EP1131560B1 - Side channel pump - Google Patents

Side channel pump Download PDF

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Publication number
EP1131560B1
EP1131560B1 EP00969250A EP00969250A EP1131560B1 EP 1131560 B1 EP1131560 B1 EP 1131560B1 EP 00969250 A EP00969250 A EP 00969250A EP 00969250 A EP00969250 A EP 00969250A EP 1131560 B1 EP1131560 B1 EP 1131560B1
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EP
European Patent Office
Prior art keywords
impeller
vane
end side
chambers
region
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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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EP00969250A
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German (de)
French (fr)
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EP1131560A1 (en
Inventor
Hans-Dieter Wilhelm
Holger Barth
Matthias Staab
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Siemens AG
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Siemens AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/188—Rotors specially for regenerative pumps

Definitions

  • the invention relates to a feed pump with a driven, rotating in a pump housing, in its end faces at least one rim blade chambers bounding vanes having impeller in which the blade chambers have an inflow and a Ausström Scheme for the medium to be conveyed, and with at least a portion of the vanes arranged in the pump housing partially annular channel, which forms with the blade chambers a delivery chamber from an inlet channel to an outlet channel, wherein the contour of the blade chambers is formed by at least one radius having an origin within the delivery chamber.
  • Such feed pumps are often used for conveying fuel in a fuel tank or for conveying washing liquid in a windscreen washer system of a motor vehicle and are known in practice.
  • the known feed pump has in each case a ring of vane chambers in both end faces of the impeller.
  • the vane chambers are bounded in the radially outer direction by a straight, perpendicular to the end faces of the impeller wall.
  • the pointing to the radially inner direction of the impeller contour of the blade chambers is generated by a radius.
  • the origin of the radius is arranged on the center line arranged perpendicular to the end faces of the impeller. This origin is also the origin of a second, the part-annular channel forming radius.
  • a disadvantage of the known feed pump is that the feed pump generates turbulence in the medium to be conveyed. These turbulences lead to a low efficiency of the feed pump. At close to the boiling point media, such as hot gasoline fuel, there is also the risk of the formation of vapor bubbles within the delivery chamber. The vapor bubbles lead to a strong reduction in the volume flow delivered by the feed pump.
  • the invention is based on the problem of designing a feed pump of the type mentioned so that it has the highest possible efficiency and reliably avoids the formation of vapor bubbles.
  • the blade chamber has, in its region formed by the radius, a contour that rises very flatly from the end face.
  • This flat design changes a circulation flow in the delivery chamber between the impeller and the pump housing. Since the circulation flow experiences only a small deflection in this area, the risk of turbulence is kept particularly low. This also avoids the formation of vapor bubbles.
  • the impeller can be manufactured inexpensively according to an advantageous embodiment of the invention, when the origins of a plurality of radii for opposing contours of the blade chambers on a common, parallel to the end face of the impeller extending plane are arranged within the impeller.
  • the circulation flow swirled here can settle down again quickly if the blade chambers have boundaries perpendicular to the end face of the impeller from the plane parallel to the end face of the impeller to the front end ,
  • the impeller has according to another advantageous embodiment of the invention simply constructed blade chambers and can therefore be manufactured particularly cost-effective, if the origins of two, each opposing contours generating radii are arranged mirror images of the center line of the blade chamber.
  • the center line can be designed as a line of symmetry for the contour pointing to the center of the impeller and the contour pointing away from the center of the impeller.
  • the feed pump according to the invention has a particularly high efficiency when the distance of the origins of the radii from the center line has approximately the same amount as their distance from the end face.
  • Opposed vane chambers could be interconnected as in the known feed pump in a radially outer region of the impeller. To further increase the efficiency of the feed pump according to the invention, however, it contributes, when mirror-inverted in both end faces of the impeller oppositely arranged vane chambers are interconnected exclusively in the region of the center line. This allows the circulation flow With very little turbulence from the one delivery chamber into the other delivery chamber overflow. The danger of the formation of vapor bubbles is thereby also kept particularly low.
  • FIG. 1 shows a longitudinal section through a driven by an electric motor 1, designed as an axially flow-through side channel pump feed pump 2, which may be provided for example for conveying fuel from a fuel tank of a motor vehicle, not shown.
  • the feed pump 2 has a pump housing 3, in which a rotatably mounted on a shaft 4 of the electric motor 1 fixed impeller 5 is arranged.
  • the pump housing 3 has on its side facing away from the electric motor 1 an inlet channel 6 and on the side facing the electric motor 1 an outlet 7.
  • the inlet channel 6 opens into a delivery chamber 8.
  • a second delivery chamber 9 opens into the outlet 7.
  • the delivery chambers 8, 9th each have in the pump housing 3 incorporated, part-annular channels 10, 11 and arranged in the impeller 5 blade chambers 12, 13.
  • the blade chambers 12, 13 are each delimited by guide vanes 14, 15 and each have an inflow region 16, 17 for the inflow of the medium to be conveyed and an outflow area 18, 19. Between the inflow region 16, 17 and the outflow region 18, 19, mutually opposed blade chambers 12, 13 are connected to one another.
  • FIG 2 shows greatly enlarged the feed pump 2 of Figure 1 in the region of the delivery chambers 8, 9.
  • the blade chambers 12, 13 are each designed symmetrically to a perpendicular to an end face extending center line.
  • the vane chambers 12, 13 each have a contour formed by radii R in the inflow regions 16, 17 and in the outflow regions 18, 19.
  • the radii R in this case have seen from the respective contour from behind the center line origin.
  • the origins of the radii R are also located in a common plane parallel to the end face of the impeller 5 level.
  • the planes of the blade chambers 12, 13 are shown in phantom in the drawing.
  • the circulation flow passes with particularly small turbulences from the part-annular channels 10, 11 in the blade chambers 12, 13.
  • the plane of the origins of the radii R has approximately the same distance from the end face of the impeller 5 as the origins of the radii R from the center line.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Rotary Pumps (AREA)
  • Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)
  • Liquid Developers In Electrophotography (AREA)
  • Shaping Of Tube Ends By Bending Or Straightening (AREA)
  • Inductance-Capacitance Distribution Constants And Capacitance-Resistance Oscillators (AREA)

Abstract

In a feed pump designed as a side-channel pump, a blade chamber of an impeller has a contour which is formed by a radius and in which, as seen from the contour, the origin of the radius is located behind a center line of the blade chamber. A circulation flow thereby passes into the blade chamber with particularly low turbulences. The feed pump has particularly high efficiency as a result.

Description

Die Erfindung betrifft eine Förderpumpe mit einem angetriebenen, sich in einem Pumpengehäuse drehenden, in seinen Stirnseiten zumindest einen Kranz Schaufelkammern begrenzende Leitschaufeln aufweisenden Laufrad, bei dem die Schaufelkammern einen Einströmbereich und einen Ausströmbereich für das zu fördernde Medium haben, und mit zumindest einem Bereich der Leitschaufeln in dem Pumpengehäuse angeordneten teilringförmigen Kanal, welcher mit den Schaufelkammern eine Förderkammer von einem Einlasskanal zu einem Auslasskanal bildet, wobei die Kontur der Schaufelkammern von zumindest einem Radius mit einem Ursprung innerhalb der Förderkammer gebildet ist.The invention relates to a feed pump with a driven, rotating in a pump housing, in its end faces at least one rim blade chambers bounding vanes having impeller in which the blade chambers have an inflow and a Ausströmbereich for the medium to be conveyed, and with at least a portion of the vanes arranged in the pump housing partially annular channel, which forms with the blade chambers a delivery chamber from an inlet channel to an outlet channel, wherein the contour of the blade chambers is formed by at least one radius having an origin within the delivery chamber.

Solche Förderpumpen werden häufig zum Fördern von Kraftstoff in einem Kraftstoffbehälter oder zum Fördern von Waschflüssigkeit in einer Scheibenwaschanlage eine Kraftfahrzeuges eingesetzt und sind aus der Praxis bekannt. Die bekannte Förderpumpe hat in beiden Stirnseiten des Laufrades jeweils einen Kranz Schaufelkammern. Die Schaufelkammern werden in der radial äußeren Richtung von einer geraden, senkrecht zu den Stirnseiten des Laufrades angeordneten Wand begrenzt. Die zur radial inneren Richtung des Laufrades weisende Kontur der Schaufelkammern wird von einem Radius erzeugt. Der Ursprung des Radius ist auf der senkrecht zu den Stirnseiten des Laufrades angeordneten Mittellinie angeordnet. Dieser Ursprung ist gleichzeitig Ursprung eines zweiten, den teilringförmigen Kanal bildenden Radius.Such feed pumps are often used for conveying fuel in a fuel tank or for conveying washing liquid in a windscreen washer system of a motor vehicle and are known in practice. The known feed pump has in each case a ring of vane chambers in both end faces of the impeller. The vane chambers are bounded in the radially outer direction by a straight, perpendicular to the end faces of the impeller wall. The pointing to the radially inner direction of the impeller contour of the blade chambers is generated by a radius. The origin of the radius is arranged on the center line arranged perpendicular to the end faces of the impeller. This origin is also the origin of a second, the part-annular channel forming radius.

Aus der DE 197 49 404 Cl ist eine Förderpumpe mit zueinander versetzt angeordneten Schaufelkammern bekannt, in dem die durch Radien gebildete radial innere und radial äußere Kontur der Schaufelkammern zueinander asymmetrisch gestaltet sind.From DE 197 49 404 Cl a feed pump with mutually staggered blade chambers is known in which the radial inner and radially outer contour of the blade chambers formed by radii are designed to be asymmetrical to each other.

Nachteilig bei der bekannten Förderpumpe ist, dass die Förderpumpe in dem zu fördernden Medium Verwirbelungen erzeugt. Diese Verwirbelungen führen zu einem niedrigen Wirkungsgrad der Förderpumpe. Bei nahe am Siedepunkt befindlichen Medien, wie beispielsweise heißer Otto-Kraftstoff, besteht zudem die Gefahr der Bildung von Dampfblasen innerhalb der Förderkammer. Die Dampfblasen führen zu einer starken Verringerung des von der Förderpumpe geförderten Volumenstroms.A disadvantage of the known feed pump is that the feed pump generates turbulence in the medium to be conveyed. These turbulences lead to a low efficiency of the feed pump. At close to the boiling point media, such as hot gasoline fuel, there is also the risk of the formation of vapor bubbles within the delivery chamber. The vapor bubbles lead to a strong reduction in the volume flow delivered by the feed pump.

Der Erfindung liegt das Problem zugrunde, eine Förderpumpe der eingangs genannten Art so zu gestalten, daß sie einen möglichst hohen Wirkungsgrad aufweist und die Bildung von Dampfblasen zuverlässig vermeidet.The invention is based on the problem of designing a feed pump of the type mentioned so that it has the highest possible efficiency and reliably avoids the formation of vapor bubbles.

Dieses Problem wird erfindungsgemäß dadurch gelöst, daß der Ursprung des Radius von der durch den Radius bestimmten Kontur der Schaufelkammer aus gesehen in dem einer senkrecht zur Stirnseite des Laufrades verlaufenden Mittellinie der Schaufelkammer gegenüberliegenden Bereich angeordnet ist.This problem is inventively solved in that the origin of the radius of the determined by the radius contour of the blade chamber is arranged in the region opposite to a perpendicular to the end face of the impeller center line of the blade chamber.

Durch diese Gestaltung hat die Schaufelkammer in ihrem von dem Radius gebildeten Bereich eine von der Stirnseite aus sehr flach ansteigende Kontur. Über diese flach gestaltete Kontur wechselt eine Zirkulationsströmung in der Förderkammer zwischen dem Laufrad und dem Pumpengehäuse. Da die Zirkulationsströmung in diesem Bereich nur eine geringe Umlenkung erfährt, wird die Gefahr von Verwirbelungen besonders gering gehalten. Hierdurch wird zudem die Bildung von Dampfblasen vermieden.By virtue of this design, the blade chamber has, in its region formed by the radius, a contour that rises very flatly from the end face. This flat design changes a circulation flow in the delivery chamber between the impeller and the pump housing. Since the circulation flow experiences only a small deflection in this area, the risk of turbulence is kept particularly low. This also avoids the formation of vapor bubbles.

Das Laufrad läßt sich gemäß einer vorteilhaften Weiterbildung der Erfindung kostengünstig fertigen, wenn die Ursprünge mehrerer Radien für einander gegenüberstehender Konturen der Schaufelkammern auf einer gemeinsamen, parallel zu der Stirnseite des Laufrades verlaufenden Ebene innerhalb des Laufrades angeordnet sind.The impeller can be manufactured inexpensively according to an advantageous embodiment of the invention, when the origins of a plurality of radii for opposing contours of the blade chambers on a common, parallel to the end face of the impeller extending plane are arranged within the impeller.

In dem Bereich, in dem die Zirkulationsströmung zwischen der Schaufelkammer und dem teilringförmigen Kanal wechselt, entstehen häufig Verwirbelungen. Die hier verwirbelte Zirkulationsströmung kann sich gemäß einer anderen vorteilhaften Weiterbildung der Erfindung schnell wieder beruhigen, wenn die Schaufelkammern von der parallel zu der Stirnseite des Laufrades verlaufenden Ebene bis zu der Stirnseite in ihren an die Leitschaufeln angrenzenden Bereichen senkrecht zu der Stirnseite des Laufrades geführte Begrenzungen aufweisen.In the region in which the circulation flow between the blade chamber and the part-annular channel changes, turbulences often arise. According to another advantageous development of the invention, the circulation flow swirled here can settle down again quickly if the blade chambers have boundaries perpendicular to the end face of the impeller from the plane parallel to the end face of the impeller to the front end ,

Das Laufrad hat gemäß einer anderen vorteilhaften Weiterbildung der Erfindung einfach aufgebaute Schaufelkammern und läßt sich daher besonders kostengünstig fertigen, wenn die Ursprünge zweier, jeweils einander gegenüberliegende Konturen erzeugender Radien spiegelbildlich zu der Mittellinie der Schaufelkammer angeordnet sind. Hierdurch kann die Mittellinie als Symmetrielinie für die zum Zentrum des Laufrades weisende Kontur und die von dem Zentrum des Laufrades wegweisende Kontur gestaltet sein.The impeller has according to another advantageous embodiment of the invention simply constructed blade chambers and can therefore be manufactured particularly cost-effective, if the origins of two, each opposing contours generating radii are arranged mirror images of the center line of the blade chamber. As a result, the center line can be designed as a line of symmetry for the contour pointing to the center of the impeller and the contour pointing away from the center of the impeller.

Die erfindungsgemäße Förderpumpe hat einen besonders hohen Wirkungsgrad, wenn der Abstand der Ursprünge der Radien von der Mittellinie ungefähr denselben Betrag aufweist wie deren Abstand von der Stimseite.The feed pump according to the invention has a particularly high efficiency when the distance of the origins of the radii from the center line has approximately the same amount as their distance from the end face.

Einander gegenüberliegend angeordnete Schaufelkammern könnten wie bei der bekannten Förderpumpe in einem radial äußeren Bereich des Laufrades miteinander verbunden sein. Zur weiteren Erhöhung des Wirkungsgrades der erfindungsgemäßen Förderpumpe trägt es jedoch bei, wenn spiegelbildlich in beiden Stirnseiten des Laufrades einander gegenüberliegend angeordnete Schaufelkammern ausschließlich im Bereich der Mittellinie miteinander verbunden sind. Hierdurch kann die Zirkulationsströmung mit besonders geringen Verwirbelungen von der einen Förderkammer in die andere Förderkammer überströmen. Die Gefahr der Bildung von Dampfblasen wird hierdurch zudem ebenfalls besonders gering gehalten.Opposed vane chambers could be interconnected as in the known feed pump in a radially outer region of the impeller. To further increase the efficiency of the feed pump according to the invention, however, it contributes, when mirror-inverted in both end faces of the impeller oppositely arranged vane chambers are interconnected exclusively in the region of the center line. This allows the circulation flow With very little turbulence from the one delivery chamber into the other delivery chamber overflow. The danger of the formation of vapor bubbles is thereby also kept particularly low.

Die Erfindung läßt zahlreiche Ausführungsformen zu. Zur weiteren Verdeutlichung ihres Grundprinzips ist eine davon in der Zeichnung dargestellt und wird nachfolgend beschrieben. Diese zeigt in

Figur 1
eine Schnittdarstellung durch eine erfindungsgemäße Förderpumpe,
Figur 2
eine vergrößerte Darstellung der Förderpumpe aus Figur 1 im Bereich von Förderkammern.
The invention allows numerous embodiments. To further clarify its basic principle, one of them is shown in the drawing and will be described below. This shows in
FIG. 1
a sectional view through a feed pump according to the invention,
FIG. 2
an enlarged view of the feed pump of Figure 1 in the region of delivery chambers.

Figur 1 zeigt einen Längsschnitt durch eine von einem Elektromotor 1 angetriebene, als axial durchströmte Seitenkanalpumpe ausgebildete Förderpumpe 2, welche beispielsweise zum Fördern von Kraftstoff aus einem nicht dargestellten Kraftstoffbehälter eines Kraftfahrzeuges vorgesehen sein kann. Die Förderpumpe 2 hat ein Pumpengehäuse 3, in welchem ein drehfest auf einer Welle 4 des Elektromotors 1 befestigtes Laufrad 5 angeordnet ist. Das Pumpengehäuse 3 hat an seiner dem Elektromotor 1 abgewandten Seite einen Einlaßkanal 6 und auf der dem Elektromotor 1 zugewandten Seite einen Auslaßkanal 7. Der Einlaßkanal 6 mündet in eine Förderkammer 8. Eine zweite Förderkammer 9 mündet in den Auslaßkanal 7. Die Förderkammern 8, 9 weisen jeweils in dem Pumpengehäuse 3 eingearbeitete, teilringförmige Kanäle 10, 11 und in dem Laufrad 5 angeordnete Schaufelkammern 12, 13 auf. Die Schaufelkammern 12, 13 werden jeweils von Leitschaufeln 14, 15 begrenzt und weisen jeweils einen Einströmbereich 16, 17 zum Einströmen des zu fördernden Mediums und einen Ausströmbereich 18, 19 auf. Zwischen dem Einströmbereich 16, 17 und dem Ausströmbereich 18, 19 sind einander gegenüberliegende Schaufelkammern 12, 13 miteinander verbunden. Bei einer Drehung des Laufrades 5 entstehen in den Förderkammern 8, 9 jeweils Zirkulationsströmungen. Von der Zirkulationsströmung der einlaßseitigen Förderkammer 8 wird ein Teilstrom abgezweigt und strömt in die auslaßseitige Förderkammer 9 über. In der Zeichnung sind die Strömungen mit Pfeilen gekennzeichnet.Figure 1 shows a longitudinal section through a driven by an electric motor 1, designed as an axially flow-through side channel pump feed pump 2, which may be provided for example for conveying fuel from a fuel tank of a motor vehicle, not shown. The feed pump 2 has a pump housing 3, in which a rotatably mounted on a shaft 4 of the electric motor 1 fixed impeller 5 is arranged. The pump housing 3 has on its side facing away from the electric motor 1 an inlet channel 6 and on the side facing the electric motor 1 an outlet 7. The inlet channel 6 opens into a delivery chamber 8. A second delivery chamber 9 opens into the outlet 7. The delivery chambers 8, 9th each have in the pump housing 3 incorporated, part-annular channels 10, 11 and arranged in the impeller 5 blade chambers 12, 13. The blade chambers 12, 13 are each delimited by guide vanes 14, 15 and each have an inflow region 16, 17 for the inflow of the medium to be conveyed and an outflow area 18, 19. Between the inflow region 16, 17 and the outflow region 18, 19, mutually opposed blade chambers 12, 13 are connected to one another. Upon rotation of the impeller 5 arise in the delivery chambers 8, 9 respectively circulation flows. From the circulation flow of the inlet-side delivery chamber 8, a partial flow is branched off and flows into the outlet-side delivery chamber 9 via. In the drawing, the flows are marked with arrows.

Figur 2 zeigt stark vergrößert die Förderpumpe 2 aus Figur 1 im Bereich der Förderkammern 8, 9. Hierbei ist zu erkennen, daß die Schaufelkammern 12, 13 jeweils zu einer senkrecht zu einer Stirnseite verlaufenden Mittellinie symmetrisch gestaltet sind. Die Schaufelkammern 12, 13 weisen in den Einströmbereichen 16, 17 und in den Ausströmbereichen 18, 19 jeweils eine von Radien R gebildete Kontur auf. Die Radien R haben hierbei einen von der jeweiligen Kontur aus gesehen hinter der Mittellinie angeordneten Ursprung. Die Ursprünge der Radien R befinden sich zudem in einer gemeinsamen parallel zu der Stirnseite des Laufrades 5 angeordneten Ebene. Zur Verdeutlichung sind die Ebenen der Schaufelkammern 12, 13 in der Zeichnung strichpunktiert dargestellt. Hierdurch gelangt die Zirkulationsströmung mit besonders geringen Verwirbelungen von den teilringförmigen Kanälen 10, 11 in die Schaufelkammern 12, 13. Die Ebene der Ursprünge der Radien R hat ungefähr denselben Abstand von der Stirnseite des Laufrades 5 wie die Ursprünge der Radien R von der Mittellinie.Figure 2 shows greatly enlarged the feed pump 2 of Figure 1 in the region of the delivery chambers 8, 9. Here it can be seen that the blade chambers 12, 13 are each designed symmetrically to a perpendicular to an end face extending center line. The vane chambers 12, 13 each have a contour formed by radii R in the inflow regions 16, 17 and in the outflow regions 18, 19. The radii R in this case have seen from the respective contour from behind the center line origin. The origins of the radii R are also located in a common plane parallel to the end face of the impeller 5 level. For clarity, the planes of the blade chambers 12, 13 are shown in phantom in the drawing. As a result, the circulation flow passes with particularly small turbulences from the part-annular channels 10, 11 in the blade chambers 12, 13. The plane of the origins of the radii R has approximately the same distance from the end face of the impeller 5 as the origins of the radii R from the center line.

Claims (5)

  1. Feed chamber (2) having a driven impeller (5) which rotates in a pump housing (3) and which has guide vanes (14, 15) in its end sides which delimit at least one ring of vane chambers (12, 13) in which the vane chambers (12,13) have an inflow region (16, 17) and an outflow region (18, 19) for the medium to be fed, and having at least one partially annular channel (10, 11) arranged in the pump housing (3) in the region of the guide vanes (14, 15), which partially annular channel (10, 11) forms, together with the vane chambers (12, 13), a supply channel (8, 9) from an inlet channel (6) to an outlet channel (7), the contour of the vane chambers (12, 13) being formed from at least one radius (R) having an origin within the feed chamber (8, 9), characterized in that the origin of the radii (R), as seen from the contour, which is defined by the radius (R), of the vane chamber (12, 13), is arranged in the region situated opposite a vane chamber (12, 13) centre line which runs perpendicular to the end side of the impeller (5), and in that the origins of several radii (R) for mutually opposite contours of the vane chambers (12, 13) are arranged within an impeller (5) on a common plane which runs parallel to the end side of the impeller (5).
  2. Feed chamber according to Claim 1, characterized in that the vane chambers (12, 13) have, in their regions which adjoin the guide vanes (14, 15), delimitations which extend perpendicularly with respect to the end side of the impeller (5) from the plane which runs parallel to the end side of the impeller (5) to the end side.
  3. Feed chamber according to at least one of the preceding claims, characterized in that the origins of two radii (R) which each generate contours which are opposite one another are arranged symmetrically about the centre line of the vane chamber (12, 13).
  4. Feed chamber according to at least one of the preceding claims, characterized in that the distance of the origins of the radii (R) from the centre line has approximately the same magnitude as their distance from the end side.
  5. Feed chamber according to at least one of the preceding claims, characterized in that vane chambers (12, 13) which are arranged symmetrically opposite one another in both ends of the impeller (5) are connected to one another exclusively in the region of the centre line.
EP00969250A 1999-09-10 2000-08-26 Side channel pump Expired - Lifetime EP1131560B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19943261A DE19943261A1 (en) 1999-09-10 1999-09-10 Feed pump
DE19943261 1999-09-10
PCT/EP2000/008334 WO2001020169A1 (en) 1999-09-10 2000-08-26 Side channel pump

Publications (2)

Publication Number Publication Date
EP1131560A1 EP1131560A1 (en) 2001-09-12
EP1131560B1 true EP1131560B1 (en) 2006-03-22

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EP00969250A Expired - Lifetime EP1131560B1 (en) 1999-09-10 2000-08-26 Side channel pump

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US (1) US6481958B1 (en)
EP (1) EP1131560B1 (en)
JP (1) JP4608165B2 (en)
KR (1) KR100763055B1 (en)
CN (1) CN1294360C (en)
AT (1) ATE321209T1 (en)
AU (1) AU7903700A (en)
BR (1) BR0007089B1 (en)
DE (2) DE19943261A1 (en)
ES (1) ES2256046T3 (en)
WO (1) WO2001020169A1 (en)

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DE10143809C1 (en) 2001-09-06 2002-10-17 Siemens Ag Side channel feed pump e.g. automobile fuel pump, has tangential transitions between different sections of partial annular channel enclosing paddle chambers of pump wheel
US7037066B2 (en) 2002-06-18 2006-05-02 Ti Group Automotive Systems, L.L.C. Turbine fuel pump impeller
US6932562B2 (en) * 2002-06-18 2005-08-23 Ti Group Automotive Systems, L.L.C. Single stage, dual channel turbine fuel pump
KR100568547B1 (en) * 2003-07-28 2006-04-07 현담산업 주식회사 Turbine-type Fuel Pump For Automobile Having An Improved Shape of Impeller
JP2005226496A (en) * 2004-02-10 2005-08-25 Mitsubishi Electric Corp Circumferential flow pump
US9249806B2 (en) 2011-02-04 2016-02-02 Ti Group Automotive Systems, L.L.C. Impeller and fluid pump
DE102017215731A1 (en) * 2017-09-07 2019-03-07 Robert Bosch Gmbh Side channel compressor for a fuel cell system for conveying and / or compressing a gaseous medium

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Publication number Priority date Publication date Assignee Title
DE4020521A1 (en) * 1990-06-28 1992-01-02 Bosch Gmbh Robert PERIPHERAL PUMP, ESPECIALLY FOR DELIVERING FUEL FROM A STORAGE TANK TO THE INTERNAL COMBUSTION ENGINE OF A MOTOR VEHICLE
DE19615322A1 (en) * 1996-04-18 1997-10-23 Vdo Schindling Peripheral pump
DE19749404C1 (en) * 1997-11-07 1999-05-06 Mannesmann Vdo Ag Feed pump for motor vehicle fuel tank
US5921746A (en) * 1998-10-14 1999-07-13 Ford Motor Company Fuel pump chamber with contamination control

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CN1321224A (en) 2001-11-07
EP1131560A1 (en) 2001-09-12
DE19943261A1 (en) 2001-03-15
WO2001020169A1 (en) 2001-03-22
DE50012450D1 (en) 2006-05-11
ES2256046T3 (en) 2006-07-16
US6481958B1 (en) 2002-11-19
ATE321209T1 (en) 2006-04-15
KR100763055B1 (en) 2007-10-02
KR20010080987A (en) 2001-08-25
CN1294360C (en) 2007-01-10
JP2003509625A (en) 2003-03-11
BR0007089A (en) 2001-08-07
JP4608165B2 (en) 2011-01-05
AU7903700A (en) 2001-04-17
BR0007089B1 (en) 2009-01-13

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