EP1375924B1 - Centrifugal pump volute - Google Patents
Centrifugal pump volute Download PDFInfo
- Publication number
- EP1375924B1 EP1375924B1 EP20030013665 EP03013665A EP1375924B1 EP 1375924 B1 EP1375924 B1 EP 1375924B1 EP 20030013665 EP20030013665 EP 20030013665 EP 03013665 A EP03013665 A EP 03013665A EP 1375924 B1 EP1375924 B1 EP 1375924B1
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- EP
- European Patent Office
- Prior art keywords
- annular channel
- volute
- wall
- annular
- radial
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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- 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
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
- F04D29/4266—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps made of sheet metal
Definitions
- the invention relates to a housing of a centrifugal pump according to the preamble of claim 1.
- a housing of the generic type is from the EP-A-0 455 542 known.
- a guide device is part of a pump chamber formed from two concentric chambers.
- This pump chamber consists on the one hand of a rotationally symmetrical center chamber with T-shaped axial section, which is called blade chamber and in which concentrically rotates the blade wheel, and on the other hand of a guide forming annularbians lakehunt, an axial section in the form of an inverted L with rounded corner and has a substantially constant width and which radially and then axially extends the Schaufelradhunt at the level of the arms of the T-shaped axial section.
- the two peripheral housing walls of the annular circumferential conveying chamber are each formed circular, so that the passage cross section of the circumferential conveying chamber, seen over the circumference, is immutable.
- the circumferentially-dependent change in the passage cross-section of the annular channel is achieved in that the multi-part second housing part forms a concentric to the pump axis rotating, outwardly open annular channel of constant width and radial depth, in the groove bottom a ring with over the The scope of variable radial thickness is embedded in a form-fitting manner.
- the DE-A-20 47 541 shows a pump housing formed from two deep-drawn housing parts, in which the guide device bounded on the outside by a circular peripheral wall of the first housing part and the spiral space is formed by a spirally extending pulling at least one housing wall of the housing over the circumference of the impeller.
- the proposed geometry of the pump housing and its guide designed relatively complicated and the proposed connection and sealing of the two housing parts together is cleaning technology and hygienic problematic.
- a centrifugal pump wherein the two housing parts are integrally formed and in which a raised portion which is integrally formed on the impeller carrying the second housing part has a varying around the center of the second housing part diameter to form a spiral surface
- the figures reveal 3 to 6 of the EP-B-0 316 392
- a centrifugal pump is placed under protection with a for rotation in a plane within the spiral outflow channel (annular channel) and centrally attached to the circular mecanicswandung the first housing part impeller.
- Figure 7 shows the EP-B-0 316 392 a centrifugal pump in which, in contrast to the above solution, the outflow channel (annular channel) is formed in the first housing part penetrated by the suction nozzle, wherein the spiral surface is also determined in this case by a diameter of a raised section which varies around the center of the first housing part, which is also cheap to edit.
- Housing for centrifugal pumps in sheet metal design increasingly compete there with those with cast housings, where the price / performance ratio on the one hand and the weight, the absence of pores and the surface quality of the rolled starting material on the other hand become decisive selection criteria for a centrifugal pump.
- Casing wall thicknesses manufactured in rolled material are only dependent on the working pressure of the centrifugal pump, whereas in cast casings for technical reasons a minimum wall thickness must not be undershot, which in many cases is oversized in view of the occurring stress.
- cast housings are generally regarded as dimensionally stable and thus functionally reliable; their shape is well known (see for example DE 25 29 458 C2 or company publication 5.046.1, Tuchenhagen, centrifugal pumps, series VPB, VPC, VPD ... L, Otto Tuchenhagen GmbH & Co. KG, D-21510 Büchen).
- a ring channel limiting annular channel housing not as an independent housing component, which must then be necessarily connected to a first and a second housing part (see, eg DE 195 34 258 C2 ), or provide a separate ring whose circumferentially variable cross-section determines the circumferential variation of the passage cross-section of the annular channel (see, eg GB-A-1 013 341 ), but the annular channel housing in a conventional manner ( EP-A-0 455 542 ) integrally integrate into the second housing part.
- first and the second housing part are each formed in one piece, that surrounds the impeller surrounding a vaneless annular space constant passage cross section immediately and without cross-sectional reduction in the annular channel and that the annular channel is bounded on the side of the second housing part of a first radial annular surface which is oriented substantially radially, which continues after the inner annular channel housing wall latter and which is sealed together with the outer annular channel housing wall.
- the impeller and on the outside a housing parts supporting Mounting flange arranged, whereby the center of the first housing part is available for the coaxial connection of an inlet connection.
- the more critical connection conditions are in the spiral annular channel.
- the inner annular channel housing wall is formed in the connection area of the pressure nozzle in such a way that the necessary connection cross section between the outer and inner annular channel housing wall is ensured. This is achieved by the fact that in the connection area of the pressure port, the inner annular channel housing wall is formed planar, with this flat wall surface connects tangentially to the inner annular channel housing wall in the region of the largest passage cross-section of the (spiral) annular channel. At its other end, the flat wall surface is adapted with a curved surface to the inner annular channel housing wall in the region of the narrowest passage cross-section of the (spiral) annular channel.
- the one-piece housing parts can be performed by their relatively simple geometry without particular difficulties in sheet metal design, so that there are very favorable conditions for a sufficiently good surface quality of all coming into contact with the product inner surfaces of the centrifugal pump.
- the relatively simple geometry of the first and the second housing part in the region of the outer contour of the impeller makes it possible to adapt the two housing parts with relatively narrow annular gaps to the impeller, whereby the efficiency is favorably influenced.
- the housing geometry allows for a readily the arrangement of a closed impeller in the housing without significant gap losses and Totraum Struktur, on the other hand, without further narrowing of the annular gap and the housing shape, the arrangement of an impeller radial or semi-axial design with possible from the inlet to the exit region in each case to an impeller side open blade channels.
- the axial extension region of the outer annular channel housing wall i. the axial extent of the first housing part, only enlarged.
- the axial extent is extended.
- the connection region of the two housing parts on the one hand and the geometry of the centrifugal pump, seen radially, on the inside of the annular channel remain largely unchanged.
- the discharge nozzle is arranged centrally to this length, as provided for an advantageous embodiment of the invention. If the volume flow of the centrifugal pump fails relatively small, so that the axial extension length of the passage cross-section of the annular channel is dimensioned correspondingly small, provides a further embodiment of the invention, that the discharge nozzle off-center to this length, offset towards the impeller, is arranged. In this case, the discharge nozzle engages at least partially in the blade-less annular space surrounding the impeller. However, no flow impediments result from this situation, since according to the invention the vaneless annular space passes into the annular channel without cross-sectional reduction.
- the sealing of the two housing parts together in the outer region of the annular channel is particularly hygienic and easy to clean if in the first radial annular surface a sealing groove is provided, in which a housing seal is arranged in an annular channel directed to the annular gap between the outer ring channel housing wall and the first radial annular surface simultaneouslyulstet and largely flush with the interior contour of the annular channel.
- a further embodiment of the invention provides that the first radial annular surface continues over the region of the sealing groove in a substantially radially outward direction and that adjoins the outer annular channel housing wall a corresponding to the first radial annular surface and releasably connected second radial annular surface connects, which has a recess at its outer end, with which it comprises the peripheral boundary surface of the first radial annular surface on the outside.
- Another advantageous embodiment of the guide device provides to form these in the form of a spiral annular channel.
- a continuously widening passage cross section of the spiral annular channel with the best possible efficiencies can be achieved, it is limited in its outer boundary area by the outer ring channel housing wall which surrounds the pump axis concentric and with a constant radius of curvature, thus circular.
- the required by the spiral profile cross-sectional change over the circumference of the annular channel is carried by the inner annular channel housing wall, which is designed in the required manner with a variable over the circumference, the spiral course forming local radius of curvature.
- the entire requirements for the geometry of the passage cross-section of the Ring channel in the second housing part as far as they relate to the configuration of the continuously changing over the circumference spiraling course.
- integrated annular channel offers in the context of the overall arrangement even more advantages.
- the ability to disassemble the first housing part alone, is given by the proposed solution, so that an immediate access to the impeller is maintained without putting the drive motor connected to the second housing part via a mounting flange.
- the ability to separate the impeller including shaft and drive motor from the rest of the housing without having to dismantle the suction and discharge line from the housing, is also retained by the proposed solution. This process design is ensured by the arrangement of the pressure port on the outer ring channel housing wall.
- One of a first and a second housing part 2, 3 existing housing 1 of a centrifugal pump is mounted on a mounting flange 10 on a flying motor 8 FIG. 1 ).
- a discharge nozzle 6 is connected, which ends via a conical extension 6a in a connecting piece 6b.
- the first and the second housing part 2, 3 are adapted in their radial extent range, each with a narrow annular gap, to an impeller 7 fastened to a shaft 11.
- On the annular circumferential impeller outlet cross-section is followed by a shovelless annular space 4a on the outside, which is bounded in the radial direction initially on both sides of the first and second housing part 2, 3 and then outside bounded by a transition surface 2d of the first housing part 2.
- This transition surface 2d is then continued in an outer annular channel housing wall 2a, wherein this has the shape of a cylinder jacket, ie, a constant radius of curvature, the outer radius R a , has.
- the second housing part 3 is formed in the region of the impeller 7 as a radially extending disk.
- a mainly axially oriented, the impeller 7 in the axial direction fortstrebende, the pump axis enclosing inner ring channel housing wall 3a connects, the local radius of curvature r i is variable to realize the helical course over the circumference.
- the outer and inner annular channel housing wall 2a, 3a thus form between them the ever-changing passage cross section of a spiral annular channel 4 *.
- Even a vane-free annular space 4 with a constant passage cross-section can easily be integrally integrated in the second housing part 3.
- the (spiral) annular channel (4 *), 4 adjoins the side of the blade-less annular space 4a and has an axial extent adapted to the volume flow conditions of the respective centrifugal pump.
- the axial width, which is constant over the circumference of the annular channel 4, 4 *, is in FIG. 2 marked B.
- FIG. 3 shows how the spiral annular channel 4 *, seen over the circumference, steadily widened.
- the passage cross-section of the spiral annular channel 4 * increases steadily from a minimum cross section to a point where FIG. 3 the horizontal center line forms a vertical with a parallel to the longitudinal axis of the pressure port 6.
- the inner ring channel housing wall 3a is continuously curved (end point / connection point P).
- a planar wall region 3b adjoins, which ensures a passage cross-section in the region of the spiral-shaped annular channel 4 * which corresponds at least to the passage cross-section of the pressure port 6.
- planar wall region 3b has a tilt angle ⁇ directed radially inwards at the end point P and that this flat wall region 3b bridges a peripheral region defined by an exit angle ⁇ on the inner annular channel housing wall 3a.
- This exit angle ⁇ which relates to the pump axis and the circumferential direction, results from the penetration area of the pressure port 6 with the outer annular channel housing wall 2a.
- the end region of the planar wall region 3b merges with a rounding radius k into the inner annular channel housing wall 3a. This transitional area is marked Q.
- the longitudinal distance between the end point P and the transition region Q is dimensioned such that there on the one hand the minimum required passage cross-section of the pressure port 6 and on the other hand still a sufficient circumferential length of the spiral annular channel 4 * are ensured.
- the level Wall portion 3b in the area PQ can not be dimensioned lengthwise so that the nominal passage cross-section of a connecting piece 6b is achieved, the conical extension 6a between the cylindrical pressure port 6 and the connecting piece 6b for connecting a pressure line, not shown required.
- a solution is proposed in which the conical extension 6a begins at the connecting piece 6b and extends into the penetration area with the outer annular channel housing wall 2a.
- the outer axial boundary of the spiral-shaped annular channel 4 * is reached via a first radial annular surface 3c, which is part of the second housing part 3 and adjoins the inner annular channel housing wall 3a in a radially oriented first radial annular surface 3c which is removed from the pump axis in the radial direction ( FIG. 2 ).
- the first radial annular surface 3c continues over the outermost radial extent of the outer annular channel housing wall 2a in the radial direction to the outside. Also on the outer annular channel housing wall 2a is followed by a radially oriented, with the first radial annular surface 3c and releasably connected second radial annular surface 2b connects.
- Both the first and the second radial annular surface 3c, 2b have a plurality of through-holes 12, which are distributed over their circumference and correspond to each other, via which the first and the second housing parts 2, 3 are connected to one another.
- the concentric alignment of the housing parts 2, 3 to each other succeeds by a recess 2c which is formed on the outer end of the second radial annular surface 2b and which comprises the peripheral boundary surface of the first radial annular surface 3c on the outside on a maximum possible diameter.
- the annular channel 4, 4 * is sealed in the corner region, which is formed between the first and the second housing part 2, 3, by means of a housing seal 9 against the environment, wherein the housing seal 9 in a formed in this area in the first radial annular surface 3c sealing groove 3d recording takes place.
- the housing seal 9 bulges in a to the interior of the annular channel 4, 4 * directed annular gap between the first and the second housing part 2, 3 and largely flush with the interior contour of the annular channel 4, 4 * from.
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Description
Die Erfindung betrifft ein Gehäuse einer Kreiselpumpe nach dem Oberbegriff des Anspruchs 1.The invention relates to a housing of a centrifugal pump according to the preamble of claim 1.
Ein Gehäuse der gattungsgemäßen Art ist aus der
In einer aus der
Es ist weiterhin bekannt, dass Kreiselpumpen in Blechbauweise die vorstehend erwähnten Anforderungen an die Oberflächengüte am ehesten erfüllen können. Die
Eine Kreiselpumpe, bei der die beiden Gehäuseteile einteilig ausgebildet sind und bei der ein angehobener Abschnitt, der an dem das Laufrad tragende zweiten Gehäuseteil angeformt ist, einen sich rings um das Zentrum des zweiten Gehäuseteils variierenden Durchmesser zur Ausbildung einer spiralförmigen Oberfläche aufweist, offenbaren die Figuren 3 bis 6 der
Darüber hinaus zeigt Figur 7 der
Schließlich offenbart die
Gehäuse für Kreiselpumpen in Blechbauweise treten zunehmend dort in Konkurrenz zu solchen mit gegossenen Gehäusen, wo das Preis-/Leistungsverhältnis einerseits und das Gewicht, die Porenfreiheit und die Oberflächengüte des gewalzten Ausgangsmaterials andererseits zu entscheidenden Auswahlkriterien für eine Kreiselpumpe werden. In Walzmaterial gefertigte Gehäusewandstärken sind lediglich vom Arbeitsdruck der Kreiselpumpe abhängig, während bei gegossenen Gehäusen aus technischen Gründen eine Mindestwandstärke nicht unterschritten werden darf, die in vielen Fällen im Hinblick auf die auftretende Beanspruchung überdimensioniert ist. Gussgehäuse gelten demgegenüber allgemein als formstabiler und damit funktionssicherer; ihre Formgebung ist hinlänglich bekannt (siehe beispielsweise
Es wird heute überall dort, wo geringe Wirkungsgradeinbußen einerseits hinnehmbar sind und andererseits die Kosten einer derartigen Kreiselpumpe eine entscheidende Rolle bei der Auswahl spielen, nach kostengünstigen Lösungen für Kreiselpumpen in Blechbauweise gesucht.It is now everywhere, where low efficiency losses are tolerated on the one hand and on the other hand, the cost of such a centrifugal pump play a crucial role in the selection, looking for cost-effective solutions for centrifugal pumps in sheet metal construction.
Es ist Aufgabe der vorliegen Erfindung, Leitvorrichtung und Gehäuse einer Kreiselpumpe der gattungsgemäßen Art derart zu vereinfachen, dass eine Kostenreduzierung gegenüber bekannten Gehäusegeometrien möglich ist, ohne dass die Möglichkeit, das Gehäuse in Blechbauweise auszuführen, verloren geht.It is an object of the present invention to simplify the guide device and housing of a centrifugal pump of the generic type such that a cost reduction over known housing geometries is possible without the possibility of carrying out the housing in sheet-metal construction is lost.
Diese Aufgabe wird durch die Merkmale im Anspruch 1 gelöst. Vorteilhafte Ausführungsformen des Pumpengehäuses gemäß der Erfindung sind Gegenstand der Unteransprüche.This object is solved by the features in claim 1. Advantageous embodiments of the pump housing according to the invention are the subject of the dependent claims.
Die Voraussetzung zur Lösung der gestellten Aufgabe besteht dabei darin, ein den Ringkanal begrenzendes Ringkanal-Gehäuse nicht als eigenständiges Gehäusebauteil auszubilden, das dann zwangsläufig mit einem ersten und einem zweiten Gehäuseteil verbunden werden muss (siehe z.B.
Dabei gestaltet sich der Anschluss des Druckstutzens an das erste Gehäuseteil sowohl bei dem spiralförmigen Ringkanal als auch bei dem Ringkanal mit über dem Umfang veränderlichem, dem jeweils gesammelten Flüssigkeitsstrom aus dem Laufrad Rechnung tragenden Durchtrittsquerschnitt relativ problemlos. Die kritischeren Anschlussbedingungen liegen bei dem spiralförmigen Ringkanal vor. Die innere Ringkanal-Gehäusewand ist im Anschlussbereich des Druckstutzens derart geformt, dass der notwendige Anschlussquerschnitt zwischen äußerer und innerer Ringkanal-Gehäusewand sichergestellt ist. Dies gelingt dadurch, dass im Anschlussbereich des Druckstutzens die innere Ringkanal-Gehäusewand ebenflächig ausgeformt ist, wobei sich diese ebene Wandfläche tangential an die innere Ringkanal-Gehäusewand im Bereich des größten Durchtrittsquerschnittes des (spiralförmigen) Ringkanals anschließt. An ihrem anderen Ende ist die ebene Wandfläche mit einer gekrümmten Fläche an die innere Ringkanal-Gehäusewand im Bereich des engsten Durchtrittsquerschnittes des (spiralförmigen) Ringkanals angepasst.In this case, the connection of the pressure port to the first housing part designed both in the spiral annular channel and in the annular channel with variable over the circumference, the respective collected fluid flow from the impeller bearing passage cross-section relatively easily. The more critical connection conditions are in the spiral annular channel. The inner annular channel housing wall is formed in the connection area of the pressure nozzle in such a way that the necessary connection cross section between the outer and inner annular channel housing wall is ensured. This is achieved by the fact that in the connection area of the pressure port, the inner annular channel housing wall is formed planar, with this flat wall surface connects tangentially to the inner annular channel housing wall in the region of the largest passage cross-section of the (spiral) annular channel. At its other end, the flat wall surface is adapted with a curved surface to the inner annular channel housing wall in the region of the narrowest passage cross-section of the (spiral) annular channel.
Die einteilig ausgebildeten Gehäuseteile lassen sich durch ihre relativ einfache Geometrie ohne besondere Schwierigkeiten in Blechbauweise ausführen, so dass denkbar günstige Voraussetzungen für eine hinreichend gute Oberflächenqualität aller mit Produkt in Berührung kommenden inneren Oberflächen der Kreiselpumpe vorliegen.The one-piece housing parts can be performed by their relatively simple geometry without particular difficulties in sheet metal design, so that there are very favorable conditions for a sufficiently good surface quality of all coming into contact with the product inner surfaces of the centrifugal pump.
Die relativ einfache Geometrie des ersten und des zweiten Gehäuseteils im Bereich der Außenkontur des Laufrades ermöglicht es, die beiden Gehäuseteile mit relativ engen Ringspalten an das Laufrad anzupassen, wodurch der Wirkungsgrad günstig beeinflusst wird. Dabei erlaubt die Gehäusegeometrie zum einen ohne weiteres die Anordnung eines geschlossenen Laufrades im Gehäuse ohne nennenswerte Spaltverluste und Totraumbildung, zum andern ist ohne weitere Verengung der Ringspalte und der Gehäuseform die Anordnung eines Laufrades radialer oder halbaxialer Bauart mit vom Eintritts- zum Austrittsbereich jeweils zu einer Laufradseite offenen Schaufelkanälen möglich. Des weiteren ist aber auch die Anordnung eines Laufrades radialer oder halbaxialer Bauart mit einer geradzahligen Anzahl n Schaufeln gegeben, wobei der einzelne Schaufelkanal zwischen den ihn jeweils begrenzenden Schaufeln entweder von einem Deckscheiben- oder von einem Rückflächensegment berandet ist und, in Umfangsrichtung betrachtet, Deckscheiben- und Rückflächensegment im jeweiligen Wechsel aufeinander folgen (
Bei einer Verbreiterung des Laufrades mit dem Ziel, den Förderstrom der Kreisel-pumpe bei sonst gleicher Baugeometrie zu vergrößern, wird der axiale Erstreckungsbereich der äußeren Ringkanal-Gehäusewand, d.h. die axiale Erstreckung des ersten Gehäuseteils, lediglich vergrößert. Im gleichen Maße wird, ohne die radialen Abmessungen der inneren Ringkanal-Gehäusewand zu verändern, deren axiale Erstreckung verlängert. Der Verbindungsbereich der beiden Gehäuseteile einerseits und die Geometrie der Kreiselpumpe, radial gesehen, innenseits vom Ringkanal bleiben dabei weitestgehend unverändert.In a broadening of the impeller with the aim of increasing the flow rate of the centrifugal pump with otherwise the same construction geometry, the axial extension region of the outer annular channel housing wall, i. the axial extent of the first housing part, only enlarged. To the same extent, without changing the radial dimensions of the inner annular channel housing wall, the axial extent is extended. The connection region of the two housing parts on the one hand and the geometry of the centrifugal pump, seen radially, on the inside of the annular channel remain largely unchanged.
Unabhängig von der axialen Erstreckungslänge des Durchtrittsquerschnittes des Ringkanals ist es in jedem Falle strömungstechnisch von Vorteil, dass der Druckstutzen mittig zu dieser Länge angeordnet ist, wie dies eine vorteilhafte Ausführungsform der Erfindung vorsieht. Falls der Volumenstrom der Kreiselpumpe relativ klein ausfällt, so dass die axiale Erstreckungslänge des Durchtrittsquerschnittes des Ringkanals entsprechend klein bemessen ist, sieht eine weitere Ausführungsform der Erfindung vor, dass der Druckstutzen außermittig zu dieser Länge, in Richtung zum Laufrad hin versetzt, angeordnet ist. In diesem Falle greift der Druckstutzen wenigstens teilweise in den das Laufrad umschließenden schaufellosen Ringraum ein. Aus diesem Sachverhalt resultieren jedoch keine Strömungbehinderungen, da der schaufellose Ringraum erfindungsgemäß ohne Querschnittsreduzierung in den Ringkanal übergeht.Regardless of the axial extension length of the passage cross-section of the annular channel, it is in each case fluidly advantageous that the discharge nozzle is arranged centrally to this length, as provided for an advantageous embodiment of the invention. If the volume flow of the centrifugal pump fails relatively small, so that the axial extension length of the passage cross-section of the annular channel is dimensioned correspondingly small, provides a further embodiment of the invention, that the discharge nozzle off-center to this length, offset towards the impeller, is arranged. In this case, the discharge nozzle engages at least partially in the blade-less annular space surrounding the impeller. However, no flow impediments result from this situation, since according to the invention the vaneless annular space passes into the annular channel without cross-sectional reduction.
Die Abdichtung der beiden Gehäuseteile miteinander im Außenbereich des Ringkanals gestaltet sich besonders hygienisch und reinigungsfreundlich, wenn in der ersten radialen Ringfläche eine Dichtungsnut vorgesehen ist, in der eine Gehäusedichtung angeordnet ist, die sich in einen zum Ringkanal gerichteten Ringspalt zwischen der äußeren Ringkanal-Gehäusewand und der ersten radialen Ringfläche auswulstet und weitgehend bündig mit der Innenraumkontur des Ringkanals abschließt.The sealing of the two housing parts together in the outer region of the annular channel is particularly hygienic and easy to clean if in the first radial annular surface a sealing groove is provided, in which a housing seal is arranged in an annular channel directed to the annular gap between the outer ring channel housing wall and the first radial annular surface herausulstet and largely flush with the interior contour of the annular channel.
Während die Abdichtung des ersten und des zweiten Gehäuseteils miteinander in optimaler Weise unmittelbar an deren Zusammenführung im Bereich des Ringkanals erfolgt, wird die koaxiale Zentrierung der beiden Gehäuseteile zueinander in besonders wirkungsvoller Weise auf einem größtmöglichen Außendurchmesser vorgenommen, den das Gehäuse der Kreiselpumpe zu bieten hat. Zu diesem Zweck sieht eine weitere Ausgestaltung der Erfindung vor, dass sich die erste radiale Ringfläche über den Bereich der Dichtungsnut im Wesentlichen in radialer Richtung nach außen fortsetzt und dass sich an die äußere Ringkanal-Gehäusewand eine mit der ersten radialen Ringfläche korrespondierende und lösbar verbundene zweite radiale Ringfläche anschließt, die an ihrem äußeren Ende einen Rezess aufweist, mit dem sie die umfangsseitige Begrenzungsfläche der ersten radialen Ringfläche außenseits umfasst.While the sealing of the first and the second housing part takes place optimally directly on their merger in the region of the annular channel, the coaxial centering of the two housing parts is made to each other in a particularly effective manner to a maximum outer diameter, the housing of the centrifugal pump has to offer. For this purpose, a further embodiment of the invention provides that the first radial annular surface continues over the region of the sealing groove in a substantially radially outward direction and that adjoins the outer annular channel housing wall a corresponding to the first radial annular surface and releasably connected second radial annular surface connects, which has a recess at its outer end, with which it comprises the peripheral boundary surface of the first radial annular surface on the outside.
Eine andere vorteilhafte Ausgestaltung der Leitvorrichtung sieht vor, diese in Form eines spiralförmigen Ringkanals auszubilden. Ein sich stetig erweiternder Durchtrittsquerschnitt des spiralförmigen Ringkanals, mit dem bestmögliche Wirkungsgrade erzielt werden können, wird dabei in seinem äußeren Begrenzungsbereich durch die äußere Ringkanal-Gehäusewand begrenzt, die die Pumpenachse konzentrisch und mit konstantem Krümmungsradius, somit kreisförmig, umschließt. Die durch den spiralförmigen Verlauf erforderliche Querschnittsveränderung über den Umfang des Ringkanals erfolgt durch die innere Ringkanal-Gehäusewand, die in erforderlicher Weise mit einem über den Umfang veränderlichen, den spiralförmigen Verlauf bildenden örtlichen Krümmungsradius ausgeführt ist. Damit liegen die gesamten Anforderungen an die Geometrie des Durchtrittsquerschnittes des Ringkanals im zweiten Gehäuseteil, soweit diese die Ausgestaltung des sich über den Umfang stetig verändernden spiralförmigen Verlaufs betreffen.Another advantageous embodiment of the guide device provides to form these in the form of a spiral annular channel. A continuously widening passage cross section of the spiral annular channel, with the best possible efficiencies can be achieved, it is limited in its outer boundary area by the outer ring channel housing wall which surrounds the pump axis concentric and with a constant radius of curvature, thus circular. The required by the spiral profile cross-sectional change over the circumference of the annular channel is carried by the inner annular channel housing wall, which is designed in the required manner with a variable over the circumference, the spiral course forming local radius of curvature. Thus, the entire requirements for the geometry of the passage cross-section of the Ring channel in the second housing part, as far as they relate to the configuration of the continuously changing over the circumference spiraling course.
Der im zweiten Gehäuseteil erfindungsgemäß integrierte Ringkanal bietet jedoch im Rahmen der Gesamtanordnung noch weitere Vorteile. Die Möglichkeit, das erste Gehäuseteil allein zu demontieren, ist durch die vorgeschlagene Lösung gegeben, so dass ein unmittelbarer Zugang zum Laufrad erhalten bleibt, ohne den mit dem zweiten Gehäuseteil über einen Befestigungsflansch verbundenen Antriebsmotor zu versetzen. Die Möglichkeit, das Laufrad einschließlich Welle und Antriebsmotor vom übrigen Gehäuse zu trennen, ohne die Saug- und Druckleitung vom Gehäuse demontieren zu müssen, bleibt durch die vorgeschlagene Lösung gleichfalls erhalten. Diese Prozessbauweise wird durch die Anordnung des Druckstutzens an der äußeren Ringkanal-Gehäusewand sichergestellt.However, in the second housing part according to the invention integrated annular channel offers in the context of the overall arrangement even more advantages. The ability to disassemble the first housing part alone, is given by the proposed solution, so that an immediate access to the impeller is maintained without putting the drive motor connected to the second housing part via a mounting flange. The ability to separate the impeller including shaft and drive motor from the rest of the housing without having to dismantle the suction and discharge line from the housing, is also retained by the proposed solution. This process design is ensured by the arrangement of the pressure port on the outer ring channel housing wall.
Ein Ausführungsbeispiel der Leitvorrichtung für ein Gehäuse einer Kreiselpumpe gemäß der Erfindung ist in den Figuren der Zeichnung dargestellt und wird nachfolgend beschrieben. Es zeigen
- Figur 1
- in perspektivischer Darstellung eine Kreiselpumpe gemäß der Erfin- dung in Verbindung mit einem Antriebsmotor;
-
Figur 2 - einen Meridianschnitt durch die Kreiselpumpe gemäß
Figur 1 , resul- tierend aus einem inFigur 1 mit A-A gekennzeichneten und durch die Pumpenachse waagerecht verlaufenden Schnittverlauf, wobei die Leitvorrichtung gemäß einer vorteilhaften Ausführungsform als spiral- förmiger Ringkanal ausgebildet ist und -
Figur 3 - einen Querschnitt durch die Kreiselpumpe gemäß
Figur 1 , wobei der Schnittverlauf inFigur 1 mit B-B gekennzeichnet ist, die Schnittebene senkrecht von der Pumpenachse durchdrungen wird, die Innenteile der Kreiselpumpe entfernt wurden und lediglich das erste und das zweite Gehäuseteil im in Frage kommenden Bereich dargestellt sind.
- FIG. 1
- a perspective view of a centrifugal pump according to the invention in connection with a drive motor;
- FIG. 2
- a meridian section through the centrifugal pump according to
FIG. 1 , resulting from an inFIG. 1 marked with AA and extending horizontally through the pump axis cutting profile, wherein the guide device is formed according to an advantageous embodiment as a spiral-shaped annular channel and - FIG. 3
- a cross section through the centrifugal pump according to
FIG. 1 , where the cutting path inFIG. 1 is marked with BB , the cutting plane is penetrated vertically by the pump axis, the internal parts the centrifugal pump have been removed and only the first and the second housing part are shown in the area in question.
Ein aus einem ersten und einem zweiten Gehäuseteil 2, 3 bestehendes Gehäuse 1 einer Kreiselpumpe ist über einen Befestigungsflansch 10 fliegend an einem Motor 8 befestigt (
Aus dem in
Die äußere axiale Begrenzung des spiralförmigen Ringkanals 4* wird erreicht über eine sich an die innere Ringkanal-Gehäusewand 3a anschließende, in einer radial orientierten, von der Pumpenachse sich in radialer Richtung entfernenden ersten radialen Ringfläche 3c, die Teil des zweiten Gehäuseteils 3 ist (
Der Ringkanal 4, 4* ist im Eckenbereich, der zwischen dem ersten und dem zweiten Gehäuseteil 2, 3 gebildet wird, mittels einer Gehäusedichtung 9 gegen die Umgebung abgedichtet, wobei die Gehäusedichtung 9 in einer in diesem Bereich in der ersten radialen Ringfläche 3c ausgeformten Dichtungsnut 3d Aufnahme findet. Dabei wulstet sich die Gehäusedichtung 9 in einen zum Innenraum des Ringkanals 4, 4* gerichteten Ringspalt zwischen dem ersten und dem zweiten Gehäuseteil 2, 3 aus und schließt weitgehend bündig mit der Innenraumkontur des Ringkanales 4, 4* ab.The
- 11
- Gehäusecasing
- 22
- erstes Gehäuseteilfirst housing part
- 2a2a
- äußere Ringkanal-Gehäusewandouter ring channel housing wall
- 2b2 B
- zweite radiale Ringflächesecond radial annular surface
- 2c2c
- Rezesswritten settlement
- 2d2d
- ÜbergangsflächeTransition surface
- 33
- zweites Gehäuseteilsecond housing part
- 3a3a
- innere Ringkanal-Gehäusewandinner ring channel housing wall
- 3b3b
- ebener Wandbereichlevel wall area
- 3c3c
- erste radiale Ringflächefirst radial annular surface
- 3d3d
- Dichtungsnutseal groove
- 44
- Ringkanalannular channel
- 4*4 *
- spiralförmiger Ringkanalspiral annular channel
- 4a4a
- schaufelloser RingraumBladeless annulus
- 55
- Eintrittsstutzeninlet connection
- 66
- Druckstutzenpressure port
- 6a6a
- konische Erweiterungconical extension
- 6b6b
- Anschlussstutzenspigot
- 7.7th
- LaufradWheel
- 88th
- Motorengine
- 99
- Gehäusedichtunghousing seal
- 1010
- Befestigungsflanschmounting flange
- 1111
- Wellewave
- 1212
- DurchgangsbohrungenThrough holes
- BB
- axiale Breite des Ringkanalsaxial width of the annular channel
- PP
- Endpunkt/AnschlusspunktEndpoint / terminal
- ÜbergangsbereichTransition area
- Ra R a
- Außenradiusouter radius
- Rl R l
- Innenradiusinner radius
- kk
- Abrundungsradiusradius of curvature
- nn
- Drehrichtungdirection of rotation
- ri i
- örtlicher Krümmungsradiuslocal radius of curvature
- αα
- Austrittswinkelexit angle
- ββ
- Neigungswinkel (des ebenen Wandbereichs)Tilt angle (of the flat wall area)
Claims (6)
- A volute of a centrifugal pump that is composed of a first and a second volute part (2, 3), which are each formed as one-piece, wherein the first volute part (2) has a circular, essentially cylindrically extending outer annular channel - volute wall (2a) forming the outer periphery of an annular channel (4; 4*) and leading out from said annular channel a discharge port (6), which is tangentially connected to the outer annular channel - volute wall (2a), wherein the second volute part (3) has an inner annular channel - volute wall (3a) forming the inner periphery of the annular channel (4; 4*), said inner annular channel - volute wall (3a) runs parallel to the outer annular channel - volute wall (2a) and with an impeller area (7) disposed coaxially to the outer annular channel - volute wall (2a), and viewed in the axial direction, outside of an area enclosed by the annular channel (4; 4*), wherein a inlet port (5) is disposed coaxially to the first volute part (2), wherein a mounting flange (10) supporting the volute parts (2, 3) is disposed on the second volute part (3) inside of the impeller area (7) and outside, wherein a blade-less annular space (4a) encircling the impeller area (7) of constant passage cross section transitions directly and without a reduction in cross section into the annular channel (4; 4*), and wherein the annular channel (4; 4*) is bounded on the side of the second volute part (3) by a first radial annular surface (3c), which is essentially oriented radially, which connecting to the inner annular channel - volute wall (3a) continues the latter and which is brought together sealed with the outer annular channel - volute wall (2a)
characterized in that,
the inner annular channel-volute wall (3a) has a radius of curvature (ri) variable locally over the periphery, which determines the periphery-dependent change of the passage cross section of the annular channel (4; 4*), that the inner annular channel - volute wall (3a) in the penetration area of the discharge port (6) is designed planar in the shape of a flat wall area (3b), and that this flat wall area (3b) on the one end has at its connection point (P) to the continuously curved inner annular channel - volute wall (3a) an angle of inclination (β) directed radially inward relative to the tangent at the connection point (P), and that on the other end, as viewed in the peripheral direction transitions into the inner annular channel - volute wall (3a) with a rounding-off radius (k). - The centrifugal pump volute according to Claim 1, characterized in that in the first radial annular surface (3c) a sealing groove (3d) is provided in which a volute seal (9) is disposed which bulges out into an annular gap directed towards the annular channel (4, 4*) between the outer annular channel - volute wall (2a) and the first radial annular surface (3c), and is extensively flush with the internal contour of the annular channel (4, 4*).
- The centrifugal pump volute according to Claim 1 or 2, characterized in that the first radial annular surface (3c) continues outwards in an essentially radial direction beyond the region of the sealing groove (3d), and that a second radial annular surface (2b) corresponding to and detachably connected to the first radial annular surface (3c) is joined to the outer annular channel - volute wall (2a), said second radial annular surface (2b) has at its outer end a recess (2c) with which it covers the outside of the peripheral side boundary surface of the first radial annular surface (3c) on the outside.
- The centrifugal pump volute according to one of the claims 1 to 3, characterized by a spiral shaped annular channel (4*) whose external annular channel - volute wall (2a) is designed with constant outside radius (Ra), and whose inner annular channel - volute wall (3a) is designed with the local radius of curvature (ri) changing over the periphery, forming the spiral-shaped progression.
- The centrifugal pump volute according to one of the Claims 1 to 4, characterized in that, the discharge port (6) is disposed centered to the axial extension length of the passage cross section of the annular channel (4, 4*).
- The centrifugal pump volute according to one of the Claims 1 to 4, characterized in that, the discharge port (6) is disposed eccentric to the axial extension length of the passage cross section of the annular channel (4, 4*), offset in the direction toward the impeller (7).
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10227963 | 2002-06-22 | ||
DE10227963 | 2002-06-22 | ||
DE10314425 | 2003-03-31 | ||
DE10314425A DE10314425B4 (en) | 2002-06-22 | 2003-03-31 | Guide device for a designed in sheet metal housing of a centrifugal pump |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1375924A2 EP1375924A2 (en) | 2004-01-02 |
EP1375924A3 EP1375924A3 (en) | 2004-03-10 |
EP1375924B1 true EP1375924B1 (en) | 2010-01-06 |
Family
ID=29718101
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20030013665 Expired - Lifetime EP1375924B1 (en) | 2002-06-22 | 2003-06-17 | Centrifugal pump volute |
Country Status (1)
Country | Link |
---|---|
EP (1) | EP1375924B1 (en) |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE924188C (en) * | 1942-05-07 | 1955-02-28 | Siemen & Hinsch Gmbh | Spiral housing for centrifugal pumps |
FR2661717B1 (en) * | 1990-05-04 | 1992-07-03 | Esswein Sa | LIQUID MUFFLER CENTRIFUGAL MOTOR PUMP. |
US5076758A (en) * | 1990-07-18 | 1991-12-31 | Ingersoll-Rand Company | Centrifugal pumps |
DE9422236U1 (en) * | 1993-08-27 | 1999-12-16 | Motoren Ventilatoren Gmbh | Pump for liquids |
-
2003
- 2003-06-17 EP EP20030013665 patent/EP1375924B1/en not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
EP1375924A2 (en) | 2004-01-02 |
EP1375924A3 (en) | 2004-03-10 |
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