EP2359009B1 - Reducible relief opening - Google Patents
Reducible relief opening Download PDFInfo
- Publication number
- EP2359009B1 EP2359009B1 EP09774627A EP09774627A EP2359009B1 EP 2359009 B1 EP2359009 B1 EP 2359009B1 EP 09774627 A EP09774627 A EP 09774627A EP 09774627 A EP09774627 A EP 09774627A EP 2359009 B1 EP2359009 B1 EP 2359009B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- impeller
- inserts
- pressure
- centrifugal pump
- sleeve
- 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.)
- Active
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- 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
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0027—Varying behaviour or the very pump
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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
- F04D29/02—Selection of particular materials
- F04D29/026—Selection of particular materials especially adapted for liquid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2300/00—Materials; Properties thereof
- F05D2300/50—Intrinsic material properties or characteristics
- F05D2300/501—Elasticity
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2300/00—Materials; Properties thereof
- F05D2300/50—Intrinsic material properties or characteristics
- F05D2300/518—Ductility
Definitions
- the invention relates to a centrifugal pump one or more stages with arranged in the pump housing, driven impeller or impellers, a shaft seal and wherein at least one cover plate of at least one impeller one or more adjustable discharge openings are arranged.
- centrifugal pumps the resultant of the axial forces acting on a pump impeller is referred to as the axial thrust.
- Their exact determination is described in the KSB centrifugal pumps Lexikon, 3rd edition, under the keyword "axial thrust" on pages 32 ff.
- axial thrust In single-stage centrifugal pumps, an axial force relief with discharge openings in a pressure-side impeller cover disc has proven to be the frequent measure.
- the arrangement of the relief openings is also in combination with additional sealing gaps and housing ribs or impeller blades.
- a comparable solution shows the SU A 523 994 in which such adjustability of the discharge openings takes place on an open impeller, but on the rear side in an analogous manner.
- centrifugal pumps regardless of whether they are single-stage or multi-stage, one or more impellers, in most cases a shaft seal and a bearing carrier, are arranged downstream.
- the discharge openings for the axial thrust are usually selected so large that a residual residual axial thrust can be easily absorbed by the shaft bearings. Its magnitude is below a permissible axial bearing load of the bearing.
- one or more sleeve-shaped inserts is or are arranged in one or more discharge openings.
- the arranged in the normal Axialschubaus convincedsö Maschinenen the impeller sleeve-shaped and flow-through inserts have a smaller cross-sectional area of the flow area. This results in a precise throttling of a return flow from the impeller side space back into the suction of the impeller.
- a pressure increase which in turn results in a defined contact pressure of a shaft seal.
- the latter for example, the sliding ring of a loaded mechanical seal, even with fluctuating operating conditions always with a sufficiently high pressure safely and sealingly pressed against the mating ring.
- Embodiments provide that the insert is formed as a clamping sleeve and is held elastically deformable in a discharge opening.
- inserts For centrifugal pumps with metal and / or plastic impellers arranged therein, inserts have proved to be advantageous, which are equipped with a radially projecting collar. These sleeve-shaped inserts are used in the manner of hollow rivets as needed in standardized relief openings and held therein by plastic deformation or frictional engagement.
- the pump housing with the pump impeller arranged therein is followed by a kind of thermal barrier.
- This provides a longer shaft, which is guided within a longer and thin-walled shaft housing and held in a spaced bearing support with and between the bearings arranged mechanical seal.
- the heat transfer between the pump housing and bearing carrier is reduced.
- By additionally held in the relief openings throttling inserts behind the impeller creates a higher pressure.
- This higher pressure arises along the shaft also in the sealing space of the bearing carrier and always requires there a defined load on the shaft seal.
- Several inserts with different diameters can also be arranged inserted one inside the other. With this measure, a targeted adaptation of an axial thrust or its compensation can be achieved. For example, if the system, operating conditions or operating conditions change for a centrifugal pump.
- the Fig. 1 shows a centrifugal pump impeller radial and closed type.
- the impeller 1 receiving housing as well as the impeller 1 via a hub 2 driving shaft and a shaft seal was omitted for reasons of clarity.
- Trained as a casting impeller 1 has a pressure-side impeller cover 3, which is provided in the transition region to the hub 2 with a plurality of evenly distributed on a diameter arranged discharge openings 4. These are often designed as holes.
- a fluid conveyed by the impeller 1 flows from the impeller inlet 5 through the blade channels 7 bounded by blades 6 to the impeller outlet 8 and flows into the interior of a housing.
- the pressure prevailing at the impeller outlet 8 acts and exerts a force in the axial direction both on the pressure-side impeller cover disk 3 and on the opposite intake-side impeller cover disk 9.
- a resulting axial force As a result of the different size of the surfaces of the impeller cover discs resulting from the pressure acting thereon, a resulting axial force. With a wrong interpretation of the conditions, this will have negative effects on the bearings of a shaft driving the impeller.
- An impeller 1 is usually provided with a suction side gap surface 10 and pressure side gap surface 11, which are arranged opposite stationary housing cleavage surfaces, thus forming gap seals between stationary and rotating parts.
- a gap surface 11 for a gap seal is arranged by way of example.
- a fluid located on the pressure side DRS flows through the relief openings 4 back into the region of the impeller inlet 5 and the region of the inlet edges of the blades 6, where there is a low inlet pressure.
- the sum of the cross section of the individual discharge openings 4 is chosen so large that it ensures a defined remaining residual axial thrust. Whose size should not exceed the permissible bearing load of arranged in a bearing carrier bearings in all possible operating conditions.
- the number of relief openings 4 is usually dependent on the number of blades used an impeller 1 and the consequent number of blade channels.
- one of these relief openings 4 is shown in section and is located above the hub 2.
- the relief hole 4 corresponds to the cross section and the number forth a design state of the pump.
- at least one sleeve-shaped insert 12 which reduces the cross-section, is arranged in one or more relief openings 4. This can be a pressed-in bushing or an elastically deformable clamping sleeve, clamping sleeve, clamping pin or an analogously acting machine element.
- Such a throttling insert can be installed at a final assembly of the pump in a factory, if the exact operating conditions for a pumped fluid of the pump are known. Likewise, an axial thrust adjustment by retrofitting or disassembly of one or more inserts 12 can easily take place at a later installation location of the pump.
- spring-trained clamping sleeves have proven that can be used in the simplest way in existing relief openings 4. Due to the elastic shape change of the inserts 12 they are at a mounting elastically reduced in diameter and held by their residual stress safely in the relief hole 4.
- the Fig. 2 shows a similar, but designed as a sheet metal part impeller 1.
- plastically deformable sleeves 13 are used.
- sleeves 13 proved to be advantageous because they are simply used in such relief openings and held by the collar 14.
- the other sleeve end 15 can be widened and thus the sleeve 13 can be securely fixed in the impeller 1. This can be done with the aid of a riveting or crimping tool, whereby one or both ends of the sleeve 13 are reshaped.
- a sleeve 13 may also be an elastic deformable sleeve 12, as shown in FIG Fig. 1 is shown, additionally arranged, so as to further restrict the flow area.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
Die Erfindung betrifft eine Kreiselpumpe ein- oder mehrstufige Bauart mit im Pumpengehäuse angeordneten, angetriebenem Laufrad oder Laufrädern, einer Wellenabdichtung und wobei an mindestens einer Deckscheibe von mindestens einem Laufrad ein oder mehreren einstellbaren Entlastungsöffnungen angeordnet sind.The invention relates to a centrifugal pump one or more stages with arranged in the pump housing, driven impeller or impellers, a shaft seal and wherein at least one cover plate of at least one impeller one or more adjustable discharge openings are arranged.
Bei Kreiselpumpen wird die Resultierende der auf ein Pumpenlaufrad einwirkenden Axialkräfte als der Axialschub bezeichnet. Deren genaue Ermittlung ist in dem KSB-Kreiselpumpenlexikon, 3. Auflage, unter dem Stichwort "Axialschub" auf den Seiten 32 ff, beschrieben. Bei einstufigen Kreiselpumpen hat sich eine Axialkraftentlastung mit Entlastungsöffnungen in einer druckseitigen Laufraddeckscheibe als die häufige Maßnahme erwiesen. Die Anordnung der Entlastungsöffnungen erfolgt auch in Kombination mit zusätzlichen Dichtspalten und Gehäuserippen oder Laufradschaufeln.In centrifugal pumps, the resultant of the axial forces acting on a pump impeller is referred to as the axial thrust. Their exact determination is described in the KSB centrifugal pumps Lexikon, 3rd edition, under the keyword "axial thrust" on pages 32 ff. In single-stage centrifugal pumps, an axial force relief with discharge openings in a pressure-side impeller cover disc has proven to be the frequent measure. The arrangement of the relief openings is also in combination with additional sealing gaps and housing ribs or impeller blades.
Schwierigkeiten bereitet die Berechnung von dem Durchlassquerschnitt solcher Entlastungsöffnungen, dessen Größe eine hinreichend vollständige Entlastung des Laufrades gewährleistet. Um solche Ungenauigkeiten zu kompensieren ist durch die
Bei Kreiselpumpen, unabhängig davon, ob es sich um einstufige oder mehrstufige Bauarten handelt, sind einem Laufrad oder mehreren Laufrädern, in den meisten Fällen eine Wellenabdichtung und ein Lagerträger nachgeordnet. Zum Schutz der Lager werden die Entlastungsöffnungen für den Axialschub üblicherweise so groß ausgewählt, dass ein verbleibender Rest-Axialschub von den Wellenlagern problemlos aufnehmbar ist. Dessen Größenordnung liegt unterhalb einer zulässigen axialen Lagerbelastung der Lager.For centrifugal pumps, regardless of whether they are single-stage or multi-stage, one or more impellers, in most cases a shaft seal and a bearing carrier, are arranged downstream. To protect the bearings, the discharge openings for the axial thrust are usually selected so large that a residual residual axial thrust can be easily absorbed by the shaft bearings. Its magnitude is below a permissible axial bearing load of the bearing.
Für Kreiselpumpen mit dem Laufrad oder den Laufrädern nachgeordneten Wellenabdichtungen wird für eine definierte Druckbelastung in einem Dichtungsraum eine zuverlässige und funktionssichere Lösung gesucht. Insbesondere für die so genannten nicht entlasteten Wellendichtungen, wobei es sich auch um Gleitringdichtungen handelt, deren mit der Welle rotierender Gleitring auf eine Belastung durch einen definierten Flüssigkeitsdruck angewiesen ist. Andernfalls besteht die Gefahr, beispielsweise durch betriebsbedingte Druckschwankungen, das in Folge eines zu geringen Druck im Dichtungsraum eine Dichtung öffnet und somit durch externen Lufteintrag und daraus resultierenden Trockenlauf an der GLRD diese zerstört wird.For centrifugal pumps with the impeller or the impellers downstream shaft seals a reliable and reliable solution is sought for a defined pressure load in a seal chamber. In particular, for the so-called non-relieved shaft seals, which are also mechanical seals whose rotating with the shaft seal is reliant on a load by a defined fluid pressure. Otherwise, there is a risk, for example due to operational pressure fluctuations, which opens a seal as a result of too low pressure in the seal chamber and thus it is destroyed by external air inlet and resulting dry run at the mechanical seal.
Die Lösung des Problems sieht vor, dass in einer oder mehreren Entlastungsöffnungen ein oder mehrere hülsenförmige Einsätze angeordnet ist oder sind. Die in den normalen Axialschubausgleichsöffnungen des Laufrades angeordneten hülsenförmigen und durchströmbaren Einsätze besitzen eine kleinere Querschnittsfläche der Durchströmfläche. Damit erfolgt eine genaue Drosselung einer Rückströmung vom Laufradseitenraum zurück in den Saugbereich des Laufrades. In Abhängigkeit von der Größe der gewünschten Drosselung, welche durch die Querschnittsminderung in den Einsätzen entsteht, ergibt sich im Radseitenraum ein Druckanstieg, woraus wiederum eine definierte Anpressung einer Wellendichtung resultiert. So wird Letztere, beispielsweise der Gleitring einer belasteten Gleitringdichtung, auch bei schwankenden Betriebszuständen immer mit einem ausreichend hohen Druck sicher und dichtend an den Gegenring gepresst.The solution to the problem provides that one or more sleeve-shaped inserts is or are arranged in one or more discharge openings. The arranged in the normal Axialschubausgleichsöffnungen the impeller sleeve-shaped and flow-through inserts have a smaller cross-sectional area of the flow area. This results in a precise throttling of a return flow from the impeller side space back into the suction of the impeller. Depending on the size of the desired throttling, which is caused by the reduction in cross-section in the inserts, results in the Radseitenraum a pressure increase, which in turn results in a defined contact pressure of a shaft seal. Thus, the latter, for example, the sliding ring of a loaded mechanical seal, even with fluctuating operating conditions always with a sufficiently high pressure safely and sealingly pressed against the mating ring.
Ausgestaltungen sehen vor, dass der Einsatz als eine Klemmhülse ausgebildet und elastisch verformbar in einer Entlastungsöffnung gehalten ist. Für Kreiselpumpen mit darin angeordneten Blech- und/oder Kunststofflaufrädern haben sich Einsätze als vorteilhaft erwiesen, die mit einem radial vorstehenden Bund ausgestattet sind. Diese hülsenförmigen Einsätze werden nach Art von Hohlnieten bei Bedarf in standardisierte Entlastungsöffnungen eingesetzt und darin durch plastische Verformung oder reibschlüssig gehalten.Embodiments provide that the insert is formed as a clamping sleeve and is held elastically deformable in a discharge opening. For centrifugal pumps with metal and / or plastic impellers arranged therein, inserts have proved to be advantageous, which are equipped with a radially projecting collar. These sleeve-shaped inserts are used in the manner of hollow rivets as needed in standardized relief openings and held therein by plastic deformation or frictional engagement.
Mit diesen Lösungen wird bei Betriebszuständen von Kreiselpumpen, bei denen ein auf die Wellenabdichtung einwirkender Pumpendruck in der Größenordnung des Atmosphärendruckes oder sogar darunter liegt, zuverlässig und in einfachster Weise die nachteilige Folge einer sich öffnenden Wellendichtung und damit Undichtigkeiten verhindert.With these solutions, in the case of operating states of centrifugal pumps in which a pumping pressure acting on the shaft seal is of the order of magnitude of atmospheric pressure or even less, the disadvantageous consequence of an opening shaft seal and thus leaks is prevented reliably and in the simplest manner.
Auch bei Kreiselpumpen zur Förderung heißer Fluide, beispielsweise von Wärmeträgerölen und dergleichen, hat sich diese Lösung vorteilhaft bewährt. Hierbei ist dem Pumpengehäuse mit dem darin angeordneten Pumpenlaufrad eine Art von Wärmesperre nachgeordnet. Diese sieht eine längere Welle vor, die innerhalb eines längeren und dünnwandigen Wellengehäuses geführt und in einem beabstandeten Lagerträger mit und zwischen den Lagern angeordneten Gleitringdichtung gehalten ist. Mit dieser Form wird der Wärmeübergang zwischen Pumpengehäuse und Lagerträger reduziert. Durch die zusätzlich in den Entlastungsöffnungen gehaltenen drosselnden Einsätze entsteht hinter dem Laufrad ein höherer Druck. Dieser höhere Druck stellt sich entlang der Welle auch im Dichtungsraum des Lagerträgers ein und bedingt dort immer eine definierte Belastung der Wellenabdichtung. Mehrere Einsätze mit unterschiedlichen Durchmessern können auch ineinander gesteckt angeordnet sein. Mit dieser Maßnahme kann gezielt eine - auch nachträgliche - Anpassung eines Axialschubes oder seines Ausgleiches erreicht werden. Beispielsweise wenn sich für eine Kreiselpumpe die Anlagen-, Betriebsbedingungen- oder Einsatzbedingungen ändern.Even with centrifugal pumps for the promotion of hot fluids, such as heat transfer oils and the like, this solution has proven advantageous. Here, the pump housing with the pump impeller arranged therein is followed by a kind of thermal barrier. This provides a longer shaft, which is guided within a longer and thin-walled shaft housing and held in a spaced bearing support with and between the bearings arranged mechanical seal. With this form, the heat transfer between the pump housing and bearing carrier is reduced. By additionally held in the relief openings throttling inserts behind the impeller creates a higher pressure. This higher pressure arises along the shaft also in the sealing space of the bearing carrier and always requires there a defined load on the shaft seal. Several inserts with different diameters can also be arranged inserted one inside the other. With this measure, a targeted adaptation of an axial thrust or its compensation can be achieved. For example, if the system, operating conditions or operating conditions change for a centrifugal pump.
Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und werden im Folgenden näher beschrieben. Es zeigen die
- Figur 1:
- ein gegossenes Laufrad im Schnitt mit eingepresster Hülse und die
- Figur 2:
- ein Blechlaufrad mit eingepresster und umgeformter Hülse.
- FIG. 1:
- a cast impeller in section with pressed sleeve and the
- FIG. 2:
- a sheet metal wheel with pressed-in and formed sleeve.
Die
Ein vom Laufrad 1 gefördertes Fluid strömt vom Laufradeintritt 5 durch die von Schaufeln 6 begrenzte Schaufelkanäle 7 zum Laufradaustritt 8 und fließt in den Innenraum eines Gehäuses ab. Innerhalb des Gehäuses wirkt der am Laufradaustritt 8 vorherrschende Druck und übt in axialer Richtung sowohl auf die druckseitige Laufraddeckscheibe 3 als auch auf die gegenüberliegende saugseitige Laufraddeckscheibe 9 eine Kraft aus. Infolge der unterschiedlichen Größe von den Flächen der Laufraddeckscheiben ergibt sich durch den darauf einwirkenden Druck eine resultierende Axialkraft. Bei einer falschen Auslegung der Verhältnisse ergeben sich dadurch negative Auswirkungen auf die Lager von einer das Laufrad antreibenden Welle.A fluid conveyed by the
Ein Laufrad 1 ist gewöhnlich mit einer saugseitigen Spaltfläche 10 und druckseitigen Spaltfläche 11 versehen, denen gegenüberliegend stillstehende Gehäuse-Spaltflächen angeordnet sind, um somit Spaltdichtungen zwischen stillstehenden und rotierenden Teilen zu bilden. Auf der Druckseite DRS des Laufrades 1, also im Bereich der druckseitigen Deckscheibe 3, ist beispielhaft eine Spaltfläche 11 für eine Spaltdichtung angeordnet. Ein auf der Druckseite DRS befindliche Fluid fließt durch die Entlastungsöffnungen 4 zurück in den Bereich des Laufradeintritts 5 und den Bereich der Eintrittskanten der Schaufeln 6, wo ein niedriger Zulaufdruck herrscht. Die Summe vom Querschnitt der einzelnen Entlastungsöffnungen 4 ist so groß gewählt, dass diese einen definierten verbleibenden Restaxialschub gewährleistet. Dessen Größe soll bei allen möglichen Betriebszuständen die zulässige Lagerbelastung der in einem Lagerträger angeordneten Wälzlager nicht überschreiten. Die Anzahl der Entlastungsöffnungen 4 ist üblicherweise abhängig von der verwendeten Schaufelanzahl eines Laufrades 1 und den dadurch bedingten Anzahl der Schaufelkanäle.An
In der
Ein solcher drosselnder Einsatz kann bei einer Endmontage der Pumpe in einem Herstellerwerk angebracht werden, wenn die genauen Einsatzbedingungen für ein zu förderndes Fluid der Pumpe bekannt sind. Ebenso kann an einem späteren Einbauort der Pumpe eine Axialschubanpassung durch nachträglich Montage oder auch Demontage von ein oder mehreren Einsätzen 12 problemlos stattfinden. Als sehr gut geeignet für drosselnde Einsätze 12 haben sich federnd ausgebildete Spannhülsen erwiesen, die sich in einfachster Weise in vorhandene Entlastungsöffnungen 4 einsetzen lassen. Aufgrund der elastischen Formänderung der Einsätze 12 werden sie bei einer Montage elastisch im Durchmesser verkleinert und durch ihre Eigenspannung sicher in der Entlastungsbohrung 4 gehalten. Der somit verringerte Durchströmquerschnitt übt eine Drosselwirkung auf das hindurch- und abströmende Fluid aus, woraus im Radseitenraum auf der Pumpendruckseite DRS eine geringe Druckerhöhung resultiert. Mit dieser Druckerhöhung wird eine gezielte Druckbelastung für eine Wellenabdichtung erzeugt und damit deren unzulässiges Öffnen bei eventuellen Druckschwankungen vom Fluid erreicht. Ebenso ist damit eine genaue Einstellung einer axialen Lagerbelastung möglich.Such a throttling insert can be installed at a final assembly of the pump in a factory, if the exact operating conditions for a pumped fluid of the pump are known. Likewise, an axial thrust adjustment by retrofitting or disassembly of one or more inserts 12 can easily take place at a later installation location of the pump. As very suitable for throttling inserts 12 spring-trained clamping sleeves have proven that can be used in the simplest way in existing
Die
Claims (5)
- Centrifugal pump of single-stage or multiple-stage design, having a driven impeller or impellers arranged in the pump casing, and a shaft seal, one or more adjustable relief openings being arranged on at least one cover shroud of at least one impeller, characterized in that one or more sleeve-shaped inserts (12, 13) is or are arranged in one or more relief openings (4).
- Centrifugal pump according to Claim 1, characterized in that the insert (12) is configured as a clamping sleeve and is held in a relief opening (4) in an elastically deformable manner.
- Centrifugal pump according to Claim 1 or 2, characterized in that sleeves which are equipped with at least one radially projecting collar (14) are arranged as inserts (13) in centrifugal pumps with sheet-metal and/or plastic rotors (4).
- Centrifugal pump according to Claim 3, characterized in that the inserts (13) are held in a plastically deformable manner.
- Centrifugal pump according to one of Claims 1 to 4, characterized in that a plurality of inserts (12, 13) are arranged such that they are inserted into one another.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008062584A DE102008062584A1 (en) | 2008-12-16 | 2008-12-16 | Reducible discharge opening |
PCT/EP2009/008531 WO2010072307A1 (en) | 2008-12-16 | 2009-12-01 | Reducible relief opening |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2359009A1 EP2359009A1 (en) | 2011-08-24 |
EP2359009B1 true EP2359009B1 (en) | 2012-09-19 |
Family
ID=41674168
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09774627A Active EP2359009B1 (en) | 2008-12-16 | 2009-12-01 | Reducible relief opening |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP2359009B1 (en) |
CN (1) | CN102245904A (en) |
DE (1) | DE102008062584A1 (en) |
DK (1) | DK2359009T3 (en) |
WO (1) | WO2010072307A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN110925244A (en) * | 2019-12-13 | 2020-03-27 | 徐亮 | Low-noise shielding pump with axial force balance tube structure |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010026132A1 (en) * | 2010-07-05 | 2012-01-05 | Mahle International Gmbh | Rotor for liquid pump for cooling circuit of internal combustion engine, has pressure relief valve integrated into rotor and forming path depending on difference between pressure side and suction side, where back path opens pressure side |
CN109723668B (en) * | 2018-12-23 | 2023-04-07 | 无锡市华冷机械有限公司 | Mining pump impeller convenient to dismantle |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4938641B1 (en) * | 1970-08-06 | 1974-10-19 | ||
SU383892A1 (en) | 1971-03-04 | 1973-05-23 | Кишиневский завод герметических насосов М. В. Фрунзе | LRPASTNAYA MACHINE |
DE7132016U (en) * | 1971-08-21 | 1973-03-08 | Klein Schanzlin & Becker Ag | MULTI-LEVEL CRUMP WITH SELF-ACTING AXIAL THRUST COMPENSATION |
SU523994A1 (en) | 1974-11-05 | 1976-08-05 | Предприятие П/Я В-8721 | Blade machine |
DE2640990A1 (en) * | 1976-09-11 | 1978-03-16 | Klein Schanzlin & Becker Ag | Centrifugal pump with axially compensated impeller - has axially fixed balance ring behind axially free impeller |
DE8707360U1 (en) * | 1987-05-22 | 1987-07-09 | Deutsche Vortex GmbH, 7140 Ludwigsburg | Rotor for an electric motor |
JP3537349B2 (en) * | 1998-04-20 | 2004-06-14 | 日機装株式会社 | Thrust balance device |
CN2713185Y (en) * | 2004-07-22 | 2005-07-27 | 薛肇江 | Electric fuel vane pump impeller |
CN2742199Y (en) * | 2004-09-30 | 2005-11-23 | 上海东方泵业(集团)有限公司 | Regulator for blade wheel axial gap |
CN2929259Y (en) * | 2006-07-15 | 2007-08-01 | 李琢书 | Vane pump |
-
2008
- 2008-12-16 DE DE102008062584A patent/DE102008062584A1/en not_active Withdrawn
-
2009
- 2009-12-01 WO PCT/EP2009/008531 patent/WO2010072307A1/en active Application Filing
- 2009-12-01 DK DK09774627.5T patent/DK2359009T3/en active
- 2009-12-01 EP EP09774627A patent/EP2359009B1/en active Active
- 2009-12-01 CN CN2009801504296A patent/CN102245904A/en active Pending
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN110925244A (en) * | 2019-12-13 | 2020-03-27 | 徐亮 | Low-noise shielding pump with axial force balance tube structure |
Also Published As
Publication number | Publication date |
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EP2359009A1 (en) | 2011-08-24 |
DE102008062584A1 (en) | 2010-06-17 |
CN102245904A (en) | 2011-11-16 |
WO2010072307A1 (en) | 2010-07-01 |
DK2359009T3 (en) | 2013-01-02 |
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