EP0528845B1 - Single-blade impeller for rotary pumps - Google Patents
Single-blade impeller for rotary pumps Download PDFInfo
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- EP0528845B1 EP0528845B1 EP91908572A EP91908572A EP0528845B1 EP 0528845 B1 EP0528845 B1 EP 0528845B1 EP 91908572 A EP91908572 A EP 91908572A EP 91908572 A EP91908572 A EP 91908572A EP 0528845 B1 EP0528845 B1 EP 0528845B1
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- European Patent Office
- Prior art keywords
- vane
- impeller
- blade
- angle
- rotation
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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
- F04D29/2238—Special flow patterns
- F04D29/225—Channel wheels, e.g. one blade or one flow channel
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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
- F04D29/2205—Conventional flow pattern
- F04D29/2222—Construction and assembly
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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
- F04D29/24—Vanes
- F04D29/242—Geometry, shape
- F04D29/245—Geometry, shape for special effects
Definitions
- the invention relates to an impeller for centrifugal pumps for conveying liquids mixed with solid admixtures, in particular for conveying dirty water with long-fiber constituents, with a channel between the front and rear cover plates of the impeller and the blade, the strength of which changes over the extent thereof is formed.
- centrifugal pumps with paddle wheels are operated at a constant drive speed.
- the delivery conditions of such a centrifugal pump are usually subject to constant change.
- the inlet height fluctuates between a maximum and a minimum value.
- the operating point of the centrifugal pump i.e. the intersection between the constant pump characteristic and the variable system characteristic, is therefore also subject to the change.
- the shift in the operating point now involves both a change in the relative blade inflow velocity and a change in the relative inflow direction. This results in a static pressure distribution along the blade contour, which is specific for the respective blade shape.
- the integration of the pressure distribution from the blade inlet to the blade outlet edge results in a blade force that rotates relative to a fixed reference point as a deflecting transverse force.
- This transverse force which is also referred to as hydrodynamic buoyancy, forms a harmonically acting excitation force, which in a system capable of oscillation, that is to say e.g. B. a system that can cause major problems. It should therefore be kept as small as possible.
- the US-PS 17 54 992 deals with the problem of balancing the mass imbalance on a single or single channel.
- the cited patent provides two measures: First, the blade forming the channel has a continuously decreasing thickness over its extension, so that, despite the asymmetrical mass distribution, an overall relatively low mass unbalance is caused. Second, a counterweight is used on the back of the impeller to balance the mass.
- the arrangement of cavities on the back of the paddle wheel is also provided, and the location can be varied to optimize the unbalance compensation.
- the invention has for its object to provide a paddle wheel of the type mentioned, which has a balanced design with respect to mechanical unbalance and hydrodynamic buoyancy when the basic requirement for blockage is met and which has a cavitation in the inlet area of the paddle wheel for trouble-free operation harmless minimum reduced.
- the paddle wheel produced by a casting process forms a channel (4) between a front cover plate (1), a rear cover plate (2) and a blade (3), the cross section of which decreases from the inlet (5) of the paddle wheel to the outlet (6).
- the blade (3) equipped with a suction side (7) and a pressure side (8) has a flattened blade head (9).
- a stagnation point flow results on a blade head with a very large rounded radius, which has a repellent effect on solids contained in the flow medium.
- the flattening which in the limit case has an infinitely large rounding radius, prevents the attachment of long-fiber components.
- the paddle wheel is designed so that the suction side of the paddle forms a semicircle concentrically to the axis of rotation of the paddle wheel for the first 180 degrees of the angle of rotation.
- the blade angle ⁇ measured at the skeleton line (10) of the blade (3) from the blade head (9), the entry (5) into the impeller is up to 180 ° of the angle of rotation less than 0 °, while it is positive at the outlet (6), that is in the area of the blade end (11).
- the suction side (7) of the blade (3) forms a semicircle with the radius r, which is arranged concentrically to the axis of rotation of the impeller.
- the blade (3) has a continuously decreasing thickness towards the outlet. It therefore has a mass distribution that is favorable for the imbalance behavior of the impeller. This advantage can be determined for the impeller as a whole, since it does not have large accumulations of material, particularly in the outer circumferential area.
- the suction side (7) and the pressure side (8) of the blade (3), seen in the meridian view, are axially parallel over their entire extent, with a rounding into the cover disks (1) and (2).
- the radius of such a rounding corresponds here to approximately one third of the width of the channel (4) at the outlet (6). It can be up to half the channel width at the outlet (6) of the paddle wheel.
- the paddle wheel according to the invention has a comparatively uncomplicated shape. It is therefore not only easy to pour, it can also be produced in sheet metal construction, which above all brings additional advantages with regard to the unbalance behavior.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
Gegenstand der Erfindung ist ein Einschaufelrad für Kreiselpumpen zur Förderung von mit festen Beimengungen durchsetzten Flüssigkeiten, insbesondere zur Förderung von Schmutzwasser mit langfaserigen Bestandteilen, wobei zwischen der vorderen und der hinteren Deckscheibe des Einschaufelrades und der Schaufel, deren Stärke sich über deren Erstreckung verändert, ein Kanal gebildet wird.The invention relates to an impeller for centrifugal pumps for conveying liquids mixed with solid admixtures, in particular for conveying dirty water with long-fiber constituents, with a channel between the front and rear cover plates of the impeller and the blade, the strength of which changes over the extent thereof is formed.
Der Konstrukteur eines vornehmlich in der Abwasserförderung zu verwendenden Einschaufelrades steht vor einer komplexen Aufgabenstellung. Er muß nicht nur das Einschaufelrad und dessen Kanal so gestalten, daß eine Anlagerung fester Bestandteile im Förderweg, vor allem aber eine dadurch hervorgerufene Verstopfung, mit Sicherheit vermieden werden. Er muß auch bedacht sein, die hierzu in einem gewissen Widerspruch stehende Forderung nach einer möglichst günstigen Massenverteilung des zwangsläufig unsymmetrisch gestalteten Einschaufelrades zu erfüllen. Und nicht zuletzt hat er einen hohen Energieumsatz in dem von ihm entwickelten Einschaufelrad anzustreben.The designer of a paddle wheel that is primarily used in wastewater production faces a complex task. He must not only design the paddle wheel and its channel in such a way that an accumulation of solid components in the conveying path, but above all a blockage caused thereby, can be avoided with certainty. He must also be careful to meet the somewhat contradictory requirement for the most favorable possible mass distribution of the inevitably asymmetrical designed impeller. And last but not least, he has to aim for a high energy turnover in the bucket wheel he developed.
Die Erfüllung der genannten Forderungen wird beeinträchtigt durch verschiedenartige Probleme, die sich aus den Förderbedingungen und den Besonderheiten des Einschaufelrades ergeben und die sich in einer vielfach nicht vorhersehbaren Weise gegenseitig beeinflussen und überlagern können.The fulfillment of the requirements mentioned is impaired by various problems which result from the funding conditions and the special features of the paddle wheel and which can influence and overlap one another in a manner which is often not predictable.
In der Mehrzahl aller Einsatzfälle werden Kreiselpumpen mit Einschaufelrädern mit einer konstanten Antriebsdrehzahl betrieben. Die Förderbedingungen einer solchen Kreiselpumpe sind normalerweise aber einer ständigen Änderung unterworfen. So schwankt beispielsweise die Zulaufhöhe zwischen einem Maximal- und einem Minimalwert. Der Arbeitspunkt der Kreiselpumpe, also der Schnittpunkt zwischen der konstanten Pumpenkennlinie und der variablen Anlagenkennlinie, ist somit ebenfalls der Änderung unterworfen.In the majority of all applications, centrifugal pumps with paddle wheels are operated at a constant drive speed. The delivery conditions of such a centrifugal pump are usually subject to constant change. For example, the inlet height fluctuates between a maximum and a minimum value. The operating point of the centrifugal pump, i.e. the intersection between the constant pump characteristic and the variable system characteristic, is therefore also subject to the change.
Mit der Verschiebung des Arbeitspunktes ist nun sowohl eine Änderung der relativen Schaufelzuströmgeschwindigkeit wie eine Änderung der relativen Anströmrichtung verbunden. Hieraus ergibt sich eine statische Druckverteilung längs der Schaufelkontur, die für die jeweilige Schaufelform spezifisch ist. Aus der Integration der Druckverteilung von der Schaufeleintritts- bis zur Schaufelaustrittskante ergibt sich eine Schaufelkraft, die relativ zu einem ortsfesten Bezugspunkt als auslenkende Querkraft umläuft. Diese Querkraft, die auch als hydrodynamischer Auftrieb bezeichnet wird, bildet eine harmonisch wirkende Erregerkraft, die in einem schwingungsfähigen System, also z. B. einer Anlage, große Probleme verursachen kann. Sie sollte daher möglichst klein gehalten werden.The shift in the operating point now involves both a change in the relative blade inflow velocity and a change in the relative inflow direction. This results in a static pressure distribution along the blade contour, which is specific for the respective blade shape. The integration of the pressure distribution from the blade inlet to the blade outlet edge results in a blade force that rotates relative to a fixed reference point as a deflecting transverse force. This transverse force, which is also referred to as hydrodynamic buoyancy, forms a harmonically acting excitation force, which in a system capable of oscillation, that is to say e.g. B. a system that can cause major problems. It should therefore be kept as small as possible.
Ein weiteres Problem der Einschaufel- oder Einkanalräder bildet die mechanische Unwucht, die aus der ungleichen Massenverteilung des Laufrades resultiert. Es läge nun nahe, die mechanische Unwucht zur Kompensation des hydrodynamischen Auftriebes einzusetzen, wobei die sich bei vektorieller Addition der beiden Kräfte ergebende Restkraft durch ein Zusatzgewicht ausgeglichen würde. Nun sind aber die mechanische Unwucht und die Fliehkräfte lastunabhängige Kräfte, während der hydrodynamische Auftrieb mit der Fördermenge auch den Angriffswinkel relativ zur Schaufel ändert. Daraus ergibt sich, daß sich eine Kompensation der mechanischen Unwucht und der hydrodynamischen Kraft nur für einen Arbeitspunkt der Kreiselpumpe erreichen läßt.Another problem with single-impeller or single-channel impellers is the mechanical imbalance that results from the uneven mass distribution of the impeller. It would now be obvious to use the mechanical imbalance to compensate for the hydrodynamic lift, the residual force resulting from the vectorial addition of the two forces being compensated for by an additional weight. Now, however, the mechanical imbalance and the centrifugal forces are forces independent of the load, while the hydrodynamic buoyancy changes with the delivery rate also the angle of attack relative to the blade. It follows that there is a compensation of mechanical unbalance and the hydrodynamic force can only be achieved for one working point of the centrifugal pump.
Es besteht daher die Forderung, neben der hydrodynamischen Auftriebskraft auch die mechanische Unwucht des Einschaufelrades möglichst klein zu halten. Für die Schaufel gilt es eine geometrische Gestaltung anzustreben, deren hydrodynamischer Auftrieb keine Richtungsänderung innerhalb des Arbeitsbereiches erfährt. Bei einem Tragflügel würde man hier von einem druckpunktfesten Profil sprechen.There is therefore a requirement to keep the mechanical imbalance of the impeller as small as possible in addition to the hydrodynamic buoyancy. For the bucket, it is important to strive for a geometric design, the hydrodynamic buoyancy of which does not undergo a change of direction within the working area. With a wing one would speak of a pressure point fixed profile.
Ein weiterer wichtiger Aspekt bei der Schaufelgestaltung ist die Optimierung des Kavitationsverhaltens der Kreiselpumpe. Durch früh kavitierende Einschaufelräder können aufgrund der systembedingten hydrodynamischen Unsymmetrie stationäre und instationäre Erregerkräfte freigesetzt werden, die in Form von Schwingungen auftreten und die den Betrieb der Kreiselpumpe gefährden.Another important aspect in the design of the blades is the optimization of the cavitation behavior of the centrifugal pump. Because of the system-related hydrodynamic asymmetry, stationary and unsteady excitation forces, which occur in the form of vibrations and which endanger the operation of the centrifugal pump, can be released by early cavitating paddle wheels.
Aus der Literatur sind verschiedene Beiträge bekannt, die sich mit dem Massenausgleich und der Verstopfungsgefahr eingehend beschäftigen. Es wurde dabei allerdings dem gegenseitigen Einfluß der verschiedenen auf das Laufrad wirkenden Kräfte weniger Beachtung geschenkt. Vor allem dem Einfluß der Kavitation wurde nicht die Bedeutung beigemessen, die ihm in Wirklichkeit zukommt.Various articles are known from the literature that deal in detail with mass balancing and the risk of constipation. However, less attention was paid to the mutual influence of the various forces acting on the impeller. Above all, the influence of cavitation was not given the importance that it really has.
So befaßt sich die US-PS 17 54 992 mit dem Problem des Ausgleichs der Massenunwucht an einem Einschaufel- bzw. Einkanalrad. Zur Bewältigung dieses Problems sieht die zitierte Patentschrift zwei Maßnahmen vor: Erstens besitzt die den Kanal bildende Schaufel eine über ihre Erstreckung stetig abnehmende Stärke, so daß, trotz der unsymmetrischen Massenverteilung, eine insgesamt relativ geringe Massenunwucht verursacht wird. Zweitens ist auf der Rückseite des Laufrades ein dem Massenausgleich dienendes Gegengewicht angeordnet. Als mögliche dritte Maßnahme ist noch die Anordnung von Hohlräumen auf der Rückseite des Einschaufelrades vorgesehen, wobei der Anbringungsort zur Optimierung des Unwuchtausgleichs variiert werden kann.Thus, the US-PS 17 54 992 deals with the problem of balancing the mass imbalance on a single or single channel. To cope with this problem, the cited patent provides two measures: First, the blade forming the channel has a continuously decreasing thickness over its extension, so that, despite the asymmetrical mass distribution, an overall relatively low mass unbalance is caused. Second, a counterweight is used on the back of the impeller to balance the mass. When possible third measure, the arrangement of cavities on the back of the paddle wheel is also provided, and the location can be varied to optimize the unbalance compensation.
Ausgehend von der Feststellung, daß auch die zur Förderung von festen Beimengungen besonders geeigneten Kanalräder unter ungünstigen Umständen weiterhin zur Verstopfung neigen, sann die Fachwelt auf eine Lösung des Problems. In der Annahme, daß Unregelmäßigkeiten in der Kanalführung und dadurch bedingtes ungleichmäßiges Fließverhalten zu Ablagerungen und zur Verstopfung führt, trachtete man nach einer möglichst gleichmäßigen Kanalführung.On the basis of the finding that the channel wheels, which are particularly suitable for conveying solid admixtures, continue to tend to blockage under unfavorable circumstances, the experts have thought of a solution to the problem. On the assumption that irregularities in the channel routing and the resulting uneven flow behavior lead to deposits and clogging, the aim was to ensure that the channel routing was as uniform as possible.
Durch den Aufsatz "Pumpen regeln Wasserhaushalt" (VDI-Nachrichten Nr. 25/23. Juni 1965) wurde dann eine Laufradform für Abwasseranlagen vorgeschlagen, die zur Vermeidung einer akuten Verstopfungsgefahr mit einem glatten Durchgang ausgestattet war. Wesentlich für dieses Laufrad war im übrigen, daß der Querschnitt des Eintritts über die gesamte Kanallänge erhalten blieb.The essay "Pumps regulate water balance" (VDI News No. 25/23 June 1965) then proposed an impeller shape for sewage systems that was equipped with a smooth passage to avoid an acute risk of constipation. It was also essential for this impeller that the cross-section of the inlet was preserved over the entire length of the channel.
Durch die US-PS 45 75 312 wurde ein ähnlich gestaltetes Laufrad bekannt, bei dem sich allerdings die Form des Kanalquerschnittes über den Verlauf veränderte. Dabei sollte aber die Querschnittsgröße gleichbleiben oder zum Auslaß hin leicht zunehmen. Da die im Querschnitt einem Rohrbogen ähnliche Kanalführung aber mit einer sehr dicken Schaufel erkauft werden mußte, sah die US-PS 45 75 312 die Möglichkeit vor, die Schaufel teilweise hohl auszubilden. Dies beseitigt allerdings noch nicht das Problem der Radunwucht, die ja nicht vollständig und für einen gesamten Drehzahlbereich ausgeglichen werden kann. Hier fällt vor allem die selbst bei einer teilweise ausgehöhlten Schaufel noch verhältnismäßig große Masse ins Gewicht. Im übrigen erfordert ein solches Laufrad einen erhöhten Aufwand bei der Herstellung.A similarly designed impeller was known from US Pat. No. 4,575,312, but the shape of the channel cross section changed over the course. However, the cross-sectional size should remain the same or increase slightly towards the outlet. Since the duct guide, which was similar in cross section to a pipe bend, had to be purchased with a very thick shovel, US Pat. No. 4,575,312 provided the possibility of making the shovel partially hollow. However, this does not yet eliminate the problem of wheel imbalance, which cannot be completely compensated for over an entire speed range. Here, the relatively large mass is particularly important, even with a partially hollowed-out blade. Moreover, such an impeller requires increased manufacturing effort.
Der Erfindung liegt die Aufgabe zugrunde, ein Einschaufelrad der eingangs genannten Art zu schaffen, welches bei Erfüllung der Grundvoraussetzung der Verstopfungsfreiheit eine bezüglich der mechanischen Unwucht und des hydrodynamischen Auftriebes ausgewogene Gestaltung besitzt und die eine im Einlaufbereich des Einschaufelrades vorhandene Kavitation auf ein für den störungsfreien Betrieb unschädliches Minimum reduziert.The invention has for its object to provide a paddle wheel of the type mentioned, which has a balanced design with respect to mechanical unbalance and hydrodynamic buoyancy when the basic requirement for blockage is met and which has a cavitation in the inlet area of the paddle wheel for trouble-free operation harmless minimum reduced.
Die gestellte Aufgabe wird erfindungsgemäß durch die im Anspruch 1 angegebene Merkmale Kombination gelöst.The object is achieved according to the invention by the combination of features specified in claim 1.
Dieser Lösung liegt folgende Überlegung zugrunde:This solution is based on the following consideration:
In der Praxis ist davon auszugehen, daß erste Dampfblasen an der Schaufel dann entstehen, wenn der statische Druck der Strömung auf den Dampfdruck absinkt. Die durch die Schaufel erzeugte Druckdifferenz überlagert sich dem mittleren Druck der Zuströmung. Der sich im System einstellende Minimaldruck, der sich zwangsläufig im Bereich des Schaufelanfangs bildet, ist vom Niveau der mittleren Relativgeschwindigkeit und vor allem von der mittleren Dralländerung abhängig. Die mittlere Dralländerung wiederum wird bestimmt durch den Schaufelwinkel. Ein längs des Strömungsweges gleichbleibender oder abnehmender Schaufelwinkel, wie er in der Erfindung realisiert wird, hat eine kleine mittlere Dralländerung und damit einen weniger tief abgesenkten mittleren Druck zur Folge. Durch die erfindungsgemäße Formgebung der Schaufel wird also eine frühzeitige, intensive Blasenbildung verhindert. Die bei einem Abschwimmen und Implodieren der Blasen (Kavitation) negativ beeinflußte Laufruhe der Kreiselpumpe wird somit vermieden.In practice, it can be assumed that the first steam bubbles form on the blade when the static pressure of the flow drops to the steam pressure. The pressure difference generated by the blade is superimposed on the mean pressure of the inflow. The minimum pressure that arises in the system, which inevitably forms in the area of the blade start, depends on the level of the mean relative speed and, above all, on the mean change in swirl. The mean change in swirl is in turn determined by the blade angle. A blade angle that is constant or decreases along the flow path, as is realized in the invention, results in a small mean swirl change and thus a less deeply lowered mean pressure. The shape of the blade according to the invention thus prevents premature, intensive bubble formation. The smoothness of the centrifugal pump which is negatively influenced when the bubbles swim away and implode (cavitation) is thus avoided.
Die Unteransprüche nennen vorteilhafte Ausgestaltungen der Erfindung.The subclaims name advantageous embodiments of the invention.
Anhand eines Ausführungsbeispieles wird der Erfindung näher erläutert. Die Zeichnung zeigt in
- Fig. 1
- einen Axialschnitt durch ein erfindungsgemäß gestaltetes Laufrad und in
- Fig. 2
- einen Radialschnitt durch das Laufrad der Fig. 1.
- Fig. 1
- an axial section through an impeller designed according to the invention and in
- Fig. 2
- a radial section through the impeller of FIG. 1st
Das durch ein Gießverfahren hergestellte Einschaufelrad bildet zwischen einer vorderen Deckscheibe (1), einer hinteren Deckscheibe (2) und einer Schaufel (3) einen Kanal (4), dessen Querschnitt vom Einlauf (5) des Einschaufelrades zum Austritt (6) hin abnimmt.The paddle wheel produced by a casting process forms a channel (4) between a front cover plate (1), a rear cover plate (2) and a blade (3), the cross section of which decreases from the inlet (5) of the paddle wheel to the outlet (6).
Die mit einer Saugseite (7) und einer Druckseite (8) ausgestattete Schaufel (3) besitzt einen abgeflachten Schaufelkopf (9). Im Gegensatz zum herkömmlichen Schaufelkopf, der mit einem Abrunderadius von der halben Schaufeldicke versehen ist, ergibt sich an einem Schaufelkopf mit einem sehr großen Abrunderadius eine Staupunkt-Strömung, die eine abweisende Wirkung auf im Strömungsmedium enthaltene Feststoffe ausübt. Die Abflachung, die im Grenzfall einen unendlich großen Abrundradius besitzt, verhindert also das Anlagern langfaseriger Bestandteile.The blade (3) equipped with a suction side (7) and a pressure side (8) has a flattened blade head (9). In contrast to the conventional blade head, which is provided with an rounded radius of half the blade thickness, a stagnation point flow results on a blade head with a very large rounded radius, which has a repellent effect on solids contained in the flow medium. The flattening, which in the limit case has an infinitely large rounding radius, prevents the attachment of long-fiber components.
Das Einschaufelrad ist so gestaltet, daß die Saugseite der Schaufel auf den ersten 180 Grad des Drehwinkels einen konzentrisch zur Drehachse des Einschaufelrades angeordneten Halbkreis bildet. Der Bedingung der Erfindung folgend, ist somit hier der an der Skelettlinie (10) der Schaufel (3) gemessene Schaufelwinkel β vom Schaufelkopf (9), dem Eintritt (5) in das Laufrad, bis 180° des Drehwinkels kleiner als 0°, während er am Austritt (6), also im Bereich des Schaufelendes (11), positiv ist.The paddle wheel is designed so that the suction side of the paddle forms a semicircle concentrically to the axis of rotation of the paddle wheel for the first 180 degrees of the angle of rotation. Following the condition of the invention, the blade angle β measured at the skeleton line (10) of the blade (3) from the blade head (9), the entry (5) into the impeller, is up to 180 ° of the angle of rotation less than 0 °, while it is positive at the outlet (6), that is in the area of the blade end (11).
Die Saugseite (7) der Schaufel (3) bildet auf den ersten 180° des Drehwinkels einen konzentrisch zur Drehachse des Einschaufelrades angeordneten Halbkreis mit dem Radius r.On the first 180 ° of the angle of rotation, the suction side (7) of the blade (3) forms a semicircle with the radius r, which is arranged concentrically to the axis of rotation of the impeller.
Die Schaufel (3) besitzt eine zum Auslaß hin stetig abnehmende Dicke. Sie hat somit eine für das Unwuchtverhalten des Einschaufelrades günstige Massenverteilung. Dieser Vorteil läßt sich für das Einschaufelrad insgesamt feststellen, da es keine großen Materialanhäufungen, insbesondere im äußeren Umfangsbereich, besitzt.The blade (3) has a continuously decreasing thickness towards the outlet. It therefore has a mass distribution that is favorable for the imbalance behavior of the impeller. This advantage can be determined for the impeller as a whole, since it does not have large accumulations of material, particularly in the outer circumferential area.
Die Saugseite (7) und die Druckseite (8) der Schaufel (3) verlaufen, in der Meridiandarstellung gesehen, auf ihrer gesamten Erstreckung achsparallel, wobei sie mit einer Rundung in die Deckscheiben (1) und (2) übergehen. Der Radius einer solchen Rundung entspricht hier etwa einem Drittel der Breite des Kanals (4) am Austritt (6). Er kann bis zur Hälfte der Kanalbreite am Austritt (6) des Einschaufelrades betragen.The suction side (7) and the pressure side (8) of the blade (3), seen in the meridian view, are axially parallel over their entire extent, with a rounding into the cover disks (1) and (2). The radius of such a rounding corresponds here to approximately one third of the width of the channel (4) at the outlet (6). It can be up to half the channel width at the outlet (6) of the paddle wheel.
Das erfindungsgemäße Einschaufelrad verfügt über eine vergleichsweise unkomplizierte Gestalt. Es ist daher nicht nur leicht gießbar, es läßt sich auch in Blechbauweise herstellen, was vor allem zusätzliche Vorteile im bezug auf das Unwuchtverhalten mit sich bringt.The paddle wheel according to the invention has a comparatively uncomplicated shape. It is therefore not only easy to pour, it can also be produced in sheet metal construction, which above all brings additional advantages with regard to the unbalance behavior.
Claims (7)
- A single vane impeller for centrifugal pumps for liquids mixed with solids, and more particularly for dirty water containing long fiber components, a channel (4) being formed between the front cover disk (1) and the rear cover disk (2) of the single vane impeller and the vane (3), whose thickness changes along the extent thereof, characterized in that from the inlet (5) as far as 90° of the angle of rotation the vane angle (β) as measured on the skeleton line (10) of the vane (3) is smaller than 0°, whereas the suction side (7) of the vane (3) in this part forms a part of a circle centered on the axis of rotation of the single vane impeller and whereas the vane angle (β) is positive at the outlet (6), such conditions applying for all planes of section perpendicular to the axis of rotation, and in that the vane head (9) constituting the transition between the suction side (7) and the pressure side (8) of the vane (3) possesses a radius of rounding which is substantially larger than half the thickness of the vane.
- The single vane impeller as claimed in claim 1, characterized in that pressure side (8) and the suction side (7) of the vane (3), with the exception of any transition parts leading to the covers (1 and 2), as viewed meridianally, are axially parallel for their full extent.
- The single vane impeller as claimed in claim 1 and in claim 2, characterized in that the pressure side (8) and/or the suction side (7) of the vane (3) merge as a rounded part, whose radius is equal to approximately one third of the width of the channel (4) at the outlet (6) of the single vane impeller with the cover disks (1 and 2).
- The single vane impeller as claimed in claim 1, characterized in that the first 180° of the angle of rotation the suction side (7) of the vane (3) constitutes a half circle centered on the axis of rotation of the single vane impeller.
- The single vane impeller as claimed in claim 1, characterized in that the vane head constituting the transition between the suction side (7) and the pressure side (8) of the vane (3) has a radius of rounding which is substantially greater than half the thickness of the vane.
- The single vane impeller as claimed in claim 1, characterized in that the vane head (9) constitutes a flat surface.
- The single vane impeller as claimed in claim 1, characterized in that the single vane impeller consists of sheet metal, the vane consisting of two pieces of sheet metal which are welded together and respectively form the suction and the pressure side of the vane.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4015331 | 1990-05-12 | ||
| DE4015331A DE4015331A1 (en) | 1990-05-12 | 1990-05-12 | PADDLE WHEEL FOR CENTRIFUGAL PUMPS |
| PCT/EP1991/000833 WO1991018210A1 (en) | 1990-05-12 | 1991-05-02 | Single-blade impeller for rotary pumps |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0528845A1 EP0528845A1 (en) | 1993-03-03 |
| EP0528845B1 true EP0528845B1 (en) | 1995-07-19 |
Family
ID=6406293
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP91908572A Expired - Lifetime EP0528845B1 (en) | 1990-05-12 | 1991-05-02 | Single-blade impeller for rotary pumps |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US5348444A (en) |
| EP (1) | EP0528845B1 (en) |
| AR (1) | AR244396A1 (en) |
| DE (2) | DE4015331A1 (en) |
| WO (1) | WO1991018210A1 (en) |
Families Citing this family (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5290236A (en) * | 1991-09-25 | 1994-03-01 | Baxter International Inc. | Low priming volume centrifugal blood pump |
| US5263924A (en) * | 1991-09-25 | 1993-11-23 | Baxter International Inc. | Integrated low priming volume centrifugal pump and membrane oxygenator |
| US5890883A (en) * | 1997-03-19 | 1999-04-06 | The Cleveland Clinic Foundation | Rotodynamic pump with non-circular hydrodynamic bearing journal |
| AU7360798A (en) * | 1997-09-24 | 1999-04-12 | Cleveland Clinic Foundation, The | Flow controlled blood pump system |
| JP4713066B2 (en) * | 2003-07-18 | 2011-06-29 | 新明和工業株式会社 | Impeller and sewage treatment pump equipped therewith |
| US7767159B2 (en) * | 2007-03-29 | 2010-08-03 | Victor Nikolaevich Glotov | Continuous flow sonic reactor and method |
| JP5118951B2 (en) * | 2007-12-11 | 2013-01-16 | 新明和工業株式会社 | Centrifugal pump impeller and centrifugal pump |
| DE102011007907B3 (en) * | 2011-04-21 | 2012-06-21 | Ksb Aktiengesellschaft | Impeller for centrifugal pumps |
| US9062675B2 (en) | 2012-02-10 | 2015-06-23 | Randy Dixon | Rotary lobe pump with wiper blades |
| DE102015213451B4 (en) | 2015-07-17 | 2024-02-29 | KSB SE & Co. KGaA | Centrifugal pump blade profile |
| CN106837856B (en) * | 2017-03-14 | 2023-03-31 | 中交疏浚技术装备国家工程研究中心有限公司 | Design method of three-blade impeller of efficient wear-resistant dredge pump and impeller |
| DE102017213507A1 (en) | 2017-08-03 | 2019-02-07 | KSB SE & Co. KGaA | Impeller for wastewater pump |
| DE102017221930A1 (en) | 2017-12-05 | 2019-06-06 | KSB SE & Co. KGaA | Impeller for wastewater pump |
| CN110513326B (en) * | 2019-08-27 | 2024-04-23 | 浙江理工大学 | Centrifugal pump impeller capable of actively controlling pressure pulsation |
| CN112483461B (en) * | 2020-10-21 | 2022-07-22 | 南通大学 | Self-balancing method for radial force of single-blade centrifugal pump |
| CN112069630B (en) * | 2020-11-11 | 2021-01-22 | 中国航发上海商用航空发动机制造有限责任公司 | Compressor, blade, two-dimensional blade profile design method of blade and computer equipment |
| CN112811483B (en) * | 2021-01-06 | 2022-11-04 | 江苏大学 | Green sewage treatment plant |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BE506117A (en) * | ||||
| CH94909A (en) * | 1921-05-21 | 1922-06-01 | Peter Alfred | Channelless centrifugal pump, especially for pumping impure liquids with different specific weights. |
| US1754992A (en) * | 1926-12-06 | 1930-04-15 | American Well Works | Centrifugal pump |
| CH189936A (en) * | 1936-01-18 | 1937-03-31 | Bucher Guyer Ag Masch | Centrifugal pump for pumping liquid manure, sludge water and the like. |
| US2272469A (en) * | 1939-12-23 | 1942-02-10 | Chicago Pump Co | Centrifugal pump |
| DE1034031B (en) * | 1956-03-31 | 1958-07-10 | Amag Hilpert Pegnitzhuette A G | Channel wheel, in particular single-channel wheel for centrifugal pumps to convey sludge-containing waste water |
| FR1274289A (en) * | 1960-11-29 | 1961-10-20 | Centrifugal pump with single duct rotor | |
| DE2732863C3 (en) * | 1977-07-21 | 1980-04-17 | Balcke-Duerr Ag, 4030 Ratingen | Single-channel centrifugal pump for pumping wastewater |
| US4575312B1 (en) * | 1982-06-02 | 1989-05-16 | Impeller | |
| FI73501C (en) * | 1984-06-06 | 1987-10-09 | Sarlin Ab Oy E | Impeller at a pump. |
| US4681508A (en) * | 1984-11-14 | 1987-07-21 | Kim Choong W | Supercavitation centrifugal pump |
| DE3615686A1 (en) * | 1986-05-09 | 1987-11-12 | Klein Schanzlin & Becker Ag | CHANNEL WHEEL FOR CENTRIFUGAL PUMPS |
-
1990
- 1990-05-12 DE DE4015331A patent/DE4015331A1/en not_active Withdrawn
-
1991
- 1991-04-24 AR AR91319516A patent/AR244396A1/en active
- 1991-05-02 EP EP91908572A patent/EP0528845B1/en not_active Expired - Lifetime
- 1991-05-02 WO PCT/EP1991/000833 patent/WO1991018210A1/en active IP Right Grant
- 1991-05-02 DE DE59106053T patent/DE59106053D1/en not_active Expired - Lifetime
- 1991-05-02 US US07/945,966 patent/US5348444A/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| DE59106053D1 (en) | 1995-08-24 |
| WO1991018210A1 (en) | 1991-11-28 |
| EP0528845A1 (en) | 1993-03-03 |
| DE4015331A1 (en) | 1991-11-14 |
| US5348444A (en) | 1994-09-20 |
| AR244396A1 (en) | 1993-10-29 |
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