EP1584820B1 - Mixed flow pump - Google Patents
Mixed flow pump Download PDFInfo
- Publication number
- EP1584820B1 EP1584820B1 EP04405214A EP04405214A EP1584820B1 EP 1584820 B1 EP1584820 B1 EP 1584820B1 EP 04405214 A EP04405214 A EP 04405214A EP 04405214 A EP04405214 A EP 04405214A EP 1584820 B1 EP1584820 B1 EP 1584820B1
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- EP
- European Patent Office
- Prior art keywords
- edge
- blade
- guide vane
- impeller
- screw
- 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.)
- Expired - Lifetime
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- 239000007787 solid Substances 0.000 claims abstract description 25
- 239000007788 liquid Substances 0.000 claims abstract description 6
- 238000000034 method Methods 0.000 claims abstract description 5
- 238000007792 addition Methods 0.000 claims 5
- 239000012530 fluid Substances 0.000 claims 1
- 239000000654 additive Substances 0.000 abstract 1
- 239000008247 solid mixture Substances 0.000 abstract 1
- 230000015572 biosynthetic process Effects 0.000 description 2
- 239000000470 constituent Substances 0.000 description 2
- 238000009825 accumulation Methods 0.000 description 1
- 238000009954 braiding Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000835 fiber Substances 0.000 description 1
- 239000011521 glass Substances 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 239000004033 plastic Substances 0.000 description 1
- 239000005060 rubber Substances 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 238000007493 shaping process Methods 0.000 description 1
- 239000011343 solid material Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
- 230000003313 weakening effect Effects 0.000 description 1
- 239000002023 wood Substances 0.000 description 1
Images
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
- F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous
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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
- F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D1/04—Helico-centrifugal pumps
Definitions
- the invention relates to a screw centrifugal pump according to the preamble of claim 1.
- the invention further relates to a method for conveying a medium with a fferenzentrifugalradpumpe according to the preamble of claim 8.
- a ringenzentrifugalradpumpe also known as worm gear, known.
- a centrifugal pump comprises a single, helically extending blade, which is rotatably arranged in a pump housing.
- This pump is particularly suitable for the promotion of interspersed with solid admixtures liquids, especially for the promotion of dirty water with langturaigen components.
- the invention has for its object to provide a fferenzentrifugalradpumpe, which has more advantageous properties in the promotion of interspersed with solid admixtures liquids.
- a screw centrifugal wheel pump comprising a pump housing with an inlet opening and an impeller arranged inside the pump housing, which has a spirally running inlet blade edge, wherein in the region of the inlet opening a guide blade protruding into the interior of the impeller is arranged, which has a vane edge, which protrudes increasingly in the direction of rotation of the impeller in the direction of the axis of rotation in the interior of the impeller.
- the screw centrifugal pump according to the invention is particularly advantageous in conveying higher concentrations of fibrous solids prone to plait formation. If the fibrous stranded solids concentration is always higher, this leads to bale formation and increased friction in the suction line in the impeller channel. If a certain limit value is reached, the hydraulic forces alone are no longer sufficient to convey the material, with the result that the screw centrifugal pump clogs and blocks.
- the inventive screw centrifugal pump prevents this blockage by the helical entry vane edge of the worm wheel start rotating with respect to the fixed projecting vane, with the entry vane edge and vane cooperating such that the intervening solid masses are captured by the rotating entry vane edge and loosened along the entry vane edge in the flow direction and / or pressed.
- a mechanical force acting essentially in the conveying direction is exerted on the conveyed medium, which prevents accumulation of solid constituents in the conveying path.
- the guide vane edge forms a fixed space curve and the inlet vane edge rotatable due to the rotatable fferenzentrifugalrades space curve, these two space curves are preferably mutually adapted extending configured that they are when rotating the impeller at mutually short distance or touching each other move past each other.
- the solids located between the two space curves are thereby mechanically moved in the direction of the space curves, and thereby substantially in the flow direction, and thereby loosened or pressed in the flow direction.
- the vane edge and / or the inlet vane edge at least partially on a cutting edge, so that the solids between the mutually moving space curves are also mechanically crushed.
- this causes crushing or dicing of the braids or fibers, which prevents attachment of the braids in the conveying path and thus ensures continuous, reliable operation of the fferenzentrifugalradpumpe without interruption.
- the mutual shear, separation or clamping effect of the two space curves also allows, depending on the design of the vane edge and / or the inlet blade edge, a cutting, crushing or weakening of fibrous solids such as paper, cords, wood or solids such as plastic, rubber, metal or glass.
- the fferenzentrifugalradpumpe 1 comprises a ringenzentrifugalrad 2, which is arranged about a rotation axis 2d rotatably in the direction of rotation 4a in a pump housing 3.
- the fferenzentrifugalrad 2 has a spiral-running inlet blade edge 2a and an outer contour 2c.
- the fferenzentrifugalrad 2 is fixedly connected to a pump shaft 4.
- the pump housing 3 comprises a suction cone housing part 3a, a spiral housing part 3b, an inlet opening 3c and an outlet opening 3d.
- a guide vane 5 with a vane edge 5a protruding into the interior of the pump housing 3 and into the interior of the screw centrifugal wheel 2 is fixedly arranged.
- the term "interior of the impeller 2" in the present document is understood to mean the interior which is bounded by the external contour 2c when the centrifugal centrifugal wheel 2 rotates, so that the guide vane 5 extends at least partially into this internal space, and the centrifugal impeller 2 as shown in FIG. in the region of its tip or within the maximum extent of the helical gear portion 6a, the guide blade 5 is orbited outside.
- the fferenzentrifugalradpumpe 1 also includes a ringradanteil 6a and a Zentrifugalradanteil 6b. The pumped with the pump 1 medium flows in the flow direction S.
- FIG. 2 shows, from the direction indicated by A in FIG. 1, a front view of the inlet opening 3c, the impeller 2 and the guide blade 5 being recognizable inside the pump 1.
- the impeller 2 shows the spiraling inlet blade edge 2a, which falls off against the axis of rotation 2d and grows axially into it. The foremost portion of the inlet blade edge 2a is not directly visible because of the vane 5 and therefore shown in dashed lines.
- the vane 5 is designed in such a way that the vane edge 5 a protrudes progressively in the direction of rotation 4 a in the direction of the axis of rotation 2 d into the interior of the impeller 2, both in the radial and in the axial direction.
- the vane edge 5a forms a fixed space curve, whereas the inlet vane edge 2a forms a space curve rotatable about the wheel axis 2d.
- These two space curves 2 a, 5 a are designed to be mutually adapted in the illustrated exemplary embodiment such that the vane edge 5 a has a vane edge section 5 b and the inlet vane edge 2 a has a vane edge section 2 b within which the vane edge 5 a and the inlet vane edge 2 a depend on the respective position of the impeller 2 have mutually small distance or touch each other.
- the mutually small distance may for example have a value between 0.1 and 30 mm. This position with mutually least distance is shown with the point P1 on the blade edge portion 2b and the P2 on the vane edge portion 5b.
- the guide blade 5 can be arranged and configured in various ways in the pump housing 3 such that the stationary guide blade edge 5a and the rotating inlet blade edge 2a cooperate such that solids are mechanically conveyed by the mutual cooperation of the edges 2a, 5a, in particular in the flow direction S.
- the blade edge section 2b has a tangent T1 at the point P1 and the guide blade edge section 5b has a tangent T2 at the point P2, these two tangents T1, T2 having a cutting angle ⁇ as viewed from the inlet opening 3c.
- This angle ⁇ is at least 10 degrees, and is preferably between 30 degrees and 150 degrees, in particular between 60 degrees and 120 degrees.
- the angle ⁇ is preferably never smaller than the angle at which a sliding of the solid on the inlet blade edge 2a or between the inlet blade edge 2a and the vane edge 5a is no longer guaranteed.
- FIGS. 3 and 4 show, in two detailed views, analogous to the illustration according to FIG. 2, two differently extending space curves or inlet blade edge 2a and guide blade edge 5a, the enclosed angle ⁇ of the tangents T1, T2 of the points P1, P2 in FIG in Figure 4 is about 90 degrees.
- This angle ⁇ is determined by the course of the space curves 2a, 5a, and thus can be selected accordingly in the construction of the fferenzentrifugalradpumpe 1.
- the course of the space curves 2a, 5a can be selected such that the angle ⁇ remains substantially constant during the movement of the points P1, P2 in the direction Q2.
- the angle ⁇ during the movement of the points P1, P2 in the direction Q2 also increase and / or decrease.
- At least part of the blade edge section 2b and / or the blade edge section 5b is designed as an edge, cutting edge or blade in order to weaken or sever a solid which is located between the sections 2b, 5b.
- the length of the effective edge sections 2b, 5b can also be determined by appropriate shaping.
- the fferenzentrifugalradpumpe can be optimized in accordance with the expected solids and admixtures, that the edge portions 2b, 5b and their angle ⁇ is selected to be optimized in order to prevent clogging of the pump and, for example, also to achieve a good pump efficiency.
- FIG. 5 shows a further exemplary embodiment of a screw centrifugal pump 1, in whose inlet opening 3c a wear-resistant sleeve 7 is arranged, which is fixedly connected to the guide blade 5. With a fastening means, not shown, the sleeve 7 can be firmly connected to the pump housing 3.
- the sleeve 7 and thus the vane 5 in the direction of movement R is displaced.
- This arrangement has the particular advantage that the distance between the inlet blade edge 2a and the vane edge 5a, in particular the distance between the points P1, P2 in the direction R and Q1 is adjustable.
- the inlet blade edge 2a and / or the vane edge 5a wears off during operation of the pump, so that the distance between the points P1, P2 increases during operation with time.
- the sleeve 7 thus makes it possible to readjust the position of the guide vane 5 in the direction of displacement R or Q 1 after certain time intervals.
- the sleeve 7 can also be designed such that it can also be rotated in the inlet opening 3c, i. with respect to the wheel axle 2d is rotatable to rotate the sleeve 7 in the released state, and thus also to rotate the position of the guide vane 5.
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- Structures Of Non-Positive Displacement Pumps (AREA)
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Abstract
Description
Die Erfindung betrifft eine Schraubenzentrifugalradpumpe gemäss dem Oberbegriff von Anspruch 1. Die Erfindung betrifft weiter ein Verfahren zum Fördern eines Mediums mit einer Schraubenzentrifugalradpumpe gemäss dem Oberbegriff von Anspruch 8.The invention relates to a screw centrifugal pump according to the preamble of
Aus der Druckschrift CH 394814 ist eine Schraubenzentrifugalradpumpe, auch als Schneckenradpumpe bezeichnet, bekannt. Eine derartige Kreiselpumpe umfasst eine einzige, schraubenförmig verlaufende Schaufel, welche drehbar in einem Pumpengehäuse angeordnet ist. Diese Pumpe ist insbesondere zur Förderung von mit festen Beimengungen durchsetzten Flüssigkeiten geeignet, insbesondere zur Förderung von Schmutzwasser mit langfaserigen Bestandteilen.From the document CH 394814 a Schraubenzentrifugalradpumpe, also known as worm gear, known. Such a centrifugal pump comprises a single, helically extending blade, which is rotatably arranged in a pump housing. This pump is particularly suitable for the promotion of interspersed with solid admixtures liquids, especially for the promotion of dirty water with langfaserigen components.
Die Fördermöglichkeit von Flüssigkeiten mit hoher Konzentration an faserigen, beispielsweise zur Zopfbildung neigenden Feststoffen ist begrenzt. Dies kann Anlagerungen fester Bestandteile im Förderweg oder eine dadurch hervorgerufene Verstopfung bis hin zum Pumpenstillstand zur Folge haben.The delivery of liquids with a high concentration of fibrous, for example, prone to braiding solids is limited. This can lead to deposits of solid constituents in the conveying path or a consequent blockage up to the pump standstill result.
Der Erfindung liegt die Aufgabe zugrunde, eine Schraubenzentrifugalradpumpe zu schaffen, die beim Fördern von mit festen Beimengungen durchsetzten Flüssigkeiten vorteilhaftere Eigenschaften aufweist.The invention has for its object to provide a Schraubenzentrifugalradpumpe, which has more advantageous properties in the promotion of interspersed with solid admixtures liquids.
Diese Aufgabe wird gelöst mit einer Schraubenzentrifugalradpumpe aufweisend die Merkmale von Anspruch 1. Die Unteransprüche 2 bis 8 betreffen weitere, vorteilhafte Ausgestaltungen. Die Aufgabe wird weiter gelöst mit einem Verfahren aufweisend die Merkmale von Anspruch 8.This object is achieved with a Schraubenzentrifugalradpumpe having the features of
Die Aufgabe wird insbesondere gelöst mit einer Schraubenzentrifugalradpumpe umfassend ein Pumpengehäuse mit einer Eintrittsöffnung sowie ein innerhalb des Pumpengehäuses angeordnetes Laufrad, welches eine spiralförmig verlaufende Eintrittsschaufelkante aufweist, wobei im Bereich der Eintrittsöffnung eine in den Innenraum des Laufrades vorstehende Leitschaufel angeordnet ist, die eine Leitschaufelkante aufweist, welche in Drehrichtung des Laufrades zunehmend in Richtung der Drehachse in den Innenraum des Laufrades vorsteht.The object is achieved in particular with a screw centrifugal wheel pump comprising a pump housing with an inlet opening and an impeller arranged inside the pump housing, which has a spirally running inlet blade edge, wherein in the region of the inlet opening a guide blade protruding into the interior of the impeller is arranged, which has a vane edge, which protrudes increasingly in the direction of rotation of the impeller in the direction of the axis of rotation in the interior of the impeller.
Die erfindungsgemässe Schraubenzentrifugalradpumpe ist insbesondere vorteilhaft beim Fördern höherer Konzentration von faserigen zu Zopfbildung neigenden Feststoffen. Wird die faserige angeschwemmte Feststoffkonzentration immer höher, so führt dies in der Saugleitung zu einer Ballenbildung und einer erhöhten Reibung im Laufradkanal. Wird dabei ein gewisser Grenzwert erreicht, so genügen die hydraulischen Kräfte alleine nicht mehr um das Material zu fördern, was zur Folge hat, dass die Schraubenzentrifugalradpumpe verstopft und blockiert. Die erfindungsgemässe Schraubenzentrifugalradpumpe verhindert dieses Blockieren indem sich die spiralförmige Eintrittsschaufelkante des Schneckenradanfangs gegenüber der fest angeordneten, vorstehenden Leitschaufel dreht, wobei die Eintrittsschaufelkante und die Leitschaufel derart zusammenwirken, dass die sich dazwischen befindlichen Feststoffmassen durch die rotierende Eintrittsschaufelkante erfasst werden und in Flussrichtung entlang der Eintrittsschaufelkante aufgelockert und/oder gepresst werden. Durch dieses Zusammenwirken von Leitschaufel und Schraubenzentrifugalrad wird auf das geförderte Medium zusätzlich zu den hydraulischen Kräften noch eine mechanische, im wesentlichen in Förderrichtung wirkende Kraft ausgeübt, was eine Anlagerung fester Bestandteile im Förderweg verhindert.The screw centrifugal pump according to the invention is particularly advantageous in conveying higher concentrations of fibrous solids prone to plait formation. If the fibrous stranded solids concentration is always higher, this leads to bale formation and increased friction in the suction line in the impeller channel. If a certain limit value is reached, the hydraulic forces alone are no longer sufficient to convey the material, with the result that the screw centrifugal pump clogs and blocks. The inventive screw centrifugal pump prevents this blockage by the helical entry vane edge of the worm wheel start rotating with respect to the fixed projecting vane, with the entry vane edge and vane cooperating such that the intervening solid masses are captured by the rotating entry vane edge and loosened along the entry vane edge in the flow direction and / or pressed. As a result of this interaction between the guide vane and the screw centrifugal wheel, in addition to the hydraulic forces, a mechanical force acting essentially in the conveying direction is exerted on the conveyed medium, which prevents accumulation of solid constituents in the conveying path.
In einer weiteren vorteilhaften Ausgestaltung bildet die Leitschaufelkante eine feste Raumkurve und die Eintrittsschaufelkante eine auf Grund des rotierbaren Schraubenzentrifugalrades rotierbare Raumkurve, wobei diese beiden Raumkurven vorzugsweise derart gegenseitig angepasst verlaufend ausgestaltet sind, dass sich diese beim Rotieren des Laufrades unter gegenseitig geringem Abstand oder sich gegenseitig berührend aneinander vorbei bewegen. Die sich zwischen den beiden Raumkurven befindlichen Feststoffe werden dabei mechanisch in Verlaufsrichtung der Raumkurven, und dadurch im wesentlichen in Strömungsrichtung bewegt, und dabei aufgelockert oder in Strömungsrichtung gepresst.In a further advantageous embodiment, the guide vane edge forms a fixed space curve and the inlet vane edge rotatable due to the rotatable Schraubenzentrifugalrades space curve, these two space curves are preferably mutually adapted extending configured that they are when rotating the impeller at mutually short distance or touching each other move past each other. The solids located between the two space curves are thereby mechanically moved in the direction of the space curves, and thereby substantially in the flow direction, and thereby loosened or pressed in the flow direction.
In einer weiteren vorteilhaften Ausgestaltung weisen die Leitschaufelkante und/oder die Eintrittsschaufelkante zumindest teilweise eine Schneidkante auf, sodass die Feststoffe zwischen den sich gegenseitig bewegenden Raumkurven zudem noch mechanisch zerkleinert werden. Bei zu Zopfbildung neigenden Feststoffen bewirkt dies ein Zerkleinern oder Zertrennen der Zöpfe bzw. Fasern, was eine Anlagerung der Zöpfe im Förderweg verhindert und somit einen kontinuierlichen, zuverlässigen Betrieb der Schraubenzentrifugalradpumpe ohne Unterbruch gewährleistet.In a further advantageous embodiment, the vane edge and / or the inlet vane edge at least partially on a cutting edge, so that the solids between the mutually moving space curves are also mechanically crushed. In solids prone to plait this causes crushing or dicing of the braids or fibers, which prevents attachment of the braids in the conveying path and thus ensures continuous, reliable operation of the Schraubenzentrifugalradpumpe without interruption.
Die gegenseitige Scher-, Trenn- oder Klemmwirkung der beiden Raumkurven ermöglich auch, abhängig von der Ausgestaltung der Leitschaufelkante und/oder der Eintrittsschaufelkante, ein Durchtrennen, Zerkleinern oder Schwächen von faserförmigen Feststoffen wie Papier, Schnüren, Holz oder Feststoffen wie Kunststoff, Gummi, Metall oder Glas.The mutual shear, separation or clamping effect of the two space curves also allows, depending on the design of the vane edge and / or the inlet blade edge, a cutting, crushing or weakening of fibrous solids such as paper, cords, wood or solids such as plastic, rubber, metal or glass.
Die Erfindung wird nachfolgend an Hand von Ausführungsbeispielen im Detail beschrieben. Es zeigen:
Figur 1- einen Axialschnitt durch eine Schraubenzentrifugalradpumpe;
Figur 2- eine Frontansicht der Eintrittsöffnung der Schraubenzentrifugalradpumpe;
Figur 3 und 4- zwei unterschiedliche Gesamtwinkel von Eintrittsschaufelkante und Leitschaufelkante;
Figur 5- eine verschiebbar angeordnete Leitschaufel.
- FIG. 1
- an axial section through a Schraubenzentrifugalradpumpe;
- FIG. 2
- a front view of the inlet opening of the Schraubenzentrifugalradpumpe;
- FIGS. 3 and 4
- two different total angles of entrance blade edge and vane edge;
- FIG. 5
- a slidably disposed vane.
Die Schraubenzentrifugalradpumpe 1 gemäss Figur 1 umfasst ein Schraubenzentrifugalrad 2, welches um eine Drehachse 2d in Drehrichtung 4a drehbar in einem Pumpengehäuse 3 angeordnet ist. Das Schraubenzentrifugalrad 2 weist eine spiralförmig verlaufende Eintrittsschaufelkante 2a sowie eine Aussenkontur 2c auf. Das Schraubenzentrifugalrad 2 ist mit einer Pumpenwelle 4 fest verbunden. Das Pumpengehäuse 3 umfasst ein Saugkonusgehäuseteil 3a, ein Spiralgehäuseteil 3b, eine Eintrittsöffnung 3c sowie eine Austrittsöffnung 3d. Im Bereich der Eintrittsöffnung 3c ist eine in den Innenraum des Pumpengehäuses 3 sowie in den Innenraum des Schraubenzentrifugalrades 2 vorstehende Leitschaufel 5 mit Leitschaufelkante 5a fest angeordnet. Unter "Innenraum des Laufrades 2" wird im vorliegenden Dokument der Innenraum verstanden, welcher bei rotierendem Schraubenzentrifugalrad 2 von der Aussenkontur 2c umgrenzt wird, sodass sich die Leitschaufel 5 zumindest teilweise in diesen Innenraum erstreckt, und das Schraubenzentrifugalrad 2, wie in Figur 1 dargestellt, im Bereich von dessen Spitze bzw. maximal innerhalb des Schraubenradanteils 6a die Leitschaufel 5 aussen umkreist. Die Schraubenzentrifugalradpumpe 1 umfasst zudem einen Schraubenradanteil 6a sowie einen Zentrifugalradanteil 6b. Das mit der Pumpe 1 geförderte Medium strömt in Strömungsrichtung S.The
Figur 2 zeigt aus der in Figur 1 mit A bezeichneten Richtung eine Frontansicht der Eintrittsöffnung 3c, wobei im Innern der Pumpe 1 das Laufrad 2 sowie die Leitschaufel 5 erkennbar ist. Beim Laufrad 2 ist die spiralförmig verlaufende Eintrittsschaufelkante 2a ersichtlich, welche gegen die Drehachse 2d hin abfällt und axial in diese hineinwächst. Der vorderste Abschnitt der Eintrittsschaufelkante 2a ist wegen der Leitschaufel 5 nicht direkt sichtbar und deshalb strichliert dargestellt.FIG. 2 shows, from the direction indicated by A in FIG. 1, a front view of the inlet opening 3c, the
In den Figuren 1 und 2 ist die Leitschaufel 5 derart ausgestaltet, dass die Leitschaufelkante 5a in Drehrichtung 4a zunehmend in Richtung der Drehachse 2d, sowohl in radialer als auch in axialer Richtung, in den Innenraum des Laufrades 2 vorsteht. Die Leitschaufelkante 5a bildet eine feste Raumkurve, wogegen die Eintrittsschaufelkante 2a eine um die Radachse 2d rotierbare Raumkurve bildet. Diese beiden Raumkurven 2a,5a sind im dargestellten Ausführungsbeispiel derart gegenseitig angepasst verlaufend ausgestaltet, dass die Leitschaufelkante 5a einen Leitschaufelkantenabschnitt 5b und die Eintrittsschaufelkante 2a einen Schaufelkantenabschnitt 2b aufweist, innerhalb welchen die Leitschaufelkante 5a und die Eintrittsschaufelkante 2a abhängig von der jeweiligen Stellung des Laufrades 2 einen gegenseitig geringen Abstand aufweisen oder sich gegenseitig berühren. Der gegenseitig geringe Abstand kann beispielsweise einen Wert zwischen 0,1 und 30 mm aufweisen. Diese Stellung mit gegenseitig geringstem Abstand ist mit dem Punkt P1 auf dem Schaufelkantenabschnitt 2b sowie dem P2 auf den Leitschaufelkantenabschnitt 5b dargestellt. Auf Grund der Rotation des Laufrades 2 in Drehrichtung 4a bewegen sich die Punkt P1, P2 in der in Figur 1 dargestellten Ansicht im wesentlichen in Richtung Q 1 der Drehachse 2d, und in der in Figur 2 dargestellten Ansicht im wesentlichen in Richtung Q2, welche dem Verlauf der Leitschaufelkante 5a entspricht. Dadurch wird ein sich zwischen dem Schaufelkantenabschnitt 2b und dem Leitschaufelkantenabschnitt 5b befindlicher Feststoff mechanisch im wesentlichen in Richtung Q1 beziehungsweise in Strömungsrichtung S gefördert.In FIGS. 1 and 2, the
Die Leitschaufel 5 kann auf unterschiedlichste Weise derart im Pumpengehäuse 3 angeordnet und ausgestaltet sein, dass die feststehende Leitschaufelkante 5a und die rotierende Eintrittsschaufelkante 2a derart zusammenwirken, dass Feststoffe durch das gegenseitige Zusammenwirken der Kanten 2a, 5a mechanisch gefördert werden, insbesondere in Strömungsrichtung S.The
Wie aus Figur 2 ersichtlich weist der Schaufelkantenabschnitt 2b im Punkt P1 eine Tangente T1 auf und der Leitschaufelkantenabschnitt 5b im Punkt P2 eine Tangente T2 auf, wobei diese beiden Tangenten T1,T2 wie dargestellt von der Eintrittsöffnung 3c aus betrachtet einen Schnittwinkel α aufweisen. Dieser Winkel α beträgt zumindest 10 Grad, und liegt vorzugsweise zwischen 30 Grad und 150 Grad, insbesondere zwischen 60 Grad und 120 Grad. Der Winkel α ist vorzugweise nie kleiner als derjenige Winkel, bei welchem ein Gleiten des Feststoffes auf der Eintrittsschaufelkante 2a bzw. zwischen Eintrittsschaufelkante 2a und Leitschaufelkante 5a nicht mehr gewährleistet ist.As can be seen from FIG. 2, the blade edge section 2b has a tangent T1 at the point P1 and the guide blade edge section 5b has a tangent T2 at the point P2, these two tangents T1, T2 having a cutting angle α as viewed from the inlet opening 3c. This angle α is at least 10 degrees, and is preferably between 30 degrees and 150 degrees, in particular between 60 degrees and 120 degrees. The angle α is preferably never smaller than the angle at which a sliding of the solid on the inlet blade edge 2a or between the inlet blade edge 2a and the
Die Figuren 3 und 4 zeigen in zwei Detailansichten, analog zur Darstellung gemäss Figur 2, zwei unterschiedlich verlaufende Raumkurven bzw. Eintrittsschaufelkante 2a und Leitschaufelkante 5a, wobei der umschlossene Winkel α der TangentenT1, T2 der Punkte P1,P2 in Figur 3 etwa 110 Grad und in Figur 4 etwa 90 Grad beträgt. Dieser Winkel α ist durch den Verlauf der Raumkurven 2a, 5a bestimmt, und kann somit bei der Konstruktion der Schraubenzentrifugalradpumpe 1 entsprechend gewählt werden. Der Verlauf der Raumkurven 2a,5a kann derart gewählt werden, dass der Winkel α während der Bewegung der Punkte P1,P2 in Richtung Q2 im wesentlichen konstant bleibt. Durch entsprechend verlaufende Raumkurven 2a,5a kann der Winkel α während der Bewegung der Punkte P1, P2 in Richtung Q2 auch zu- und/oder abnehmen.FIGS. 3 and 4 show, in two detailed views, analogous to the illustration according to FIG. 2, two differently extending space curves or inlet blade edge 2a and
In einer vorteilhaften Ausgestaltung ist zumindest ein Teil des Schaufelkantenabschnittes 2b und/oder des Leitschaufelkantenabschnittes 5b als Kante, Schneidkante oder Klinge ausgestaltet, um einen Feststoff, welcher sich zwischen den Abschnitten 2b,5b befindet, zu schwächen oder zu durchtrennen.In an advantageous embodiment, at least part of the blade edge section 2b and / or the blade edge section 5b is designed as an edge, cutting edge or blade in order to weaken or sever a solid which is located between the sections 2b, 5b.
Generell gilt, je grösser der Winkel α gewählt ist, desto mehr wird ein Feststoff entlang der Kantenabschnitte 2b,5b geschoben, beziehungsweise je kleiner der Winkel α gewählt wird, desto eher wird ein Feststoff durch die Kantenabschnitte 2b, 5b zertrennt. Zusätzlich kann durch eine entsprechende Formgebung auch die Länge der wirksamen Kantenabschnitte 2b, 5b bestimmt werden. Somit kann die Schraubenzentrifugalradpumpe entsprechend den zu erwartenden Feststoffen und Beimengungen dadurch optimiert werden, dass die Kantenabschnitte 2b, 5b und deren Winkel α entsprechend optimiert gewählt wird, um ein Verstopfen der Pumpe zu verhindern und beispielsweise zudem einen guten Pumpenwirkungsgrad zu erzielen.In general, the greater the angle α is selected, the more a solid is pushed along the edge sections 2b, 5b, or the smaller the angle α is chosen, the sooner a solid is split by the edge sections 2b, 5b. In addition, the length of the effective edge sections 2b, 5b can also be determined by appropriate shaping. Thus, the Schraubenzentrifugalradpumpe can be optimized in accordance with the expected solids and admixtures, that the edge portions 2b, 5b and their angle α is selected to be optimized in order to prevent clogging of the pump and, for example, also to achieve a good pump efficiency.
Figur 5 zeigt ein weiteres Ausführungbeispiel einer Schraubenzentrifugalradpumpe 1, in deren Eintrittsöffnung 3c eine verschleissfeste Hülse 7 angeordnet ist, welche mit der Leitschaufel 5 fest verbunden ist. Mit einem nicht dargestellten Befestigungsmittel kann die Hülse 7 fest mit dem Pumpengehäuse 3 verbunden werden.FIG. 5 shows a further exemplary embodiment of a screw
Bei gelöstem Befestigungsmittel ist die Hülse 7 und damit auch die Leitschaufel 5 in Bewegungsrichtung R verschiebbar. Diese Anordnung weist insbesondere den Vorteil auf, dass die Distanz zwischen Eintrittsschaufelkante 2a und Leitschaufelkante 5a, insbesondere der Abstand der Punkte P1,P2 in Richtung R bzw. Q1 einstellbar ist. Die Eintrittsschaufelkante 2a und/oder die Leitschaufelkante 5a nutzt sich während dem Betrieb der Pumpe ab, sodass sich der Abstand der Punkte P1,P2 während dem Betrieb mit der Zeit vergrössert. Die Hülse 7 ermöglicht somit die Lage der Leitschaufel 5 in Verschiebungsrichtung R bzw. Q 1 nach gewissen Zeitabständen wieder neu einzustellen. Die Hülse 7 kann auch derart ausgestaltet sein, dass diese zudem in der Eintrittsöffnung 3c rotierbar, d.h. bezüglich der Radachse 2d rotierbar ist, um die Hülse 7 im gelösten Zustand zu rotieren, und damit auch die Lage der Leitschaufel 5 zu rotieren.When dissolved fastener, the sleeve 7 and thus the
Claims (9)
- Screw-centrifugal pump (1) comprising a pump housing (3) having an inlet opening (3c) and also an impeller (2) arranged within the pump housing (3) and rotatable about an axis of rotation (2d) in a direction of rotation (4a), the impeller (2) having a spirally extending blade entry edge (2a), characterized in that a guide vane (5) projecting into the interior space of the impeller (2) is disposed in the region of the inlet opening (3c), and that the guide vane (5) has a guide vane edge (5a) which, in the direction of rotation (4a), increasingly projects in the direction of the axis of rotation (2d) into the interior space of the impeller (2), and that the impeller (2) and the guide vane (5) are arranged to interact in such a way that at least part of the solid additions are moved along the blade entry edge.
- Screw-centrifugal pump (1) in accordance with claim 1, characterized in that the guide vane (5) is displaceable in the direction of the axis of rotation (2d) and fixably mounted.
- Screw-centrifugal pump (1) in accordance with one of the proceeding claims, characterized in that the guide vane edge (5a) forms a fixed three-dimensional curve, in that the blade entry edge (2a) forms a rotatable three-dimensional curve and that these two three-dimensional curves are designed and extend in a mutually matched manner such the guide blade edge (5a) has a guide blade edge section (5b) and the blade entry edge (2a) has a blade edge section (2b) in which the guide vane edge (5a) and the blade entry edge (2a) have a mutual spacing depending on the position of the impeller (2) or mutually touch one another.
- Screw-centrifugal pump (1) in accordance with claim 3, characterized in that a respective point (P1, P2) results within both the blade edge section (2b) and also within the guide vane edge section (5b) which have the smallest mutual spacing between the blade edge section (2b) and the guide vane edge section (5b), with these points (P1, P2) moving in the flow direction (S) on rotation of the impeller (2).
- Screw-centrifugal pump (1) in accordance with claim 4, characterized in that the blade edge section (2b) has a tangent (T1) at the point (P1), in that the guide vane edge section (5b) has a tangent (T2) at the point (P2) and in that these two tangents (T1, T2) form an intersection angle (α) of at least 10 degrees when considered from the inlet opening (3c).
- Screw-centrifugal pump (1) in accordance with claim 5, characterized in that the intersection angle (α) lies between 30 degrees and less than 180 degrees, in particular between 60 degrees and 120 degrees.
- Screw-centrifugal pump (1) in accordance with one of the claims 3 to 6, characterized in that the blade edge section (2b) and/or the guide vane edge section (5b) is formed at least partly as a cutting edge.
- Method for the conveying of a liquid permeated with solid additions by means of a screw-centrifugal pump (1) the impeller (2) having a spirally extending blade entry edge (2a), characterized in that the liquid is directed with the aid of a guide vane (5) to the blade entry edge (2a) of a rotating impeller (2) in such a way that at least one part of the solid additions slides along the blade entry edge, such that the solid additions are moved mechanically in flow direction of the fluid by the impact of the blade entry edge (2a).
- Method in accordance with claim 8, characterized in that a guide vane edge (5a) of the guide vane (5) and the blade entry edge (2a) mutually cooperate when the impeller (2) is rotating such that the solid addition located between the blade entry edge (2a) and the guide vane edge (5a) is mechanically comminuted by the blade and vane edges (2a, 5a) and/or shifted in the flow direction (S).
Priority Applications (9)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP04405214A EP1584820B1 (en) | 2004-04-07 | 2004-04-07 | Mixed flow pump |
| DK04405214T DK1584820T3 (en) | 2004-04-07 | 2004-04-07 | screw-centrifugal pump |
| AT04405214T ATE330126T1 (en) | 2004-04-07 | 2004-04-07 | SCREW CENTRIFUGAL WHEEL PUMP |
| DE502004000769T DE502004000769D1 (en) | 2004-04-07 | 2004-04-07 | Screw-centrifugal pump |
| PCT/CH2004/000664 WO2005098237A1 (en) | 2004-04-07 | 2004-11-02 | Screw-centrifugal pump |
| CNB2004800426761A CN100419271C (en) | 2004-04-07 | 2004-11-02 | Screw-centrifugal pump |
| RU2006139075/06A RU2358159C2 (en) | 2004-04-07 | 2004-11-02 | Screw centrifugal pump |
| JP2007506630A JP5070039B2 (en) | 2004-04-07 | 2004-11-02 | Screw centrifugal pump and method for transporting liquid filled with solid additives using screw centrifugal pump |
| US10/588,736 US7510368B2 (en) | 2004-04-07 | 2004-11-02 | Screw-centrifugal pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP04405214A EP1584820B1 (en) | 2004-04-07 | 2004-04-07 | Mixed flow pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1584820A1 EP1584820A1 (en) | 2005-10-12 |
| EP1584820B1 true EP1584820B1 (en) | 2006-06-14 |
Family
ID=34896183
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP04405214A Expired - Lifetime EP1584820B1 (en) | 2004-04-07 | 2004-04-07 | Mixed flow pump |
Country Status (9)
| Country | Link |
|---|---|
| US (1) | US7510368B2 (en) |
| EP (1) | EP1584820B1 (en) |
| JP (1) | JP5070039B2 (en) |
| CN (1) | CN100419271C (en) |
| AT (1) | ATE330126T1 (en) |
| DE (1) | DE502004000769D1 (en) |
| DK (1) | DK1584820T3 (en) |
| RU (1) | RU2358159C2 (en) |
| WO (1) | WO2005098237A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2169234A2 (en) | 2007-07-17 | 2010-03-31 | Gerardus Augustinus Maria Manshanden | Sinking pump safe for fish |
| CN112636910A (en) * | 2020-12-29 | 2021-04-09 | 北京深思数盾科技股份有限公司 | Method, device and system for generating and verifying temporary password |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP5404140B2 (en) * | 2009-04-01 | 2014-01-29 | 株式会社東芝 | Template and semiconductor device manufacturing method |
| US8506236B2 (en) * | 2009-08-03 | 2013-08-13 | Ebara International Corporation | Counter rotation inducer housing |
| US8550771B2 (en) * | 2009-08-03 | 2013-10-08 | Ebara International Corporation | Inducer for centrifugal pump |
| US20110027071A1 (en) * | 2009-08-03 | 2011-02-03 | Ebara International Corporation | Multi-stage inducer for centrifugal pumps |
| US9631622B2 (en) * | 2009-10-09 | 2017-04-25 | Ebara International Corporation | Inducer for centrifugal pump |
| EP2397698B1 (en) * | 2010-06-17 | 2012-09-26 | Frideco AG | Conveying device |
| CN102400919A (en) * | 2011-11-18 | 2012-04-04 | 江苏国泉泵业制造有限公司 | Solid-liquid two-phase flow spiral centrifugal pump |
| CN102661282A (en) * | 2012-04-16 | 2012-09-12 | 杭州萧山美特轻工机械有限公司 | Open type spiral paper pulp pump |
| CN103195755B (en) * | 2013-04-11 | 2015-10-07 | 南京布鲁克林环保设备有限公司 | A kind of single blade screw centrifugal impeller |
| EP2894342B1 (en) * | 2014-01-12 | 2016-12-28 | Alfa Laval Corporate AB | Self-priming centrifugal pump |
| DK2894343T3 (en) | 2014-01-12 | 2017-12-11 | Alfa Laval Corp Ab | SELF-TILTING CENTRIFUGAL PUMP |
| US10094384B2 (en) | 2014-01-24 | 2018-10-09 | Mcfinn Technologies, Llc | Radial impeller and casing for centrifugal pump |
| KR102231079B1 (en) * | 2014-07-08 | 2021-03-24 | 엘지전자 주식회사 | Drain pump assembly and dryer for clothes having the same |
| KR101588137B1 (en) * | 2014-10-24 | 2016-01-22 | 엘지전자 주식회사 | Drain pump assembly and dryer for clothes having the same |
| DE102020125805A1 (en) * | 2020-10-02 | 2022-04-07 | Frideco Ag | Pump system and method of operating a pump system |
| CN115994394B (en) * | 2023-02-21 | 2023-11-17 | 上海中韩杜科泵业制造有限公司 | Centrifugal pump impeller molding method, device and equipment |
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| CH394814A (en) * | 1961-08-29 | 1965-06-30 | Staehle Marin | Worm gear pump |
| AT255912B (en) * | 1964-07-01 | 1967-07-25 | Schlesiger & Co Kg Feluwa | Dirty water centrifugal pump |
| GB1315547A (en) | 1969-05-23 | 1973-05-02 | Staehle M | Axial flow pump for pumping liquids containing solids in suspension |
| JPS5136721Y2 (en) * | 1973-09-06 | 1976-09-09 | ||
| JPS5357507A (en) * | 1976-11-04 | 1978-05-24 | Kubota Ltd | Cutter underwater pumps |
| FR2460404A1 (en) | 1979-07-05 | 1981-01-23 | Schneider Hans Ulrich | Sludge pump impeller with worm portion - which is at inlet end leading into spiral duct at delivery end |
| SU1132062A1 (en) | 1983-03-10 | 1984-12-30 | Научно-Исследовательский И Конструкторско-Технологический Институт Городского Хозяйства | Centrifugal pump for conveying heterogeneous media |
| SU1286817A1 (en) | 1985-04-09 | 1987-01-30 | Центральный Научно-Исследовательский И Проектно-Технологический Институт Механизации И Электрификации Животноводства Южной Зоны Ссср | Pump |
| ES2015517B3 (en) * | 1986-02-14 | 1991-04-16 | Rohren- Und Pumpenwerk Rudolf Bauer Ag | SELF-ASPIRATING CENTRIFUGAL PUMP FOR TREATMENT AND TRANSPORTATION OF LIQUIDS WITH HIGH CONTENT IN FIBER. |
| US4778336A (en) * | 1987-07-09 | 1988-10-18 | Weil Pump Company | Cutter pump subassembly |
| SU1677371A1 (en) | 1989-06-08 | 1991-09-15 | А. Э. Кин, О. В. Дадашев и А. И. Рудштейн | Pump for pumping heterogeneous medium |
| CN2388377Y (en) * | 1999-08-06 | 2000-07-19 | 山东青州市南张石油机械厂 | Pre-shearing device of shear pump |
-
2004
- 2004-04-07 DK DK04405214T patent/DK1584820T3/en active
- 2004-04-07 AT AT04405214T patent/ATE330126T1/en not_active IP Right Cessation
- 2004-04-07 DE DE502004000769T patent/DE502004000769D1/en not_active Expired - Lifetime
- 2004-04-07 EP EP04405214A patent/EP1584820B1/en not_active Expired - Lifetime
- 2004-11-02 RU RU2006139075/06A patent/RU2358159C2/en not_active IP Right Cessation
- 2004-11-02 JP JP2007506630A patent/JP5070039B2/en active Active
- 2004-11-02 WO PCT/CH2004/000664 patent/WO2005098237A1/en active Application Filing
- 2004-11-02 US US10/588,736 patent/US7510368B2/en active Active
- 2004-11-02 CN CNB2004800426761A patent/CN100419271C/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2169234A2 (en) | 2007-07-17 | 2010-03-31 | Gerardus Augustinus Maria Manshanden | Sinking pump safe for fish |
| CN112636910A (en) * | 2020-12-29 | 2021-04-09 | 北京深思数盾科技股份有限公司 | Method, device and system for generating and verifying temporary password |
Also Published As
| Publication number | Publication date |
|---|---|
| US7510368B2 (en) | 2009-03-31 |
| WO2005098237A1 (en) | 2005-10-20 |
| RU2006139075A (en) | 2008-05-20 |
| CN100419271C (en) | 2008-09-17 |
| EP1584820A1 (en) | 2005-10-12 |
| DK1584820T3 (en) | 2006-07-31 |
| DE502004000769D1 (en) | 2006-07-27 |
| JP5070039B2 (en) | 2012-11-07 |
| RU2358159C2 (en) | 2009-06-10 |
| CN1926338A (en) | 2007-03-07 |
| US20070172345A1 (en) | 2007-07-26 |
| ATE330126T1 (en) | 2006-07-15 |
| JP2007532812A (en) | 2007-11-15 |
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