rollers 30c.
- FIG. 7 illustrated embodiment shows a longitudinal section of an arrangement of a hub 13 and an axis 14, which differs from the corresponding arrangement in the embodiment according to the FIGS. 1 to 5 differs in that for the two deep groove ball bearings 15 and 16 no separate inner race is provided. Instead, 14 grooves 15 d and 16 d are provided in the axis, so that the axis 14 itself, which consists of a ceramic material, the function of the inner races of the radial deep groove ball bearings 15 and 16 takes over.
- FIG. 8 shows an arrangement of a longitudinally-cut hub 13 and an axis 14, which in relation to in the FIGS. 1 to 5 illustrated arrangement is modified to the effect that instead of the front deep groove ball bearing 16, a radial roller bearing 30 is provided and that instead of the rear deep groove ball bearing 15 as two shoulder bearings 31 and 32 formed radial deep groove ball bearings are provided.
- the roller bearing 30 uses as a running surface 34 for its cylindrical rollers 30c a suitably turned off and ending on a shoulder 33 cylindrical portion 34 of the shaft 4, which serves as a running surface for the cylindrical rollers 30c, which are trapped between a shoulder 33 of the axle 14 and a shoulder 30d of the outer race 30b instead of an inner race.
- the two radial shoulder bearings 31 and 32 are arranged so that their unilateral shoulders 31 d and 32 d abut each other. This makes it possible to transfer or absorb higher axial thrusts between the axle 14 and the hub 13.
- FIG. 9 shows a hub 13 for a pump according to the prior art, wherein an axis 14 is supported in a conventional manner by means of ceramic plain bearings 35 and 36, which are held by a spacer sleeve 37 at a distance.
- a helical groove 38 is provided in the plain bearings 35 and 36.
- one or more elastomeric rings 39 are provided which compensate for the lower metallic compressive strength of the ceramic materials.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Ceramic Engineering (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
Aus der
Bei einer als Zentrifugalpumpe ausgebildeten Kreiselpumpe, wie in der
Angetrieben wird das Laufrad mittelbar durch einen elektrischen Motor, welcher mechanisch mit dem treibenden Läufer verbunden ist, welcher den Mantel des Spalttopfes wenigstens teilweise umgibt und die Permanentmagnete trägt, welche durch magnetische Kupplung mit den Permanentmagneten des Laufrades die Drehbewegung des treibenden Läufers auf das Laufrad übertragen. Der magnetgekuppelte Antrieb ermöglicht es, mit der Kreiselpumpe korrosive und aggressive Medien zu pumpen, ohne das Antriebsaggregat zu gefährden, weil dieses durch den ruhenden Spalttopf hermetisch vom Pumpenraum getrennt ist. Für das Pumpen aggressiver und korrosiver Medien sind die im Pumpenraum mit dem Medium in Berührung kommenden Oberflächen nicht metallisch, sondern bestehen aus einem Kunststoff wie z.B. Polypropylen (PP), Polyvinylidenfluorid (PVDF), Polyphenylensulfid (PPS), Polyetheretherketon (PEEK) oder Polytetrafluorethylen (PTFE) oder aus einer Oxidkeramik, insbesondere aus Aluminiumoxid.The impeller is driven indirectly by an electric motor, which is mechanically connected to the driving rotor, which at least partially surrounds the jacket of the split pot and carries the permanent magnets which transmit the rotational movement of the driving rotor to the impeller by magnetic coupling with the permanent magnets of the impeller , The magnetically coupled drive makes it possible to pump corrosive and aggressive media with the centrifugal pump without endangering the drive unit because it is hermetically separated from the pump chamber by the stationary containment shell. For pumping aggressive and corrosive media, the surfaces in contact with the medium in the pump room are not metallic, but are made of a plastic such as plastic. Polypropylene (PP), polyvinylidene fluoride (PVDF), polyphenylene sulfide (PPS), polyetheretherketone (PEEK) or polytetrafluoroethylene (PTFE) or of an oxide ceramic, in particular of aluminum oxide.
Als Lager für die magnetgekuppelte Kreiselpumpe für aggressive und korrosive Medien werden Gleitlager aus einer Aluminiumoxidkeramik, aus Kohle oder aus Kunststoff verwendet, welche durch das zu pumpende Medium selbst geschmiert werden, indem das Medium am Mantel des Spalttopfes entlang zu dessen Boden strömt, dort umgelenkt wird und anschließend die Gleitlager durchströmt, wozu Spalte vorgesehen sind.As a bearing for the magnetically coupled centrifugal pump for aggressive and corrosive media slide bearings are used from an alumina ceramic, carbon or plastic, which are lubricated by the pumped medium itself by the medium flows on the jacket of the split pot along to the bottom, where it is deflected and then the plain bearings flows through, for which purpose gaps are provided.
Die Anwender solcher Pumpen fordern, dass die Pumpen trockenlaufsicher sein sollen. Trotz aller konstruktiver Bemühungen gibt es jedoch bisher keine wirklich trockenlaufsichere Pumpe für aggressive und korrosive Medien. Kommt es zu einem Trockenlaufen, dann erhitzen sich die Gleitlager sehr schnell auf Temperaturen, die für die im Pumpenraum verwendeten Kunststoffe unverträglich sind und zu einem Versagen der Pumpe führen, so dass diese ausgetauscht werden muss, was aufwendig ist und Betriebsstörungen und Betriebsunterbrechungen nach sich zieht.The users of such pumps demand that the pumps should be dry running safe. Despite all constructive efforts, however, there is so far no really run dry pump for aggressive and corrosive media. If it comes to a dry running, then the plain bearings heat up very quickly to temperatures that are incompatible for the plastics used in the pump room and lead to failure of the pump, so that they must be replaced, which is expensive and malfunctions and business interruptions entails ,
Aus der
Für das Pumpen korrosiver Medien, wofür insbesondere in der chemischen Verfahrenstechnik ein Bedarf besteht, ist die aus der
Der vorliegenden Erfindung liegt die Aufgabe zugrunde, eine magnetgekuppelte Kreiselpumpe zu schaffen, welche sich besonders für das Pumpen korrosiver und aggressiver Medien eignet, in hohem Maße für einen Trockenlauf geeignet ist und auch bei hoher Pumpleistung einen ruhigen Lauf zeigt.The present invention has for its object to provide a magnetically coupled centrifugal pump, which is particularly suitable for pumping corrosive and aggressive media, is highly suitable for dry running and shows a smooth running even at high pumping power.
Diese Aufgabe wird gelöst durch eine magnetgekuppelte Kreiselpumpe mit den im Anspruch 1 angegebenen Merkmalen. Vorteilhafte Weiterbildungen der Erfindung sind Gegenstand der Unteransprüche.This object is achieved by a magnetically coupled centrifugal pump having the features specified in
Überraschenderweise hat es sich gezeigt, dass bei magnetgekuppelten Kreiselpumpen in der für das Pumpen korrosiver Medien gebräuchlichen Bauart, bei welcher die mit Permanentmagneten bestückte Nabe des Laufrades der Pumpe in einem tiefen Spalttopf angeordnet ist, die Lagerung der Nabe auf der Achse des Laufrades mit einem oder mehreren keramischen Wälzlagern anstelle von keramischen Gleitlagern die Betriebssicherheit und insbesondere die Sicherheit gegenüber einem Trockenlaufen der Lager unerwartet stark erhöht. Außerdem haben sich Befürchtungen als unbegründet erwiesen, Ablagerungen, die im Ringspalt von Gleitlagern zermalen und ausgeschwemmt werden können, würden bei Einsatz eines Wälzlagers bald zu einem Lagerschaden führen. Dazu zeichnet sich die erfindungsgemäße Bauart durch ruhigen, die keramischen Wälzlager schonenden Lauf auch bei hoher Pumpenleistung aus.Surprisingly, it has been shown that in magnetically coupled centrifugal pumps in the conventional type for pumping corrosive media in which the hub fitted with permanent magnets of the impeller of the pump is arranged in a deep containment shell, the bearing of the hub on the axis of the impeller with or several ceramic bearings instead of ceramic bearings the reliability and especially the security against dry running of the bearings unexpectedly increased. In addition, fears have proved to be unfounded, deposits that can be crushed and flushed out in the annular gap of plain bearings would soon lead to a bearing damage when using a rolling bearing. For this purpose, the design of the invention is characterized quiet, the ceramic bearings gentle running even at high pump performance.
Die Vorteile, die durch die Erfindung erzielt werden, sind überzeugend:
- Der mit der erfindungsgemäßen Pumpe erzielte sprunghafte Fortschritt in der Betriebssicherheit, insbesondere im Ausmaß der Trockenlaufeignung, rechtfertigt es erstmals, bei Pumpen der erfindungsgemäßen Gattung von einer wirklichen Trockenlaufsicherheit zu reden.
- Bei der Konstruktion der magnetgekuppelten Kreiselpumpe muss nicht mehr darauf Rücksicht genommen werden, dass eine Schmierung der Lager durch das zu pumpende Medium in jedem Fall gewährleistet ist.
- Die Nabe des Laufrades der Pumpe kann praktisch beliebig verlängert werden, ohne dass man ein Versagen der Pumpe durch Trockenlaufen befürchten muss.
- Für die Anzahl der Magnete, die das Drehmoment übertragen, gibt es praktisch keine Einschränkungen mehr, so dass auch sehr leistungsfähige Pumpen gebaut werden können.
- Magnetgekuppelte Kreiselpumpen erleiden bei der Übertragung des Drehmomentes vom treibenden Läufer auf das Laufrad der Pumpe Induktionsverluste, die mit der Relativgeschwindigkeit zwischen den rotierenden Permanentmagneten und dem stillstehenden Mantel des Spalttopfes zunehmen, sofern der Spalttopf elektrisch leitfähiges Material aufweist. Die Induktionsverluste können bei einer erfindungsgemäßen Pumpe verringert werden, indem man den Durchmesser der Nabe und entsprechend den Durchmesser des Kranzes der Permanentmagnete des treibenden Läufers verringert. Zwar lassen sich auf einem verringerten Umfang nur noch weniger Dauermagnete anordnen, doch kann das durch eine Verlängerung der Nabe und des treibenden Läufers ausgeglichen werden, ohne eine Beschädigung der Pumpe durch Trockenlaufen befürchten zu müssen.
- Herkömmliche magnetgekuppelte Kreiselpumpen mit Gleitlagern haben ein Axialspiel, welches durch zusätzliche, axial wirksame Magnete begrenzt werden muss, wie es z.B. die
EP 1 152 151 A1 - Durch die stark verbesserte Trockenlaufeignung lassen sich im Pumpenraum Kunststoffe einsetzen, die eine geringere Temperaturbeständigkeit haben, als das bisher möglich war. Die Temperaturbeständigkeit der Kunststoffe ist für eine erfindungsgemäße magnetgekuppelte Kreiselpumpe kein einschränkendes Auswahlkriterium mehr, vielmehr können die Kunststoffe ohne Rücksicht auf ihre Temperaturbeständigkeit allein unter den Gesichtspunkten der chemischen Beständigkeit, der mechanischen Eigenschaften und des Preises ausgewählt werden.
- Die Anordnung der Magnete im Bereich der Nabe, dicht an der Achse des Laufrades, erleichtert einen stabilen Aufbau und einen ruhigen Lauf des Laufrades und erhöht die Lebensdauer der Pumpe.
- The leaky progress in operational safety achieved with the pump according to the invention, in particular in the extent of dry running suitability, justifies it for the first time to speak of pumps of the genus according to the invention of a true dry running safety.
- When designing the magnetically coupled centrifugal pump, it no longer needs to be taken into account that lubrication of the bearings by the medium to be pumped is guaranteed in any case.
- The hub of the impeller of the pump can be extended practically arbitrarily, without having to fear a failure of the pump by dry running.
- For the number of magnets that transmit the torque, there are virtually no restrictions, so that even very powerful pumps can be built.
- Magnetically coupled centrifugal pumps suffer during the transmission of torque from the driving rotor to the impeller of the pump induction losses, which increase with the relative speed between the rotating permanent magnet and the stationary shell of the can, provided the containment shell electrically conductive material. The induction losses can be reduced in a pump according to the invention by reducing the diameter of the hub and correspondingly the diameter of the ring of the permanent magnets of the driving rotor. Although only a small number of permanent magnets can be arranged on a reduced circumference, this can be compensated for by lengthening the hub and the driving rotor, without having to fear damage to the pump due to dry running.
- Conventional magnetically coupled centrifugal pumps with plain bearings have an axial clearance, which must be limited by additional, axially effective magnets, such as the
EP 1 152 151 A1 - Due to the greatly improved dry-running suitability, plastics can be used in the pump room that have a lower temperature resistance than was previously possible. The temperature resistance of the plastics is no longer a limiting selection criterion for a magnetically coupled centrifugal pump according to the invention, but rather the plastics can be selected solely from the standpoints of chemical resistance, mechanical properties and price, regardless of their temperature resistance.
- The arrangement of the magnets in the region of the hub, close to the axis of the impeller, facilitates a stable construction and a smooth running of the impeller and increases the life of the pump.
Der Mantel des Spalttopfes ist, wie an sich bekannt, zylindrisch oder nahezu zylindrisch. Nahezu zylindrisch bedeutet eine geringfügige, das Entformen des Spalttopfes erleichternde Konizität.The jacket of the split pot is, as is known, cylindrical or almost cylindrical. Almost cylindrical means a slight, the demolding of the split pot facilitating conicity.
Die Länge des Spalttopfes ist zur Erzielung eines ruhigen Laufes und einer exakten Ausrichtung des Laufrades der Pumpe und zur Übertragung hoher Drehmomente größer als der Außendurchmesser des Mantels des Spalttopfes. Die Länge des Spalttopfes stimmt dabei ungefähr mit der Länge der Nabe überein, die im Spalttopf steckt. Sie kann ohne weiteres bis zu einem Mehrfachen des Außendurchmessers des Mantels des Spalttopfes betragen.The length of the split pot is to achieve a smooth running and precise alignment of the impeller of the pump and for transmitting high torques greater than the outer diameter of the shell of the split pot. The length of the split pot is approximately equal to the length of the hub, which is in the containment shell. It can easily be up to a multiple of the outer diameter of the shell of the split pot.
Als Material für die Wälzkörper und die Laufringe der keramischen Wälzlager eignen sich besonders Zirkonoxid, Silizumkarbid und Siliziumnitrid. Sie zeichnen sich durch eine hohe Härte, Festigkeit und chemische Beständigkeit aus und lassen sich mit hoher Maßhaltigkeit und Oberflächengüte herstellen.Zirconium oxide, silicon carbide and silicon nitride are particularly suitable as material for the rolling elements and the races of the ceramic rolling bearings. They are characterized by high hardness, strength and chemical resistance and can be produced with high dimensional stability and surface quality.
Vorzugsweise haben die Wälzkörper eine mittlere Rauhigkeit von weniger als 0,1 µm, noch besser von weniger als 0,05 µm, und die Laufflächen der Wälzlagerringe haben vorzugsweise eine mittlere Rauhigkeit von nicht mehr als 0,35 µm, insbesondere eine mittlere Rauhigkeit von nicht mehr als 0,32 µm. Untersuchungen an einer erfindungsgemäßen Kreiselpumpe mit solchen Wälzlagern haben gezeigt, dass selbst im Trockenlauf über Stunden und Tage die Temperatur der Wälzlager nur um wenige Grad Celsius ansteigt, so dass bei einer erfindungsgemäßen Pumpe mit solchen keramischen Wälzlagern erstmals eine absolute Trockenlaufsicherheit vorliegt. Dabei ist der dafür erforderliche zusätzliche Aufwand gemessen an dem damit erzielbaren technischen Fortschritt und der erzielbaren hohen Betriebssicherheit unbedeutend.Preferably, the rolling elements have an average roughness of less than 0.1 microns, more preferably less than 0.05 microns, and the running surfaces of the rolling bearing rings preferably have an average roughness of not more than 0.35 microns, in particular an average roughness of not more than 0.32 μm. Investigations on a centrifugal pump according to the invention with such rolling bearings have shown that even in dry running for hours and days, the temperature of the bearings only by a few degrees Celsius, so that in a pump according to the invention with such ceramic bearings is for the first time an absolute dry running safety. In this case, the additional effort required for this is insignificant in terms of the technical progress achievable thereby and the achievable high operational reliability.
Die Wälzlager können als Kugellager oder als Rollenlager ausgebildet sein. Besonders bevorzugt ist die Verwendung von radialen Rillenkugellagern. Vorzugsweise wird die Nabe auf zwei Radiallagern gelagert. Falls die Fähigkeit der Radiallager, axiale Kräfte aufzunehmen, in Einzelfall unzureichend sein sollte, können zusätzlich ein oder zwei keramische Axiallager vorgesehen werden oder ein radiales Kugellager durch zwei als radiale Schulterlager ausgebildete Kugellager ersetzt werden kann.The rolling bearings can be designed as ball bearings or roller bearings. Particularly preferred is the use of radial deep groove ball bearings. Preferably the hub is stored on two radial bearings. If the ability of the radial bearing to absorb axial forces, should be insufficient in individual cases, one or two ceramic thrust bearings can be additionally provided or a radial ball bearing can be replaced by two designed as a radial shoulder bearing ball bearings.
Bei Verwendung einer keramischen Achse können unmittelbar auf dieser die Laufflächen für die Wälzkörper der Wälzlager ausgebildet werden, wodurch sich gesonderte innere Laufringe der Wälzlager einsparen lassen.When using a ceramic axis can be formed directly on this, the running surfaces for the rolling elements of the bearings, which can save separate inner races of rolling bearings.
Zwar wird eine erfindungsgemäße Pumpe durch Trockenlaufen nicht mehr gefährdet, doch kann das Trockenlaufen eine Ursache haben, die eine Gefährdung der Anlage, in welcher die Pumpe betrieben wird, oder des darin gepumpten Medium bedeuten. Um dieses zu erkennen, ist im Zusammenhang mit der Pumpe vorzugsweise ein Sensor vorgesehen, welcher eine beim Trockenlaufen der Pumpe auftretende oder sich verändernde Messgröße erfasst. Das Auftreten einer solchen Messgröße oder die Veränderung einer solchen Messgröße kann als ein Hinweis auf ein Trockenlaufen an eine Bedienungsperson oder an eine Schaltwarte übermittelt werden und veranlassen, dass die Ursache überprüft wird. Vorzugsweise ist ein akustischer Sensor vorgesehen. Es hat sich nämlich gezeigt, dass keramische Wälzlager im Trockenlauf charakteristische Geräusche aussenden, welche nicht vorhanden sind, wenn die keramischen Wälzlager von dem zu pumpenden Medium umgeben und durchdrungen sind. Diese charakteristischen Geräusche lassen sich durch einen akustischen Sensor leicht entdecken und von anderen Geräuschen unterscheiden, wobei die Unterscheidung dadurch verbessert werden kann, dass das typische Frequenzspektrum der Geräusche ermittelt und die Empfindlichkeit des akustischen Sensors auf einen Frequenzbereich eingeengt wird, in welchem die charakteristischen Trockenlaufgeräusche besonders stark auftreten.Although a pump according to the invention is no longer endangered by dry running, dry running can have a cause which represents a risk to the system in which the pump is operated or to the medium pumped therein. To recognize this, a sensor is preferably provided in connection with the pump, which detects a occurring during dry running of the pump or changing the measured variable. The occurrence of such a measurand or the change of such a measurand may be communicated as an indication of dry running to an operator or to a control room and cause the cause to be checked. Preferably, an acoustic sensor is provided. It has been shown that ceramic bearings emit characteristic noise in dry running, which are not present when the ceramic bearings are surrounded by the medium to be pumped and penetrated. These characteristic noises can be easily detected by an acoustic sensor and distinguished from other noises, the distinction being able to be improved by determining the typical frequency spectrum of the noises and narrowing the sensitivity of the acoustic sensor to a frequency range in which the characteristic dry running noise is particularly pronounced strongly occur.
Bei herkömmlichen magnetgekuppelten Kreiselpumpen, deren Laufrad auf keramischen Gleitlagern gelagert ist, wäre eine solche Überwachung schon deshalb sinnlos, weil die Pumpe bereits nach wenigen Sekunden eines Trockenlaufens ausgefallen sein würde.In conventional magnetically coupled centrifugal pumps, the impeller is mounted on ceramic plain bearings, such monitoring would be pointless because the pump would have failed after a few seconds of dry running.
Ausführungsbeispiele der Erfindung sind in den beigefügten Zeichnungen dargestellt.
Figur 1- zeigt eine magnetgekuppelte Kreiselpumpe in einer als Zentrifugal-pumpe ausgebildeten Bauform in einer teilweise längs geschnittenen Seitenansicht,
Figur 2- zeigt als Detail das Laufrad der Kreiselpumpe im Längsschnitt,
Figur 3- zeigt als Detail die Nabe für das Laufrad der Pumpe in einem Längsschnitt,
Figur 4- zeigt die Achse, welche das Laufrad und die Nabe aufnimmt, in einer Seitenansicht,
Figur 5- zeigt die Achse in einer Ansicht auf das in
rechte Ende der Achse, dieFigur 4 - Figuren 6 bis 8
- zeigen im Längsschnitt abgewandelte Naben für eine Pumpe der in
dargestellten Bauart, undFigur 1 Figur 9- zeigt im Längsschnitt eine Nabe mit herkömmlichen Gleitlagern.
- FIG. 1
- shows a magnetically coupled centrifugal pump in a designed as a centrifugal pump design in a partially longitudinal sectional side view,
- FIG. 2
- shows as a detail the impeller of the centrifugal pump in longitudinal section,
- FIG. 3
- shows as a detail the hub for the impeller of the pump in a longitudinal section,
- FIG. 4
- shows the axis, which receives the impeller and the hub, in a side view,
- FIG. 5
- shows the axis in a view on the in
FIG. 4 right end of the axis, the - FIGS. 6 to 8
- show in longitudinal section modified hubs for a pump of in
FIG. 1 shown type, and - FIG. 9
- shows in longitudinal section a hub with conventional plain bearings.
Die in den
Der Läufer 10 ist topfförmig ausgebildet und umgibt den Spalttopf 3. Am inneren Umfang des Läufers 10 sind Permanentmagnete 11 angebracht. Ihnen liegen Permanentmagnete 12 gegenüber, welche in eine Hülse 29 eingebettet sind, welche auf einer Nabe 13 angebracht ist, die in dem Spalttopf 3 angeordnet und drehbar auf einer Achse 14 gelagert ist. Die Hülse 29 mit den Permanentmagneten 12 ist mit der Nabe 13 drehfest verbunden.The
Zwischen der Achse 14 und der Nabe 13 sind zwei keramische radiale Rillenkugellager 15 und 16 angeordnet. Der innere Laufring 15a des hinteren Kugellagers 15 liegt an einer hinteren Bundfläche 17 der Achse 14 an. Der innere Laufring 16a des vorderen Kugellagers 16 liegt an einer vorderen Bundfläche 18 der Achse 14 an. Der äußere Laufring 15b des hinteren Kugellagers 15 ist durch einen in die Nabe 13 eingreifenden Sicherungsring 19 gesichert. Der äußere Laufring 16a des vorderen Kugellagers 16 ist zwischen einer Bundfläche 20 an der Nabe 13 und einem zylindrischen Fortsatz 21 eines Laufrades 22 eingespannt, welches außerhalb des Spalttopfes 3 am vorderen Ende der Nabe 13 angebracht ist.Between the
Die Achse 14 steckt mit ihrem hinteren Ende in einer am Boden 4 des Spalttopfes 3 vorgesehenen Ausnehmung 23 und mit ihrem vorderen Ende in einer im vorderen Gehäuseteil 7 ausgebildeten Halterung 24. Das hintere Ende der Achse 14 ist, wie in
Die Laufringe 15a, 15b, 16,a und 16b der Kugellager sowie die Kugeln 15c und 16c bestehen aus einem keramischen Werkstoff, insbesondere aus Siliziumnitrid oder Zirkonoxyd. Ein nicht dargestellter Kugelkäfig besteht vorzugsweise aus Kunststoff. Aus Kunststoff bestehen auch das vordere Gehäuseteil 7, die Nabe 13 und das Laufrad 22, welches durch seine Drehung die Pumpwirkung erzeugt. Der Motor 27 treibt den Läufer 10. Dieser wiederum treibt durch die magnetische Kopplung zwischen den Permanentmagneten 11 und 12 die Nabe 13 und wird deshalb als treibender Läufer 10 bezeichnet. Das Laufrad 22 dreht sich zusammen mit der Nabe 13, an welcher es befestigt ist, saugt das zu pumpende Medium durch eine axial angeordnete Ansaugöffnung 25 an und fördert es durch eine radial angeordnete Auslassöffnung 26 aus dem Pumpenraum 8 heraus.The
Der Spalttopf 3 besteht vorzugsweise aus Kunststoff, kann aber auch aus einer Keramik bestehen, z.B. aus Aluminiumoxid. Die Achse 14 besteht vorzugsweise aus Aluminiumoxid, kann aber auch aus einem Kunststoff bestehen.The
Ein von der Pumpe angesaugtes flüssiges Medium kann durch einen zwischen der Nabe 13 beziehungsweise deren Hülse 29 und dem Spalttopf 3 bestehenden Ringspalt zum Boden 4 des Spalttopfs 3 strömen. Dort wird das Medium umgelenkt und strömt durch einen zwischen der Achse 14 und dem Laufrad 22 bestehenden Ringspalt zurück, wobei es die beiden keramischen Kugellager 15 und 16 durchdringt und schmiert. Bei einer Unterbrechung der Schmierung der keramischen Kugellager 15 und 16 können diese ohne Schaden trockenlaufen, was durch einen z.B. an der Außenseite des Gehäuses 1 angebrachten akustischen Sensor aufgrund einer für den Trockenlauf charakteristischen, von den keramischen Kugellagern 15 und 16 ausgehenden Geräuschentwicklung erkannt und gemeldet werden kann.A sucked by the pump liquid medium can flow through an existing between the
Das in
Die beiden radialen Schulterlager 31 und 32 sind so angeordnet, dass ihre einseitigen Schultern 31 d und 32d aneinander liegen. Das erlaubt es, zwischen der Achse 14 und der Nabe 13 höhere Axialschübe zu übertragen beziehungsweise aufzufangen.The two
Alle vorstehend beschriebenen Arten der Lagerung der Nabe 13 auf einer Achse 14 können auch bei einer als Peripheralpumpe oder Seitenkanalpumpe ausgebildeten magnetgekuppelten Kreiselpumpe verwirklicht werden.All of the above-described ways of mounting the
Es ist ein Vorteil der Erfindung, dass eine Pumpe gemäß dem Stand der Technik, welche eine mittels Gleitlagern gemäß
In allen Ausführungsbeispielen ist beziehungsweise sind zwischen der Nabe 13 und den Lagern, insbesondere in einer oder mehrere Ringnuten der Nabe 13, eine oder mehrere elastomere Ringe 39 vorgesehen, welche einen Ausgleich für die gegenüber metallischen Werkstoffen geringere Druckfestigkeit der keramischen Werkstoffe schaffen.In all embodiments, or between the
- 11
- Gehäusecasing
- 22
- hinteres Teil des Gehäusesrear part of the housing
- 33
- Spalttopfcontainment shell
- 44
- Bodenground
- 55
- Mantelcoat
- 66
- Flanschflange
- 77
- vorderes Gehäuseteilfront housing part
- 88th
- Pumpenraumpump room
- 99
- hinterer Raumback room
- 1010
- treibender Läuferdriving runner
- 1111
- Permanentmagnetepermanent magnets
- 1212
- Permanentmagnetepermanent magnets
- 1313
- Nabehub
- 1414
- Achseaxis
- 1515
- RillenkugellagerDeep groove ball bearings
- 15a15a
- innerer Laufringinner race
- 15b15b
- äußerer Laufringouter race
- 15c15c
- Kugelnroll
- 15d15d
- Rillegroove
- 1616
- RillenkugellagerDeep groove ball bearings
- 16a16a
- innerer Laufringinner race
- 16b16b
- äußerer Laufringouter race
- 16c16c
- Kugelnroll
- 16d16d
- Rillegroove
- 1717
- hintere Bundflächerear waistband
- 1818
- vordere Bundflächefront waistband
- 1919
- Sicherungsringcirclip
- 2020
- BundflächeBund area
- 2121
- Fortsatz von 22Extension of 22
- 2222
- LaufradWheel
- 2323
- Ausnehmungrecess
- 2424
- Halterungbracket
- 2525
- Ansaugöffnungsuction
- 2626
- Auslassöffnungoutlet
- 2727
- Elektromotorelectric motor
- 2828
- Abflachungflattening
- 2929
- Hülseshell
- 3030
- Rollenlagerroller bearing
- 30a30a
- innerer Laufringinner race
- 30b30b
- äußerer Laufringouter race
- 30c30c
- Rollenroll
- 3131
- Schulterlagershoulder bearing
- 31a31a
- innerer Laufringinner race
- 31b31b
- äußerer Laufringouter race
- 31c31c
- Kugelnroll
- 31d31d
- Schultershoulder
- 3232
- Schulterlagershoulder bearing
- 32a32a
- innerer Laufringinner race
- 32b32b
- äußerer Laufringouter race
- 32c32c
- Kugelnroll
- 32d32d
- Schultershoulder
- 3333
- Schultershoulder
- 3434
- Lauffläche, Abschnitt von 14Tread, section of 14
- 3535
- Gleitlagerbearings
- 3636
- Gleitlagerbearings
- 3737
- DistanzhülseStand Off
- 3838
- wendelförmige Rillehelical groove
- 3939
- elastomere Ringeelastomeric rings
Claims (11)
- A magnetically coupled centrifugal pump for pumping a fluid medium,
comprising a housing (1), in which a separating can (3), which has a bottom (4), a shell (5) and a flange (6) that is clamped between two parts (2, 7) of the housing (1), separates a pump chamber (8), through which the medium flows, from a driving rotor (10) supporting permanent magnets (11) on the circumference thereof, the rotor being driven by a motor (27),
comprising an intake opening (25) leading to the pump chamber (8) and comprising an outlet opening (26) leading out of the pump chamber (8),
comprising an impeller (22), which is arranged in the pump chamber (8) and can be rotated about an axis (14) and is rotationally fixed to a hub (13) and is supported so as to be capable of being rotated by means of a plurality of ceramic bearings (15, 16) and supports permanent magnets (12), to which it is connected in a rotationally fixed manner and which the permanent magnets (11) of the driving rotor (10) face,
wherein
the ceramic bearings (15, 16) and the permanent magnets (12) facing the permanent magnets (11) of the driving rotor (10) are arranged in the separating can (3), whereas the impeller (22) is arranged outside of the separating can (3) in the pump chamber (8) and the permanent magnets (11) of the driving rotor (10) are arranged in a section of the driving rotor (10), which at least partially surrounds the shell (5) of the separating can (3),
the back end of the axis (14) is inserted in a recess (23), which is provided on the bottom (4) of the separating can (3), and the front end of the axis (14) is inserted in a holder (24), which is embodied in the front housing part (7),
and at least the surfaces, which come in contact with the medium in the pump chamber (8), are non-metallic, characterized in that the ceramic bearings are rolling bearings (15, 16), by means of which the hub (13) is supported on the axis (14), and
that the length of the separating can (3) is greater than the outer diameter of its shell (5). - The centrifugal pump according to claim 1, characterized in that the shell (5) of the separating can (3) is cylindrical or almost cylindrical.
- The centrifugal pump according to any one of the preceding claims, characterized in that the rolling bodies (15c, 16c) and the ball races (15a, 15b, 16a, 16b) of the rolling bearings (15, 16) consist of zirconium oxide or silicon nitride.
- The centrifugal pump according to any one of the preceding claims, characterized in that the rolling bodies (15c, 16c) have an average roughness Ra ≤ 0.05 µm.
- The centrifugal pump according to any one of the preceding claims, characterized in that the bearing surfaces of the rolling bearing rings (15a, 15b, 16a, 16b) have an average roughness of ≤ 0.32 µm.
- The centrifugal pump according to any one of the preceding claims, characterized in that the rolling bearings (15, 16) are embodied as radial bearings.
- The centrifugal pump according to any one of the preceding claims, characterized in that at least one ceramic rolling bearing in axial design is provided between the hub (13) and its axis (14).
- The centrifugal pump according to any one of the preceding claims, characterized in that a bearing surface (15d, 16d, 34) for the rolling bodies (15c, 16c, 30c) of a ceramic rolling bearing (15, 16, 30) is embodied on the axis (14).
- The centrifugal pump according to any one of the preceding claims, characterized in that a sensor is provided, which detects a measurand, which occurs or which changes in response to the dry running of the pump.
- The centrifugal pump according to claim 8, characterized in that the sensor is sensitive to acoustic signals.
- A use of a centrifugal pump according to any one of the preceding claims for the pumping of corrosive media, in particular in chemical engineering.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE202007003214U DE202007003214U1 (en) | 2007-02-22 | 2007-02-22 | Magnetically coupled centrifugal pump for pumping e.g. corrosive media, has permanent magnets in hub arranged in section of rotor surrounded by mantle of can, where surfaces encountering in pump space with medium are non-metallic |
PCT/EP2008/001361 WO2008101698A1 (en) | 2007-02-22 | 2008-02-21 | Magnetically coupled centrifugal pump for corrosive media |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1979621A1 EP1979621A1 (en) | 2008-10-15 |
EP1979621B1 true EP1979621B1 (en) | 2012-03-07 |
Family
ID=38056558
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08715923A Revoked EP1979621B1 (en) | 2007-02-22 | 2008-02-21 | Magnetically coupled centrifugal pump for corrosive media |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP1979621B1 (en) |
AT (1) | ATE548567T1 (en) |
DE (1) | DE202007003214U1 (en) |
WO (1) | WO2008101698A1 (en) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102008064099B4 (en) * | 2008-12-19 | 2016-05-04 | Bühler Motor GmbH | Centrifugal pump with a fixed axis |
CN105020147A (en) * | 2014-04-15 | 2015-11-04 | 高涵文 | Nearly-zero inner leakage stainless steel magnetic drive pump |
CN105020166A (en) * | 2014-04-15 | 2015-11-04 | 高涵文 | Nearly-zero inner leakage fluoroplastic magnetic drive pump |
CN105020145A (en) * | 2014-04-15 | 2015-11-04 | 高涵文 | Anti-dry grinding fluoroplastic magnetic drive pump |
DE102015118022B4 (en) | 2015-10-22 | 2024-05-29 | Pfeiffer Vacuum Gmbh | Rotary displacement vacuum pump |
DE102016204301A1 (en) * | 2016-03-16 | 2017-09-21 | Schaeffler Technologies AG & Co. KG | Pump device, in particular for a coolant pump and vehicle with the pump device |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1496035A (en) * | 1974-07-18 | 1977-12-21 | Iwaki Co Ltd | Magnetically driven centrifugal pump |
DE3207166A1 (en) * | 1981-05-22 | 1982-12-09 | Hermetic Pumpen Gmbh | Centrifugal pump with canned magnetic coupling drive |
EP1329638A1 (en) * | 2002-01-18 | 2003-07-23 | CP Pumpen AG | Magnetically coupled centrifugal pump |
US20060245955A1 (en) * | 2005-04-18 | 2006-11-02 | Kiyotaka Horiuchi | Canned pump |
-
2007
- 2007-02-22 DE DE202007003214U patent/DE202007003214U1/en not_active Expired - Lifetime
-
2008
- 2008-02-21 WO PCT/EP2008/001361 patent/WO2008101698A1/en active Application Filing
- 2008-02-21 EP EP08715923A patent/EP1979621B1/en not_active Revoked
- 2008-02-21 AT AT08715923T patent/ATE548567T1/en active
Also Published As
Publication number | Publication date |
---|---|
ATE548567T1 (en) | 2012-03-15 |
EP1979621A1 (en) | 2008-10-15 |
DE202007003214U1 (en) | 2007-05-10 |
WO2008101698A1 (en) | 2008-08-28 |
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