EP3608544A1 - Centrifugal pump - Google Patents

Centrifugal pump Download PDF

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Publication number
EP3608544A1
EP3608544A1 EP18405018.5A EP18405018A EP3608544A1 EP 3608544 A1 EP3608544 A1 EP 3608544A1 EP 18405018 A EP18405018 A EP 18405018A EP 3608544 A1 EP3608544 A1 EP 3608544A1
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EP
European Patent Office
Prior art keywords
centrifugal pump
annular space
impeller
pump according
housing
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Granted
Application number
EP18405018.5A
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German (de)
French (fr)
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EP3608544B1 (en
Inventor
Ernst Müller
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Individual
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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 conveying liquids.
  • Peripheral wheel centrifugal pumps have been known for a long time. With a peripheral wheel centrifugal pump, a high pressure at the outlet and thus a large delivery head can be achieved at a low delivery rate. However, the characteristic curves drop steeply, i.e. a significant increase in the delivery rate is only possible when the outlet pressure is greatly reduced, i.e. the achievable delivery head. The required pumping power also drops sharply.
  • the characteristic curves of the radial centrifugal pumps which have also been known for a long time, are rather flat, i.e. a significant increase in the delivery rate can already be achieved by slightly reducing the outlet pressure in accordance with the achievable delivery head, while the required pump output 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 similarly high output pressures can be achieved as with a comparable peripheral centrifugal pump, the characteristics of which are, however, significantly flatter.
  • the centrifugal pump according to the invention essentially corresponds to a peripheral wheel centrifugal pump, which has an extension on the inlet side, which has the features of a radial wheel centrifugal pump. It is very simple and space-saving and can be produced at a correspondingly low cost.
  • the characteristics are qualitatively similar to those of a peripheral impeller centrifugal pump, but drop much less steeply.
  • the pump power required slowly decreases as the delivery rate increases. A high degree of efficiency can be achieved.
  • the centrifugal pump according to the embodiment according to the invention has ( Fig. 1 ) on a housing, which is composed of a front suction housing 1 and a rear pressure housing 2 connected to it 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 approximately rotationally symmetrical and enclose an essentially 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 connector 7, which is attached centrally to the suction housing 1 and opens into the cavity at the front.
  • the pressure housing 2 carries a peripherally arranged outlet connection 8, which leads approximately tangentially upwards out of the rear annular space 6 and whose clear cross section corresponds approximately to that of the inlet connection 7.
  • An impeller 11 (see also FIG. 3) is mounted on a drivable drive shaft 10 guided through a mechanical seal 9 Fig. 2 where the suction housing 1 is omitted and 4a-c ) attached in the cavity in one direction (see arrow in Fig. 2 ) is rotatable about a central axis 12.
  • the impeller 11 has a disk-shaped base, which carries webs 13 projecting vertically on a front side facing the inlet connection piece 7, which webs extend from the inside, that is to say bent back from near the axis in the running direction, towards the outer edge of the base, but with an edge region of the base The front remains free.
  • the impeller 11 has radial webs 15 of the same height, which run radially from the inside, ie from an annular web 14 surrounding the axis 12 to the outer edge of the base, which are spaced from a rear wall of the pressure housing 2, so that there is an inside the space 16 adjoining the rear annular space 6 remains free.
  • the webs can also protrude beyond the outer edge of the base.
  • the distance between the ring web 14 and a rear wall of the pressure housing 2 is bridged by a fixed ring web 17 projecting therefrom against the ring web 14, such that there is only a narrow circumferential gap between the ring webs 14 and 17.
  • the intermediate wall 18 has a recess 19 ', which has the shape of a Has circular sector, which extends from the inner edge of the intermediate wall 18 to close to its outer edge and occupies an angular range of approximately 45 ° and forms an annular sector-shaped passage 19.
  • the area of the passage 19 corresponds approximately to the clear cross section of the outlet connection 8, any deviations are preferably at most 20%.
  • the passage 19 is in the direction of rotation of the impeller 11, a lock 20 (s. Fig. 3 , where the suction housing 1, the impeller 11, the intermediate wall 18 and the shaft 10 are omitted) immediately ahead, which in turn closely follows the opening in the rear annular space 6, which leads into the outlet port 8.
  • the lock 20 is designed as an approximately radial ledge projecting from the rear wall of the pressure housing 2, extending through the intermediate space 16 and the rear annular space 6 and interrupting it, which reaches close to the webs 15 of the impeller 11 and abuts the intermediate wall 18. Its front is slightly inclined outwards in the running direction, so that it leads continuously to the outlet connection 8.
  • the shaft 10 is driven and the impeller 11 rotates in the example in Fig. 2 specified direction.
  • the liquid to be transported is sucked in through the inlet connection 7 (arrow x in Fig. 1 . 2 ), carried along by the webs 13 on the front of the impeller 11 and pressed into the front annular space 5 by the centrifugal force.
  • the liquid then gets into the rear annular space 6, where it is pressed inwards and partly between the webs 15 on the rear of the impeller 11 and into the intermediate space 16.
  • the effect of the centrifugal pump according to the invention is similar to that of connecting a radial wheel centrifugal pump and a peripheral wheel centrifugal pump in series, but the structure is much simpler.
  • the characteristics ( Fig. 6 ) lie approximately between the characteristics of these two known types of centrifugal pumps.
  • the achievable outlet pressure and thus the maximum delivery head H is high, similar to a peripheral centrifugal pump.
  • the outlet pressure, ie the delivery head H drops less rapidly with increasing delivery rate Q.
  • the power requirement P does not depend very much on the delivery rate Q either.
  • the characteristic curves are approximated to those of a radial wheel centrifugal pump.

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

Abstract

Die Erfindung betrifft eine Kreiselpumpe. Ein Gehäuse mit einem zentralen Eintrittsstutzen (7) und einem peripheren Austrittsstutzen (8) enthält ein Laufrad (11) mit an einer Vorderseite entgegen einer Laufrichtung zurückgebogenen Stegen (13) und an einer Rückseite radialen Stegen (15). Ein das Laufrad (11) umgebender Ringraum ist durch eine Zwischenwand (18) in einen vorderen Ringraum (5) und einen hinteren Ringraum (6), an den nach innen ein Zwischenraum (16) anschliesst, geteilt, die jedoch durch einen Durchlass (19) in der Zwischenwand (18) verbunden sind. Auf den Austrittsstutzen (8) folgt in Laufrichtung eine nahe an die Rückseite des Laufrades (11) heranreichende und an die Zwischenwand (18) stossende Sperre, die dem Durchlass (19) unmittelbar voraufgeht. Flüssigkeit wird durch den Eintrittsstutzen (7) angesaugt, gelangt in den vorderen Ringraum (5), dann durch den Durchlass (19) in den hinteren Ringraum (6), zwischen die Stege (15) und in den Zwischenraum (17). Sie wird von der Sperre in den Austrittstutzen (8) gelenkt. Die Kreiselpumpe weist verhältnismässig flache Kennlinien auf, ermöglicht aber einen hohen Ausgangsdruck.The invention relates to a centrifugal pump. A housing with a central inlet connection (7) and a peripheral outlet connection (8) contains an impeller (11) with webs (13) which are bent back against a running direction on a front side and radial webs (15) on a rear side. An annular space surrounding the impeller (11) is divided by an intermediate wall (18) into a front annular space (5) and a rear annular space (6), to which an intermediate space (16) adjoins on the inside, but is separated by a passage (19 ) are connected in the intermediate wall (18). The outlet connection (8) is followed in the running direction by a barrier which comes close to the rear of the impeller (11) and abuts the intermediate wall (18) and which immediately precedes the passage (19). Liquid is sucked in through the inlet connection (7), reaches the front annular space (5), then through the passage (19) into the rear annular space (6), between the webs (15) and into the intermediate space (17). It is directed by the lock into the outlet nozzle (8). The centrifugal pump has relatively flat characteristics, but enables a high outlet pressure.

Description

Technisches GebietTechnical field

Die Erfindung betrifft eine Kreiselpumpe zur Förderung von Flüssigkeiten.The invention relates to a centrifugal pump for conveying 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 wheel centrifugal pumps have been known for a long time. With a peripheral wheel centrifugal pump, a high pressure at the outlet and thus a large delivery head can be achieved at a low delivery rate. However, the characteristic curves drop steeply, i.e. a significant increase in the delivery rate is only possible when the outlet pressure is greatly reduced, i.e. the achievable delivery head. The required pumping power also drops sharply. The characteristic curves of the radial centrifugal pumps, which have also been known for a long time, are rather flat, i.e. a significant increase in the delivery rate can already be achieved by slightly reducing the outlet pressure in accordance with the achievable delivery head, while the required pump output increases slightly. However, the maximum outlet pressure that can be achieved is rather low.

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 similarly high output pressures can be achieved as with a comparable peripheral centrifugal pump, the characteristics of which are, however, 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 achieved by the invention as characterized in the claims. The centrifugal pump according to the invention essentially corresponds to a peripheral wheel centrifugal pump, which has an extension on the inlet side, which has the features of a radial wheel centrifugal pump. It is very simple and space-saving and can be produced at a correspondingly low cost.

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 characteristics are qualitatively similar to those of a peripheral impeller centrifugal pump, but drop much less steeply. In particular, the pump power required slowly decreases as the delivery rate increases. A high degree 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 only represent an exemplary embodiment. Show it
Fig. 1
3 shows a cross section along an axis of the centrifugal pump according to the invention,
Fig. 2
2 shows a front view of the centrifugal pump according to the invention, with a housing part being omitted,
Fig. 3
5 shows a further front view of the centrifugal pump according to the invention, with further parts being omitted,
Fig. 4a
2 shows a front view of an impeller of the centrifugal pump according to the invention,
Fig. 4b
a side view of the impeller, partially cut along the axis,
Fig. 4c
a rear view of the impeller,
Fig. 5a
2 shows a front view of an intermediate wall of the centrifugal pump according to the invention,
Fig. 5b
a section through the partition along BB in Fig. 5a and
Fig. 6
Characteristic curves of the centrifugal pump according to the invention.

Wege zur Ausführung der ErfindungWays of Carrying 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. 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.The centrifugal pump according to the embodiment according to the invention has ( Fig. 1 ) on a housing, which is composed of a front suction housing 1 and a rear pressure housing 2 connected to it 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 approximately rotationally symmetrical and enclose an essentially 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 connector 7, which is attached centrally to the suction housing 1 and opens into the cavity at the front. The pressure housing 2 carries a peripherally arranged outlet connection 8, which leads approximately tangentially upwards out of the rear annular space 6 and whose clear cross section corresponds approximately to that of the inlet connection 7. An impeller 11 (see also FIG. 3) is mounted on a drivable drive shaft 10 guided through a mechanical seal 9 Fig. 2 where the suction housing 1 is omitted and 4a-c ) attached in the cavity in one direction (see arrow in Fig. 2 ) is rotatable about a central axis 12. The impeller 11 has a disk-shaped base, which carries webs 13 projecting vertically on a front side facing the inlet connection piece 7, which webs extend from the inside, that is to say bent back from near the axis in the running direction, towards the outer edge of the base, but with an edge region of the base The front remains free. At the rear, the impeller 11 has radial webs 15 of the same height, which run radially from the inside, ie from an annular web 14 surrounding the axis 12 to the outer edge of the base, which are spaced from a rear wall of the pressure housing 2, so that there is an inside the space 16 adjoining the rear annular space 6 remains free. The webs can also protrude beyond the outer edge of the base. The distance between the ring web 14 and a rear wall of the pressure housing 2 is bridged by a fixed ring web 17 projecting therefrom against the ring web 14, such that there is only a narrow circumferential gap between the ring webs 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 is an approximately circular thin partition 18 (see also 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 of the base of the impeller 11 with a small axial distance, so that the impeller 11 and the intermediate wall 18 are separated only by a narrow gap. The intermediate wall 18 has a recess 19 ', which has the shape of a Has circular sector, which extends from the inner edge of the intermediate wall 18 to close to its outer edge and occupies an angular range of approximately 45 ° and forms an annular sector-shaped passage 19. The area of the passage 19 corresponds approximately to the clear cross section of the outlet connection 8, any deviations are preferably 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.The passage 19 is in the direction of rotation of the impeller 11, a lock 20 (s. Fig. 3 , where the suction housing 1, the impeller 11, the intermediate wall 18 and the shaft 10 are omitted) immediately ahead, which in turn closely follows the opening in the rear annular space 6, which leads into the outlet port 8. The lock 20 is designed as an approximately radial ledge projecting from the rear wall of the pressure housing 2, extending through the intermediate space 16 and the rear annular space 6 and interrupting it, which reaches close to the webs 15 of the impeller 11 and abuts the intermediate wall 18. Its front is slightly inclined outwards in the running direction, so that it leads continuously to the outlet connection 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 example in Fig. 2 specified direction. The liquid to be transported is sucked in through the inlet connection 7 (arrow x in Fig. 1 . 2 ), carried along by the webs 13 on the front of the impeller 11 and pressed into the front annular space 5 by the centrifugal force. Through the passage 19 (arrow y in Fig. 1 . 2, 3 ) the liquid then gets into the rear annular space 6, where it is pressed inwards and partly between the webs 15 on the rear of the impeller 11 and into the intermediate space 16. It is therefore partially carried directly by the webs 15 and partially due to its viscosity in the Intermediate space 16 and in the rear annular space 6 are entrained by the movement of the liquid entrained by the webs 15. The latter part of the liquid is deflected from the barrier 20 into the outlet port 8 after a little less than one revolution (arrow z in Fig. 1 . 3 ). The flow has no sharp turns. Therefore, there is no pronounced turbulence that reduces efficiency. This is supported by the dimensioning of the passage 19, ie the similarity of its area to the clear width of the outlet connector 8, which favors 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 connecting a radial wheel centrifugal pump and a peripheral wheel centrifugal pump in series, but the structure is much simpler. The characteristics ( Fig. 6 ) lie approximately between the characteristics of these two known types of centrifugal pumps. The achievable outlet pressure and thus the maximum delivery head H is high, similar to a peripheral centrifugal pump. However, the outlet pressure, ie the delivery head H, drops 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 characteristic curves are approximated to those of a radial wheel centrifugal pump.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

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 connection
88th
Austrittsstutzenoutlet connection
99
GleitringdichtungMechanical seal
1010
Wellewave
1111
LaufradWheel
1212
Achseaxis
1313
Steg (Vorderseite Laufrad 11)Bridge (front of impeller 11)
1414
Ringsteg (Laufrad 11)Ring web (impeller 11)
1515
Steg (Rückseite Laufrad 11)Bridge (rear of impeller 11)
1616
Zwischenraumgap
1717
Ringsteg (Druckgehäuse 2)Ring web (pressure housing 2)
1818
Zwischenwandpartition
19'19 '
Ausnehmungrecess
1919
Durchlasspassage
2020
Sperrebarrier

Claims (11)

Kreiselpumpe mit einem Gehäuse, welches einen mindestens annäherend rotationssymmetrischen Hohlraum umschliesst, mit einem Ringraum sowie einem an einer Vorderseite in den Hohlraum mündenden mit dem Ringraum verbundenen Eintrittsstutzen (7) und einem vom Ringraum nach aussen führenden peripheren Austrittsstutzen (8) sowie mit einem im Hohlraum in einer Laufrichtung um eine Achse (12) drehbaren Laufrad (11), das an einer Rückseite radial von innen gegen einen äusseren Rand laufende Stege (15) aufweist, dadurch gekennzeichnet, dass der Eintrittsstutzen (7) zentral angeordnet ist und das Laufrad (11) einen äusseren Rand aufweist, der von der äusseren Begrenzung des Ringraums beabstandet ist und an einer dem Eintrittsstutzen (7) zugewandten Vorderseite abstehende Stege (13), welche entgegen der Laufrichtung zurückgebogen von der Nähe der Achse (12) gegen den äusseren Rand laufen und der Ringraum durch das Laufrad (11) und eine von seiner äusseren Begrenzung bis mindestens zum äusseren Rand des Laufrades (11) sich erstreckende umlaufende Zwischenwand (18) in einen vorderen Ringraum (5), welcher mit dem Eintrittsstutzen (7) verbunden ist und einen hinteren Ringraum (6), welcher mit dem Austrittsstutzen (8) verbunden ist, geteilt ist und der hintere Ringraum (6) von einer mindestens annähernd radialen, an das Laufrad (11) heranreichenden Sperre (20) unterbrochen ist, welche in Laufrichtung auf den Austrittsstutzen (8) folgt, während die Zwischenwand (18) einen in Laufrichtung auf die Sperre (20) folgenden, sich über einen begrenzten Winkelbereich erstreckenden Durchlass (19) aufweist.Centrifugal pump with a housing, which encloses an at least approximately rotationally symmetrical cavity, with an annular space and with an inlet connection (7) opening into the hollow space on a front side, and with a peripheral outlet connection (8) leading outwards from the annular space and with one in the cavity Impeller (11) rotatable about an axis (12) in a running direction and having webs (15) running radially from the inside against an outer edge on a rear side, characterized in that the inlet connector (7) is arranged centrally and the impeller (11 ) has an outer edge which is spaced from the outer boundary of the annular space and on a front side facing the inlet connector (7) protruding webs (13) which run backwards against the direction of travel from the vicinity of the axis (12) against the outer edge and the annulus through the impeller (11) and one of its outer limit to at least usseren edge of the impeller (11) extending circumferential partition (18) into a front annular space (5), which is connected to the inlet connector (7) and a rear annular chamber (6), which is connected to the outlet connector (8) and the rear annular space (6) is interrupted by an at least approximately radial barrier (20) reaching towards the impeller (11), which lock follows the outlet connection (8) in the running direction, while the intermediate wall (18) follows one in the running direction Lock (20) following passage (19) extending over a limited angular range. Kreiselpumpe nach Anspruch 1, dadurch gekennzeichnet, dass die Vorderseite des Laufrads (11) an einem äusseren Randbereich von den Stegen (13) frei ist und dort mit der Zwischenwand (18) überlappt.Centrifugal pump according to claim 1, characterized in that the front of the impeller (11) is free from the webs (13) at an outer edge region and overlaps there with the intermediate wall (18). Kreiselpumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Durchlass (19) der Sperre (20) unmittelbar benachbart ist.Centrifugal pump according to claim 1 or 2, characterized in that the passage (19) of the barrier (20) is immediately adjacent. Kreiselpumpe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass der Durchlass (19) eine Fläche einnimmt, welche von einem lichten Querschnitt des Austrittsstutzens (8) um höchstens 20% abweicht.Centrifugal pump according to one of claims 1 to 3, characterized in that the passage (19) occupies an area which deviates from a clear cross section of the outlet connector (8) by at most 20%. Kreiselpumpe nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass der Durchlass (19) die Form eines Kreisringsektors aufweist.Centrifugal pump according to one of claims 1 to 4, characterized in that the passage (19) has the shape of a circular ring sector. Kreiselpumpe nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass angrenzend an die Rückseite des Laufrades (11) ein innen an den hinteren Ringraum (6) anschliessender Zwischenraum (16) vorgesehen ist und die Sperre (20) sich auch durch den Zwischenraum (16) erstreckt.Centrifugal pump according to one of claims 1 to 5, characterized in that adjacent to the rear of the impeller (11) there is an intermediate space (16) adjoining the rear annular space (6) and the lock (20) also extends through the intermediate space ( 16) extends. Kreiselpumpe nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass der Austrittsstutzen (18) tangential aus dem hinteren Ringraum (6) hinausführt.Centrifugal pump according to one of claims 1 to 6, characterized in that the outlet connection (18) leads tangentially out of the rear annular space (6). Kreiselpumpe nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die Vorderseite des Gehäuses von einem Sauggehäuse (1) gebildet wird, welches den vorderen Ringraum (5) umgibt und den Eintrittsstutzen (7) umfasst und eine Rückseite des Gehäuses von einem Druckgehäuse (2), das den hinteren Ringraum (6) umgibt und den Austrittsstutzen (8) umfasst.Centrifugal pump according to one of claims 1 to 7, characterized in that the front of the housing is formed by a suction housing (1) which surrounds the front annular space (5) and comprises the inlet connector (7) and a rear of the housing by one Pressure housing (2) which surrounds the rear annular space (6) and comprises the outlet nozzle (8). Kreiselpumpe nach Anspruch 8, dadurch gekennzeichnet, dass ein äusserer Rand der Zwischenwand (18) zwischen dem Sauggehäuse (1) und dem Druckgehäuse (2) geklemmt ist.Centrifugal pump according to claim 8, characterized in that an outer edge of the intermediate wall (18) is clamped between the suction housing (1) and the pressure housing (2). Kreiselpumpe nach Anspruch 8 oder 9, dadurch gekennzeichnet, dass die Sperre (20) als ein an eine Rückwand des Druckgehäuses (2) angeformter Riegel ausgebildet ist.Centrifugal pump according to claim 8 or 9, characterized in that the lock (20) is designed as a bolt formed on a rear wall of the pressure housing (2). Kreiselpumpe nach einem der Ansprüche 8 bis 10, dadurch gekennzeichnet, dass das Laufrad (11) an einer im Druckgehäuse (2) gelagerten in Laufrichtung antreibbaren Welle (10) befestigt ist.Centrifugal pump according to one of Claims 8 to 10, characterized in that the impeller (11) is fastened to a shaft (10) which can be driven in the direction of rotation and which is mounted in the pressure housing (2).
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

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

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ID=63311968

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Citations (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.

Patent Citations (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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