EP2273124B1 - Centrifugal pump and method for compensating for the axial impulse in a centrifugal pump - Google Patents
Centrifugal pump and method for compensating for the axial impulse in a centrifugal pump Download PDFInfo
- Publication number
- EP2273124B1 EP2273124B1 EP10164973.9A EP10164973A EP2273124B1 EP 2273124 B1 EP2273124 B1 EP 2273124B1 EP 10164973 A EP10164973 A EP 10164973A EP 2273124 B1 EP2273124 B1 EP 2273124B1
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- EP
- European Patent Office
- Prior art keywords
- rotor
- vanes
- pump
- centrifugal pump
- rotary drive
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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
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2261—Rotors specially for centrifugal pumps with special measures
- F04D29/2266—Rotors specially for centrifugal pumps with special measures for sealing or thrust balance
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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
- F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
- F04D13/0606—Canned motor pumps
- F04D13/0633—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
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
- F04D13/0606—Canned motor pumps
- F04D13/064—Details of the magnetic circuit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/041—Axial thrust balancing
- F04D29/0413—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
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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
- F04D29/048—Bearings magnetic; electromagnetic
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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
- F04D29/18—Rotors
- F04D29/186—Shaftless rotors
Definitions
- the invention relates to a centrifugal pump and a method for compensating the axial thrust in a centrifugal pump according to the preamble of the independent claim of the respective category.
- centrifugal pumps in which the fluid to be delivered is deflected from an axial direction out in a radial direction, the impeller or the rotor undergoes strong loads in the axial direction, which means the direction of the desired rotational axis of the impeller.
- This axial thrust is mainly caused by the pressure difference on the rotor. While there is essentially the suction pressure on the side of the rotor facing the inlet, a higher pressure is applied to the rear side of the rotor because the rotor rear side communicates with the outlet, where essentially the delivery pressure prevails. So that this axial thrust does not have to be completely absorbed by the thrust bearings, measures are known in centrifugal pumps for balancing the rotor with respect to the axial direction.
- a well-known measure are relief bores, which extend in the axial direction through the entire impeller or through the entire rotor and thus form a flow connection between the front and the back of the rotor, resulting in a pressure relief of the rotor. It is also known to combine such relief bores with rudimentary blades provided at the rear of the rotor.
- An integral rotor of the type is eg from the DE 18 11 430 A1 known, which discloses the basic structure of a so-called "Intergralrotors" with a recirculation through the electrical part of the rotor for the purpose of Axialschubaus protests.
- centrifugal pump which is designed as a bearingless motor, wherein the rotor is passive magnetically stabilized with respect to the axial direction against displacement and tilting.
- the rotor In order to balance the rotor of such a bearingless motor, apart from the magnetic reluctance force, only constructional measures are available which influence the axial position via fluid-dynamic compensation forces.
- a magnetically mounted centrifugal pump is proposed with a canned motor, with a pump housing having an inlet and an outlet, a rotor with a front side facing the inlet and a rear side facing away from the inlet, the rotor having a first impeller with first vanes Generating a main flow from the inlet to the outlet, and wherein on the rotor, a second impeller with second vanes and at least one relief bore is provided for generating a Rezirkulations kges, which is directed from the back of the rotor through the at least one relief bore, wherein the relief bore axially from the rear side of the rotor extends through the rotor part of the electric rotary drive to the second impeller, and wherein between the two pump wheels, a separating element is provided, which at least partially the Rezirkulationshim in the region of the second impeller from Hauptfl uss separates.
- a recirculation flow can be generated for axially balancing or for compensating the axial thrust, which flow can be largely separated from the main flow.
- the at least one relief bore it is possible using the at least one relief bore to balance the rotor largely independent of the main flow with respect to the axial direction.
- the separating element is preferably disc-shaped, wherein the first vanes of the first impeller are provided on the side facing the inlet, and the second vanes of the second impeller are provided on the side facing away from the inlet.
- first vanes are arranged so that a central region of the first impeller is free of vanes and wherein the separating element is designed such that it extends over the entire central region of the first impeller.
- the separating element can advantageously contribute to the axial pressure relief as a dynamic pressure plate similar to the one already cited EP-A-0 860 046 in connection with Fig. 8c for which there is designated 1 k baffle plate is disclosed.
- first and the second vanes extend beyond the separating element with respect to the radial direction.
- each overall wing is divided into two parts at least in a radially inward section through the separating element with respect to the axial direction.
- an additional axial stabilization can be effected if rudimentary blades are provided on the back of the rotor.
- a plurality of relief bores are provided, which are arranged symmetrically with respect to the axis of the rotor.
- the rotor is magnetically supported.
- the pump is driven by an electric rotary drive for the rotor, wherein the rotary drive is designed as a canned motor.
- an electric rotary drive for the rotor wherein the rotary drive comprises a stator, wherein the rotor forms the rotor of the electric rotary drive, and forms a bearingless motor together with the stator, wherein the stator as a storage and drive stator for the rotor is designed.
- the rotor of the bearingless motor is permanently magnetic and is passive magnetically stabilized with respect to the axial direction against displacement and tilting.
- the invention further provides a method for compensating axial thrust in a magnetically-mounted centrifugal pump having a canned motor and a pump housing having an inlet and an outlet, a rotor having an inlet facing front side and a rear side facing away from the inlet which method is used to generate a main flow from inlet to outlet with first vanes of a first impeller of the rotor, with second vanes of a second impeller of the rotor producing a recirculation flow which is from the rear side of the rotor through at least one relief well provided in the second impeller is directed, wherein the recirculation flow in the region of the second impeller is at least partially separated from the main flow out, wherein the relief bore extends axially from the back of the rotor through the rotor part of the electric rotary drive to the second impeller.
- a recirculation flow for axial balancing or for compensating the axial thrust can be generated, which can be largely separated from the main flow.
- a compensation of the axial thrust in a very large work area is also possible for different viscosities and densities with only one configuration of the rotor.
- the method according to the invention is particularly suitable when the rotor is mounted magnetically, preferably completely magnetically.
- the inventive method is particularly suitable for centrifugal pumps, which operate on the principle of the bearingless motor, in which the centrifugal pump has an electric rotary drive with a stator, the rotor is permanently magnetic and the rotor of the electric Rotary drive forms, which forms a bearingless motor together with the stator, in which the stator is designed as a bearing and drive stator for the permanent magnet rotor, wherein the rotor is passive magnetically stabilized with respect to the axial direction against displacement and tilting.
- Fig. 1 shows a highly schematic representation of an embodiment of an inventive centrifugal pump, which is generally designated by the reference numeral 1.
- centrifugal pump according to the invention is designed with an electric rotary drive on the principle of a bearingless motor.
- FIG. 1 illustrated embodiment of the inventive centrifugal pump 1 comprises a pump housing 2 with an inlet 21 and an outlet 22 for the fluid to be delivered.
- a rotor 3 is provided in the pump housing, with a front side 31 facing the inlet 21 and a rear side 32 facing away from the inlet.
- the rotor 3 is provided with the vanes provided for pumping the fluid.
- the rotor axis which means the axis of rotation A, by which the rotor 3 is intended to rotate in the operating state, determines the axial direction.
- the rotational axis A refers to the nominal rotational axis about which the rotor 3 rotates when it is centered and not tilted.
- an electric rotary drive 8 For driving the rotor 3, an electric rotary drive 8 is provided which comprises a stator 81 with windings 82.
- the rotor 3 in the pump housing 2 is at the same time the rotor 3 of the electric rotary drive 8.
- This embodiment is also used as an integral rotor referred to, because the rotor of the electric rotary drive is identical to the pump rotor, which promotes the fluid.
- the rotary drive 8 is formed in this preferred embodiment as a bearingless motor in which the stator 81 is configured as a bearing and drive stator for the magnetic bearing of the rotor 3 and the drive of the rotation of the rotor 3 about the axis of rotation A.
- the rotor 3 is designed as a permanent magnetic rotor 3, which forms a bearingless motor together with the stator 81, in which the stator is configured as a bearing and drive stator for the permanent magnet rotor 3.
- the magnetic bearing of the rotor 3 is in Fig. 1 indicated by the field lines M.
- Such a bearingless engine for example, in the already cited EP-A-0 860 046 and also in the EP-A-0 819 330 disclosed.
- bearingless motor is meant that the rotor 3 is mounted completely magnetic, with no separate magnetic bearings are provided.
- the stator 81 is designed for this purpose as a bearing and drive stator, so it is both stator of the electric drive and stator of the magnetic bearing.
- the winding 82 of the stator 81 comprises a drive winding of the pole pair number p and a control winding of the pole pair number p ⁇ 1.
- a magnetic rotating field can be generated, which on the one hand exerts a torque on the rotor 3, which causes its rotation, and which on the other exerts an arbitrarily adjustable transverse force on the rotor 3, so that its radial position can be actively controlled or regulated is.
- three degrees of freedom of the rotor 3 are actively controlled.
- the rotor is passively magnetic, that is not controllable, stabilized by reluctance forces.
- Fig. 1 illustrated rotary drive 8 designed as a canned motor, wherein the pump housing 2 forms the gap between the stator 81 and the rotor 3.
- Fig. 2 and 3 show in a schematic sectional view of the pump housing 2 and the rotor 3 of the embodiment Fig. 1 , in which Fig. 2 the illustration of the basic operation and the flow paths in the pump housing 2 is used during Fig. 3 illustrating the definition of some geometric quantities.
- FIG. 4-7 a more detailed representation of the rotor 3 is shown, wherein Fig. 4 a section through the rotor 3 along the section line IV-IV in Fig. 6 shows, Fig. 5 a perspective view of the rotor 3, Fig. 6 a plan view of the front side 31 of the rotor 3 (without cover plate) and Fig. 7 a plan view of the back 32 of the rotor. 3
- Fig. 8 shows another perspective view similar to Fig. 5 (But without cover plate) for a variant of the rotor 3.
- no cover plate is provided on the front side of the rotor 3.
- the differences refer to the back 32 of the rotor 3, that is, the rest of the rotor 3 and in particular the impellers are identical to that in the Fig. 4-7 shown rotor.
- FIG. 2 shows, the rotor 3 on its side facing the inlet 21 on a first impeller 4 with first blades 41.
- the first impeller 41 generates, in a manner known per se, a main flow with which the fluid to be delivered, which is conveyed from the axial direction through the inlet 21 to the outlet 22, is conveyed.
- This main river is in Fig. 2 illustrated by the solid arrows.
- a second impeller 5 with second vanes 51, which has at least one relief bore 6, is provided on the rotor 3.
- This second impeller 5 generates a recirculation flow which is directed from the rear side 32 of the rotor 3 through the relief bore 6.
- the recirculation flow is in Fig. 2 illustrated by the dashed arrows.
- Essential for the invention is that between the first impeller 4 and the second impeller 5, a separating element 7 is provided which at least partially separates the recirculation flow in the region of the second impeller 5 from the main flow.
- the relief holes 6 extend from the back 32 of the rotor 3 to and through the second impeller 5, but not by the first impeller 4, so that a direct contact of the recirculation flow with the main flow in the region of the output of the relief holes 6 at the second Impeller 5 is avoided.
- the separating element 7 By means of the separating element 7, the recirculation flow required for axial balancing or for compensating the axial thrust can largely be separated from the main flow. As a result, the rotor can be balanced with respect to the axial thrust largely independently of the main flow. Thus, a very large working range, that is, a wide range of different flow rates and different delivery pressures for different viscosities and densities of the fluid to be delivered with only one configuration of the rotor 3 can be realized without the concessions to the quality of the axial balance are necessary. In particular, it is also avoided by the separating element 7 that the recirculation flow and the main flow collide frontally - that is to say as oppositely directed flows, which would lead to turbulences which are disadvantageous for the axial balancing.
- the separating element 7 is disc-shaped (see also Fig. 4 and Fig. 8 ), wherein on the inlet 21 facing side, the first wings 41 of the first impeller 4 are provided and on the side facing away from the inlet, the second Wings 51 of the second impeller 5.
- the first wings 41 are arranged so that a central portion 35 of the first pump impeller 4 is free of vanes 41.
- the disk-shaped separating element 7 extends with respect to the radial direction at least over the entire central region 35, so that there is no direct flow connection between the first impeller 4 and the second impeller 5 in this central region 35.
- the separating element 7 thus shields the second impeller 5 at least in the central region 35 with respect to the inlet 21.
- the separating element 7 In its central region, the separating element 7 has a round elevation 71, which serves to better deflect the fluid in the radial direction.
- Both the second vanes 51 of the second impeller 5 and the first vanes 41 of the first impeller 4 each extend curved in the radial direction.
- radial direction is meant a direction perpendicular to the axial direction.
- the wings 41 of the first impeller 4 are aligned with the wings 51 of the second impeller 5. This is advantageous, but not necessary.
- the first wings 41 and the second wings 51 may also be offset from each other with respect to the circumferential direction. Further, the number of the first wings 41 may be different from the number of the second wings 51. In the embodiment described here, the number of the first wings 41 is equal to the number of the second wings 51.
- a cover plate 34 is provided (see also Fig. 4 and Fig. 5 ), which is designed annular disk-shaped.
- the cover plate 34 extends in the radial direction to the radially outer end of the first wing 41. It has in the middle a central circular opening whose diameter is the same size as the diameter of the central region 35. The thickness of the cover plate 34 decreases outside from.
- the first wings 41 are completely covered by the cover plate 34, so that only the central region 35 of the first impeller 4 is in direct flow communication with the inlet 21 with respect to the axial direction.
- the cover plate 34 is used for flow guidance and ensures that the fluid flowing through the inlet 21 can only pass through the central region 35 to the first impeller 4.
- first wings 41 and the second wings 51 extend beyond the separating element 7 with respect to the axial direction.
- This measure is best used in the presentation of Fig. 2 , of the Fig. 4 , of the Fig. 6 and the Fig. 8 seen.
- the separating element 7 extends only over the radially inner region of the first wing 41 and the second wing 51. In the radially outer region of the first wing 41 and the second wing 51 no separating element between them is present.
- the separator 7 extends with respect to the radial direction between the first vanes 41 and the second vanes 51 depends on the application and is one of the parameters available for the optimization of the axial thrust balance.
- the separating element should extend at least so far with respect to the radial direction that it covers the entire central area 35.
- the separating element 7 can also extend over the entire radial extent of the wings 41 or 51, so that the separating element 7 terminates flush in the radial direction with the wings 41 or 51.
- a structurally particularly favorable measure is it (see Fig. 6 and Fig. 8 ) when the first wings 41 and the second wings 51 form overall wings. Or expressed in reverse, there are overall wings are provided which form both the first wing 41 and the second wing 51. In this case, each entire wing is separated in its radially inner portion by the separating element with respect to the axial direction in two parts, so that in Fig. 8 according to the representation upper part, which is above the partition member 7, the first wing 41 of the first impeller 4 forms, and the lower part of which is below the partition member 7, the second wing 51 of the second impeller. 5
- Fig. 7 shows a plan view of the inlet 21 remote from the rear side 32 of the rotor 3.
- the grooves 37 do not extend inwardly to the center of the back 32 of the rotor 3, but terminate in a central region as well as in FIG Fig. 2 is shown.
- the radially outer regions between each two adjacent grooves 37 then form the Rudimentäreriel 36. These can cause additional axial stabilization of the rotor 3.
- a plurality of relief bores 6, which are arranged symmetrically, in particular with respect to the axis of rotation of the rotor 3.
- Fig. 7 shows, in the embodiment described here, a central relief hole 6 in the center of the back 32 of the rotor 3 are provided, and eight other relief holes 6, which are arranged in a circle and equidistant around the central relief hole 6 around.
- Fig. 8 shows a view of a variant of the rotor Fig. 4 , wherein in this variant, no cover plate 34 is provided. Further, there is a difference from the embodiment in FIG Fig. 4 in that at the in Fig. 8 illustrated variant on the back 32 of the rotor 3 no grooves 37 and thus no Rudimentärschaufeln 36 are provided.
- the waiver of the cover plate and the Rudimentärschaufeln can be implemented as a single measure but also in combination with each other.
- the rotor 3 comprises an annular permanent magnet 33 which, according to the illustration in FIG Fig. 4 below the two pump wheels 4, 5 is arranged.
- the permanent magnet 33 is located in a sheath 38, which is preferably made of plastic, metal or ceramic. As this is the illustration in Fig. 1 indicates, the permanent magnet 33 acts with the stator 81 of the electric rotary drive eighth together and serves both the magnetic bearing and the drive of the rotor. 3
- the second wings 51 of the second impeller 5 are integral with the casing 38, as this Fig. 4 and Fig. 5 shows.
- the second wings 51 by a material-removing processing step, for. B. by milling, are machined out of the surface of the sheath 38.
- DR is the outer diameter of the rotor 3, which is usually identical to the outer diameter of the first and / or the second impeller 4 and 5
- DT is the outer diameter of the disc-shaped separating element 7
- H denotes the height of the overall wings
- HT the height of the separating element 7
- H1 and H2 the height of the first wings 41 and the second wings 51, respectively.
- the height means the extent in the axial direction.
- the ratio of DT and DR is greater than 0.5 and less than or equal to 1, in particular the range from 0.6 to 0.7 is preferred.
- the height H2 of the second wings 52 is smaller than the height HT of the partitioning member 7 and HT is smaller than the height H1 of the first wings
- the height H2 of the second wings 52 is preferably less than half of H, in particular at most 25% of H and especially between 15% and 20%. of H.
- the height H1 of the first wings 41 is preferably greater than half of H, in particular at most 75% of H and especially between 50% and 60% of H.
- the inventive centrifugal pump as a bearingless motor with permanent magnetic rotor 3
- the pump housing 2 has more than one outlet 22 and / or more than one inlet 21. If two or more inlets 21 are provided, they are to be arranged on the same side of the rotor 3 and the first impeller 4, that is, it is to avoid the fluid directly from one of the inlets from the axial direction to the second impeller can get.
Description
Die Erfindung betrifft eine Zentrifugalpumpe und ein Verfahren zum Ausgleichen des axialen Schubs in einer Zentrifugalpumpe gemäss dem Oberbegriff des unabhängigen Patentanspruchs der jeweiligen Kategorie.The invention relates to a centrifugal pump and a method for compensating the axial thrust in a centrifugal pump according to the preamble of the independent claim of the respective category.
In Zentrifugalpumpen, bei denen das zu fördernde Fluid aus einer axialen Richtung heraus in eine radiale Richtung umgelenkt wird, erfährt das Pumpenrad bzw. der Rotor starke Belastungen in der axialen Richtung, womit die Richtung der Solldrehachse des Pumpenrads gemeint ist. Dieser axiale Schub wird vor allem durch die Druckdifferenz am Rotor verursacht. Während auf der dem Einlass zugewandten Seite des Rotors im wesentlichen der Saugdruck herrscht, liegt auf der Rückseite des Rotors ein höherer Druck an, denn die Rotorrückseite steht mit dem Auslass in Verbindung, wo im wesentlichen der Förderdruck herrscht. Damit dieser Axialschub nicht vollständig von den Axiallagern aufgenommen werden muss, sind in Zentrifugalpumpen Massnahmen bekannt, um den Rotor bezüglich der axialen Richtung auszubalancieren.In centrifugal pumps, in which the fluid to be delivered is deflected from an axial direction out in a radial direction, the impeller or the rotor undergoes strong loads in the axial direction, which means the direction of the desired rotational axis of the impeller. This axial thrust is mainly caused by the pressure difference on the rotor. While there is essentially the suction pressure on the side of the rotor facing the inlet, a higher pressure is applied to the rear side of the rotor because the rotor rear side communicates with the outlet, where essentially the delivery pressure prevails. So that this axial thrust does not have to be completely absorbed by the thrust bearings, measures are known in centrifugal pumps for balancing the rotor with respect to the axial direction.
Eine bekannte Massnahme sind Entlastungsbohrungen, die sich in axialer Richtung durch das gesamte Pumpenrad bzw. durch den gesamten Rotor hindurch erstrecken und so eine Strömungsverbindung zwischen der Vorderseite und der Rückseite des Rotors bilden, was zu einer Druckentlastung des Rotors führt. Auch ist es bekannt, solche Entlastungsbohrungen mit an der Rückseite des Rotors vorgesehenen Rudimentärschaufeln zu kombinieren. Ein Integralrotor der Art ist z.B. aus der
Die axiale Ausbalancierung des Rotors mit solchen Massnahmen ist jedoch zumindest an einigen Arbeitspunkten schwierig, wenn nicht sogar unmöglich. Erschwerend kommt hinzu, dass die für die Ausbalancierung benötigten Kräfte vom Arbeitspunkt abhängig sind, also insbesondere vom Fluss und von der Druckdiffererenz, die mit der Pumpe generiert werden.However, axial balancing of the rotor with such measures is difficult, if not impossible, at least at some operating points. To make matters worse, that the forces required for balancing are dependent on the operating point, ie in particular on the flow and on the pressure differential generated by the pump.
Besonders gravierend ist das Problem des Axialschubausgleichs bei Pumpen mit magnetisch gelagertem Laufrad, insbesondere wenn die axiale Lagerung vollkommen ohne mechanische Lager magnetisch erfolgt. Aus der
Insbesondere auch bei solchen Zentrifugalpumpen, die nach dem Prinzip des lagerlosen Motors arbeiten, sind heute bekannte Massnahmen zum axialen Ausbalancieren des Rotors für hohe Pumpleistungen oder bei höher viskosen Fluiden, wie beispielsweise Photoresist oder Slurry, welche Viskositäten von bis zu über 100 Centipoise aufweisen können, oft nicht ausreichend.In particular, even in such centrifugal pumps, which operate on the principle of the bearingless motor, are now known measures for axial balancing of the rotor for high pump power or higher viscosity fluids, such as photoresist or slurry, which may have viscosities of up to 100 centipoise, often not enough.
Ausgehend von diesem Stand der Technik ist es daher eine Aufgabe der Erfindung, eine Zentrifugalpumpe vorzuschlagen, bei welcher ein Ausgleich des axialen Schubs über einen weiten Betriebsbereich zuverlässig möglich ist. Ferner ist es eine Aufgabe der Erfindung ein entsprechendes Verfahren zum Ausgleichen des axialen Schubs in einer Zentrifugalpumpe vorzuschlagen. Insbesondere soll dieses Verfahren auch für Zentrifugalpumpen mit magnetisch gelagertem Rotor einsetzbar sein.Based on this prior art, it is therefore an object of the invention to propose a centrifugal pump, in which a compensation of the axial thrust over a wide operating range is reliably possible. Furthermore, it is an object of the invention to propose a corresponding method for compensating the axial thrust in a centrifugal pump. In particular, this method should also be used for centrifugal pumps with magnetically mounted rotor.
Die diese Aufgabe lösenden Gegenstände der Erfindung sind durch die Merkmale der unabhängigen Patentansprüche gekennzeichnet. Erfindungsgemäss wird also eine magnetisch gelagerte Zentrifugalpumpe vorgeschlagen mit einem Spaltrohrmotor, mit einem Pumpengehäuse, das einen Einlass und einen Auslass aufweist, einen Rotor mit einer dem Einlass zugewandten Vorderseite und einer dem Einlass abgewandten Rückseite, wobei der Rotor ein erstes Pumpenrad mit ersten Flügeln aufweist zur Erzeugung eines Hauptflusses vom Einlass zum Auslass, und wobei am Rotor ein zweites Pumpenrad mit zweiten Flügeln und mit mindestens einer Entlastungsbohrung vorgesehen ist zur Erzeugung eines Rezirkulationsflusses, der von der Rückseite des Rotors durch die mindestens eine Entlastungsbohrung gerichtet ist, wobei sich die Entlastungsbohrung axial von der Rückseite des Rotors durch den Rotorteil des elektrischen Drehantriebs bis zum zweiten Pumpenrad erstreckt, und wobei zwischen den beiden Pumpenrädern ein Trennelement vorgesehen ist, welches den Rezirkulationsfluss im Bereich des zweiten Pumpenrads zumindest teilweise vom Hauptfluss trennt.The problem-solving objects of the invention are characterized by the features of the independent claims. According to the invention, therefore, a magnetically mounted centrifugal pump is proposed with a canned motor, with a pump housing having an inlet and an outlet, a rotor with a front side facing the inlet and a rear side facing away from the inlet, the rotor having a first impeller with first vanes Generating a main flow from the inlet to the outlet, and wherein on the rotor, a second impeller with second vanes and at least one relief bore is provided for generating a Rezirkulationsflusses, which is directed from the back of the rotor through the at least one relief bore, wherein the relief bore axially from the rear side of the rotor extends through the rotor part of the electric rotary drive to the second impeller, and wherein between the two pump wheels, a separating element is provided, which at least partially the Rezirkulationsfluss in the region of the second impeller from Hauptfl uss separates.
Durch das zweite Pumpenrad und das Trennelement kann ein Rezirkulationsfluss zur axialen Ausbalancierung bzw. zum Ausgleichen des axialen Schubs generiert werden, der weitgehend vom Hauptfluss getrennt werden kann. Somit ist es möglich, mithilfe der mindestens einen Entlastungsbohrung den Rotor weitgehend unabhängig vom Hauptfluss bezüglich der axialen Richtung auszubalancieren. Mittels einer optimierten Geometrie des Trennelements sowie der Abmessungen, insbesondere der Höhe der ersten und zweiten Flügel relativ zueinander, sowie der Anzahl und der Geometrie der Entlastungsbohrungen ist ein sehr grosser Arbeitsbereich auch für verschiedene Viskositäten und Dichten mit nur einer Konfiguration des Rotors möglich.By means of the second impeller and the separating element, a recirculation flow can be generated for axially balancing or for compensating the axial thrust, which flow can be largely separated from the main flow. Thus, it is possible using the at least one relief bore to balance the rotor largely independent of the main flow with respect to the axial direction. By means of an optimized geometry of the separating element and the dimensions, in particular the height of the first and second wings relative to each other, as well as the number and the geometry of the relief bores, a very large working range is possible even for different viscosities and densities with only one configuration of the rotor.
Das Trennelement ist vorzugsweise scheibenförmig ausgebildet, wobei auf der dem Einlass zugewandten Seite die ersten Flügel des ersten Pumpenrads vorgesehen sind und auf der dem Einlass abgewandten Seite die zweiten Flügel des zweiten Pumpenrads vorgesehen sind.The separating element is preferably disc-shaped, wherein the first vanes of the first impeller are provided on the side facing the inlet, and the second vanes of the second impeller are provided on the side facing away from the inlet.
Insbesondere vorteilhaft ist eine Ausgestaltung, bei welcher die ersten Flügel so angeordnet sind, dass ein zentraler Bereich des ersten Pumpenrads frei von Flügeln ist und wobei das Trennelement so ausgestaltet ist, dass es sich über den gesamten zentralen Bereich des ersten Pumpenrads erstreckt. Durch diese Konstruktion ist nämlich gewährleistet, dass einerseits der Hauptfluss und der Rezirkulationsfluss in diesem zentralen Bereich keinen Kontakt miteinander bekommen und andererseits kann das Trennelement vorteilhaft als Staudruckplatte zur axialen Druckentlastung beitragen, in ähnlicher Weise wie dies in der bereits zitierten
Es hat sich in der Praxis als vorteilhaft erwiesen, wenn sich die ersten und die zweiten Flügel bezüglich der radialen Richtung über das Trennelement hinaus erstrecken.It has proved to be advantageous in practice if the first and the second vanes extend beyond the separating element with respect to the radial direction.
Konstruktiv besonders einfach ist es, wenn Gesamtflügel vorgesehen sind, die sowohl die ersten als auch die zweiten Flügel bilden, wobei jeder Gesamtflügel zumindest in einem radial innenliegenden Abschnitt durch das Trennelement bezüglich der axialen Richtung in zwei Teile getrennt ist.It is structurally particularly simple if overall wings are provided which form both the first and the second wings, wherein each overall wing is divided into two parts at least in a radially inward section through the separating element with respect to the axial direction.
Je nach Anwendungsfall kann eine zusätzliche axiale Stabilisierung bewirkt werden, wenn auf der Rückseite des Rotors Rudimentärschaufeln vorgesehen sind.Depending on the application, an additional axial stabilization can be effected if rudimentary blades are provided on the back of the rotor.
Im Hinblick auf eine optimale axiale Balancierung kann es vorteilhaft sein, wenn mehrere Entlastungsbohrungen vorgesehen sind, die bezüglich der Achse des Rotors symmetrisch angeordnet sind.With regard to an optimal axial balancing, it may be advantageous if a plurality of relief bores are provided, which are arranged symmetrically with respect to the axis of the rotor.
Erfindungsmäßig ist der Rotor magnetisch gelagert.According to the invention, the rotor is magnetically supported.
Die Pumpe wird mit einem elektrischen Drehantrieb für den Rotor, angetrieben, wobei der Drehantrieb als Spaltrohrmotor ausgestaltet ist.The pump is driven by an electric rotary drive for the rotor, wherein the rotary drive is designed as a canned motor.
Speziell bevorzugt ist ein Ausführungsbeispiel mit einem elektrischen Drehantrieb für den Rotor, wobei der Drehantrieb einen Stator aufweist, wobei der Rotor den Rotor des elektrischen Drehantriebs bildet, und zusammen mit dem Stator einen lagerlosen Motor bildet, bei welchem der Stator als Lager- und Antriebsstator für den Rotor ausgestaltet ist. Insbesondere ist es dabei vorteilhaft, wenn der Rotor des lagerlosen Motors permanentmagnetisch ist und bezüglich der axialen Richtung passiv magnetisch gegen Verschiebungen und Verkippungen stabilisiert ist.Especially preferred is an embodiment with an electric rotary drive for the rotor, wherein the rotary drive comprises a stator, wherein the rotor forms the rotor of the electric rotary drive, and forms a bearingless motor together with the stator, wherein the stator as a storage and drive stator for the rotor is designed. In particular, it is advantageous if the rotor of the bearingless motor is permanently magnetic and is passive magnetically stabilized with respect to the axial direction against displacement and tilting.
Durch die Erfindung wird ferner ein Verfahren vorgeschlagen zum Ausgleichen des axialen Schubs in einer magnetisch gelagerten Zentrifugalpumpe mit einem Spaltrohrmotor und mit einem Pumpengehäuse, das einen Einlass und einen Auslass aufweist, einen Rotor mit einer dem Einlass zugewandten Vorderseite und einer dem Einlass abgewandten Rückseite, bei welchem Verfahren mit ersten Flügeln eines erstes Pumpenrads des Rotors ein Hauptfluss vom Einlass zum Auslauss erzeugt wird, wobei mit zweiten Flügeln eines zweiten Pumpenrads des Rotors ein Rezirkulationsfluss erzeugt wird, der von der Rückseite des Rotors durch mindestens eine Entlastungsbohrung, welche im zweiten Pumpenrad vorgesehen ist, gerichtet ist, wobei der Rezirkulationsfluss im Bereich des zweiten Pumpenrads zumindest teilweise vom Hauptfluss getrennt geführt wird, wobei sich die Entlastungsbohrung axial von der Rückseite des Rotors durch den Rotorteil des elektrischen Drehantriebs bis zum zweiten Pumpenrad ersteckt.The invention further provides a method for compensating axial thrust in a magnetically-mounted centrifugal pump having a canned motor and a pump housing having an inlet and an outlet, a rotor having an inlet facing front side and a rear side facing away from the inlet which method is used to generate a main flow from inlet to outlet with first vanes of a first impeller of the rotor, with second vanes of a second impeller of the rotor producing a recirculation flow which is from the rear side of the rotor through at least one relief well provided in the second impeller is directed, wherein the recirculation flow in the region of the second impeller is at least partially separated from the main flow out, wherein the relief bore extends axially from the back of the rotor through the rotor part of the electric rotary drive to the second impeller.
Mit dem erfindungsgemässen Verfahren kann ein Rezirkulationsfluss zur axialen Ausbalancierung bzw. zum Ausgleichen des axialen Schubs generiert werden, der weitgehend vom Hauptfluss getrennt werden kann. Somit ist es möglich, mithilfe der mindestens einen Entlastungsbohrung den Rotor weitgehend unabhängig vom Hauptfluss bezüglich der axialen Richtung auszubalancieren. Mit diesem Verfahren ist ein Ausgleich des axialen Schubs in einem sehr grosser Arbeitsbereich auch für verschiedene Viskositäten und Dichten mit nur einer Konfiguration des Rotors möglich.With the method according to the invention, a recirculation flow for axial balancing or for compensating the axial thrust can be generated, which can be largely separated from the main flow. Thus, it is possible using the at least one relief bore to balance the rotor largely independent of the main flow with respect to the axial direction. With this method, a compensation of the axial thrust in a very large work area is also possible for different viscosities and densities with only one configuration of the rotor.
Für einige Anwendungen hat es sich als vorteilhaft erwiesen, wenn der Rezirkulationsfluss im wesentlichen getrennt vom Hauptfluss geführt wird.For some applications, it has proven to be advantageous if the recirculation flow is conducted substantially separate from the main flow.
Das erfindungsgemässe Verfahren eignet sich insbesondere, wenn der Rotor magnetisch, vorzugsweise vollständig magnetisch, gelagert ist.The method according to the invention is particularly suitable when the rotor is mounted magnetically, preferably completely magnetically.
Das erfindungsgemässe Verfahren ist speziell für Zentrifugalpumpen geeignet, die nach dem Prinzip des lagerlosen Motors arbeiten, bei welchem die Zentrifugalpumpe einen elektrischen Drehantrieb mit einem Stator aufweist, der Rotor permanentmagnetisch ist und den Rotor des elektrischen Drehantriebs bildet, der zusammen mit dem Stator einen lagerlosen Motor bildet, bei welchem der Stator als Lager- und Antriebsstator für den permanentmagnetischen Rotor ausgestaltet ist, wobei der Rotor bezüglich der axialen Richtung passiv magnetisch gegen Verschiebungen und Verkippungen stabilisiert ist.The inventive method is particularly suitable for centrifugal pumps, which operate on the principle of the bearingless motor, in which the centrifugal pump has an electric rotary drive with a stator, the rotor is permanently magnetic and the rotor of the electric Rotary drive forms, which forms a bearingless motor together with the stator, in which the stator is designed as a bearing and drive stator for the permanent magnet rotor, wherein the rotor is passive magnetically stabilized with respect to the axial direction against displacement and tilting.
Weiter vorteilhafte Massnahmen und Ausgestaltungen der Erfindung ergeben sich aus den abhängigen Ansprüchen.Further advantageous measures and embodiments of the invention will become apparent from the dependent claims.
Im Folgenden wird die Erfindung sowohl in apparativer als auch in verfahrenstechnischer Hinsicht anhand von Ausführungsbeispielen und anhand der Zeichnung näher erläutert. In der schematischen Zeichnung zeigen teilweise im Schnitt:
- Fig. 1:
- eine stark schematische Darstellung eines Ausführungsbeispiels einer erfindungsgemässen Zentrifugalpumpe,
- Fig. 2:
- eine schematische Schnittdarstellung des Pumpengehäuses und des Rotors des Ausführungsbeispiels aus
Fig. 1 , wobei der Hauptfluss und der Rezirkulationsfluss angedeutet sind, - Fig. 3:
- eine schematische Darstellung ähnlich zu
Fig. 2 zur Erläuterung von Abmessungen, - Fig. 4:
- eine Schnittdarstellung durch den Rotor des Ausführungsbeispiels entlang der Schnittlinie IV-IV in
Fig. 6 - Fig. 5:
- eine Ansicht des Rotors aus
Fig. 4 , - Fig. 6:
- eine Aufsicht auf die Vorderseite des Rotors aus
Fig. 4 , wobei die Deckplatte entfernt ist, - Fig. 7:
- eine Aufsicht auf die Rückseite des Rotors aus
Fig. 4 , und - Fig. 8:
- ein Ansicht einer Variante des Rotors aus
Fig. 4 , ohne Deckplatte.
- Fig. 1:
- a highly schematic representation of an embodiment of an inventive centrifugal pump,
- Fig. 2:
- a schematic sectional view of the pump housing and the rotor of the embodiment
Fig. 1 wherein the main flow and the recirculation flow are indicated, - 3:
- a schematic representation similar to
Fig. 2 to explain dimensions, - 4:
- a sectional view through the rotor of the embodiment along the section line IV-IV in
Fig. 6 - Fig. 5:
- a view of the rotor
Fig. 4 . - Fig. 6:
- a view of the front of the rotor
Fig. 4 with the cover plate removed, - Fig. 7:
- a view of the back of the rotor
Fig. 4 , and - Fig. 8:
- a view of a variant of the rotor
Fig. 4 , without cover plate.
Bei der folgenden Beschreibung der Erfindung wird mit beispielhaftem Charakter auf den für die Praxis besonders wichtigen Fall Bezug genommen, dass die erfindungsgemässe Zentrifugalpumpe mit einem elektrischen Drehantrieb nach dem Prinzip eines lagerlosen Motors ausgestaltet ist.In the following description of the invention, reference is made by way of example to the case, which is particularly important in practice, in that the centrifugal pump according to the invention is designed with an electric rotary drive on the principle of a bearingless motor.
Dies betrifft Zentrifugalpumpen mit vollständig oder teilweise magnetischer Lagerung des Pumpenrotors.This concerns centrifugal pumps with fully or partially magnetic bearing of the pump rotor.
Das in
Zum Antreiben des Rotors 3 ist ein elektrischer Drehantrieb 8 vorgesehen, welcher einen Stator 81 mit Wicklungen 82 umfasst.For driving the
Der Rotor 3 im Pumpengehäuse 2 ist gleichzeitig auch der Rotor 3 des elektrischen Drehantriebs 8. Diese Ausgestaltung wird auch als Integralrotor bezeichnet, weil der Rotor des elektrischen Drehantriebs identisch ist mit dem Pumpenrotor, der das Fluid fördert.The
Wie bereits erwähnt, ist der Drehantrieb 8 bei diesem bevorzugten Ausführungsbeispiel als lagerloser Motor ausgebildet, bei welchem der Stator 81 als Lager- und Antriebsstator für die magnetische Lagerung des Rotors 3 und den Antrieb der Rotation des Rotors 3 um die Drehachse A ausgestaltet ist. Besonders bevorzugt ist der Rotor 3 als permanentmagnetischer Rotor 3 ausgestaltet, der zusammen mit dem Stator 81 einen lagerlosen Motor bildet, bei welchem der Stator als Lager- und Antriebsstator für den permanentmagnetischen Rotor 3 ausgestaltet ist. Die magnetische Lagerung des Rotors 3 ist in
Ein solcher lagerloser Motor wird beispielsweise in der bereits zitierten
Im speziellen ist der in
Die
Zum besseren Verständnis wird in den
Wie dies
Erfindungsgemäss ist am Rotor 3 ein zweites Pumpenrad 5 mit zweiten Flügeln 51 vorgesehen, welches mindestens eine Entlastungsbohrung 6 aufweist. Dieses zweite Pumpenrad 5 erzeugt einen Rezirkulationsfluss, der von der Rückseite 32 des Rotors 3 durch die Entlastungsbohrung 6 gerichtet ist. Der Rezirkulationsfluss ist in
Wie dies insbesondere
Durch das Trennelement 7 kann der zur axialen Ausbalancierung bzw. zum Ausgleichen des axialen Schubs erforderliche Rezirkulationsfluss weitgehend vom Hauptfluss getrennt werden. Dadurch kann der Rotor bezüglich des axialen Schubs weitgehend unabhängig vom Hauptfluss ausbalanciert werden. Somit ist ein sehr grosser Arbeitsbereich, das heisst ein grosser Bereich verschiedener Durchflüsse und verschiedener Förderdrücke auch für verschiedene Viskositäten und Dichten des zu fördernden Fluids mit nur einer Konfiguration des Rotors 3 realisierbar, ohne das Zugeständnisse an die Qualität der axialen Ausbalancierung notwendig sind. Durch das Trennelement 7 wird insbesondere auch vermieden, dass der Rezirkulationsfluss und der Hauptfluss frontal - das heisst als entgegengesetzt gerichtete Strömungen aufeinanderprallen, was zu Verwirbelungen führen würde, die für die axiale Ausbalancierung nachteilig sind.By means of the separating
Der Hauptfluss und der Rezirkulationsfluss kommen erst nach Passieren des radial äusseren Endes des Trennelements 7 miteinander in Kontakt. Hier sind beide Flüsse im wesentlichen in radialer Richtung gerichtet, sodass auch hier ein frontales Aufeinanderprallen des Haupt- und des Rezirkulationsflusses vermieden wird.The main flow and the recirculation flow come into contact only after passing through the radially outer end of the separating
Bei dem hier beschriebenen Ausführungsbeispiel ist das Trennelement 7 scheibenförmig ausgebildet (siehe auch
In seinem zentralen Bereich weist das Trennelement 7 eine runde Erhebung 71 auf ,welche dem besseren Umlenken des Fluids in die radiale Richtung dient.In its central region, the separating
Sowohl die zweiten Flügel 51 des zweiten Pumpenrads 5 als auch die ersten Flügel 41 der ersten Pumpenrads 4 erstrecken sich jeweils in radialer Richtung gekrümmt. Mit radialer Richtung ist dabei eine zur axialen Richtung senkrechte Richtung gemeint. Wie dies insbesondere auch
Auf der Vorderseite 31 des Rotors 3 ist eine Deckplatte 34 vorgesehen (siehe auch
In der Praxis hat es sich für manche Anwendungen als vorteilhaft erwiesen, wenn sich die ersten Flügel 41 und die zweiten Flügel 51 bezüglich der axialen Richtung über das Trennelement 7 hinaus erstrecken. Diese Massnahme wird am besten in der Darstellung der
Wie weit sich das Trennelement 7 bezüglich der radialen Richtung zwischen den ersten Flügeln 41 und den zweiten Flügeln 51 erstreckt, hängt vom Anwendungsfall ab und ist einer der Parameter, die für die Optimierung des axialen Schubausgleichs zur Verfügung stehen. Bei der hier beschriebenen Ausführungsform mit dem scheibenförmigen Trennelement 7 sollte das Trennelement sich bezüglich der radialen Richtung mindestens so weit erstrecken, dass es den gesamten zentralen Bereich 35 überdeckt. Andererseits kann sich das Trennelement 7 auch über die gesamte radiale Erstreckung der Flügel 41 oder 51 erstrecken, sodass das Trennelement 7 in radialer Richtung bündig mit den Flügeln 41 oder 51 abschliesst. Auf diese geometrischen Verhältnisse wird weiter hinten noch eingegangen.How far the
Eine konstruktiv besonders günstige Massnahme ist es (siehe
Eine weitere Massnahme, die vorteilhaft sein kann, ist es auf der Rückseite 32 des Rotors 3 Rudimentärschaufeln 36 vorzusehen.
Um einen möglichst guten Ausgleich des Axialschubs zu erzielen, kann es vorteilhaft sein, mehrere Entlastungsbohrungen 6 vorzusehen, die insbesondere bezüglich der Drehachse des Rotors 3 symmetrisch angeordnet sind. Wie dies
Da das hier beschriebene Ausführungsbeispiel der erfindungsgemässen Zentrifugalpumpe als lagerloser Motor mit permanentmagnetischem Rotor 3 ausgestaltet ist, umfasst der Rotor 3 einen ringförmigen Permanentmagneten 33, der gemäss der Darstellung in
Konstruktiv besonders einfach und kompakt ist es, wenn die zweiten Flügel 51 des zweiten Pumpenrads 5 einstückig mit der Ummantelung 38 sind, wie dies
Um mit dem erfindungsgemässen Verfahren bzw. bei der erfindungsgemässen Zentrifugalpumpe den Ausgleich des axialen Schubs möglichst effizient und für einen möglichst grossen Arbeitsbereich, also insbesondere für einen grossen Durchflussbereich und für einen grossen Druckbereich - auch bei verschiedenen Viskositäten und Dichten - zu realisieren, gibt es verschiedene Parameter, mit denen die Konfiguration des Rotors optimiert werden kann.In order to realize the compensation of the axial thrust as efficiently as possible and for the largest possible working range, ie in particular for a large flow range and for a large pressure range - even with different viscosities and densities - with the method according to the invention or with the centrifugal pump according to the invention, there are various Parameters with which the configuration of the rotor can be optimized.
Hierzu sind in
Ein wichtiger Parameter ist das Verhältnis aus DT und DR. In der Praxis hat es sich bisher bewährt, wenn das Verhältnis DT/DR grösser als 0.5 und kleiner oder gleich 1 ist, insbesondere ist der Bereich von 0.6 bis 0.7 bevorzugt. Bezüglich der Höhe der Flügel 41, 51 und des Trennelements 7 zwischen den Flügeln 41, 51 ist es bevorzugt, wenn die Höhe H2 der zweiten Flügel 52 kleiner ist als die Höhe HT des Trennelements 7 und HT kleiner ist als die Höhe H1 der ersten Flügel. Bezogen auf die Höhe H der Gesamtflügel ist die Höhe H2 der zweiten Flügel 52 vorzugsweise kleiner als die Hälfte von H, insbesondere höchstens 25% von H und speziell zwischen 15% und 20% von H. Die Höhe H1 der ersten Flügel 41 ist vorzugsweise grösser als die Hälfte von H, insbesondere höchstens 75% von H und speziell zwischen 50% und 60% von H.An important parameter is the ratio of DT and DR. In practice, it has hitherto been successful if the ratio DT / DR is greater than 0.5 and less than or equal to 1, in particular the range from 0.6 to 0.7 is preferred. With respect to the height of the
Bei der bevorzugten Ausführungsform der erfindungsgemässen Zentrifugalpumpe als lagerloser Motor mit permanentmagnetischem Rotor 3 ist es im Hinblick auf die magnetische Lagerung, insbesondere auf die passiv magnetische Stabilisierung bezüglich der axialen Richtung vorteilhaft, wenn das Verhältnis aus der Gesamthöhe HR des Rotors 3 (siehe
Es sind auch solche Ausgestaltungen der erfindungsgemässen Zentrifugalpumpe möglich, bei denen das Pumpengehäuse 2 mehr als einen Auslass 22 und/oder mehr als einen Einlass 21 aufweist. Falls zwei oder mehr Einlässe 21 vorgesehen sind, so sind diese auf der gleichen Seite des Rotors 3 bzw. des ersten Pumpenrads 4 anzuordnen, das heisst, es ist zu vermeiden, dass das Fluid direkt von einem der Einlässe aus der axialen Richtung zum zweiten Pumpenrad gelangen kann.Such embodiments of the centrifugal pump according to the invention are also possible in which the
Claims (15)
- A centrifugal pump having a pump housing (2) which has an inlet (21) and an outlet (22), a rotor (3) having a front side (31) facing the inlet (21) and a rear side (32) remote from the inlet (21), wherein the rotor (3) is configured as an integral rotor so that the rotor (3) is simultaneously a rotor of an electric rotary drive (8), wherein the rotor is magnetically supported, and wherein the rotor (3) has a first pump wheel (4) having first vanes (41) for the generation of a main flow from the inlet (21) to the outlet (22), wherein a second pump wheel (5) having second vanes (52) and having at least one relief bore (6) is provided at the rotor (3) for the generation of a recirculation flow which is directed from the rear side (32) of the rotor (3) through the at least one relief bore (6), and wherein a partition element (7), which separates the recirculation flow at least partly from the main flow in the region of the second pump wheel (5), is provided between the two pump wheels (4, 5), wherein the rotary drive (8) is configured as a canned motor such that the relief bore (6) extends axially from the rear side (32) of the rotor (3) through the rotor part of the electric rotary drive (8) up to the second pump wheel (5).
- A centrifugal pump in accordance with claim 1, wherein the partition element (7) is made in disk shape, wherein the first vanes (41) of the first pump wheel (4) are provided on the side facing the inlet (21) and the second vanes (51) of the second pump wheel (5) are provided on the side remote from the inlet (21).
- A centrifugal pump in accordance with one of the preceding claims, wherein the first vanes (41) are arranged such that a central region (35) of the first pump wheel (4) is free of vanes, and wherein the partition element (7) is designed so that it extends over the total central region (35) of the first pump wheel (4).
- A centrifugal pump in accordance with any one of the preceding claims, wherein the first vanes (41) and the second vanes (51) extend beyond the partition element (7) with respect to the radial direction.
- A centrifugal pump in accordance with any one of the preceding claims, wherein total vanes are provided which form both the first vanes (41) and the second vanes (51), wherein each total vane is separated by the partition element (7) into two parts with respect to the axial direction in at least a radially inwardly disposed section.
- A centrifugal pump in accordance with any one of the preceding claims, wherein rudimentary blades (36) are provided at the rear side (32) of the rotor (3).
- A centrifugal pump in accordance with any one of the preceding claims, wherein a plurality of relief bores (6) are provided which are arranged symmetrically with respect to the axis of the rotor (3).
- A centrifugal pump in accordance with any one of the preceding claims, wherein the rotor (3) is magnetically supported.
- A centrifugal pump in accordance with any one of the preceding claims having an electric rotary drive (8) for the rotor (3), wherein the rotor (8) is designed as a canned motor.
- A centrifugal pump in accordance with any one of the preceding claims having an electric rotary drive (8) for the rotor (3), wherein the rotary drive (8) has a stator (81), wherein the rotor (3) forms the rotor of the electric rotary drive (8) and forms, together with the stator (81), a bearingless motor in which the stator (81) is designed as a bearing and drive stator for the rotor (3).
- A centrifugal pump in accordance with claim 10, wherein the rotor (3) of the bearingless motor is permanently magnetic and is stabilized in a passively magnetic manner with respect to the axial direction against displacements and tilting.
- A method for the compensation of the axial thrust in a centrifugal pump having a pump housing (2) which has an inlet (21) and an outlet (22), a rotor (3) having a front side (31) facing the inlet (21) and a rear side (32) remote from the inlet (21), wherein the rotor (3) is configured as an integral rotor so that the rotor (3) is simultaneously a rotor of an electric rotary drive (8), wherein the rotor is magnetically supported.
in which method a main flow is generated from the inlet (21) to the outlet (22) by first vanes (41) of a first pump wheel (4) of the rotor (3), wherein a recirculation flow is generated by second vanes (51) of a second pump wheel (5) of the rotor (3), said recirculation flow being directed from the rear side (32) of the rotor (3) through at least one relief bore (6) which is provided in the second pump wheel (5), wherein the recirculation flow is guided at least partly separately from the main flow in the region of the second pump wheel (5), wherein the rotary drive (8) is configured as a canned motor such that the relief bore (5) extends axially from the rear side (32) of the rotor (3) through the rotor part of the electric rotary drive (8) up to the second pump wheel (5). - A method in accordance with claim 12, wherein the recirculation flow is guided substantially separately from the main flow.
- A method in accordance with one of the claims 12 or 13, wherein the rotor (3) is supported magnetically, preferably completely magnetically.
- A method in accordance with any one of the claims 12 to 14, wherein the centrifugal pump has an electric rotary drive (8) having a stator (8), wherein the rotor is permanently magnetic and forms the rotor (3) of the electric rotary drive (8) which forms, together with the stator (81), a bearingless motor in which the stator (81) is designed as a bearing and drive stator for the permanently magnetic rotor (3), and wherein the rotor (3) is stabilized in a passively magnetic manner with respect to the axial direction against displacements and tilting.
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EP10164973.9A EP2273124B1 (en) | 2009-07-06 | 2010-06-04 | Centrifugal pump and method for compensating for the axial impulse in a centrifugal pump |
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EP09164690 | 2009-07-06 | ||
EP10164973.9A EP2273124B1 (en) | 2009-07-06 | 2010-06-04 | Centrifugal pump and method for compensating for the axial impulse in a centrifugal pump |
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WO2020173545A1 (en) | 2019-02-26 | 2020-09-03 | Gea Mechanical Equipment Gmbh | Separator |
DE102020121420A1 (en) | 2020-08-14 | 2022-02-17 | Gea Westfalia Separator Group Gmbh | separator |
WO2022033953A1 (en) | 2020-08-14 | 2022-02-17 | Gea Westfalia Separator Group Gmbh | Separator insert and separator |
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Also Published As
Publication number | Publication date |
---|---|
US20110002794A1 (en) | 2011-01-06 |
EP2273124A1 (en) | 2011-01-12 |
US9115725B2 (en) | 2015-08-25 |
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