EP1325232A1 - Centrifugal wheel pump - Google Patents

Centrifugal wheel pump

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Publication number
EP1325232A1
EP1325232A1 EP01986749A EP01986749A EP1325232A1 EP 1325232 A1 EP1325232 A1 EP 1325232A1 EP 01986749 A EP01986749 A EP 01986749A EP 01986749 A EP01986749 A EP 01986749A EP 1325232 A1 EP1325232 A1 EP 1325232A1
Authority
EP
European Patent Office
Prior art keywords
blades
impeller
bearing tube
impeller according
angle
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.)
Granted
Application number
EP01986749A
Other languages
German (de)
French (fr)
Other versions
EP1325232B1 (en
Inventor
Manfred Britsch
Leonard Wald
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Allweiler GmbH
Original Assignee
Allweiler AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Allweiler AG filed Critical Allweiler AG
Publication of EP1325232A1 publication Critical patent/EP1325232A1/en
Application granted granted Critical
Publication of EP1325232B1 publication Critical patent/EP1325232B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F04D29/242—Geometry, shape
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2277—Rotors specially for centrifugal pumps with special measures for increasing NPSH or dealing with liquids near boiling-point

Definitions

  • the invention relates to an impeller for a centrifugal pump with a bearing tube, which contains an axial bore for receiving a pump shaft and which is provided with blades for guiding a liquid flow - between a suction area and a pressure area.
  • a centrifugal pump with an impeller provided on the front stepped end of an inner shaft with an axial bore can be found in DE 41 08 257 C2 by the applicant.
  • This impeller rotates in a spiral housing - screwed to a bearing bracket housing with the housing cover and seals interposed. There is a plain bearing in the housing cover.
  • helical axial ballasts with their own head - so-called inducers - can be used, which increase the static pressure in the suction mouth of the subsequent radial wheel.
  • inducers it is possible to achieve a substantial reduction - up to 50% - of the so-called NPSH value ("Net Positive Suction Head") from the best efficiency point to the minimum output.
  • NPSH3% value Net Positive Suction Head
  • That NPSH3% value in pump construction describes in general the net energy level in the inlet cross-section of the pump, at which the pump head drops by 3%.
  • the net energy level is the absolute energy level minus the evaporation pressure level.
  • NPSH vapor pressure
  • NPSHA existing NPSH
  • NPSHR pump-specific value
  • the inventor set himself the task of developing an impeller for radial centrifugal pumps with significantly better NPSH values without deteriorating the other performance data of the centrifugal pump.
  • the rigidity and strength of the construction are to be increased and there is less power loss as a result of the gap flow at the impeller blades.
  • This impeller should be technically easy to implement - with the lowest possible manufacturing costs.
  • an even number of blades are molded onto the bearing tube, of which every second is guided beyond the outer edges of two adjacent shorter blades in the direction of the longitudinal axis of the bearing tube.
  • These blades preferably extend equidistantly from one another from the bearing tube and are also guided in a spiral - or spindle-like manner - around the bearing tube.
  • the inlet-side outer edges of the long blades are arranged at an angle - to a straight line in the diameter of the bearing tube - which is adapted to the respective operating point.
  • the course of these leading edges is drawn obliquely backwards. It has proven to be advantageous to have the inlet-side outer edges of the short blades run at an entry angle to a straight line of the diameter of the bearing tube and to adapt the entry angle of the short blades to the local flow conditions.
  • the entry angles of the long blades are larger than the angle between the direction of rotation of the blades of the inflow in the relative system.
  • the exit angles should apply to everyone. Shovels be the same; the outlet-side end edges of the blades enclose an acute angle between 10 ° and 20 ° - preferably about 15 ° - with an axis parallel.
  • impeller ring or a cover disk extends according to the invention from the end edges of the blades to the outer edges of the short blades on the inlet side. It is also important that the impeller ring should protrude slightly from the outer edges of the short blades.
  • the impeller ring has a part-circular curvature in longitudinal section, which merges into a region that ends at a front edge and is approximately axially parallel; the area of the impeller ring adjoining the front edge should contain a step.
  • the outer surface of the impeller ring delimits a sealing gap with the inner surface of a housing wall that is spaced apart; the cover disk or the impeller ring extends from the impeller outlet to just over the leading edge of the short blades, where that suction-side sealing gap is located.
  • the stiffness and strength of the construction are increased in particular by the impeller ring or the cover disk.
  • the shape of the impeller according to the invention leads to the following advantages:
  • Figure 1 is an oblique view of an impeller with an impeller ring for a centrifugal pump.
  • Fig. 3 the front view of the impeller
  • Fig. 7 is a sketch to illustrate an entry angle.
  • the length a of approximately 315 mm and the outer diameter d of, for example, 90 mm is rearward of a bearing tube 18 which is provided with a through hole 12 in the longitudinal axis A. a radial wall 20 is formed.
  • the through-bore 12 has between two end sections 14, 14 e of the diameter d ⁇ of approximately 50 mm a central section 15 of larger diameter d 2 of approximately 60 mm, which is located on the left-hand side in FIG. 2 for the liquid in FIG. 2.
  • - Shorter end section 14 reduced by means of a conical shoulder area 16. This end section 14 adjoins an annular end face 17 of the bearing tube 18.
  • the impeller 10 is rotatably mounted in a housing of the centrifugal pump, not shown, between a suction and a pressure chamber for conveying a liquid.
  • the inner contour K of the radial wall 20 is determined in the longitudinal section of FIG. 2 between the outer tube surface 19 of the bearing tube 18 and an annular outer edge 22 of the radial wall 20 by a partial arc.
  • an essentially radial longitudinal sectional contour Q forms a back surface 24 of the radial wall 20, from which a coaxial ring wall 26 of low height h of 20 mm is formed.
  • the distance z of the back surface 24 from the adjacent end wall 17 e of the bearing tube 18 - and thus its free rear cantilever length - measures here about 50 mm.
  • the longitudinal section of the impeller ring 30 is formed from the ring edge 28 by a partial arc section Ki which merges axially into a wall section parallel to the longitudinal axis A; this ends at a front edge 32 which is stepped longitudinally by a change of the impeller ring 30 at 31 - in turn annular - its diameter e._ of here 290 mm corresponds to approximately three quarters of the mentioned diameter e.
  • an even number of blades 36, 36 n which are designed in the form of a helix in their longitudinal extent, is arranged; every second blade 36 is brought with its outer edge 38 - in a spiral shape - close to the entry-side end face 17 of the bearing tube 18. Between each of these two long blades 36 there is a short blade 36 n , the outer edge 38 n of which is located within the impeller ring 30. End-side end edges 40, 40 n of the blades 36, 36 n extend between the annular outer edge 22 of the radial wall 20 and the parallel ring edge 28 of the impeller ring 30.
  • the blades 36, 36 n are formed both on the bearing tube 18 or its radial wall 20 and on the impeller ring 30, and the long blades 36 protrude - as described - in the axial direction from the front edge 32 of the impeller ring 30. There is their side edge 38 curved according to that helix, as is particularly illustrated in FIG. 5.
  • a section of a housing wall 42 is assigned to the impeller ring 30, the longitudinal surface of which is provided on its inner surface 44 with an inner step 46 opposite the step 31 of the impeller ring 30.
  • the latter ends at an outer step 48, which runs at a distance n parallel to the front edge 32 of the impeller ring 30. So arises between this and the housing wall 42 Sealing gap 50 with a gap length c of approximately 15 to 20 mm and a gap width q of 0.3 to 0.5 mm here.
  • the entry angles s x of the short legs 36 n are selected such that they correspond to the local inflow angles of the flow in the area of the operating point of the pump.

Abstract

The invention relates to a centrifugal wheel pump comprising a bearing tube (18) which contains an axial bore hole (12) for receiving a pump shaft, and blades (36, 36n) for guiding a liquid flow between a suction area and a pressure area. Said blades (36, 36n), formed in an even number, are provided on the bearing tube (18), emanate therefrom and are arranged at an equal distance from each other. Among said blades (36) which are disposed in a spiral or spindle shaped manner around the bearing tube (18), every second blade is guided along the outside edge (38n) of two shorter neighbouring blades (36n), in the direction of the longitudinal axis (A) of the bearing tube (18). Furthermore, the outside edges (38) next to the input side of the long blades (36) extend at an inlet angle with the straight diameter of the bearing tube (18), said angle being adapted to each respective working point.

Description

Laufrad für eine Kreiselpumpe Impeller for a centrifugal pump
Die Erfindung betrifft ein Laufrad für eine Kreiselpumpe mit einem Lagerrohr, das eine axiale Bohrung zur Aufnahme einer Pumpenwelle enthält und das mit Schaufeln zum Führen eines Flüssigkeitsstromes -- zwischen einem Saugbereich und einem Druckbereich -- versehen ist.The invention relates to an impeller for a centrifugal pump with a bearing tube, which contains an axial bore for receiving a pump shaft and which is provided with blades for guiding a liquid flow - between a suction area and a pressure area.
Eine Kreiselpumpe mit auf dem vorderen gestuften Ende einer innenliegenden Welle mit axialer Bohrung vorgesehenem Laufrad ist der DE 41 08 257 C2 der Anmelderin zu entnehmen. Dieses Laufrad dreht sich in einem -- mit einem Lager- tragergehäuse unter Zwischenschaltung von Gehäusedeckel und Dichtungen verschraubten -- Spiralgehäuse. Im Gehäusedeckel befindet sich ein Gleitlager.A centrifugal pump with an impeller provided on the front stepped end of an inner shaft with an axial bore can be found in DE 41 08 257 C2 by the applicant. This impeller rotates in a spiral housing - screwed to a bearing bracket housing with the housing cover and seals interposed. There is a plain bearing in the housing cover.
Zur Verbesserung der Saugfähigkeit von radialen Kreiselpumpen können schneckenförmige axiale Vorschaltläufer mit eigener Förderhöhe -- sog. Inducer -- eingesetzt werden, die den statischen Druck im Saugmund des anschließenden Radialrades erhöhen. Mit den derzeitigen Inducern vermag man eine wesentliche Reduktion -- bis zu 50 % -- des sog. NPSH- Wertes ("Net Positive Suction Head") vom Wirkungsgradbestpunkt bis zur Mindestfördermenge zu erreichen. Zur Bewertung des Saugverhaltens hat sich der sog. NPSH3 %-Wert durchgesetzt, der verhältnismäßig leicht für verschiedene Voiumenströme gemessen werden kann. Jener NPSH3 %-Wert beschreibt im Pumpenbau ganz allgemein die Netto-Energiehohe im Eintrittsquerschnitt der Pumpe, bei der die Förderhöhe der Pumpe um 3 % abfällt. Die Netto-Energiehohe ist die absolute Energiehόhe abzüglich der Verdampfungsdruckhöhe. Dabei ist die Verdampfungsdruckhöhe HD = pD/ mit demTo improve the absorbency of radial centrifugal pumps, helical axial ballasts with their own head - so-called inducers - can be used, which increase the static pressure in the suction mouth of the subsequent radial wheel. With the current inducers it is possible to achieve a substantial reduction - up to 50% - of the so-called NPSH value ("Net Positive Suction Head") from the best efficiency point to the minimum output. To evaluate the suction behavior, the so-called NPSH3% value has become established, which can be measured relatively easily for different volume flows. That NPSH3% value in pump construction describes in general the net energy level in the inlet cross-section of the pump, at which the pump head drops by 3%. The net energy level is the absolute energy level minus the evaporation pressure level. The evaporation pressure level is H D = p D / with the
Dampfdruck pD zu berechnen, der zu der im Eintrittsquerschnitt der Pumpe herrschenden Temperatur gehört. Wie bei der spezifischen Halteenergie unterscheidet man auch beim NPSH-Wert zwischen einem auf die Anlage bezogenen Wert NPSHA (vorhandener NPSH) und einem pumpenspezifischen Wert NPSHR (erforderlicher NPSH) .To calculate vapor pressure p D , which belongs to the temperature prevailing in the inlet cross section of the pump. As with the specific holding energy, a distinction is also made between the NPSH value and a value related to the system NPSHA (existing NPSH) and a pump-specific value NPSHR (required NPSH).
Bei Versuchen, die Saugfähigkeit zu verbessern, stieß man schnell an Grenzen, von denen aus es zu keiner weiteren Minderung der NPSH-Werte kam oder aber andere Kenngrößen der Pumpe deutlich verschlechtert wurden. Gute NPSH-Werte können derzeit nur durch den Einsatz eines Inducers erreicht werden. Dessen Verwendung führt jedoch zu höheren Herstellungskosten, zu einer Verschlechterung des Wirkungsgrades, zu vermehrten Geräuschemissionen und erfordert zudem ein spezielles Saugrohr, außerdem oftmals eine modifizierte Antriebswelle.Attempts to improve the absorbency quickly reached limits from which there was no further reduction in the NPSH values or other parameters of the pump deteriorated significantly. Good NPSH values can currently only be achieved by using an inducer. However, its use leads to higher manufacturing costs, to a deterioration in efficiency, to increased noise emissions and also requires a special intake manifold and also often a modified drive shaft.
In Kenntnis dieses Standes der Technik hat sich der Erfinder die Aufgabe gestellt, ein Laufrad für radiale Kreiselpumpen mit deutlich besseren NPSH-Werten zu entwickeln, ohne die sonstigen Leistungsdaten der Kreiselpumpe zu verschlechtern. Zudem sollen die Steifigkeit und Festigkeit der Konstruktion erhöht werden sowie geringerer Leistungsverlust infolge der Spaltströmung an den Laufradschaufeln entstehen. Dieses Laufrad soll sich -- bei möglichst geringen Herstellungskosten -- technisch gut realisieren lassen.Knowing this state of the art, the inventor set himself the task of developing an impeller for radial centrifugal pumps with significantly better NPSH values without deteriorating the other performance data of the centrifugal pump. In addition, the rigidity and strength of the construction are to be increased and there is less power loss as a result of the gap flow at the impeller blades. This impeller should be technically easy to implement - with the lowest possible manufacturing costs.
Zur Lösung dieser Aufgabe führt die Lehre des unabhängigen Anspruches, die Unteransprüche gegen günstige Weiterbildungen an. Zudem fallen in den Rahmen der Erfindung alle Kombinationen aus zumindest zwei der in der Beschreibung, der Zeichnung und/oder den Ansprüchen offenbarten Merkmale.The teaching of the independent claim leads to the solution of this task, the subclaims against favorable further training. In addition, all combinations of at least two of the features disclosed in the description, the drawing and / or the claims fall within the scope of the invention.
Erfindungsgemäß wird an das Lagerrohr eine gerade Anzahl von Schaufeln angeformt, von denen jede zweite über die Außenkanten zweier benachbarter kürzerer Schaufeln hinaus in Richtung der Längsachse des Lagerrohres geführt wird. Diese Schaufeln gehen vom Lagerrohr bevorzugt zueinander äquidistant aus und sind zudem spiralartig — oder spindelartig -- um das Lagerrohr geführt. Es hat sich nämlich gezeigt, dass der NPSH3%-Wert der Pumpe entscheidend von der Laufradform beeinflusst wird und herkömmliche Laufräder für radiale Kreiselpumpen mit in der Regel fünf oder sieben geometrisch gleichen Schaufeln zu keinem günstigen Ergebnis führen. So zeichnet sich die neue Laufradform vor allem dadurch aus, dass sie eine gerade Anzahl von Schaufeln besitzt -- in der Regel vier, sechs oder acht Schaufeln --, wobei jede zweite Schaufel spiralförmig weit in axialer Richtung nach vorne verlängert ist .According to the invention, an even number of blades are molded onto the bearing tube, of which every second is guided beyond the outer edges of two adjacent shorter blades in the direction of the longitudinal axis of the bearing tube. These blades preferably extend equidistantly from one another from the bearing tube and are also guided in a spiral - or spindle-like manner - around the bearing tube. It has been shown that the NPSH3% value of the pump is decisively influenced by the shape of the impeller and that conventional impellers for radial centrifugal pumps with generally five or seven geometrically identical blades do not lead to a favorable result. The new impeller shape is characterized primarily by the fact that it has an even number of blades - usually four, six or eight blades - with every second blade being spirally extended forward in the axial direction.
Nach einem weiteren Merkmal der Erfindung sind die einlauf- seitigen Außenkanten der langen Schaufeln in einem Winkel - - zu einer Durchmessergeraden des Lagerrohres -- angeordnet, der dem jeweiligen Betriebspunkt angepasst ist. Der Verlauf dieser Eintrittskanten ist dabei schräg nach hinten gezogen. Als günstig hat es sich dazu erwiesen, die einlaufseitigen Außenkanten der kurzen Schaufeln in einem Eintrittswinkel zu einer Durchmessergeraden des Lagerrohres verlaufen zu lassen sowie den Eintrittswinkel der kurzen Schaufeln an die lokalen Strόmungsverhältnisse anzupassen.According to a further feature of the invention, the inlet-side outer edges of the long blades are arranged at an angle - to a straight line in the diameter of the bearing tube - which is adapted to the respective operating point. The course of these leading edges is drawn obliquely backwards. It has proven to be advantageous to have the inlet-side outer edges of the short blades run at an entry angle to a straight line of the diameter of the bearing tube and to adapt the entry angle of the short blades to the local flow conditions.
Erfindungsgemäß sind dazu die Eintrittswinkel der langen Schaufeln größer als die Winkel zwischen der Drehrichtung der Schaufeln der Zuströ ung im Relativsystem.According to the invention, the entry angles of the long blades are larger than the angle between the direction of rotation of the blades of the inflow in the relative system.
Hingegen sollen die Austrittswinkel bei allen. Schaufeln gleich sein; die auslaufseitigen Endkanten der Schaufeln schließen mit einer Achsparallelen einen spitzen Winkel zwischen 10° und 20° — bevorzugt etwa 15° — ein.On the other hand, the exit angles should apply to everyone. Shovels be the same; the outlet-side end edges of the blades enclose an acute angle between 10 ° and 20 ° - preferably about 15 ° - with an axis parallel.
Im Rahmen der Erfindung liegt es, dass sich jene auslaufseitigen Endkanten der Schaufeln einends an eine Radialwand des Lagerrohres sowie andernends an einen zur Radialwand etwa parallelen Laufradring anschließen sollen. Zudem erstreckt sich der Laufradring bzw. eine Deckscheibe erfindungsgemäß von den Endkanten der Schaufeln bis an die eintrittsseitigen Außenkanten der kurzen Schaufeln. Von Bedeutung ist auch, dass der Laufradring die Außenkanten der kurzen Schaufeln geringfügig überragen soll. Nach einem anderen Merkmal weist der Laufradring längsschnittlich eine teilkreisförmige Krümmung auf, die in einen an einer Frontkante endenden etwa achsparallelen Bereich übergeht; der an die Frontkante anschließende Bereich des Laufradringes soll eine Stufung enthalten.It is within the scope of the invention that those outlet-side end edges of the blades should be connected at one end to a radial wall of the bearing tube and at the other end to an impeller ring approximately parallel to the radial wall. In addition, the impeller ring or a cover disk extends according to the invention from the end edges of the blades to the outer edges of the short blades on the inlet side. It is also important that the impeller ring should protrude slightly from the outer edges of the short blades. According to another characteristic, the impeller ring has a part-circular curvature in longitudinal section, which merges into a region that ends at a front edge and is approximately axially parallel; the area of the impeller ring adjoining the front edge should contain a step.
Von Vorteil ist auch, dass die Außenfläche des Laufradringes mit der Innenfläche einer in Abstand gegenüberstehenden Gehäusewand einen Dichtspalt begrenzt; die Deckscheibe bzw. der Laufradring erstreckt sich vom Laufradaustritt bis knapp über die Eintrittskante der kurzen Schaufeln, wo sich jener saugseitige Dichtspalt befindet .It is also advantageous that the outer surface of the impeller ring delimits a sealing gap with the inner surface of a housing wall that is spaced apart; the cover disk or the impeller ring extends from the impeller outlet to just over the leading edge of the short blades, where that suction-side sealing gap is located.
Insbesondere durch den Laufradring bzw. die Deckscheibe wird die Steifigkeit und Festigkeit der Konstruktion erhöht. Zudem führt die erfindungsgemäße Form des Laufrades noch zu den folgenden Vorteilen:The stiffness and strength of the construction are increased in particular by the impeller ring or the cover disk. In addition, the shape of the impeller according to the invention leads to the following advantages:
• deutlich bessere NPSH-Werte gegenüber herkömmlichen Radiallaufrädern ;• significantly better NPSH values than conventional radial impellers;
• geringere Leistungsverluste infolge der Spaltströmung an den Laufradschaufeln;• lower power losses due to the gap flow at the impeller blades;
• keine wesentliche Verschlechterung der sonstigen Leistungsdaten;• no significant deterioration in other performance data;
• keine wesentliche Erhöhung der Hersteilungskosten gegenüber einem normalen Laufrad;• no significant increase in manufacturing costs compared to a normal impeller;
• niedrigere Herstellungskosten als die eines normalen Laufrades mit Inducer;• lower manufacturing costs than a normal impeller with inducer;
• verminderte Geräuschemission gegenüber Laufrädern mit Inducer; o kürzere axiale Abmessungen als ein normales Laufrad mit Inducer. Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung eines bevorzugten Ausführungsbeispiels sowie anhand der Zeichnung; diese zeigt in• reduced noise emissions compared to impellers with inducers; o Shorter axial dimensions than a normal impeller with an inducer. Further advantages, features and details of the invention emerge from the following description of a preferred exemplary embodiment and with reference to the drawing; this shows in
Fig. 1 eine Schrägsicht auf ein Laufrad mit Laufradring für eine Kreiselpumpe;Figure 1 is an oblique view of an impeller with an impeller ring for a centrifugal pump.
Fig. 2, 4 jeweils einen Längsschnitt durch das Laufrad in dessen Längsachse nach Linie II - II der Fig. 1 bzw. Linie IV-IV der Fig. 3;2, 4 each show a longitudinal section through the impeller in its longitudinal axis along line II-II of FIG. 1 and line IV-IV of FIG. 3;
Fig. 3: die Frontsicht auf das Laufrad;Fig. 3: the front view of the impeller;
Fig. 5: eine Schrägsicht auf das Laufrad ohne Laufradring;5: an oblique view of the impeller without the impeller ring;
Fig. 6; den vergrößerten Längsschnitt des Laufradringes mit einem zugeordneten Gehäuseabschnitt ;Fig. 6; the enlarged longitudinal section of the impeller ring with an associated housing section;
Fig. 7 eine Skizze zur Darstellung eines Eintrittswinkels .Fig. 7 is a sketch to illustrate an entry angle.
Bei einem Laufrad 10 für eine aus Gründen der Übersichtlichkeit ansonsten nicht dargestellte Kreiselpumpe ist an ein -- in der Längsachse A mit einer Durchgangsbohrung 12 ausgestattetes -- Lagerrohr 18 der Lange a von etwa 315 mm und des Außendurchmessers d von beispielsweise 90 mm heck- wärts eine Radialwand 20 angeformt. Die Durchgangsbohrung 12 weist zwischen zwei Endabschnitten 14, 14e des Durchmessers dλ von etwa 50 mm einen Mittelabschnitt 15 größeren Durchmessers d2 von etwa 60 mm auf, der sich zu deren an der Eintrittsseite für die Flüssigkeit befindlichen — in Fig. 2 linken -- kürzeren Endabschnitt 14 mittels eines konischen Schulterbereiches 16 reduziert. Dieser Endabschnitt 14 schließt an eine ringförmige Stirnfläche 17 des Lagerrohres 18 an.In the case of an impeller 10 for a centrifugal pump, which is otherwise not shown for reasons of clarity, the length a of approximately 315 mm and the outer diameter d of, for example, 90 mm is rearward of a bearing tube 18 which is provided with a through hole 12 in the longitudinal axis A. a radial wall 20 is formed. The through-bore 12 has between two end sections 14, 14 e of the diameter d λ of approximately 50 mm a central section 15 of larger diameter d 2 of approximately 60 mm, which is located on the left-hand side in FIG. 2 for the liquid in FIG. 2. - Shorter end section 14 reduced by means of a conical shoulder area 16. This end section 14 adjoins an annular end face 17 of the bearing tube 18.
Das Laufrad 10 ist in einem Gehäuse der nicht gezeigten Kreiselpumpe zwischen einem Saug- und einem Druckraum zum Fördern einer Flüssigkeit drehbar gelagert.The impeller 10 is rotatably mounted in a housing of the centrifugal pump, not shown, between a suction and a pressure chamber for conveying a liquid.
Die Innenkontur K der Radialwand 20 wird im Längsschnitt der Fig. 2 zwischen der Rohraußenfläche 19 des Lagerrohres 18 sowie einer ringförmigen Außenkante 22 der Radialwand 20 von einem Teilkreisbogen bestimmt. Andererseits bildet eine i. w. radiale Längsschnittkontur Q eine Rückenfläche 24 der Radialwand 20, aus der eine koaxiale Ringwand 26 geringer Hohe h von 20 mm herausgeformt ist. Der Abstand z der Rückenfläche 24 von der benachbarten Stirnwand 17e des Lagerrohres 18 -- und damit dessen freie rückwärtige Kraglänge -- misst hier etwa 50 mm.The inner contour K of the radial wall 20 is determined in the longitudinal section of FIG. 2 between the outer tube surface 19 of the bearing tube 18 and an annular outer edge 22 of the radial wall 20 by a partial arc. On the other hand, an essentially radial longitudinal sectional contour Q forms a back surface 24 of the radial wall 20, from which a coaxial ring wall 26 of low height h of 20 mm is formed. The distance z of the back surface 24 from the adjacent end wall 17 e of the bearing tube 18 - and thus its free rear cantilever length - measures here about 50 mm.
In einem axialen Abstand i (hier 85 mm) von der Außenkante 22 der Radialwand 20 verläuft eine Ringkante 28 eines Laufradringes oder einer Deckscheibe 30 der Breite b von etwa 50 mm sowie eines Durchmessers e von 375 mm, der jenem der Außenkante 22 entspricht und etwas größer ist als der vierfache Außendurchmesser d des Lagerrohres 18 bzw. jenes Abstandes i zwischen Radialwand 20 und Laufradring 30.At an axial distance i (here 85 mm) from the outer edge 22 of the radial wall 20 runs an annular edge 28 of an impeller ring or a cover plate 30 of width b of approximately 50 mm and a diameter e of 375 mm, which corresponds to that of the outer edge 22 and somewhat is greater than four times the outer diameter d of the bearing tube 18 or that distance i between the radial wall 20 and the impeller ring 30.
Der Längsschnitt des Laufradringes 30 wird von der Ringkante 28 ab durch einen Teilkreisbogenabschnitt Ki gebildet, der achswärts in einen zur Längsachse A parallelen Wandabschnitt übergeht; dieser endet an einer längsschnittlich durch eine Ändrehung des Laufradringes 30 bei 31 gestuften -- ihrerseits ringförmigen -- Frontkante 32. Deren Durchmesser e._ von hier 290 mm entspricht etwa drei Vierteln des erwähnten Durchmessers e. In einem von der Radialwand 20 und dem Laufradring 30 begrenzten Zwischenraum 34 ist eine gerade Zahl von — in ihrer Längserstreckung schraubenlinienartig gestalteten -- Schaufeln 36, 36n angeordnet; jede zweite Schaufel 36 ist mit ihrer Außenkante 38 — spiralförmig -- nahe an die ein- trittsseitige Stirnfläche 17 des Lagerrohres 18 herangeführt. Zwischen jeweils zwei dieser langen Schaufeln 36 verläuft eine kurze Schaufel 36n, deren Außenkante 38n sich innerhalb des Laufradringes 30 befindet. Zwischen der ringförmigen Außenkante 22 der Radialwand 20 und der parallelen Ringkante 28 des Laufradringes 30 erstrecken sich auslauf- seitige Endkanten 40, 40n der Schaufeln 36, 36n. Sie verlaufen in einem spitzen Winkel w von etwa 15° zu einer Achsparallelen Ai . Dieser auslaufseitige Neigungswinkel w ist für alle Schaufeln 36, 36n bzw. Endkanten 40, 40n von gleicher Größe, wohingegen die sog. Eintrittswinkel s bzw. Si an den einlaufseitigen Außenkanten 38 bzw. 38n zu Durchmessergeraden D unterschiedlich sind; die Eintrittswinkel y der langen Schaufeln 36 sind an den jeweiligen Betriebspunkt angepasst, die Eintrittswinkel y^ der kurzen Schaufeln 36n an die lokalen Strömungsverhältnisse (Fig. 5) .The longitudinal section of the impeller ring 30 is formed from the ring edge 28 by a partial arc section Ki which merges axially into a wall section parallel to the longitudinal axis A; this ends at a front edge 32 which is stepped longitudinally by a change of the impeller ring 30 at 31 - in turn annular - its diameter e._ of here 290 mm corresponds to approximately three quarters of the mentioned diameter e. In an intermediate space 34 delimited by the radial wall 20 and the impeller ring 30, an even number of blades 36, 36 n, which are designed in the form of a helix in their longitudinal extent, is arranged; every second blade 36 is brought with its outer edge 38 - in a spiral shape - close to the entry-side end face 17 of the bearing tube 18. Between each of these two long blades 36 there is a short blade 36 n , the outer edge 38 n of which is located within the impeller ring 30. End-side end edges 40, 40 n of the blades 36, 36 n extend between the annular outer edge 22 of the radial wall 20 and the parallel ring edge 28 of the impeller ring 30. They run at an acute angle w of about 15 ° to an axis parallel Ai. This outlet-side angle of inclination w is of the same size for all blades 36, 36 n or end edges 40, 40 n , whereas the so-called entry angles s or Si on the inlet-side outer edges 38 or 38 n differ from straight lines D in diameter; the entry angles y of the long blades 36 are adapted to the respective operating point, the entry angles y ^ of the short blades 36 n to the local flow conditions (FIG. 5).
Die Schaufeln 36, 36n sind sowohl an das Lagerrohr 18 bzw. seine Radialwand 20 als auch an den Laufradring 30 angeformt, und die langen Schaufeln 36 überragen -- wie beschrieben -- in Achsrichtung die Frontkante 32 des Laufradringes 30. Dort ist ihre Seitenkante 38 entsprechend jener Schraubenlinie gekrümmt, wie vor allem Fig. 5 verdeutlicht .The blades 36, 36 n are formed both on the bearing tube 18 or its radial wall 20 and on the impeller ring 30, and the long blades 36 protrude - as described - in the axial direction from the front edge 32 of the impeller ring 30. There is their side edge 38 curved according to that helix, as is particularly illustrated in FIG. 5.
In Fig. 6 ist dem Laufradring 30 ein Abschnitt einer Gehausewand 42 zugeordnet, die an ihrer Innenfläche 44 längs- schnittlich mit einer -- der Stufung 31 des Laufradringes 30 gegenüberliegenden — inneren Stufe 46 versehen ist. Letztere endet an einer äußeren Stufe 48, die in Abstand n parallel zur Frontkante 32 des Laufradringes 30 verlauft. So entsteht zwischen diesem und der Gehausewand 42 ein Dichtspalt 50 einer Spaltlänge c von etwa 15 bis 20 mm und einer Spaltweite q von hier 0,3 bis 0,5 mm.In FIG. 6, a section of a housing wall 42 is assigned to the impeller ring 30, the longitudinal surface of which is provided on its inner surface 44 with an inner step 46 opposite the step 31 of the impeller ring 30. The latter ends at an outer step 48, which runs at a distance n parallel to the front edge 32 of the impeller ring 30. So arises between this and the housing wall 42 Sealing gap 50 with a gap length c of approximately 15 to 20 mm and a gap width q of 0.3 to 0.5 mm here.
Im Schnitt einer langen Schaufel 36 nach Fig. 7 sind deren Eintrittskante mit 37 und die Laufraddrehrichtung mit x, die Zuströmrichtung im Absolutsystem mit y bezeichnet. Die Eintrittswinkel s der langen Schaufeln 36 sind so an den Betriebspunkt angepasst, dass diese 4° bis 10° größer sind als die Eintrittswinkel t der Zuströmrichtung yι im Relativsystem.In the section of a long blade 36 according to FIG. 7, its leading edge is denoted by 37 and the impeller direction of rotation by x, the inflow direction in the absolute system by y. The entry angles s of the long blades 36 are adapted to the operating point in such a way that they are 4 ° to 10 ° larger than the entry angles t of the inflow direction y 1 in the relative system.
Die Eintrittswinkel sx der kurzen Schenkeln 36n sind so gewählt, dass diese im Bereich des Betriebspunktes der Pumpe den Örtlichen Zuströmwinkeln der Strömung entsprechen. The entry angles s x of the short legs 36 n are selected such that they correspond to the local inflow angles of the flow in the area of the operating point of the pump.

Claims

PATENTÄNSPRUCHE PATENTÄNSPRUCHE
1. Laufrad für eine Kreiselpumpe mit einem Lagerrohr1. Impeller for a centrifugal pump with a bearing tube
(18), das eine axiale Bohrung (12) zur Aufnahme einer Pumpenwelle enthält und das mit Schaufeln (36, 36n) zum Führen eines Flüssigkeitsstromes zwischen einem Saugbereich und einem Druckbereich versehen ist,(18), which contains an axial bore (12) for receiving a pump shaft and which is provided with blades (36, 36 n ) for guiding a liquid flow between a suction area and a pressure area,
dadurch gekennzeichnet,characterized,
dass jede zweite der an das Lagerrohr (18) in gerader Anzahl angeformten Schaufeln (36, 36n) über die Außenkante (38n) zweier benachbarter kürzerer Schaufeln (36n) hinaus in Richtung der Längsachse (A) des Lagerrohres (18) geführt ist.that every second one of the blades (36, 36 n ) formed onto the bearing tube (18) in an even number extends beyond the outer edge (38 n ) of two adjacent shorter blades (36 n ) in the direction of the longitudinal axis (A) of the bearing tube (18) is.
2. Laufrad nach Anspruch 1, dadurch gekennzeichnet, dass die auslaufseitigen Endkanten (40, 40n) der Schaufeln2. Impeller according to claim 1, characterized in that the outlet-side end edges (40, 40 n ) of the blades
(36, 36n) einends an eine Radialwand (20) des Lagerrohres (18) anschließen sowie andernends an einen zur Radialwand etwa parallelen Laufradring (30) .(36, 36 n ) at one end to a radial wall (20) of the bearing tube (18) and at the other to an approximately parallel to the radial wall impeller ring (30).
3. Laufrad nach Anspruch 2, dadurch gekennzeichnet, dass sich der Laufradring (30) von den Endkanten (40, 40n) der Schaufeln (36, 36n) bis an die eintrittseitigen Außenkanten (38n) der kurzen Schaufeln (36n) erstreckt .3. Impeller according to claim 2, characterized in that the impeller ring (30) from the end edges (40, 40 n ) of the blades (36, 36 n ) to the inlet-side outer edges (38 n ) of the short blades (36 n ) extends.
4. Laufrad nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass der Laufradring (30) die Außenkanten (38n) der kurzen Schaufeln (36n) geringfügig überragt.4. Impeller according to claim 2 or 3, characterized in that the impeller ring (30) slightly overhangs the outer edges (38 n ) of the short blades (36 n ).
5. Laufrad nach einem der Ansprüche 2 bis 4, dadurch gekennzeichnet, dass der Laufradring (30) längsschnittlich eine teilkreisförmige Krümmung (Kj) auf- weist, die in einen an einer Frontkante (32) endenden etwa achsparallelen Bereich übergeht.5. Impeller according to one of claims 2 to 4, characterized in that the impeller ring (30) has a part-circular curvature (Kj) in longitudinal section. points, which merges into an axially parallel region ending at a front edge (32).
6. Laufrad nach Anspruch 5, dadurch gekennzeichnet, dass der an die Frontkante (32) anschließende Bereich des Laufradringes (30) eine Stufung (31) enthält.6. Impeller according to claim 5, characterized in that the region of the impeller ring (30) adjoining the front edge (32) contains a step (31).
7. Laufrad nach einem der Ansprüche 2 bis 6, dadurch gekennzeichnet, dass die Außenfläche des Laufradringes (30) mit der Innenfläche ( 44 ) einer in Abstand (q) gegenüberstehenden Gehäusewand (42) einen Dichtspalt (50) begrenzt.7. Impeller according to one of claims 2 to 6, characterized in that the outer surface of the impeller ring (30) with the inner surface (44) of a spaced (q) opposite housing wall (42) delimits a sealing gap (50).
8. Laufrad nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die Schaufeln (36, 36n) vom Lagerrohr (18) zueinander äquidistant ausgehen.8. Impeller according to one of claims 1 to 7, characterized in that the blades (36, 36 n ) from the bearing tube (18) extend equidistantly from one another.
9. Laufrad nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, dass die Schaufeln (36, 36n) spiralartig oder spindelartig um das Lagerrohr (18) geführt sind.9. Impeller according to one of claims 1 or 2, characterized in that the blades (36, 36 n ) are guided in a spiral or spindle-like manner around the bearing tube (18).
10. Laufrad nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die einlaufseitigen Außenkanten (38) der langen Schaufeln (36) in einem Eintrittswinkel (s) zu einer Durchmessergeraden (D) des Lagerrohres (18) verlaufen und der Winkel dem jeweiligen Betriebspunkt angepasst ist.10. Impeller according to one of claims 1 to 4, characterized in that the inlet-side outer edges (38) of the long blades (36) at an entry angle (s) to a straight line (D) of the bearing tube (18) and the angle to the respective Operating point is adjusted.
11. Laufrad nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, dass die einlaufseitigen Außenkanten (38n) der kurzen Schaufeln (36n) in einem Eintrittswinkel (si) zu einer Durchmessergeraden (D) des Lagerrohres (18) verlaufen und der Winkel auf die lokalen Strömungsverhältnisse abgestimmt ist.11. Impeller according to one of claims 1 to 10, characterized in that the inlet-side outer edges (38 n ) of the short blades (36 n ) at an entry angle (si) to a straight line (D) of the bearing tube (18) and the angle is matched to the local flow conditions.
12. Laufrad nach Anspruch 10 oder 11, dadurch gekennzeichnet, dass die Eintrittswinkel (s) der langen Schaufeln (36) großer sind als die Winkel (t) zwischen der Drehrichtung (x) der Schaufeln der Zustromung im Relativsystem.12. Impeller according to claim 10 or 11, characterized in that the entry angle (s) of the long blades (36) are larger than the angle (t) between the direction of rotation (x) of the blades of the inflow in the relative system.
13. Laufrad nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, dass die auslaufseitigen Endkanten (40, 40n) der Schaufeln (36, 36n) mit einer13. Impeller according to one of claims 1 to 12, characterized in that the outlet-side end edges (40, 40 n ) of the blades (36, 36 n ) with a
Achsparallelen (Δi) einen spitzen Winkel (w) einschließen.Include parallel axes (Δi) at an acute angle (w).
14. Laufrad nach Anspruch 13, gekennzeichnet durch einen Winkel (w) zwischen 10° und 20°, bevorzugt etwa 15°. 14. Impeller according to claim 13, characterized by an angle (w) between 10 ° and 20 °, preferably about 15 °.
EP01986749A 2000-10-09 2001-10-09 Centrifugal wheel pump Expired - Lifetime EP1325232B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10050276 2000-10-09
DE10050276 2000-10-09
PCT/EP2001/011681 WO2002031361A1 (en) 2000-10-09 2001-10-09 Centrifugal wheel pump

Publications (2)

Publication Number Publication Date
EP1325232A1 true EP1325232A1 (en) 2003-07-09
EP1325232B1 EP1325232B1 (en) 2006-08-23

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ID=7659357

Family Applications (1)

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EP01986749A Expired - Lifetime EP1325232B1 (en) 2000-10-09 2001-10-09 Centrifugal wheel pump

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EP (1) EP1325232B1 (en)
AT (1) ATE337492T1 (en)
AU (1) AU2002220608A1 (en)
DE (2) DE50110823D1 (en)
DK (1) DK1325232T3 (en)
WO (1) WO2002031361A1 (en)

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CN106321449A (en) * 2015-06-16 2017-01-11 周先明 Totally-sealed integral turbine

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CN106321449A (en) * 2015-06-16 2017-01-11 周先明 Totally-sealed integral turbine

Also Published As

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DE10149648A1 (en) 2002-05-29
WO2002031361A1 (en) 2002-04-18
ATE337492T1 (en) 2006-09-15
DE50110823D1 (en) 2006-10-05
EP1325232B1 (en) 2006-08-23
DK1325232T3 (en) 2006-12-27
AU2002220608A1 (en) 2002-04-22

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