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EP0114932B1 - Centrifugal pump of the open channel rotor type - Google Patents

Centrifugal pump of the open channel rotor type Download PDF

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Publication number
EP0114932B1
EP0114932B1 EP83109755A EP83109755A EP0114932B1 EP 0114932 B1 EP0114932 B1 EP 0114932B1 EP 83109755 A EP83109755 A EP 83109755A EP 83109755 A EP83109755 A EP 83109755A EP 0114932 B1 EP0114932 B1 EP 0114932B1
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EP
European Patent Office
Prior art keywords
impeller
vane
edge
rotary pump
pump according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP83109755A
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German (de)
French (fr)
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EP0114932A1 (en
Inventor
Martin Stähle
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Individual
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Individual
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Filing date
Publication date
Priority claimed from CH750582A external-priority patent/CH660511A5/en
Priority claimed from CH212183A external-priority patent/CH662864A5/en
Application filed by Individual filed Critical Individual
Publication of EP0114932A1 publication Critical patent/EP0114932A1/en
Application granted granted Critical
Publication of EP0114932B1 publication Critical patent/EP0114932B1/en
Expired legal-status Critical Current

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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

Definitions

  • the invention relates to a centrifugal pump with a single-bladed impeller of open design, in particular for conveying viscous media, the outlet end of the bladed brushing a housing wall penetrated by the impeller axis, and the pressure-side blade flank in front of the housing wall ending in a front edge running between the tip edge of the blade and the impeller hub .
  • the present invention aims to provide a centrifugal pump of the type mentioned, in which the housing wall and the front edge cooperate in such a way that perfect delivery of viscous media is also possible.
  • the centrifugal pump according to the invention is characterized in that the housing wall is a straight truncated cone, the front edge of the impeller blade flank on the pressure side impinging the truncated cone wall with play extending from the blade outlet tip over a circumferential angle of at least 20 ° to a point where it ends in the impeller hub.
  • the end edge can be designed as a sharp shear edge which interacts with a counter-shear edge of the housing wall.
  • the relevant angles namely cone angle of the housing wall, flank angle of the blade and circumferential angle of the blade front edge, counter edge angle on the housing and shear edge angle on the blade, can vary within relatively large ranges.
  • the housing wall cone angle and the flank angle of the blade can be between 5 ° and 70 °, and the front edge circumferential angle between 20 ° and 360 ° or more.
  • the counter shear edge angle and the shear edge angle can each be between 5 ° and 90 °, but together should not be 180 °.
  • the single-bladed impeller has a conical hub 1, the axis la of which is mounted in the housing 2 in a manner not shown, passing through the pressure-side housing wall 3.
  • the housing wall 3 forms a straight truncated cone and is brushed with a small clearance 4 by the blade 5, the end edge of which is designated by 6.
  • the angle of inclination of the housing wall 3 to the radial plane is called the cone angle below.
  • the radially inner edge 9 of this cutout forms a stationary shear edge, the pitch angle of which is designated 8.
  • the blade flank 7 runs out at point 7a into the front edge 8 of the blade 5;
  • the blade front edge 8 ends in the hub 1.
  • the blade front edge 8 forming the pressure-side boundary of the blade flank 7 and covering the truncated cone housing wall 3 extends over a circumferential angle ⁇ up to the blade tip 8a , in which the blade end edge 6 runs out via a step 6a.
  • the condition here is that the two angles 8 and y together must not be 180 °, because only then does a real shear effect occur while the cut parts are pushed away at the same time.
  • the flank angle c which causes a fiber loop coming onto the flank 7 to slide towards the pressure side and must therefore be at least about 5 °, is expediently between about 15 ° and 40 °; an angle e of 30 ° has proven to be particularly suitable.
  • circumferential angle ⁇ of the blade front edge (between tip 8a and point 7a) can assume virtually any value between approximately 20 ° and 360 °.
  • circumferential angles ⁇ between 90 ° and 270 ° have been found to be particularly advantageous.
  • a longer fibrous part no longer needs to slide along the blade end edge 6 with its always relatively weak slope to the blade tip 6a in order to reach the area of the interacting shear edges 8, 9; rather, the fibrous part will slide off directly on the pressure-side flank 7 against the point 7a of the smallest radial distance of the blade front edge 8 and cut over this counter-shear edge 9 on the housing wall while slipping over this point 7a; Even if several passes or revolutions of the impeller are required to completely cut the fibrous part, this happens considerably faster than if the complete slipping of the fibrous part along the blade end edge 6 would have to be waited for.
  • the impeller of the centrifugal pump shown in FIGS. 6-10 has a conical hub 21 with a blade 25, whose axis 33 passes through the pressure-side housing wall 23, which is designed as a truncated cone.
  • the housing wall 23, which has a cone angle between 5 ° and 70 °, is coated with a small clearance 24 by the end edge 28 of the pressure-side blade flank 27. This end edge 28 extends from the blade outlet tip 35, into which the end edge 26 ends, spirally over a relatively large distance to a point 31 at which it ends in the hub 21, which has a relatively small radius r.
  • a relatively large area of the housing wall 23 is exposed over a relatively large arc v, which is expediently between 30 ° and 90 °, between the blade outlet tip 35 and the aforementioned hub location 31.
  • the exposure of the housing wall by reducing the impeller hub radius r can go so far that it can still be responsible for the strength conditions for the power transmission from the drive shaft 33 through the impeller hub to the blade.
  • the width b of the uncovered part of the rear housing wall which becomes visible between the pressure-side flank 27 and the suction-side flank 39 in the impeller delivery channel, decreases the more it extends against the impeller inlet part. This reduction in the width b in the direction of the impeller inlet takes place for reasons of the strength and stability of the blade end part.
  • the exposed part of the housing wall in the impeller conveying channel will have an arc v calculated from the impeller end edge tip 35 of e.g. Have at least 20 °, certain impeller shapes can allow an arc of up to 180 °. This means that the end edge 28 can extend over a circumferential angle between 360 ° and 540 °.
  • An outlet opening 36 is provided in the housing wall 23 in the vicinity of the drive shaft, so that gases can escape which are carried in the conveying medium and which separate out against the impeller rotation center and reach the housing wall center through the uncovering of the impeller.
  • impeller hub 21 and the housing wall 23 form a labyrinth between the exposure of the impeller rear side and the interior 37 between the hub and the rear wall, where the outlet opening 36 is located, so that no co-conveyed solid parts get into the outlet opening.
  • the labyrinth structure is interrupted at least on the housing wall side (in FIG. 9 also on the hub side) by means of a transverse groove 38, so that a self-cleaning effect occurs.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Description

Gegenstand der Erfindung ist eine Kreiselpumpe mit Einschaufel-Laufrad offener Bauart, insbesondere zur Förderung zähflüssiger Medien, wobei das Auslassende der Schaufel mit Spiel eine von der Laufradachse durchsetzte Gehäusewand bestreicht, und die druckseitige Schaufelflanke vor der Gehäusewand in einer zwischen Schaufelendkantenspitze und Schaufelradnabe verlaufenden Stirnkante endet.The invention relates to a centrifugal pump with a single-bladed impeller of open design, in particular for conveying viscous media, the outlet end of the bladed brushing a housing wall penetrated by the impeller axis, and the pressure-side blade flank in front of the housing wall ending in a front edge running between the tip edge of the blade and the impeller hub .

Bei bekannten Kreiselpumpen dieser Art, wie sie beispielsweise in der DE 2 855 385 beschrieben ist, liegt die von der Laufradachse durchsetzte Gehäusewand in einer Radialebene und wird von der Schaufel axial weitgehend abgedeckt, da die genannte Stirnkante nur sehr kurz ist. Damit gelangt nur relativ wenig Medium auf die Gehäusewand und kann somit auch nicht von der druckseitigen Schaufelflanke erfasst und in den Austrittskanal befördert werden.In known centrifugal pumps of this type, as described for example in DE 2 855 385, the housing wall penetrated by the impeller axis lies in a radial plane and is largely covered axially by the blade, since the end edge mentioned is only very short. This means that only a relatively small amount of medium gets onto the housing wall and therefore cannot be grasped by the pressure-side blade flank and cannot be conveyed into the outlet channel.

Demgegenüber bezweckt die vorliegende Erfindung die Schaffung einer Kreiselpumpe der genannten Art, bei welcher Gehäusewand und Stirnkante so zusammenwirken, dass eine einwandfreie Förderung auch von zähflüssigen Medien möglich ist.In contrast, the present invention aims to provide a centrifugal pump of the type mentioned, in which the housing wall and the front edge cooperate in such a way that perfect delivery of viscous media is also possible.

Zu diesem Zweck ist die erfindungsgemässe Kreiselpumpe dadurch gekennzeichnet, dass die Gehäusewand ein gerader Kegelstumpf ist, wobei sich die die Kegelstumpfwand mit Spiel bestreichende Stirnkante der druckseitigen Laufradschaufelflanke von der Schaufelaustrittsspitze über einen Umfangswinkel von mindestens 20° bis zu einer Stelle hin erstreckt, an der sie in der Laufradnabe endet.For this purpose, the centrifugal pump according to the invention is characterized in that the housing wall is a straight truncated cone, the front edge of the impeller blade flank on the pressure side impinging the truncated cone wall with play extending from the blade outlet tip over a circumferential angle of at least 20 ° to a point where it ends in the impeller hub.

Damit wird erreicht, dass eine relativ grosse Fläche der rückseitigen Gehäusewand für den Kontakt mit dem Förderstrom freigelegt wird. Dies hat zur Folge, dass durch die Kreiselwirkung schwierig zu fördernde zähflüssige Medien an der freigelegten Fläche der stationären Gehäusewand haften, wobei die druckseitige Schaufelflanke eine Presswirkung auf dieses Medium ausüben und durch die Verdrängerwirkung in den Pumpengehäuse-Austrittskanal fördern kann.This ensures that a relatively large area of the rear housing wall is exposed for contact with the flow. The consequence of this is that viscous media, which are difficult to convey, adhere to the exposed surface of the stationary housing wall due to the gyroscopic action, the pressure-side blade flank being able to exert a pressing action on this medium and, due to the displacement action, can convey it into the pump housing outlet channel.

Wenn die erfindungsgemässe Kreiselpumpe zur Förderung von langfasrigen aufgeschwemmten Feststoffen dient, kann nach einem weiteren Erfindungsmerkmal die Stirnkante als scharfe, mit einer Gegenscherkante der Gehäusewand zusammenwirkende Scherkante ausgebildet sein.If the centrifugal pump according to the invention is used to convey long-fiber suspended solids, according to a further feature of the invention, the end edge can be designed as a sharp shear edge which interacts with a counter-shear edge of the housing wall.

Damit wird erreicht, dass ein von der Pumpe angesaugter, sich um die Schaufel schlingender Faserstoffteil schon bei relativ kleinen Flankenwinkeln der Schaufel auf der Schaufelflanke, also in Achsrichtung nach der Gehäusewand hin, bis zu jener Stelle rutscht, an welcher die Stirnkante in die Nabe übergeht; diese unmittelbar über der Kegelstumpf-Gehäusewand rotierende Stelle der Schaufelstirnkante führt somit den Faserstoffteil über die Gegenkante der Gehäusewand, was durch Scherwirkung zum Zerschneiden des Faserstoffteils führt.This ensures that a fibrous part sucked in by the pump and looping around the blade slips on the blade flank even at relatively small flank angles, i.e. in the axial direction towards the housing wall, to the point at which the front edge merges into the hub ; this point of the blade front edge rotating directly above the truncated cone housing wall thus guides the fibrous part over the opposite edge of the housing wall, which leads to cutting of the fibrous part by shearing action.

Dabei ist zu beachten, dass zum einwandfreien Erfolg der erfindungsgemässen Massnahme die hier massgebenden Winkel, nämlich Kegelwinkel der Gehäusewand, Flankenwinkel der Schaufel und Umfangswinkel der Schaufelstirnkante, Gegenkantenwinkel am Gehäuse und Scherkantenwinkel an der Schaufel, innerhalb relativ grosser Bereiche variieren können. So können der Gehäusewand-Kegelwinkel und der Flankenwinkel der Schaufel zwischen 5° und 70°, und der Stirnkanten-Umfangswinkel zwischen 20° und 360° oder mehr liegen. Der Gegenscherkantenwinkel und der Scherkantenwinkel können je zwischen 5° und 90° liegen, sollten aber zusammen nicht 180° betragen.It should be noted that for the successful implementation of the measure according to the invention, the relevant angles, namely cone angle of the housing wall, flank angle of the blade and circumferential angle of the blade front edge, counter edge angle on the housing and shear edge angle on the blade, can vary within relatively large ranges. The housing wall cone angle and the flank angle of the blade can be between 5 ° and 70 °, and the front edge circumferential angle between 20 ° and 360 ° or more. The counter shear edge angle and the shear edge angle can each be between 5 ° and 90 °, but together should not be 180 °.

In der beiliegenden Zeichnung ist die Erfindung beispielsweise dargestellt; darin zeigt:

  • Fig. 1 im Axialschnitt das Pumpengehäuse eines ersten Beispiels mit schematisch gezeichnetem Laufrad,
  • Fig. 2 eine Draufsicht auf die Kegelstumpf-Gehäusewand nach Fig. 1,
  • Fig. 3 eine Seitenansicht von Laufrad und Kegelstumpf-Gehäusewand bei weggebrochenem Aussengehäuse,
  • Fig. 4 eine Draufsicht auf die Kegelstumpf-Gehäusewand in Ffeilrichtung A in Fig. 3 mit Laufrad-Stirnkantenprojektion,
  • Fig. 5 eine Stirnansicht des Laufrades der Pumpe nach Fig. 3 und 4 in Pfeilrichtung 8 in Fig.3,
  • Fig. 6 eine Stirnansicht des Laufrades eines zweiten Beispiels,
  • Fig. 7 eine Seitenansicht von Laufrad und Kegelstumpf-Gehäusewand des zweiten Beispiels bei weggebrochenem Aussengehäuse,
  • Fig. 8 eine Draufsicht auf das Laufrad nach Fig. 6,
  • Fig. 9 einen Axialschnitt durch Laufrad, Kegelstumpf-Gehäusewand und Aussengehäuse des zweiten Beispiels, und
  • Fig.10 einen Schnitt nach der Linie C - C in Fig.9.
The invention is shown for example in the accompanying drawing; therein shows:
  • 1 is an axial section of the pump housing of a first example with a schematically drawn impeller,
  • 2 is a plan view of the truncated cone housing wall of FIG. 1,
  • 3 shows a side view of the impeller and the truncated cone housing wall with the outer housing broken away,
  • 4 shows a plan view of the truncated cone housing wall in the direction of filing A in FIG. 3 with the impeller front edge projection,
  • 5 shows an end view of the impeller of the pump according to FIGS. 3 and 4 in the direction of arrow 8 in FIG. 3,
  • 6 is an end view of the impeller of a second example,
  • 7 is a side view of the impeller and truncated cone housing wall of the second example with the outer housing broken away,
  • 8 is a plan view of the impeller of FIG. 6,
  • Fig. 9 is an axial section through the impeller, truncated cone housing wall and outer housing of the second example, and
  • 10 shows a section along the line C - C in Fig.9.

Das Einschaufellaufrad besitzt eine Konusnabe 1, deren Achse la die druckseitige Gehäusewand 3 durchsetzend in nicht näher dargestellter Weise im Gehäuse 2 gelagert ist. Die Gehäusewand 3 bildet einen geraden Kegelstumpf und wird mit kleinem Spiel 4 von der Schaufel 5 bestrichen, deren Endkante mit 6 bezeichnet ist. Der Neigungswinkel der Gehäusewand 3 zur Radialebene ist im folgenden Kegelwinkel genannt. In der von der Schaufel 5 bestrichenen Gehäusewand 3 ist eine spiralförmig im Sinne der Laufraddrehrichtung von innen nach aussen umlaufende, im Querschnitt keilförmige Ausfräsung 10 vorhanden. Die radial innere Kante 9 dieser Ausfräsung bildet eine stationäre Scherkante, deren Steigungswinkel mit 8 bezeichnet ist.The single-bladed impeller has a conical hub 1, the axis la of which is mounted in the housing 2 in a manner not shown, passing through the pressure-side housing wall 3. The housing wall 3 forms a straight truncated cone and is brushed with a small clearance 4 by the blade 5, the end edge of which is designated by 6. The angle of inclination of the housing wall 3 to the radial plane is called the cone angle below. In the housing wall 3, which is swept by the blade 5, there is a milling 10, which is spiraling in the sense of the direction of rotation of the impeller from the inside to the outside and is wedge-shaped in cross section. The radially inner edge 9 of this cutout forms a stationary shear edge, the pitch angle of which is designated 8.

Wie aus Fig. 3 ersichtlich, ist die druckseitige Endflanke der Schaufel 5 mit 7 und deren Flankenwinkel mit c bezeichnet. Unter diesem Winkel c läuft die Schaufelflanke 7 an der Stelle 7a in die Stirnkante 8 der Schaufel 5 aus; an dieser Stelle 7a endet die Schaufelstirnkante 8 in der Nabe 1. Wie aus den Fig. 4 und 5 ersichtlich, erstreckt sich die die druckseitige Begrenzung der Schaufelflanke 7 bildende und die Kegelstumpf-Gehäusewand 3 bestreichende Schaufelstirnkante 8 über einen Umfangswinkel η bis zur Schaufelspitze 8a, in welche die Schaufelendkante 6 über eine Stufe 6a ausläuft. Diese als scharfe Scherkante ausgebildete und mit der Gegenkante 9 der Gehäusewand 3 zusammenwirkende Schaufelstirnkante 8 führt unter einem Winkel y zur Nabe 1 hin. Bedingung dabei ist, dass die beiden Winkel 8 und y zusammen nicht 180° betragen dürfen, denn nur dann tritt eine echte Scherwirkung ein unter gleichzeitigem Auswärtsstossen der Schnitteile. Zu den Winkeln ε, ζ und η ist im übrigen folgendes zu sagen: Der Flankenwinkel c, der bewirkt, dass eine auf die Flanke 7 gelangende Faserstoffschlinge nach der Druckseite hin abrutscht und deshalb mindestens etwa 5° betragen muss, liegt zweckmässig etwa zwischen 15° und 40° ; ein Winkel e von 30° hat sich als besonders geeignet erweisen. Aehnliches gilt für den Kegelwinkel der Gehäusewand 3, d.h. auch für diesen Winkel sind Werte zwischen 15° und 40° zweckmässig, und ein Winkel von 30° hat sich in der Praxis ebenfalls als gut erwiesen. Demgegenüber kann der Umfangswinkel η der Schaufelstirnkante (zwischen Spitze 8a und Stelle 7a) praktisch jeden Wert zwischen etwa 20° und 360° annehmen. Als besonders vorteilhaft haben sich jedoch Umfangswinkel η zwischen 90° und 270° herausgestellt.As can be seen from Fig. 3, the pressure side End flank of the blade 5 with 7 and the flank angle designated c. At this angle c, the blade flank 7 runs out at point 7a into the front edge 8 of the blade 5; At this point 7a the blade front edge 8 ends in the hub 1. As can be seen from FIGS. 4 and 5, the blade front edge 8 forming the pressure-side boundary of the blade flank 7 and covering the truncated cone housing wall 3 extends over a circumferential angle η up to the blade tip 8a , in which the blade end edge 6 runs out via a step 6a. This blade end edge 8, which is designed as a sharp shear edge and cooperates with the counter edge 9 of the housing wall 3, leads to the hub 1 at an angle y. The condition here is that the two angles 8 and y together must not be 180 °, because only then does a real shear effect occur while the cut parts are pushed away at the same time. The following should also be said about the angles ε, ζ and η: The flank angle c, which causes a fiber loop coming onto the flank 7 to slide towards the pressure side and must therefore be at least about 5 °, is expediently between about 15 ° and 40 °; an angle e of 30 ° has proven to be particularly suitable. The same applies to the cone angle of the housing wall 3, ie values between 15 ° and 40 ° are also expedient for this angle, and an angle of 30 ° has also proven to be good in practice. In contrast, the circumferential angle η of the blade front edge (between tip 8a and point 7a) can assume virtually any value between approximately 20 ° and 360 °. However, circumferential angles η between 90 ° and 270 ° have been found to be particularly advantageous.

Dank der beschriebenen Ausbildung braucht ein längerer Faserstoffteil nicht mehr längs der Schaufelendkante 6 mit ihrer stets relativ schwachen Steigung bis zur Schaufelspitze 6a abzurutschen, um in den Bereich der zusammenwirkenden Scherkanten 8, 9 zu gelangen; der Faserstoffteil wird vielmehr unmittelbar an der druckseitigen Flanke 7 gegen die Stelle 7a kleinsten Radialabstands der Schaufelstirnkante 8 abrutschen und während des Ueberstreifens dieser Stelle 7a über die Gegenscherkante 9 an der Gehäusewand zerschnitten; auch wenn mehrere Durchgänge bzw. Umdrehungen des Laufrades bis zum vollständigen Zerschneiden des Faserstoffteils erforderlich sind, geschieht dies doch erheblich schneller, als wenn das vollständige Abrutschen des Faserstoffteils längs der Schaufelendkante 6 abgewartet werden müsste. Es kann sogar zweckmässig sein, dieses vollständige Abrutschen längs der Endokante 6 zu verhindern, was beispielsweise gemäss Zeichnung durch die Stufe 6a dieser Endkante unmittelbar vor der Schaufelspitze 8a erfolgen kann. Dadurch kann verhindert werden, dass dünne Faserstoffteile, z.B. Textilschlaufen wie Garne und dergl., vollständig hinter das Laufrad gelangen und dort in den engen Spalt 4 zwischen Stirnkante 8 und Gehäusewand 3 eindringen und das Laufrad bremsen können.Thanks to the design described, a longer fibrous part no longer needs to slide along the blade end edge 6 with its always relatively weak slope to the blade tip 6a in order to reach the area of the interacting shear edges 8, 9; rather, the fibrous part will slide off directly on the pressure-side flank 7 against the point 7a of the smallest radial distance of the blade front edge 8 and cut over this counter-shear edge 9 on the housing wall while slipping over this point 7a; Even if several passes or revolutions of the impeller are required to completely cut the fibrous part, this happens considerably faster than if the complete slipping of the fibrous part along the blade end edge 6 would have to be waited for. It may even be expedient to prevent this complete slipping along the end edge 6, which can take place, for example, according to the drawing by the step 6a of this end edge directly in front of the blade tip 8a. This can prevent thin fiber parts, e.g. Textile loops such as yarns and the like, completely get behind the impeller and can penetrate into the narrow gap 4 between the front edge 8 and the housing wall 3 and brake the impeller.

Das Laufrad der in den Fig. 6 - 10 gezeichneten Kreiselpumpe besitzt eine Konusnabe 21 mit Schaufel 25,de-ren Achse 33 die druckseitige, als Kegelstumpf ausgebildete Gehäusewand 23 durchsetzt. Die einen Kegelwinkel zwischen 5° und 70° aufweisende Gehäusewand 23 wird von der Stirnkante 28 der druckseitigen Schaufelflanke 27 mit kleinem Spiel 24 bestrichen. Diese Stirnkante 28 erstreckt sich von der Schaufelaustrittspitze 35, in welche die Endkante 26 ausläuft, spiralförmig über eine relativ grosse Strecke bis zu einer Stelle 31, an der sie in der einen, relativ kleinen Radius r aufweisenden Nabe 21 endet. Dadurch ist über einen relativ grossen Bogen v, der zweckmässig zwischen 30° und 90° liegt, zwischen Schaufelaustrittspitze 35 und der genannten Nabenstelle 31 eine relativ grosse Fläche der Gehäusewand 23 freigelegt. Die Freilegung der Gehäusewand durch Reduzierung des Laufradnabenradius r kann soweit gehen, dass es mit den Festigkeitsbedingungen zur Kraftübertragung von der Antriebswelle 33 durch die Laufradnabe an die Schaufel noch verantwortet werden kann. Es verringert sich die Breite b des freigelegten Teiles der rückseitigen Gehäusewand,welcher zwischen druckseitiger Flanke 27 und saugseitiger Flanke 39 im Laufradförderkanal sichtbar wird, je mehr er sich gegen den Laufradeintrittsteil erstreckt. Diese Verringerung der Breite b in Richtung Laufradeintritt erfolgt aus Gründen der Festigkeit und Stabilität des Schaufelendteiles. Ebenfalls aus Festigkeitsgründen wird der freigelegte Teil der Gehäusewand im Laufradförderkanal einen von der Laufradendkantenspitze 35 an gerechneten Bogen v von z.B. mindestens 20° aufweisen, wobei gewisse Laufradformen einen Bogen von bis zu 180° erlauben können. Dies bedeutet, dass sich die Stirnkante 28 über einen Umfangswinkel zwischen 360° und 540° erstrecken kann.The impeller of the centrifugal pump shown in FIGS. 6-10 has a conical hub 21 with a blade 25, whose axis 33 passes through the pressure-side housing wall 23, which is designed as a truncated cone. The housing wall 23, which has a cone angle between 5 ° and 70 °, is coated with a small clearance 24 by the end edge 28 of the pressure-side blade flank 27. This end edge 28 extends from the blade outlet tip 35, into which the end edge 26 ends, spirally over a relatively large distance to a point 31 at which it ends in the hub 21, which has a relatively small radius r. As a result, a relatively large area of the housing wall 23 is exposed over a relatively large arc v, which is expediently between 30 ° and 90 °, between the blade outlet tip 35 and the aforementioned hub location 31. The exposure of the housing wall by reducing the impeller hub radius r can go so far that it can still be responsible for the strength conditions for the power transmission from the drive shaft 33 through the impeller hub to the blade. The width b of the uncovered part of the rear housing wall, which becomes visible between the pressure-side flank 27 and the suction-side flank 39 in the impeller delivery channel, decreases the more it extends against the impeller inlet part. This reduction in the width b in the direction of the impeller inlet takes place for reasons of the strength and stability of the blade end part. Also for reasons of strength, the exposed part of the housing wall in the impeller conveying channel will have an arc v calculated from the impeller end edge tip 35 of e.g. Have at least 20 °, certain impeller shapes can allow an arc of up to 180 °. This means that the end edge 28 can extend over a circumferential angle between 360 ° and 540 °.

In der Gehäusewand 23 ist in der Nähe der Antriebswelle eine Auslassöffnung 36 vorgesehen, damit Gase entweichen können, welche im Fördermedium mitgeführt werden und sich gegen das Laufradrotationszentrum ausscheiden und durch die laufradrückseitige Freilegung an das Gehäusewandzentrum gelangen.An outlet opening 36 is provided in the housing wall 23 in the vicinity of the drive shaft, so that gases can escape which are carried in the conveying medium and which separate out against the impeller rotation center and reach the housing wall center through the uncovering of the impeller.

Im weiteren bilden Laufradnabe 21 und Gehäusewand 23 ein Labyrinth zwischen Laufradrückseiten-Freilegung und Innenraum 37 zwischen Nabe und Rückwand, wo sich die Auslassöffnung 36 befindet, damit keine mitgeförderten Festteile in die Auslassöffnung gelangen.Furthermore, the impeller hub 21 and the housing wall 23 form a labyrinth between the exposure of the impeller rear side and the interior 37 between the hub and the rear wall, where the outlet opening 36 is located, so that no co-conveyed solid parts get into the outlet opening.

Ferner ist mindestens gehäusewandseitig (in Fig. 9 auch nabenseitig) die Labyrinthstruktur mittels einer Quernute 38 unterbrochen, damit eine selbstreinigende Wirkung entsteht.Furthermore, the labyrinth structure is interrupted at least on the housing wall side (in FIG. 9 also on the hub side) by means of a transverse groove 38, so that a self-cleaning effect occurs.

Claims (10)

1. Rotary pump comprising a monovane impeller of open structure, in particular for conveying viscous fluids, the outlet extremity of the vane (5; 25) passing with a clearance over a casing wall (3; 23) traversed by the impeller shaft (1a; 33), and the pressure-side vane flank (7; 27) terminating before the casing wall (3; 23) in a terminal edge (8; 28) extending between the vane outlet tip (8a; 35) and the impeller wheel hub (1; 21), characterised in that the casing wall (3; 23) is a right-angled cone frustum, the terminal edge (8; 28), passing with a clearance (4; 24) over the frustoconical wall, of the pressure-side impeller vane flank (7; 27) extending from the vane outlet tip (8a; 35) over a peripheral angle (TJ) of at least 20° up to a point (7a; 31) at which it terminates in the impeller hub (1; 21).
2. Rotary pump according to claim 1, characterised in that the terminal edge (28) of the pressure-side impeller vane flank (27) extending between the outlet tip (35) and the terminal point (31) on the hub (21) extends along a peripheral angle of at least 360° and at most 540°.
3. Rotary pump according to claim 2, characterised in that the surface of the casing wall (23) exposed between the pressure-side vane flank (27) and the suction-side vane flank (39) thanks to the long terminal edge (28) extends over an arc (v) of at least 30° between the impeller edge tip (35) and the said hub point (31).
4. Rotary pump according to one of the claims 1 to 3, characterised in that an outlet aperture (36) for gases emerging from the fluid conveyed is provided close to the driving shaft in the casing wall (23).
5. Rotary pump according to one of the claims 1 to 4, characterised in that between the exposed wall surface and the internal volume (37) vented by an outlet aperture (36) and formed between the hub and the real side, the impeller hub (21) and the casing wall (23) form a labyrinth which prevents any emergence of solid particles into the outlet aperture.
6. Rotary pump according to claim 5, characterised in that the labyrinth is interrupted by transverse grooves (38), at least on the wall side.
7. Rotary pump according to claim 1, in particular for conveying long-fibred solids in suspension, characterised in that the terminal edge is constructed as a sharp severing edge cooperating with a mating severing edge (9).
8. Rotary pump according to claim 7, characterised in that the angle of inclination (ε) of the pressure-side vane flank (7) and the taper angle (<p) of the casing wall (3) each amount to at least 5° and at most 70°, and appropriately to between 15° and 40°, whereas the peripheral angle (il) of the terminal edge (8) of the vane between the vane tip (8a) and the point (7a) of this edge closest to the axis approximately amounts to between 90° and 270°.
9. Rotary pump according to claim 8, characterised in that the sum of the appropriately acute angles of inclination (y, 8) of the terminal edge (8) of the vane and of the mating severing edge (9) differs from 180°.
10. Rotary pump according to claim 9, characterised in that the blade end edge (6) has a step (6a) rendering it impossible for fibrous material particles to slip off without hindrance along the end edge, immediately before the pressure-side vane tip (8a).
EP83109755A 1982-12-22 1983-09-29 Centrifugal pump of the open channel rotor type Expired EP0114932B1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CH750582A CH660511A5 (en) 1982-12-22 1982-12-22 Centrifugal pump having a single-blade impeller
CH7505/82 1982-12-22
CH2121/83 1983-04-20
CH212183A CH662864A5 (en) 1983-04-20 1983-04-20 Centrifugal pump having an open-type single-blade impeller

Publications (2)

Publication Number Publication Date
EP0114932A1 EP0114932A1 (en) 1984-08-08
EP0114932B1 true EP0114932B1 (en) 1986-09-03

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ID=25689566

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83109755A Expired EP0114932B1 (en) 1982-12-22 1983-09-29 Centrifugal pump of the open channel rotor type

Country Status (8)

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US (1) US4540334A (en)
EP (1) EP0114932B1 (en)
BR (1) BR8306883A (en)
CA (1) CA1214687A (en)
DE (1) DE3365881D1 (en)
DK (1) DK154907C (en)
ES (1) ES8501851A1 (en)
FI (1) FI72577C (en)

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Also Published As

Publication number Publication date
DE3365881D1 (en) 1986-10-09
FI72577B (en) 1987-02-27
CA1214687A (en) 1986-12-02
ES528338A0 (en) 1984-12-01
BR8306883A (en) 1984-07-31
ES8501851A1 (en) 1984-12-01
DK154907C (en) 1989-06-12
US4540334A (en) 1985-09-10
DK582683D0 (en) 1983-12-16
FI834352A0 (en) 1983-11-28
FI834352L (en) 1984-06-23
DK154907B (en) 1989-01-02
EP0114932A1 (en) 1984-08-08
FI72577C (en) 1987-06-08
DK582683A (en) 1984-06-23

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