EP0449861B1 - Centrifugal pump impeller with low specific speed - Google Patents
Centrifugal pump impeller with low specific speed Download PDFInfo
- Publication number
- EP0449861B1 EP0449861B1 EP90900104A EP90900104A EP0449861B1 EP 0449861 B1 EP0449861 B1 EP 0449861B1 EP 90900104 A EP90900104 A EP 90900104A EP 90900104 A EP90900104 A EP 90900104A EP 0449861 B1 EP0449861 B1 EP 0449861B1
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- European Patent Office
- Prior art keywords
- impeller
- vane
- centrifugal pump
- ducts
- pump impeller
- Prior art date
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- 239000007788 liquid Substances 0.000 description 3
- 238000003754 machining Methods 0.000 description 3
- 238000005266 casting Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000005520 cutting process Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000005304 joining Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2238—Special flow patterns
- F04D29/2255—Special flow patterns flow-channels with a special cross-section contour, e.g. ejecting, throttling or diffusing effect
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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
Definitions
- the invention relates to a centrifugal pump impeller according to the preamble of the main claim.
- impellers for centrifugal pumps which operate in the area of the lowest specific speed. These impellers have the feature that the actual blade channels are created by cutting tools, have a straight course and have a constant circular cross-section over their entire length. Compared to the known impellers with a diffuser-shaped blade channel, they have the advantage of being simple Manufacturability, but have the disadvantage of poor hydraulic efficiency.
- the invention has for its object to provide an increase in the pressure coefficient and an improvement in efficiency in a centrifugal pump impeller for small flow rates and high delivery heights. This object is achieved in accordance with the characterizing part of the main claim.
- the respective blade channels are cut obliquely. This enables the different inclination variations of the impeller cover disk and / or blade channels. This results in a gradual opening of the vane channels, on the basis of which a favorable influence on the liquid flowing within the vane channels is possible.
- a further embodiment of the invention described in claim 5 provides that the distance between the impeller cover plate and the opposite housing wall is at most the difference between at the impeller outlet in Axial direction of measurable blade channel depth and an outward extension of the blade channel wall on the impeller outer diameter corresponds to the blade channel depth that can be determined.
- the configurations described in claims 6 and 7 relate to the shape of the vane channel openings.
- the opening of the vane channels which from the beginning widens continuously towards the outer diameter of the impeller, enables a smoothly occurring and slowly increasing impulse exchange towards the outlet.
- the impeller (1) shown in Fig. 1 has a suction opening (2) through which the fastening means for connection to a pump shaft - not shown here - are also introduced.
- the impeller cover disk (3) on the suction side has a smooth surface here and has an inclination which obliquely cuts the vane channels (5) in the region of the outer diameter of the impeller (4).
- the blade channels (5) extend radially outward from the center of the impeller.
- the shape of the impeller channels (5) selected here has a circular cross section; however, other cross-sectional shapes are also conceivable.
- the blade channels (5) can be produced by bores made in the impeller from the outside. However, it is also possible to create the blade channel shapes using appropriate casting techniques.
- each blade channel has an opening (6) that widens outwards.
- the blade channel width (b) which can be measured directly there, is shown on the outside diameter. This is the blade channel width reduced by the inclined section.
- the determinable blade channel width (b *) which corresponds to the uninfluenced blade channel width, results from the blade channel wall which is closest to the cover disk having the opening (6) through the opening (6) to the outside is extended. As shown in FIG. 4, the intersection (z) of this extension (x) with the cylindrical plane (y) of the impeller outer diameter forms a limit value, while the blade duct wall opposite this forms another limit that includes the determinable blade duct width (b *).
- FIG. 2 shows a front view of the impeller (1), which can be seen how the blade channels run inside the impeller.
- the impeller (1) shown here as an example has a number and shape of blade channels (5) which, at the impeller inlet (2) shown here, result in an overlap of the blade channels in the inlet.
- the delivery rate can also be influenced by appropriate variation of the suction opening (2) forming the impeller inlet.
- the openings (6) have a width (w) which is smaller than the maximum width of the blade channels (5).
- the size of the width (w) can be influenced by a corresponding inclination of the blade channels or the cover disk.
- Fig. 3 which corresponds to a section of III-III of Fig. 2, the course of the inclined blade channels (5) and the inclination of the impeller cover plates (3, 7) can be seen.
- the blade channels and the impeller cover disks are inclined relative to planes (11, 12) that are perpendicular to the axis of rotation (8).
- the alternating one blade channel is inclined to the suction-side cover plate (3) and the adjacent blade channel to the pressure-side cover plate (7).
- a corresponding selection of the angle of inclination of the blade channels and / or the cover plate angle of inclination results in a cut of the blade channels in the impeller outlet area.
- the right half of the figure also shows that the impeller on the suction side is opposite the housing wall (9) and on the pressure side the housing wall (10). Although these are parallel to the respective impeller cover, this is not a mandatory requirement. Different inclinations are also conceivable.
- Fig. 4 From Fig. 4 it can be seen that in the area of the openings (6) between the impeller cover disc (3) and the suction-side housing wall (9) there is a distance (s) which is smaller than the difference (d) which can be measured on the impeller outer diameter (4) Blade channel width (b) and the determinable blade channel width (b *).
- the distance (s) may at most correspond to the difference (d). A larger value would not produce the necessary effect.
- the distance (s) used in the exemplary embodiment is smaller than the difference (d) shown.
- the pump characteristic curve can be influenced in a simple manner in accordance with the selected distance (s).
- the value (b *) can be determined by extending the blade duct wall provided with the opening (6) and closest to the housing towards the outside in the direction of the outer diameter of the impeller (4). Starting from the point of intersection (z) between the extension (x) and the cylindrical plane (y) of the outer diameter of the impeller, the blade channel width (b *) is determined into the blade channel. This can apply to both the suction and the pressure side of the impeller.
- the distance (s) is always determined for one impeller side, i.e. on the suction or pressure side.
- the distances (s) between the suction-side housing wall and the impeller cover plate or between the pressure-side housing wall and the impeller cover plate can have the same or different dimensions. If the open vane channels are only installed on one side of the impeller, then the distance (s) corresponds at most to the difference (d). If the open vane channels were attached on both sides, the distance (s) would be based on the dimensions prevailing on the respective impeller side.
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Abstract
Description
Die Erfindung betrifft ein Kreiselpumpenlaufrad gemäß dem Oberbegriff des Hauptanspruches.The invention relates to a centrifugal pump impeller according to the preamble of the main claim.
Aus der GB-A 575 346 sowie der DE-C 1 249 693 sind einteilige Laufräder für Kreiselpumpen bekannt, welche im Gebiet kleinster spezifischer Drehzahl arbeiten. Diese Laufräder weisen das Merkmal auf, daß die eigentlichen Schaufelkanäle durch spanabhebende Werkzeuge erstellt werden, einen geradlinigen Verlauf aufweisen und über ihre gesamte Länge über einen konstanten kreisförmigen Querschnitt verfügen.Gegenüber den bekannten, einen sich diffusorförmig erweiternden Schaufelkanal aufweisenden Laufrädern weisen sie den Vorteil der einfachen Herstellbarkeit auf, verfügen aber über den Nachteil eines schlechten hydraulischen Wirkungsgrades.From GB-A 575 346 and DE-C 1 249 693, one-piece impellers for centrifugal pumps are known which operate in the area of the lowest specific speed. These impellers have the feature that the actual blade channels are created by cutting tools, have a straight course and have a constant circular cross-section over their entire length. Compared to the known impellers with a diffuser-shaped blade channel, they have the advantage of being simple Manufacturability, but have the disadvantage of poor hydraulic efficiency.
Eine andere Lösung ist durch die SU-A 620 674 bekannt. Diese zeigt ein sogenanntes offenes Laufrad, bei dem der Schaufelkanal über seine gesamte Länge geöffnet bleibt. Sie stellt insofern eine Besonderheit dar, als daß es sich hier bei den Schaufelkanälen um geöffnete, mit einem Längsschlitz versehene, gebohrte Laufradkanäle handelt. Diese Lösung weist im Bereich des Druckstutzens eine gegenüber den Schaufelkanälen sehr starke Verengung des Austrittsbereiches auf, wodurch hohe Druckverluste entstehen. Der hydraulische Wirkungsgrad ist dadurch erheblich verschlechtert. Weiterhin ergibt sich durch das offene Rad ein höherer Axialschub zur Saugseite hin.Another solution is known from SU-A 620 674. This shows a so-called open impeller, in which the blade channel remains open over its entire length. It represents a peculiarity in that the vane channels are open, drilled impeller channels provided with a longitudinal slot. In the area of the pressure nozzle, this solution has a very strong narrowing of the outlet area compared to the blade channels, which results in high pressure losses. The hydraulic one Efficiency has deteriorated considerably as a result. Furthermore, the open wheel results in a higher axial thrust towards the suction side.
Der Erfindung liegt die Aufgabe zugrunde, bei einem Kreiselpumpenlaufrad für kleine Fördermengen und große Förderhöhen eine Steigerung der Druckziffer sowie eine Wirkungsgradverbesserung vorzusehen. Die Lösung dieser Aufgabe erfolgt gemäß dem kennzeichnenden Teil des Hauptanspruches.The invention has for its object to provide an increase in the pressure coefficient and an improvement in efficiency in a centrifugal pump impeller for small flow rates and high delivery heights. This object is achieved in accordance with the characterizing part of the main claim.
Aufgrund der erfindungsgemäßen Lösung wird gegenüber herkömmlichen Kreiselpumpenlaufrädern mit geschlossenen Deckscheiben eine gravierende Steigerung der laufradtypischen Druckziffer erreicht. Infolge der im Laufradaustrittsbereich offen ausgebildeten Schaufelkanäle existiert ein Impulsaustausch zwischen der Flüssigkeit im Strömungskanal und der im Radseitenraum befindlichen Flüssigkeit. Dies bedingt einen Energiezuwachs, dessen Folge eine Vergrößerung der Förderhöhe sowie eine Erhöhung der Druckziffer ist. Im Gegensatz zu den Seitenkanalpumpen erfolgt hier eine deutliche Wirkungsgradverbesserung, da die bei Seitenkanalpumpen typischen Verlustformen nicht mehr auftreten können.Due to the solution according to the invention, a significant increase in the typical impeller pressure is achieved compared to conventional centrifugal pump impellers with closed cover disks. As a result of the blade channels which are designed to be open in the impeller outlet area, there is an exchange of momentum between the liquid in the flow channel and the liquid in the wheel side space. This requires an increase in energy, the consequence of which is an increase in the delivery head and an increase in the pressure figure. In contrast to the side channel pumps, there is a significant improvement in efficiency, since the loss forms typical of side channel pumps can no longer occur.
Durch die in den Ansprüchen 2 bis 4 beschriebenen Ausgestaltungen erfolgt ein schräges Anschneiden der jeweiligen Schaufelkanäle. Dies ermöglicht die verschiedenen Neigungsvariationen von Laufraddeckscheibe und/oder Schaufelkanälen. Dadurch ergibt sich eine allmähliche Öffnung der Schaufelkanäle, aufgrund derer eine günstige Beeinflussung der innerhalb der Schaufelkanäle strömenden Flüssigkeit möglich ist. Hierzu sieht eine weitere im Anspruch 5 beschriebene Ausgestaltung der Erfindung vor, daß der Abstand zwischen Laufraddeckscheibe und gegenüberliegender Gehäusewand maximal der Differenz zwischen am Laufradaustritt in Achsrichtung meßbarer Schaufelkanaltiefe und einer nach außen erfolgenden Verlängerung der Schaufelkanalwand am Laufradaußendurchmesser ermittelbaren Schaufelkanaltiefe entspricht. Die in den Ansprüchen 6 und 7 beschriebenen Ausgestaltungen haben die Form der Schaufelkanalöffnungen zum Gegenstand. Diese Formen ermöglichen eine störungsfreie Beeinflussung der innerhalb der Schaufelkanäle befindlichen Strömungen. Mit der erfindungsgemäßen Ausgestaltung ergeben sich relativ stabile Rennlinien bei ebenfalls gutem Saugverhalten. Als weiterer Vorteil kommt hinzu, daß mit der erfindungsgemäßen Laufradgestaltung auf den üblicherweise bei Kreiselpumpenrädern vorherrschenden Saugmund bzw. dort angebrachten Drosselspalten verzichtet werden kann. Je nach Art der Herstellung der Schaufelkanäle, sei es nun durch spanabhebende Bearbeitung oder entsprechende gießtechnische Ausbildung können diese Laufräder auch bei einem Förderbereich bis 15 m³/h (n=2900 U/min) Anwendung finden.Due to the configurations described in
Mit der im Anspruch 8 beschriebenen Ausgestaltung der sich von ihrem Beginn an zum Laufradaußendurchmesser hin stetig erweiternden Öffnungen der Schaufelkanäle wird ein weich einsetzender und zum Austritt hin langsam zunehmender Impulsaustausch ermöglicht.With the embodiment described in
Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und werden im folgenden näher beschrieben. Es zeigen die
- Fig. 1 eine perspektivische Ansicht des Laufrades, die
- Fig. 2 eine Vorderansicht, die
- Fig. 3 einen Schnitt gemäß Linie III-III von Fig. 2 und die
- Fig. 4 einen Ausschnitt von dem Austrittsbereich des Laufrades.
- Fig. 1 is a perspective view of the impeller, the
- Fig. 2 is a front view
- Fig. 3 is a section along line III-III of Fig. 2 and
- Fig. 4 shows a detail of the outlet area of the impeller.
Das in Fig. 1 gezeigte Laufrad (1) weist eine Saugöffnung (2) auf, durch welche auch die Befestigungsmittel für die Verbindung mit einer - hier nicht dargestellten - Pumpenwelle eingebracht werden. Die saugseitige Laufraddeckscheibe (3) ist hier glattflächig ausgebildet und weist eine Neigung auf, welche im Bereich des Laufradaußendurchmessers (4) die Schaufelkanäle (5) schräg anschneidet. Bei dem hier gewählten Beispiel erstrecken sich die Schaufelkanäle (5) von der Laufradmitte radial nach außen. Die hier gewählte Form der Laufradkanäle (5) weist einen kreisförmigen Querschnitt auf; es sind jedoch auch andere Querschnittsformen denkbar. So können die Schaufelkanäle (5) beispielsweise durch von außen in das Laufrad eingebrachte Bohrungen hergestellt werden. Es ist aber auch möglich, durch entsprechende Gießtechniken die Schaufelkanalformen zu erstellen. Desweiteren besteht die Möglichkeit, das Laufrad in einer die Drehachse schneidenden Ebene zu teilen und mittels spanabhebender Bearbeitung in die beiden Teilhälften die Schaufelkanalformen einzuarbeiten und anschließend die beiden Hälften zu einem einheitlichen Ganzen zusammenzufügen. Die hier gezeigten Schaufelkanalbohrungen (5) können ebenso gut auch in tangentialer Richtung verlaufen. Im Bereich des Laufradaußendurchmessers (4) verfügt jeder Schaufelkanal über eine sich nach außen erweiternde Öffnung (6). Desweiteren ist am Außendurchmesser die dort direkt meßbare Schaufelkanalbreite (b) eingezeichnet. Hierbei handelt es sich um die durch den schrägen Abschnitt verkleinerte Schaufelkanalbreite. Die ermittelbare Schaufelkanalbreite (b*), welche der unbeeinflußbaren Schaufelkanalbreite entspricht, ergibt sich, indem diejenige Schaufelkanalwand, welcher der die Öffnung (6) aufweisenden Deckscheibe am nächsten liegt, durch die Öffnung (6) nach außen hin verlängert wird. Wie die Fig. 4 zeigt, bildet der Schnittpunkt (z) dieser Verlängerung (x) mit der zylindrischen Ebene (y) des Laufradaußendurchmessers einen Grenzwert, während die diesem gegenüberliegende Schaufelkanalwand eine andere, die ermittelbare Schaufelkanalbreite (b*) einschließende Begrenzung bildet.The impeller (1) shown in Fig. 1 has a suction opening (2) through which the fastening means for connection to a pump shaft - not shown here - are also introduced. The impeller cover disk (3) on the suction side has a smooth surface here and has an inclination which obliquely cuts the vane channels (5) in the region of the outer diameter of the impeller (4). In the example chosen here, the blade channels (5) extend radially outward from the center of the impeller. The shape of the impeller channels (5) selected here has a circular cross section; however, other cross-sectional shapes are also conceivable. For example, the blade channels (5) can be produced by bores made in the impeller from the outside. However, it is also possible to create the blade channel shapes using appropriate casting techniques. Furthermore, there is the possibility of dividing the impeller in a plane intersecting the axis of rotation and machining the blade channel shapes into the two partial halves by means of machining and then joining the two halves to form a uniform whole. The blade channel bores (5) shown here can equally well run in the tangential direction. In the area of the impeller outer diameter (4), each blade channel has an opening (6) that widens outwards. Furthermore, the blade channel width (b), which can be measured directly there, is shown on the outside diameter. This is the blade channel width reduced by the inclined section. The determinable blade channel width (b *), which corresponds to the uninfluenced blade channel width, results from the blade channel wall which is closest to the cover disk having the opening (6) through the opening (6) to the outside is extended. As shown in FIG. 4, the intersection (z) of this extension (x) with the cylindrical plane (y) of the impeller outer diameter forms a limit value, while the blade duct wall opposite this forms another limit that includes the determinable blade duct width (b *).
In der Fig. 2 ist eine Vorderansicht des Laufrades (1) gezeigt, der entnehmbar ist, wie die Schaufelkanäle innerhalb des Laufrades verlaufen. Entsprechend der gewählten Anzahl der Schaufelkanäle ergibt sich im Eintrittsbereich des Laufrades eine Überschneidung, erkennbar auch in Fig. 1, wodurch die Fördermenge des Laufrades beeinflußt werden kann. Bei einer geringen Anzahl von Schaufelkanälen und kleinen Schaufelkanalquerschnitten sowie einem geeigneten Laufradeintrittsdurchmesser, ist ein Laufrad herstellbar, dessen Schaufelkanäle (5) sich im Eintrittsbereich nicht überschneiden. Das hier beispielhaft gezeigte Laufrad (1) weist bei gegebenem Außendurchmeser (4) eine Anzahl und Form von Schaufelkanälen (5) auf, die bei dem hier gezeigten Laufradeintritt (2) eine Überschneidung der Schaufelkanäle im Eintritt zur Folge hat.2 shows a front view of the impeller (1), which can be seen how the blade channels run inside the impeller. In accordance with the selected number of vane channels, there is an overlap in the inlet area of the impeller, which can also be seen in FIG. 1, as a result of which the delivery quantity of the impeller can be influenced. With a small number of vane channels and small vane channel cross-sections and a suitable impeller inlet diameter, an impeller can be produced, the vane channels (5) of which do not overlap in the inlet area. For a given outer diameter (4), the impeller (1) shown here as an example has a number and shape of blade channels (5) which, at the impeller inlet (2) shown here, result in an overlap of the blade channels in the inlet.
Je mehr Kanäle über den Umfang verteilt angeordnet sind, auf desto größerem Durchmesser liegen dann die eigentlichen Eintrittskanten der jeweiligen Schaufelkanäle. Durch entsprechende Variation der den Laufradeintritt bildenden Saugöffnung (2) kann ebenfalls die Fördermenge beeinflußt werden.The more channels are arranged distributed over the circumference, the larger the actual leading edges of the respective blade channels are. The delivery rate can also be influenced by appropriate variation of the suction opening (2) forming the impeller inlet.
Die Öffnungen (6) weisen hierbei eine weite (w) auf, welche kleiner als die maximale weite der Schaufelkanäle (5) ausgebildet ist. Durch entsprechende Neigung der Schaufelkanäle oder der Deckscheibe läßt sich die Größe der weite (w) beeinflussen.The openings (6) have a width (w) which is smaller than the maximum width of the blade channels (5). The size of the width (w) can be influenced by a corresponding inclination of the blade channels or the cover disk.
Bei dem in Fig. 3 gezeigten Beispiel, welches einem Schnitt von III-III von Fig. 2 entspricht, ist der Verlauf der geneigt angeordneten Schaufelkanäle (5) sowie die Neigung der Laufraddeckscheiben (3, 7) erkennbar. Die Schaufelkanäle sowie die Laufraddeckscheiben verlaufen in dem hier gewählten Beispiel geneigt gegenüber senkrecht auf der Drehachse (8) stehenden Ebenen (11, 12). Dabei ist im jeweiligen Wechsel der eine Schaufelkanal zur saugseitigen Deckscheibe (3) und der daneben verlaufende Schaufelkanal zur druckseitigen Deckscheibe (7) geneigt. Durch eine entsprechende Auswahl der Neigungswinkel der Schaufelkanäle und/oder der Deckscheibenneigungswinkel ergibt sich ein Anschnitt der Schaufelkanäle im Laufradaustrittsbereich. Somit ist in einfacher Weise eine Gestaltung der eigentlichen Schaufelkanalöffnung (6) möglich bzw. deren in Fig. 2 gezeigten Weite (w) möglich. In der rechten Bildhälfte ist weiterhin dargestellt, daß dem Laufrad auf der Saugseite die Gehäusewand (9) und auf der Druckseite die Gehäusewand (10) gegenüberliegen. Diese weisen hier zwar einen parallelen Verlauf zur jeweiligen Laufraddeckscheibe auf, dies ist jedoch keine zwingende Voraussetzung. Es sind auch unterschiedliche Neigungen denkbar.In the example shown in Fig. 3, which corresponds to a section of III-III of Fig. 2, the course of the inclined blade channels (5) and the inclination of the impeller cover plates (3, 7) can be seen. In the example chosen here, the blade channels and the impeller cover disks are inclined relative to planes (11, 12) that are perpendicular to the axis of rotation (8). The alternating one blade channel is inclined to the suction-side cover plate (3) and the adjacent blade channel to the pressure-side cover plate (7). A corresponding selection of the angle of inclination of the blade channels and / or the cover plate angle of inclination results in a cut of the blade channels in the impeller outlet area. A design of the actual blade channel opening (6) or its width (w) shown in FIG. 2 is thus possible in a simple manner. The right half of the figure also shows that the impeller on the suction side is opposite the housing wall (9) and on the pressure side the housing wall (10). Although these are parallel to the respective impeller cover, this is not a mandatory requirement. Different inclinations are also conceivable.
Aus der Fig. 4 ist ersichtlich, daß im Bereich der Öffnungen (6) zwischen Laufraddeckscheibe (3) und saugseitiger Gehäusewand (9) ein Abstand (s) besteht, der kleiner ist als die Differenz (d) der am Laufradaußendurchmeser (4) meßbaren Schaufelkanalbreite (b) und der ermittelbaren Schaufelkanalbreite (b*). Für eine zuverlässige Wirkung der Öffnungen (6) darf der Abstand (s) maximal der Differenz (d) entsprechen. Ein größerer Wert würde nicht den notwendigen Effekt hervorbringen. Der in dem Ausführungsbeispiel verwendete Abstand (s) ist hier kleiner als die gezeigte Differenz (d).From Fig. 4 it can be seen that in the area of the openings (6) between the impeller cover disc (3) and the suction-side housing wall (9) there is a distance (s) which is smaller than the difference (d) which can be measured on the impeller outer diameter (4) Blade channel width (b) and the determinable blade channel width (b *). For a reliable effect of the openings (6), the distance (s) may at most correspond to the difference (d). A larger value would not produce the necessary effect. The distance (s) used in the exemplary embodiment is smaller than the difference (d) shown.
Entsprechend dem gewählten Abstand (s) ist in einfacher Weise eine Beeinflussung der Pumpenkennlinie möglich.The pump characteristic curve can be influenced in a simple manner in accordance with the selected distance (s).
Der Wert (b*) ist ermittelbar, indem die mit der Öffnung (6) versehene und dem Gehäuse nächstgelegene Schaufelkanalwand nach außen in Richtung Laufradaußendurchmesser (4) verlängert wird. Ausgehend von dem Schnittpunkt (z) zwischen Verlängerung (x) und der zylindrischen Ebene (y) des Laufradaußendurchmessers wird in den Schaufelkanal hinein die Schaufelkanalbreite (b*) ermittelt. Dies kann sowohl für die Saug- als auch für die Druckseite des Laufrades gelten.The value (b *) can be determined by extending the blade duct wall provided with the opening (6) and closest to the housing towards the outside in the direction of the outer diameter of the impeller (4). Starting from the point of intersection (z) between the extension (x) and the cylindrical plane (y) of the outer diameter of the impeller, the blade channel width (b *) is determined into the blade channel. This can apply to both the suction and the pressure side of the impeller.
Hierbei wird der Abstand (s) immer für eine Laufradseite ermittelt, also saug- oder druckseitig. Entsprechend den jeweiligen Gegebenheiten können die Abstände (s) zwischen saugseitiger Gehäusewand und Laufraddeckscheibe bzw. zwischen druckseitiger Gehäusewand und Laufraddeckscheibe gleiche oder unterschiedliche Abmessungen aufweisen. Falls die geöffneten Schaufelkanäle nur auf einer Laufradseite angebracht sind, dann entspricht der Abstand (s) maximal der Differenz (d). Bei einer beidseitigen Anbringung der geöffneten Schaufelkanäle würde sich der Abstand (s) entsprechend den auf der jeweiligen Laufradseite vorherrschenden Abmessungen orientieren.The distance (s) is always determined for one impeller side, i.e. on the suction or pressure side. Depending on the particular circumstances, the distances (s) between the suction-side housing wall and the impeller cover plate or between the pressure-side housing wall and the impeller cover plate can have the same or different dimensions. If the open vane channels are only installed on one side of the impeller, then the distance (s) corresponds at most to the difference (d). If the open vane channels were attached on both sides, the distance (s) would be based on the dimensions prevailing on the respective impeller side.
Claims (8)
- A centrifugal pump impeller (1) of the radial type and with a low specific speed of rotation, whose vane ducts (5) are defined by slots extending through the impeller cover plates (3 and 7) open towards the lateral space of the impeller, characterized in that the vane ducts (5) respectively together with the slots (6) directed towards the lateral space of the impeller define openings which are directed radially towards the outer part of the impeller, the radial length of the slotted part, which is directed axially with respect to the lateral wall of the impeller being equal to or less than half the length of a vane duct.
- The centrifugal pump impeller as claimed in claim 1, characterized in that the vane ducts (5) extend perpendicularly to the axis (8) of rotation and the surface, which is set at an angle thereto, of the cover plate (3 and 7) of the impeller intersects the vane ducts (5) obliquely in the outlet part of the impeller (1).
- The centrifugal pump impeller as claimed in claim 1, characterized in that the vane ducts (5) extend obliquely in relation to a radial plane of the impeller and the surface of the impeller cover plate obliquely intersects the vane ducts (5) in the output part of the impeller (1).
- The centrifugal pump impeller as claimed in claim 1, characterized in that the vane ducts (5) and the surface of the impeller cover plate (3 and 7) extend obliquely in relation to each other.
- The centrifugal pump impeller as claimed in claims 1 through 4, characterized in that the distance, able to be measured in the direction of the axis, between the cover plate (3 and 7) of the impeller and the opposite housing wall (9 and 10) is at the most equal to the difference (d) between the vane duct breadth (b) which is able to be measured at the impeller outlet in the axial direction, and a vane duct breadth (b*) of the vane duct as determined by outward projection of the vane duct wall at the external diameter (4) of the impeller.
- The centrifugal pump impeller as claimed in claims 1 through 5, characterized in that the openings (6) arranged in the impeller cover plates (3 and 7) of the vane ducts (5) have a configuration widening towards the external diameter.
- The centrifugal pump impeller as claimed in claims 1 through 6, characterized in that the openings (6) becoming wider in the radial direction, of the vane ducts (5) have maximum width equal to, at the most, the width of the vane ducts.
- The centrifugal pump impeller as claimed in any one or more of the claims 1 through 7, characterized in that the openings (6) of the vane ducts (5) steadily increase from the points at which they begin towards the external diameter (4) of the impeller.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| AT90900104T ATE89646T1 (en) | 1988-12-23 | 1989-12-12 | CENTRIFUGAL PUMP IMPELLER LOW SPECIFIC SPEED. |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE3843428A DE3843428C2 (en) | 1988-12-23 | 1988-12-23 | Centrifugal pump impeller with low specific speed |
| DE3843428 | 1988-12-23 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0449861A1 EP0449861A1 (en) | 1991-10-09 |
| EP0449861B1 true EP0449861B1 (en) | 1993-05-19 |
Family
ID=6369968
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP90900104A Expired - Lifetime EP0449861B1 (en) | 1988-12-23 | 1989-12-12 | Centrifugal pump impeller with low specific speed |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US5257910A (en) |
| EP (1) | EP0449861B1 (en) |
| DE (2) | DE3843428C2 (en) |
| WO (1) | WO1990007650A1 (en) |
Families Citing this family (10)
| 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 |
| DE102006040130A1 (en) * | 2006-08-26 | 2008-02-28 | Ksb Aktiengesellschaft | Delivery pump for delivery and dosing of fluid materials e.g. chemical, pharmaceutical or cosmetic components, has variable-speed drive and is configured as single-stage centrifugal pump having radial wheel |
| DE102007020218A1 (en) * | 2007-04-28 | 2008-10-30 | Ksb Aktiengesellschaft | feed pump |
| US8221070B2 (en) * | 2009-03-25 | 2012-07-17 | Woodward, Inc. | Centrifugal impeller with controlled force balance |
| PL216284B1 (en) * | 2010-03-22 | 2014-03-31 | Fundacja Rozwoju Kardiochirurgii Im Prof Zbigniewa Religi | Single-jet centrifugal pump |
| WO2014137206A1 (en) * | 2013-03-07 | 2014-09-12 | Chaushevski Nikola | Rotational chamber pump |
| CN106537195B (en) * | 2014-07-24 | 2019-12-06 | 日产化学工业株式会社 | Resin composition for forming color filter underlayer film |
| US9777741B2 (en) | 2014-11-20 | 2017-10-03 | Baker Hughes Incorporated | Nozzle-shaped slots in impeller vanes |
| JP6904622B1 (en) * | 2020-04-10 | 2021-07-21 | セイコー化工機株式会社 | Magnetic levitation pump |
| CN114483641B (en) * | 2022-02-15 | 2023-06-16 | 上海工业泵制造有限公司 | Impeller and water pump using same |
Family Cites Families (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CA644854A (en) * | 1962-07-17 | Patay Pumps And Turbines Limited | Rotary tube pumps, turbines and the like | |
| NL102212C (en) * | ||||
| DE1249693B (en) * | ||||
| FR529613A (en) * | 1920-12-21 | 1921-12-02 | Multitubular centrifugal pump | |
| US1986836A (en) * | 1933-01-09 | 1935-01-08 | Fairbanks Morse & Co | Method of making centrifugal pumps |
| US2074650A (en) * | 1934-01-24 | 1937-03-23 | William S Holdaway | Centrifugal pump |
| US1988875A (en) * | 1934-03-19 | 1935-01-22 | Saborio Carlos | Wet vacuum pump and rotor therefor |
| GB575346A (en) * | 1944-03-01 | 1946-02-14 | Aluminium Plant & Vessel Co | Improvements in or relating to centrifugal pumps |
| DE804064C (en) * | 1944-03-01 | 1951-04-16 | Apv Co Ltd | Impeller for centrifugal pumps, especially for conveying milk |
| US2684062A (en) * | 1950-11-18 | 1954-07-20 | Rose David | Centrifugal projector |
| US2956503A (en) * | 1956-02-15 | 1960-10-18 | Neidl Georg | Rotary pumps, particularly for delivery of sewage, thick slurries and the like liquids |
| US3107625A (en) * | 1961-09-01 | 1963-10-22 | Walter E Amberg | Centrifugal liquid pump |
| DE1453723A1 (en) * | 1963-07-19 | 1969-07-31 | Barske Ulrich Max | Centrifugal pump, especially for small to medium conveying flows |
| SU620674A1 (en) * | 1976-09-21 | 1978-08-25 | Предприятие П/Я Р-6603 | Centrifugal wheel |
| SU928080A1 (en) * | 1980-09-25 | 1982-05-15 | Специальное Конструкторско-Технологическое Бюро Герметичных И Скважинных Насосов | Centrifugal pump impeller |
| SU1052053A1 (en) * | 1982-04-29 | 1984-10-30 | Uskov G I | Centrifugal pump |
| IT1187933B (en) * | 1986-02-25 | 1987-12-23 | Gilardini Spa | ROTARY PUMP FOR LIQUIDS |
-
1988
- 1988-12-23 DE DE3843428A patent/DE3843428C2/en not_active Expired - Fee Related
-
1989
- 1989-12-12 US US07/691,049 patent/US5257910A/en not_active Expired - Fee Related
- 1989-12-12 EP EP90900104A patent/EP0449861B1/en not_active Expired - Lifetime
- 1989-12-12 WO PCT/EP1989/001522 patent/WO1990007650A1/en active IP Right Grant
- 1989-12-12 DE DE9090900104T patent/DE58904451D1/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| DE58904451D1 (en) | 1993-06-24 |
| DE3843428A1 (en) | 1990-07-05 |
| DE3843428C2 (en) | 1993-12-09 |
| US5257910A (en) | 1993-11-02 |
| EP0449861A1 (en) | 1991-10-09 |
| WO1990007650A1 (en) | 1990-07-12 |
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