EP3608544B1 - Centrifugal pump - Google Patents

Centrifugal pump Download PDF

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Publication number
EP3608544B1
EP3608544B1 EP18405018.5A EP18405018A EP3608544B1 EP 3608544 B1 EP3608544 B1 EP 3608544B1 EP 18405018 A EP18405018 A EP 18405018A EP 3608544 B1 EP3608544 B1 EP 3608544B1
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EP
European Patent Office
Prior art keywords
centrifugal pump
annular space
impeller
pump according
housing
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EP18405018.5A
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German (de)
French (fr)
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EP3608544A1 (en
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Ernst Müller
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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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/12—Combinations of two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F04D5/007—Details of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F04D5/008—Details of the stator, e.g. channel shape

Definitions

  • the invention relates to a centrifugal pump for pumping liquids.
  • Peripheral impeller centrifugal pumps have been known for a long time. With a peripheral impeller centrifugal pump, a high pressure at the outlet and thus a high delivery head can be achieved at a low delivery rate. However, the characteristic curves fall off steeply, i.e. a significant increase in the delivery rate is only possible with a sharp reduction in the outlet pressure, i.e. the achievable delivery head. The required pumping power also drops steeply.
  • the characteristic curves of radial impeller centrifugal pumps which have also been known for a long time, are rather flat, i.e. a significant increase in the delivery rate can be achieved by slightly reducing the outlet pressure, corresponding to the achievable delivery head, while the required pump capacity increases slightly. However, the maximum outlet pressure that can be achieved is rather low.
  • the invention is based on the object of specifying a centrifugal pump with which output pressures that are similarly high can be achieved as with a comparable peripheral impeller centrifugal pump, but whose characteristic curves are significantly flatter.
  • the centrifugal pump according to the invention essentially corresponds to a peripheral impeller centrifugal pump which has an addition on the inlet side which has the characteristics of a radial impeller centrifugal pump. It has a very simple and space-saving design and can be produced correspondingly inexpensively.
  • the characteristic curves are qualitatively similar to those of a peripheral impeller centrifugal pump, but fall off much less steeply.
  • the required pump power slowly decreases with an increasing delivery rate. A high level of efficiency can be achieved.
  • the centrifugal pump according to the invention has ( 1 ) has a housing which is composed of a front suction housing 1 and a rear pressure housing 2 connected to the same by screws with spring washers 3, between which a circumferential seal 4 is arranged.
  • the suction housing 1 and the pressure housing 2 are each designed to be approximately rotationally symmetrical and enclose a substantially rotationally symmetrical cavity with an outer annular space, the outer boundary of which is formed by peripheral parts of the suction housing 1 and the pressure housing 2 and which consists of a front annular space 5 and a rear annular space 6 exists.
  • the front annular space 5 is connected to an inlet nozzle 7 which is mounted centrally on the suction housing 1 and opens into the cavity at the front.
  • the pressure housing 2 carries a peripherally arranged outlet nozzle 8, which leads out approximately tangentially upwards from the rear annular space 6 and whose clear cross-section corresponds approximately to that of the inlet nozzle 7.
  • An impeller 11 (see also 2 , where the suction housing 1 is omitted and Fig. 4a-c ) fixed in the cavity in one running direction (see arrow in 2 ) is rotatable about a central axis 12.
  • the impeller 11 has a disc-shaped base, which carries vertically protruding webs 13 on a front side facing the inlet connection 7, which extend from the inside, i.e. bent back from near the axis in the direction of travel, towards the outer edge of the base, but with an edge region of the front remains free.
  • the impeller 11 has radial ribs 15 of the same height running radially from the inside, ie from an annular rib 14 surrounding the axis 12 to the outer edge of the base the rear annular space 6 adjoining space 16 remains free.
  • the webs can also protrude beyond the outer edge of the base.
  • the distance between the annular rib 14 and a rear wall of the pressure housing 2 is bridged by a fixed annular rib 17 projecting from the latter towards the annular rib 14 such that there is only a narrow circumferential gap between the annular ribs 14 and 17 .
  • the intermediate wall 18 has a recess 19 'which has the shape of a Has an annular sector, which extends from the inner edge of the intermediate wall 18 to close to its outer edge and occupies an angular range of about 45 ° and a circular ring sector-shaped passage 19 forms.
  • the area of the passage 19 corresponds approximately to the clear cross section of the outlet nozzle 8, any deviations preferably amount to at most 20%.
  • the passage 19 is preceded by a barrier 20 (see Fig. 3 , where the suction housing 1, the impeller 11, the intermediate wall 18 and the shaft 10 are omitted) immediately in front, which in turn follows closely the opening in the rear annular space 6, which leads into the outlet nozzle 8.
  • the lock 20 is designed as an approximately radial bolt projecting from the rear wall of the pressure housing 2, extending through the intermediate space 16 and the rear annular space 6 and interrupting them, which reaches close to the webs 15 of the impeller 11 and abuts the intermediate wall 18. Its front side is slightly inclined outwards in the direction of travel, so that it constantly leads to the outlet nozzle 8 .
  • the shaft 10 is driven and the impeller 11 rotates in the z 2 specified running direction.
  • the liquid to be transported is sucked in through the inlet nozzle 7 (arrow x in 1 , 2 ), taken along by the webs 13 on the front side of the impeller 11 and pressed into the front annular space 5 by the centrifugal force.
  • the liquid then reaches the rear annular space 6, where it is pressed inwards and partly between the webs 15 on the back of the impeller 11 and into the space 16. It is therefore partly entrained directly by the webs 15 and partly due to its viscosity Gap 16 and entrained in the rear annular space 6 by the movement of the entrained by the webs 15 liquid.
  • the effect of the centrifugal pump according to the invention is similar to that of a radial impeller centrifugal pump and a peripheral impeller centrifugal pump connected in series, but the construction is much simpler.
  • the characteristics ( 6 ) lie somewhere between the characteristic curves of these two known types of centrifugal pumps.
  • the output pressure that can be achieved and thus the maximum delivery head H is high, similar to that of a peripheral impeller centrifugal pump.
  • the outlet pressure, ie the delivery head H decreases less rapidly with increasing delivery rate Q.
  • the power requirement P does not depend very much on the delivery rate Q either.
  • the characteristics are similar to those of a radial impeller centrifugal pump.

Description

Technisches Gebiettechnical field

Die Erfindung betrifft eine Kreiselpumpe zur Förderung von Flüssigkeiten.The invention relates to a centrifugal pump for pumping liquids.

Stand der TechnikState of the art

Peripheralrad-Kreiselpumpen sind seit langem bekannt. Mit einer Peripheralrad-Kreiselpumpe kann bei geringer Förderrate ein hoher Druck am Ausgang und damit eine grosse Förderhöhe erzielt werden. Die Kennlinien fallen allerdings steil ab, d.h. eine deutliche Zunahme der Förderrate ist nur bei starker Verminderung des Ausgangsdrucks, d.h. der erzielbaren Förderhöhe, möglich. Die erforderliche Pumpleistung fällt dabei ebenfalls steil ab. Bei den ebenfalls seit langem bekannten Radialrad-Kreiselpumpen sind die Kennlinien eher flach, d.h. eine deutliche Zunahme der Förderrate ist schon durch geringfügige Verringerung des Ausgangsdrucks, entsprechend der erzielbaren Förderhöhe, erzielbar, während die erforderliche Pumpleistung leicht ansteigt. Allerdings ist der erzielbare maximale Ausgangsdruck eher gering.Peripheral impeller centrifugal pumps have been known for a long time. With a peripheral impeller centrifugal pump, a high pressure at the outlet and thus a high delivery head can be achieved at a low delivery rate. However, the characteristic curves fall off steeply, i.e. a significant increase in the delivery rate is only possible with a sharp reduction in the outlet pressure, i.e. the achievable delivery head. The required pumping power also drops steeply. The characteristic curves of radial impeller centrifugal pumps, which have also been known for a long time, are rather flat, i.e. a significant increase in the delivery rate can be achieved by slightly reducing the outlet pressure, corresponding to the achievable delivery head, while the required pump capacity increases slightly. However, the maximum outlet pressure that can be achieved is rather low.

Aus US 3 936 240 A ist eine Kreiselpumpe bekannt, bei der ein Laufrad an einer Vorderseite in einem vorderen Ringraum entgegen der Laufrichtung zurückgebogene von der Nähe der Achse gegen den äusseren Rand gerichtete Stege und an einer Rückseite radial von innen gegen den äusseren Rand gerichtete gerade Stege aufweist. Diese laufen durch zwei oder mehr in Umfangsrichtung aufeinanderfolgende durch radiale Trennwände voneinander geschiedene, jeweils sich über einen Teil des Umfangs erstreckende mit dem vorderen Ringraum verbundene erweiterte hintere Teilringräume, die jeweils mittels eines axialen Durchlasses mit einem anschliessenden umlaufenden Sammelvolumen verbunden sind, welches einen radial nach aussen gerichteten Austrittsstutzen aufweist. Aufgrund dieses Aufbaus ist eine derartige Kreiselpumpe nicht für die Förderung von Flüssigkeiten geeignet, da der Druckaufbau behindert würde und die unvermeidlichen scharfen Umlenkungen zu Turbulenzen führen müssten, welche den Wirkungsgrad herabsetzen und die Gefahr von Kavitationen vergrössern würden.Out U.S. 3,936,240 A a centrifugal pump is known in which an impeller on a front side in a front annular space has webs bent back counter to the running direction from near the axis towards the outer edge and on a rear side straight webs directed radially from the inside towards the outer edge. These run through two or more consecutive ones in the circumferential direction radial partition walls separated from each other, each extending over part of the circumference with the front annulus connected extended rear partial annular spaces, which are each connected by means of an axial passage with an adjoining circumferential collection volume, which has a radially outwardly directed outlet port. Because of this structure, such a centrifugal pump is not suitable for pumping liquids, since the pressure build-up would be impeded and the unavoidable sharp deflections would have to lead to turbulence, which would reduce efficiency and increase the risk of cavitation.

Darstellung der ErfindungPresentation of the invention

Der Erfindung liegt die Aufgabe zu Grunde, eine Kreiselpumpe anzugeben, mit der ähnlich hohe Ausgangsdrücke erzielt werden können wie mit einer vergleichbaren Peripheralrad-Kreiselpumpe, deren Kennlinien aber deutlich flacher sind.The invention is based on the object of specifying a centrifugal pump with which output pressures that are similarly high can be achieved as with a comparable peripheral impeller centrifugal pump, but whose characteristic curves are significantly flatter.

Diese Aufgabe wird durch die Erfindung, wie sie in den Ansprüchen gekennzeichnet ist, gelöst. Die erfindungsgemässe Kreiselpumpe entspricht im wesentlichen einer Peripheralrad-Kreiselpumpe, welche eingangsseitig eine Ergänzung aufweist, die Merkmale einer Radialrad-Kreiselpumpe hat. Dabei ist sie sehr einfach und platzsparend aufgebaut und entsprechend kostengünstig herstellbar.This object is solved by the invention as characterized in the claims. The centrifugal pump according to the invention essentially corresponds to a peripheral impeller centrifugal pump which has an addition on the inlet side which has the characteristics of a radial impeller centrifugal pump. It has a very simple and space-saving design and can be produced correspondingly inexpensively.

Die Kennlinien sind denen einer Peripheralrad-Kreiselpumpe qualitativ ähnlich, fallen aber wesentlich weniger steil ab. Insbesondere geht mit zunehmender Förderrate die erforderliche Pumpleistung langsam zurück. Es kann ein hoher Wirkungsgrad erzielt werden.The characteristic curves are qualitatively similar to those of a peripheral impeller centrifugal pump, but fall off much less steeply. In particular, the required pump power slowly decreases with an increasing delivery rate. A high level of efficiency can be achieved.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Im folgenden wird die Erfindung anhand von Figuren, welche lediglich ein Ausführungsbeispiel darstellen, näher erläutert. Es zeigen

Fig. 1
einen Querschnitt längs einer Achse der erfindungsgemässen Kreiselpumpe,
Fig. 2
eine Vorderansicht der erfindungsgemässen Kreiselpumpe, wobei ein Gehäuseteil weggelassen ist,
Fig. 3
eine weitere Vorderansicht der erfindungsgemässen Kreiselpumpe, wobei weitere Teile weggelassen sind,
Fig. 4a
eine Vorderansicht eines Laufrades der erfindungsgemässen Kreiselpumpe,
Fig. 4b
eine Seitenansicht des Laufrades, teilweise längs der Achse geschnitten,
Fig. 4c
eine Hinteransicht des Laufrades,
Fig. 5a
eine Vorderansicht einer Zwischenwand der erfindungsgemässen Kreiselpumpe,
Fig. 5b
einen Schnitt durch die Zwischenwand längs B-B in Fig. 5a und
Fig. 6
Kennlinien der erfindungsgemässen Kreiselpumpe.
The invention is explained in more detail below with reference to figures, which merely represent an exemplary embodiment. Show it
1
a cross section along an axis of the centrifugal pump according to the invention,
2
a front view of the centrifugal pump according to the invention, with a housing part being omitted,
3
a further front view of the centrifugal pump according to the invention, with further parts being omitted,
Figure 4a
a front view of an impeller of the centrifugal pump according to the invention,
Figure 4b
a side view of the impeller, partially cut along the axis,
Figure 4c
a rear view of the impeller,
Figure 5a
a front view of a partition wall of the centrifugal pump according to the invention,
Figure 5b
a section through the bulkhead along BB in Figure 5a and
6
Characteristic curves of the centrifugal pump according to the invention.

Wege zur Ausführung der ErfindungWays to carry out the invention

Die erfindungsgemässe Kreiselpumpe gemäss dem Ausführungsbeispiel weist (Fig. 1) ein Gehäuse auf, das sich aus einem vorderen Sauggehäuse 1 und einem mit demselben durch Schrauben mit Federringen 3 verbundenen hinteren Druckgehäuse 2, zwischen denen eine umlaufende Dichtung 4 angeordnet ist, zusammensetzt. Das Sauggehäuse 1 und das Druckgehäuse 2 sind jeweils annähernd rotationssymmetrisch ausgebildet und umschliessen einen im wesentlichen rotationssymmetrischen Hohlraum mit einem äusseren Ringraum, dessen äussere Begrenzung von umlaufenden Teilen des Sauggehäuses 1 und des Druckgehäuses 2 gebildet wird und der aus einem vorderen Ringraum 5 und einem hinteren Ringraum 6 besteht. Der vordere Ringraum 5 ist mit einem zentral am Sauggehäuse 1 angebrachten Eintrittsstutzen 7, der an der Vorderseite in den Hohlraum mündet, verbunden. Das Druckgehäuse 2 trägt einen peripher angeordneten Austrittsstutzen 8, der annähernd tangential nach oben aus dem hinteren Ringraum 6 hinausführt und dessen lichter Querschnitt ungefähr dem des Eintrittsstutzens 7 entspricht.The centrifugal pump according to the invention according to the exemplary embodiment has ( 1 ) has a housing which is composed of a front suction housing 1 and a rear pressure housing 2 connected to the same by screws with spring washers 3, between which a circumferential seal 4 is arranged. The suction housing 1 and the pressure housing 2 are each designed to be approximately rotationally symmetrical and enclose a substantially rotationally symmetrical cavity with an outer annular space, the outer boundary of which is formed by peripheral parts of the suction housing 1 and the pressure housing 2 and which consists of a front annular space 5 and a rear annular space 6 exists. The front annular space 5 is connected to an inlet nozzle 7 which is mounted centrally on the suction housing 1 and opens into the cavity at the front. The pressure housing 2 carries a peripherally arranged outlet nozzle 8, which leads out approximately tangentially upwards from the rear annular space 6 and whose clear cross-section corresponds approximately to that of the inlet nozzle 7.

Auf einer durch eine Gleitringdichtung 9 geführten antreibbaren Antriebswelle 10 ist ein Laufrad 11 (s. auch Fig. 2, wo das Sauggehäuse 1 weggelassen ist und Fig. 4a-c) befestigt, das im Hohlraum in einer Laufrichtung (s. Pfeil in Fig. 2) um eine zentrale Achse 12 drehbar ist. Das Laufrad 11 weist eine scheibenförmige Basis auf, welche an einer dem Eintrittsstutzen 7 zugewandten Vorderseite senkrecht abstehende Stege 13 trägt, die sich von innen, d.h. jeweils von nahe der Achse in Laufrichtung zurückgebogen gegen den äusseren Rand der Basis erstrecken, wobei jedoch ein Randbereich der Vorderseite frei bleibt. An der Rückseite weist das Laufrad 11 radial von innen, d.h. von einem die Achse 12 umgebenden Ringsteg 14 bis zum äusseren Rand der Basis laufende radiale Stege 15 von gleicher Höhe auf, welche von einer Rückwand des Druckgehäuses 2 beabstandet sind, sodass dort ein innen an den hinteren Ringraum 6 anschliessender Zwischenraum 16 frei bleibt. Die Stege können auch über den äusseren Rand der Basis hinausragen. Der Abstand zwischen dem Ringsteg 14 und einer Rückwand des Druckgehäuses 2 wird durch einen von derselben gegen den Ringsteg 14 vorragenden festen Ringsteg 17 überbrückt, derart, dass zwischen den Ringstegen 14 und 17 nur ein schmaler umlaufender Spalt liegt.An impeller 11 (see also 2 , where the suction housing 1 is omitted and Fig. 4a-c ) fixed in the cavity in one running direction (see arrow in 2 ) is rotatable about a central axis 12. The impeller 11 has a disc-shaped base, which carries vertically protruding webs 13 on a front side facing the inlet connection 7, which extend from the inside, i.e. bent back from near the axis in the direction of travel, towards the outer edge of the base, but with an edge region of the front remains free. At the rear, the impeller 11 has radial ribs 15 of the same height running radially from the inside, ie from an annular rib 14 surrounding the axis 12 to the outer edge of the base the rear annular space 6 adjoining space 16 remains free. The webs can also protrude beyond the outer edge of the base. The distance between the annular rib 14 and a rear wall of the pressure housing 2 is bridged by a fixed annular rib 17 projecting from the latter towards the annular rib 14 such that there is only a narrow circumferential gap between the annular ribs 14 and 17 .

Zwischen dem vorderen Ringraum 5 und dem hinteren Ringraum 6 ist eine ungefähr kreisringförmige dünne Zwischenwand 18 (s. auch Fig. 5a,b) angeordnet, mit einem äusseren Randbereich, der zwischen dem Sauggehäuse 1 und dem Druckgehäuse 2 geklemmt ist und einem inneren Randbereich, der mit dem von den Stegen 13 freien Randbereich an der Vorderseite der Basis des Laufrades 11 mit geringem axialen Abstand überlappt, sodass das Laufrad 11 und die Zwischenwand 18 nur durch einen schmalen Spalt getrennt sind. Die Zwischenwand 18 weist eine Ausnehmung 19' auf, welche die Form eines Kreisringsektors hat, der sich vom inneren Rand der Zwischenwand 18 bis nahe an ihren äusseren Rand erstreckt und einen Winkelbereich von ca. 45° einnimmt und einen kreisringsektorförmigen Durchlass 19 bildet. Die Fläche des Durchlasses 19 entspricht etwa dem lichten Querschnitt des Austrittsstutzens 8, allfällige Abweichungen betragen vorzugsweise höchstens 20%.Between the front annular space 5 and the rear annular space 6 there is an approximately annular thin partition 18 (see also Fig. 5a,b ) arranged, with an outer edge area which is clamped between the suction housing 1 and the pressure housing 2 and an inner edge area which overlaps with the edge area free of the webs 13 on the front side of the base of the impeller 11 at a small axial distance, so that the impeller 11 and the intermediate wall 18 are only separated by a narrow gap. The intermediate wall 18 has a recess 19 'which has the shape of a Has an annular sector, which extends from the inner edge of the intermediate wall 18 to close to its outer edge and occupies an angular range of about 45 ° and a circular ring sector-shaped passage 19 forms. The area of the passage 19 corresponds approximately to the clear cross section of the outlet nozzle 8, any deviations preferably amount to at most 20%.

Dem Durchlass 19 geht in Drehrichtung des Laufrades 11 eine Sperre 20 (s. Fig. 3, wo das Sauggehäuse 1, das Laufrad 11, die Zwischenwand 18 und die Welle 10 weggelassen sind) unmittelbar vorauf, die ihrerseits knapp auf die Öffnung im hinteren Ringraum 6 folgt, die in den Austrittsstutzen 8 führt. Die Sperre 20 ist als ein annähernd radialer von der Rückwand des Druckgehäuses 2 vorspringender, sich durch den Zwischenraum 16 und den hinteren Ringraum 6 hinziehender und sie unterbrechender Riegel ausgebildet, der nahe an die Stege 15 des Laufrades 11 heranreicht und an die Zwischenwand 18 stösst. Seine Vorderseite ist nach aussen etwas in Laufrichtung geneigt, sodass sie stetig zum Austrittsstutzen 8 hinleitet.In the direction of rotation of the impeller 11, the passage 19 is preceded by a barrier 20 (see Fig. 3 , where the suction housing 1, the impeller 11, the intermediate wall 18 and the shaft 10 are omitted) immediately in front, which in turn follows closely the opening in the rear annular space 6, which leads into the outlet nozzle 8. The lock 20 is designed as an approximately radial bolt projecting from the rear wall of the pressure housing 2, extending through the intermediate space 16 and the rear annular space 6 and interrupting them, which reaches close to the webs 15 of the impeller 11 and abuts the intermediate wall 18. Its front side is slightly inclined outwards in the direction of travel, so that it constantly leads to the outlet nozzle 8 .

Im Betrieb wird die Welle 10 angetrieben und das Laufrad 11 dreht sich in der z.B. in Fig. 2 angegebenen Laufrichtung. Die zu transportierende Flüssigkeit wird durch den Eintrittsstutzen 7 angesaugt (Pfeil x in Fig. 1, 2), von den Stegen 13 an der Vorderseite des Laufrades 11 mitgenommen und durch die Zentrifugalkraft in den vorderen Ringraum 5 gepresst. Durch den Durchlass 19 (Pfeil y in Fig. 1, 2, 3) gelangt die Flüssigkeit dann in den hinteren Ringraum 6, wo sie nach innen gedrückt wird und z.T. zwischen die Stege 15 an der Rückseite des Laufrades 11 und in den Zwischenraum 16 gelangt. Sie wird daher z.T. direkt von den Stegen 15 mitgenommen und z.T. aufgrund ihrer Viskosität im Zwischenraum 16 und im hinteren Ringraum 6 von der Bewegung der von den Stegen 15 mitgenommenen Flüssigkeit mitgerissen. Der letztere Teil der Flüssigkeit wird nach etwas weniger als einem Umlauf von der Sperre 20 in den Austrittsstutzen 8 abgelenkt (Pfeil z in Fig. 1, 3). Die Strömung weist keine scharfen Umlenkungen auf. Es entstehen daher keine ausgeprägten den Wirkungsgrad verschlechternden Turbulenzen. Dies wird durch die Bemessung des Durchlasses 19, d.h. die Ähnlichkeit seiner Fläche mit der lichten Weite des Austrittsstutzens 8 unterstützt, welche eine gleichmässige Strömung begünstigt.In operation, the shaft 10 is driven and the impeller 11 rotates in the z 2 specified running direction. The liquid to be transported is sucked in through the inlet nozzle 7 (arrow x in 1 , 2 ), taken along by the webs 13 on the front side of the impeller 11 and pressed into the front annular space 5 by the centrifugal force. Through passage 19 (arrow y in 1 , 2, 3 ) the liquid then reaches the rear annular space 6, where it is pressed inwards and partly between the webs 15 on the back of the impeller 11 and into the space 16. It is therefore partly entrained directly by the webs 15 and partly due to its viscosity Gap 16 and entrained in the rear annular space 6 by the movement of the entrained by the webs 15 liquid. The latter part of the liquid is deflected from the barrier 20 into the outlet nozzle 8 after a little less than one revolution (arrow z in 1 , 3 ). The flow shows no sharp deflections. There are therefore no pronounced turbulences that impair the efficiency. This is supported by the dimensioning of the passage 19, ie the similarity of its area with the clear width of the outlet nozzle 8, which promotes a uniform flow.

Die Wirkung der erfindungsgemässen Kreiselpumpe ähnelt der einer Hintereinanderschaltung einer Radialrad-Kreiselpumpe und einer Peripheralrad-Kreiselpumpe, doch ist der Aufbau wesentlich einfacher. Die Kennlinien (Fig. 6) liegen etwa zwischen den Kennlinien dieser beiden bekannten Typen von Kreiselpumpen. Der erzielbare Ausgangsdruck und damit die maximale Förderhöhe H ist, ähnlich wie bei einer Peripheralrad-Kreiselpumpe, hoch. Doch sinkt der Ausgangsdruck, d.h. die Förderhöhe H mit zunehmender Förderrate Q weniger rasch ab. Auch der Leistungsbedarf P hängt nicht sehr stark von der Förderrate Q ab. Insofern sind die Kennlinien denjenigen einer Radialrad-Kreiselpumpe angenähert.The effect of the centrifugal pump according to the invention is similar to that of a radial impeller centrifugal pump and a peripheral impeller centrifugal pump connected in series, but the construction is much simpler. The characteristics ( 6 ) lie somewhere between the characteristic curves of these two known types of centrifugal pumps. The output pressure that can be achieved and thus the maximum delivery head H is high, similar to that of a peripheral impeller centrifugal pump. However, the outlet pressure, ie the delivery head H, decreases less rapidly with increasing delivery rate Q. The power requirement P does not depend very much on the delivery rate Q either. In this respect, the characteristics are similar to those of a radial impeller centrifugal pump.

BezugszeichenlisteReference List

11
Sauggehäusesuction housing
22
Druckgehäusepressure housing
33
Schraube mit FederringScrew with spring washer
44
Dichtungpoetry
55
vorderer Ringraumanterior annulus
66
hinterer Ringraumrear annulus
77
Eintrittsstutzeninlet port
88th
Austrittsstutzenoutlet nozzle
99
Gleitringdichtungmechanical seal
1010
Wellewave
1111
LaufradWheel
1212
Achseaxis
1313
Steg (Vorderseite Laufrad 11)Bridge (front side impeller 11)
1414
Ringsteg (Laufrad 11)Ring bar (impeller 11)
1515
Steg (Rückseite Laufrad 11)Bridge (rear of impeller 11)
1616
Zwischenraumspace
1717
Ringsteg (Druckgehäuse 2)Ring land (pressure casing 2)
1818
Zwischenwandpartition
19'19'
Ausnehmungrecess
1919
Durchlasspassage
2020
Sperrelock

Claims (11)

  1. A centrifugal pump for conveying liquids, with a housing enclosing a cavity that is at least approximatively rotationally symmetric, with an annular space as well as an entry nozzle (7) opening to the cavity on a front side and connected to the annular space, and a peripheral outlet nozzle (8) leading out of the annular space, and with an impeller (11) rotatable in a running direction around an axis (12) in the cavity and presenting webs (15) on a back side that extend radially from the interior to an outer edge, and wherein the entry nozzle (7) is arranged centrally and the impeller (11) has an outer edge that is spaced apart from the outer boundary of the annular space, and webs (13) protruding on a front side facing the entry nozzle (7) and extending, arched backwards against the running direction, from the proximity of the axis (12) towards the outer edge, and the annular space is divided, through the impeller (11) and a peripheral intermediate wall (18) extending from its outer boundary at least to the outer edge of the impeller (11), into a front annular space (5) extending over the whole periphery and being connected to the entry nozzle (7), and a back annular space (6) extending approximately over the whole periphery, being connected to the outlet nozzle (8) and being interrupted by an at least approximately radial barrier (20) reaching up to the impeller (11) and following the outlet nozzle (8) in the running direction, while the intermediate wall (18) presents a passage (19) that follows the barrier (20) in the running direction and extends over a limited angular interval.
  2. The centrifugal pump according to claim 1, characterised in that the front side of the impeller (11) is free of webs (13) in an outer edge area and overlaps the intermediate wall (18) there.
  3. The centrifugal pump according to claim 1 or 2, characterised in that the passage (19) is immediately adjacent to the barrier (20).
  4. The centrifugal pump according to any one of claims 1 to 3, characterised in that the passage (19) occupies an area that deviates from a clear cross-section of the outlet nozzle (8) by at most 20%.
  5. The centrifugal pump according to any one of claims 1 to 4, characterised in that the passage (19) presents the shape of an annular sector.
  6. The centrifugal pump according to any one of claims 1 to 5, characterised in that, bordering on the back side of the impeller (11), an intermediate space (16) connecting to the back annular space (6) is provided and that the barrier (20) also extends through the intermediate space (16).
  7. The centrifugal pump according to any one of claims 1 to 6, characterised in that the outlet nozzle (8) tangentially leads out of the back annular space (6).
  8. The centrifugal pump according to any one of claims 1 to 7, characterised in that the frontside of the housing is formed by a suction housing (1) that surrounds the front annular space (5) and comprises the entry nozzle (7), and the backside of the housing by a delivery housing (2) that surrounds the back annular space (6) and comprises the outlet nozzle (8).
  9. The centrifugal pump according to claim 8, characterised in that an outer edge of the intermediate wall (18) is clamped between the suction housing (1) and the delivery housing (2).
  10. The centrifugal pump according to claim 8 or 9, characterised in that the barrier (20) is configured as a bar that is moulded onto a back wall of the delivery housing (2).
  11. The centrifugal pump according to any one of claims 8 to 10, characterised in that the impeller (11) is mounted on a shaft (10) that is guided by a floating ring seal (9) and drivable in the running direction.
EP18405018.5A 2018-08-09 2018-08-09 Centrifugal pump Active EP3608544B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP18405018.5A EP3608544B1 (en) 2018-08-09 2018-08-09 Centrifugal pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP18405018.5A EP3608544B1 (en) 2018-08-09 2018-08-09 Centrifugal pump

Publications (2)

Publication Number Publication Date
EP3608544A1 EP3608544A1 (en) 2020-02-12
EP3608544B1 true EP3608544B1 (en) 2022-01-12

Family

ID=63311968

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18405018.5A Active EP3608544B1 (en) 2018-08-09 2018-08-09 Centrifugal pump

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EP (1) EP3608544B1 (en)

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3936240A (en) * 1974-03-25 1976-02-03 General Electric Company Centrifugal-vortex pump
JPS529107A (en) * 1975-07-11 1977-01-24 Matsushita Electric Ind Co Ltd Pump
DE4315448A1 (en) * 1992-05-19 1993-12-23 Lederle Pumpen & Maschf Peripheral wheel or turbine pump - has flow feed path using centrifugal impeller components and guide elements.

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Publication number Publication date
EP3608544A1 (en) 2020-02-12

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