EP1192358B1 - Feed pump - Google Patents

Feed pump Download PDF

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Publication number
EP1192358B1
EP1192358B1 EP01915233A EP01915233A EP1192358B1 EP 1192358 B1 EP1192358 B1 EP 1192358B1 EP 01915233 A EP01915233 A EP 01915233A EP 01915233 A EP01915233 A EP 01915233A EP 1192358 B1 EP1192358 B1 EP 1192358B1
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EP
European Patent Office
Prior art keywords
impeller
angle
feed pump
moving blades
rotation
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Expired - Lifetime
Application number
EP01915233A
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German (de)
French (fr)
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EP1192358A1 (en
Inventor
Peter Marx
Hans-Peter Osburg
Peter Schuchardt
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Siemens AG
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Siemens AG
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Publication of EP1192358A1 publication Critical patent/EP1192358A1/en
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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
    • F04D5/00—Pumps with circumferential or transverse flow
    • 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
    • F04D5/003—Regenerative pumps of multistage type
    • F04D5/005—Regenerative pumps of multistage type the stages being radially offset
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y10S415/915—Pump or portion thereof by casting or molding

Definitions

  • the invention relates to a feed pump with a driven, impeller rotating in a pump housing with several arranged on one end of the impeller, concentric enclosing wreaths of vane chambers, with the Wreaths of the vane chambers in the wall of the pump housing oppositely arranged conveyor channels and with the Blade chambers delimiting tangentially to the impeller, inclined at an angle with respect to the axis of rotation of the impeller arranged blades.
  • Such delivery pumps are often used to deliver fuel or washing liquid used in today's motor vehicles and are practical as peripheral or side channel pumps known.
  • the impeller is usually non-rotatable on one fixed by an electric motor driven shaft. At a Rotation of the impeller occurs in the blade chambers and the delivery channel circulation flows through which the Fuel or the washing liquid from an inlet duct is promoted to an outlet channel.
  • Feed pump By concentrating each other enclosing wreaths of the vane chambers can Feed pump, for example, have several pressure levels or supply different consumers independently.
  • the impeller is manufactured using the appropriate impeller Tool forms mostly in the injection molding or injection molding process. Due to the inclined arrangement of the blades the feed pump has a very high efficiency.
  • a pump with a ring of blades on each face the impeller is known from US 2,042,499.
  • the Blades are with their side facing in the direction of rotation formed at an angle to a parallel to the axis of rotation, where the angle is over the parallel of the axis of rotation the radial extension of the blades is constant.
  • a pump with a ring of Blades are known on each end face of the impeller, wherein the blades at their base in axial extension are arranged parallel to the axis of rotation.
  • the article "Influence of the blade shape on the characteristic behavior of peripheral side channel pumps” in mechanical engineering 21 (1972) discloses an impeller of a peripheral pump a ring of vane chambers on each face.
  • the The blades of the impeller have their radial extension two areas with different angles with respect a parallel of the axis of rotation. In the radially inner area the blades are arranged parallel to the axis of rotation. in the radially outer area are the blades at an angle formed to a parallel of the axis of rotation, the angle is constant over the radial extent.
  • the invention is based on the problem of a feed pump of the type mentioned at the outset in such a way that they high efficiency can be produced particularly cost-effectively is.
  • the impeller can be used to create multiple rings Blade chambers used a common mold part become. By using a single mold part you can use the impeller without considering relative movements removed from the mold. This allows the inventive Feed pump with a high degree of efficiency particularly inexpensive finished. Damage to the blades from an incorrectly guided relative movement also becomes reliable avoided. Furthermore, this design of the impeller to a small number of mold parts in production. In the best case, the impeller can be used as a whole generate two opposing mold parts. This leads to a particularly cost-effective use of tools in the manufacture of the impeller.
  • a particularly high efficiency of the feed pump according to the invention can be easily generated with a simple demoldability of the impeller if the angle of the rotor blades according to the formula runs, where r is an arbitrary distance of an intended point of the blades from the center of the impeller and ⁇ (r a ) is a predetermined angle.
  • This design makes it easy to determine the proportionality of the change in angle with increasing distance from the center of the impeller. Since the size relationships given in the formula have a decisive influence on the circulating flow, flow losses are kept particularly low.
  • the flows in the delivery channel are adapted to those in the vane chambers.
  • flow losses within the delivery channel or the vane chambers can be kept particularly low if the rotor blades have an angle ⁇ (r) of 10 ° to 50 °.
  • the range of the angle ⁇ (r) can be in the intended distance between the corresponding rings of the rotor blades from the center of the impeller simply by selection of the presettable angle ⁇ (r a) set.
  • Feed pump helps when the vane chambers do that Penetrate the impeller and on the end faces of the impeller in each case have a moving blade and that the moving blades too the end faces in the intended direction of rotation of the impeller are oriented. As a result, the feed pump are flowed through axially and therefore very much in the radial direction be compact.
  • FIG. 1 shows a sectional view through a side channel pump trained feed pump.
  • the feed pump has a fixed on a shaft 1, between two fixed Housing parts 2, 3 rotatable impeller 4.
  • the Delivery pump has two concentrically surrounding delivery chambers 5, 6.
  • the delivery chambers 5, 6 each extend from an inlet duct 7, 8 to an outlet duct 9, 10 and are each arranged in the housing parts 2, 3 Delivery channels 11, 12 and arranged in the impeller 4 and blade chambers delimited by rotor blades 13, 14 15, 16 together.
  • the blade chambers 15, 16 are each arranged as a depression in one of the end faces. Opposing vane chambers 15, 16 are one below the other connected.
  • Figure 2 shows a sectional view through the feed pump from Figure 1 along the line II - II a plan view on one of the end faces of the impeller 4.
  • Figure 3 shows the blade chambers 15, 16 delimiting blades 13, 14, 14 ', 14' ', 14' ''.
  • FIG. 3 shows a sectional view through the impeller 4 from FIG. 2, by way of example, a plurality of moving blades 14 ′, 14 ′′, 14 '' '13 with angles ⁇ 1 - ⁇ 4, with which their the intended Direction of rotation of the impeller 4 side facing the vertical and thus to a parallel of the axis of rotation of the impeller 4 is inclined.
  • the angle ⁇ 1 of Blade 13 of the inner ring of that shown in Figure 2 Blade chambers 15 is smaller than the angle ⁇ 2 - ⁇ 4 of the blades 14 ', 14' ', 14' '' of the outer ring of the Blade chambers 16.
  • angles ⁇ 2 - ⁇ 4 are dependent from the distance of the intersection of the blade 14 ', 14 '', 14 '' 'from the axis of rotation of the impeller 4.
  • the inclination the blade 14 ', 14 ", 14"' to a parallel of the The axis of rotation of the impeller 4 increases with increasing distance from the axis of rotation of the impeller 4.
  • the angle ⁇ 4 is thus larger than the angle ⁇ 2.
  • the intended direction of rotation the side facing away from the impeller 4 has an angle ⁇ .
  • This Angle ⁇ is slightly larger than the angle ⁇ Direction of rotation of the impeller 4 side.
  • exemplary the angle ⁇ 3 is shown to be slightly larger is said to be the angle ⁇ 3. This contributes to easy demoldability the impeller 4 made by injection molding the tool shape, not shown.
  • the angle ⁇ (r) increases with increasing distance r from the axis of rotation. However, the increase in the angle ⁇ (r) decreases with increasing distance r from the axis of rotation of the impeller 4.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Injection Moulding Of Plastics Or The Like (AREA)

Description

Die Erfindung betrifft eine Förderpumpe mit einem angetriebenen, sich in einem Pumpengehäuse drehenden Laufrad mit mehreren an einer Stirnseite des Laufrades angeordneten, sich konzentrisch umschließenden Kränzen von Schaufelkammern, mit den Kränzen der Schaufelkammern in der Wandung des Pumpengehäuses gegenüberliegend angeordneten Förderkanälen und mit die Schaufelkammern jeweils tangential zum Laufrad begrenzenden, im Bezug zur Drehachse des Laufrades um einen Winkel geneigt angeordneten Laufschaufeln.The invention relates to a feed pump with a driven, impeller rotating in a pump housing with several arranged on one end of the impeller, concentric enclosing wreaths of vane chambers, with the Wreaths of the vane chambers in the wall of the pump housing oppositely arranged conveyor channels and with the Blade chambers delimiting tangentially to the impeller, inclined at an angle with respect to the axis of rotation of the impeller arranged blades.

Solche Förderpumpen werden häufig zum Fördern von Kraftstoff oder Waschflüssigkeit in heutigen Kraftfahrzeugen eingesetzt und sind als Peripheral- oder Seitenkanalpumpen aus der Praxis bekannt. Das Laufrad ist in der Regel drehfest auf einer von einem Elektromotor angetriebenen Welle befestigt. Bei einer Drehung des Laufrades entstehen in den Schaufelkammern und dem Förderkanal Zirkulationsströmungen, durch die der Kraftstoff oder die Waschflüssigkeit von einem Einlasskanal zu einem Auslasskanal gefördert wird. Durch die einander konzentrisch umschließenden Kränze der Schaufelkammern kann die Förderpumpe beispielsweise mehrere Druckstufen aufweisen oder verschiedene Verbraucher unabhängig voneinander versorgen. Die Fertigung des Laufrades erfolgt mit dem Laufrad entsprechenden Werkzeugformen meist im Spritzguss- oder Spritzprägeverfahren. Durch die geneigte Anordnung der Laufschaufeln hat die Förderpumpe einen sehr hohen Wirkungsgrad.Such delivery pumps are often used to deliver fuel or washing liquid used in today's motor vehicles and are practical as peripheral or side channel pumps known. The impeller is usually non-rotatable on one fixed by an electric motor driven shaft. At a Rotation of the impeller occurs in the blade chambers and the delivery channel circulation flows through which the Fuel or the washing liquid from an inlet duct is promoted to an outlet channel. By concentrating each other enclosing wreaths of the vane chambers can Feed pump, for example, have several pressure levels or supply different consumers independently. The impeller is manufactured using the appropriate impeller Tool forms mostly in the injection molding or injection molding process. Due to the inclined arrangement of the blades the feed pump has a very high efficiency.

Nachteilig bei der bekannten Förderpumpe ist jedoch, dass ihre Fertigung sehr kostenintensiv ist. Beispielsweise erfordern die Kränze der Schaufelkammern jeweils eine aufwendige Werkzeugform. Bei der Entformung des Laufrades aus den Werkzeugformen sind diese in vorgesehenen Relativbewegungen zueinander zu bewegen. Um eine Beschädigung der Laufschaufeln zu vermeiden, müssen diese Relativbewegungen zudem sehr exakt durchgeführt werden.A disadvantage of the known feed pump, however, is that Manufacturing is very expensive. For example, require the wreaths of the vane chambers each an elaborate Mold. When the impeller is removed from the mold these are in intended relative movements to each other to move. To damage the blades To avoid, these relative movements must also be very precise be performed.

Eine Pumpe mit einem Kranz von Laufschaufeln an jeder Stirnseite des Laufrades ist aus der US 2,042,499 bekannt. Die Laufschaufeln sind mit ihrer in Drehrichtung zugewandten Seite in einem Winkel zu einer Parallelen der Drehachse ausgebildet, wobei der Winkel zu der Parallelen der Drehachse über die radiale Erstreckung der Laufschaufeln konstant ist.A pump with a ring of blades on each face the impeller is known from US 2,042,499. The Blades are with their side facing in the direction of rotation formed at an angle to a parallel to the axis of rotation, where the angle is over the parallel of the axis of rotation the radial extension of the blades is constant.

Durch die US 1,973,669 ist eine Pumpe mit einem Kranz von Laufschaufeln an jeder Stirnseite des Laufrades bekannt, wobei die Laufschaufeln an ihrem Fußpunkt in axialer Erstreckung parallel zur Drehachse angeordnet sind.A pump with a ring of Blades are known on each end face of the impeller, wherein the blades at their base in axial extension are arranged parallel to the axis of rotation.

Der Artikel "Einfluss der Schaufelform auf das Kennlinienverhalten von Peripheral-Seitenkanalpumpen" in Maschinenbautechnik 21 (1972) offenbart ein Laufrad einer Peripheralpumpe mit einem Kranz von Schaufelkammern an jeder Stirnseite. Die Laufschaufeln des Laufrades besitzen über ihre radiale Erstreckung zwei Bereiche mit verschiedenen Winkeln bezüglich einer Parallelen der Drehachse. Im radial inneren Bereich sind die Laufschaufeln parallel zur Drehachse angeordnet. Im radial äußeren Bereich sind die Laufschaufeln in einem Winkel zu einer Parallelen der Drehachse ausgebildet, wobei der Winkel über die radiale Erstreckung konstant ist.The article "Influence of the blade shape on the characteristic behavior of peripheral side channel pumps "in mechanical engineering 21 (1972) discloses an impeller of a peripheral pump a ring of vane chambers on each face. The The blades of the impeller have their radial extension two areas with different angles with respect a parallel of the axis of rotation. In the radially inner area the blades are arranged parallel to the axis of rotation. in the radially outer area are the blades at an angle formed to a parallel of the axis of rotation, the angle is constant over the radial extent.

Der Erfindung liegt das Problem zugrunde, eine Förderpumpe der eingangs genannten Art so zu gestalten, dass sie bei einem hohen Wirkungsgrad besonders kostengünstig herstellbar ist.The invention is based on the problem of a feed pump of the type mentioned at the outset in such a way that they high efficiency can be produced particularly cost-effectively is.

Dieses Problem wird erfindungsgemäß dadurch gelöst, dass der Winkel der Laufschaufeln zu einer Parallelen der Drehachse des Laufrades in der radialen Erstreckung der Laufschaufeln mit zunehmendem Abstand von dem Mittelpunkt des Laufrades proportional ansteigend verläuft und dass die Winkel mehrerer, auf einer der Stirnseiten angeordneter Kränze der Laufschaufeln dieselbe proportionale Abhängigkeit aufweisen.This problem is solved according to the invention in that the Angle of the blades to a parallel of the axis of rotation of the impeller in the radial extension of the blades with increasing distance from the center of the impeller proportionally increasing and that the angles of several, on one of the end faces arranged wreaths of the rotor blades have the same proportional dependency.

Durch eine geeignete Wahl der Proportionalität des Verlaufes des Winkels von dem Abstand der Laufschaufeln zum Mittelpunkt des Laufrades kann zur Erzeugung von mehreren Kränzen der Schaufelkammern ein gemeinsames Werkzeugformteil eingesetzt werden. Durch die Verwendung eines einzigen Werkzeugformteiles kann man das Laufrad ohne Berücksichtigung von Relativbewegungen entformen. Hierdurch lässt sich die erfindungsgemäße Förderpumpe bei einem hohen Wirkungsgrad besonders kostengünstig fertigen. Eine Beschädigung der Laufschaufeln durch eine fehlerhaft geführte Relativbewegung wird zudem zuverlässig vermieden. Weiterhin führt diese Gestaltung des Laufrades zu einer geringen Anzahl von Werkzeugformteilen in der Fertigung. Im günstigsten Fall lässt sich das Laufrad mit insgesamt zwei einander gegenüberstehenden Werkzeugformteilen erzeugen. Dies führt zu einem besonders kostengünstigen Werkzeugeinsatz bei der Fertigung des Laufrades.Through a suitable choice of the proportionality of the course of the angle from the distance of the blades to the center The impeller can be used to create multiple rings Blade chambers used a common mold part become. By using a single mold part you can use the impeller without considering relative movements removed from the mold. This allows the inventive Feed pump with a high degree of efficiency particularly inexpensive finished. Damage to the blades from an incorrectly guided relative movement also becomes reliable avoided. Furthermore, this design of the impeller to a small number of mold parts in production. In the best case, the impeller can be used as a whole generate two opposing mold parts. This leads to a particularly cost-effective use of tools in the manufacture of the impeller.

Ein besonders hoher Wirkungsgrad der erfindungsgemäßen Förderpumpe lässt sich bei einer einfachen Entformbarkeit des Laufrades einfach erzeugen, wenn der Winkel der Laufschaufeln gemäß der Formel

Figure 00030001
verläuft, wobei r ein beliebiger Abstand eines vorgesehenen Punktes der Laufschaufeln von dem Mittelpunkt des Laufrades ist und α(ra) ein vorgegebener Winkel ist. Durch diese Gestaltung lässt sich die Proportionalität der Winkeländerung mit zunehmendem Abstand von dem Mittelpunkt des Laufrades einfach festlegen. Da die durch die in der Formel gegebenen Größenverhältnisse einen entscheidenden Einfluss auf die sich ausbildende Zirkulationsströmung haben, werden Strömungsverluste besonders gering gehalten. Die Strömungen in dem Förderkanal werden denen in den Schaufelkammern angepasst.A particularly high efficiency of the feed pump according to the invention can be easily generated with a simple demoldability of the impeller if the angle of the rotor blades according to the formula
Figure 00030001
runs, where r is an arbitrary distance of an intended point of the blades from the center of the impeller and α (r a ) is a predetermined angle. This design makes it easy to determine the proportionality of the change in angle with increasing distance from the center of the impeller. Since the size relationships given in the formula have a decisive influence on the circulating flow, flow losses are kept particularly low. The flows in the delivery channel are adapted to those in the vane chambers.

Zur weiteren Vereinfachung der Entformung des Laufrades trägt es gemäß einer anderen vorteilhaften Weiterbildung der Erfindung bei, wenn der Winkel β der Laufschaufeln an dem Abstand r an ihrer in der vorgesehenen Drehrichtung des Laufrades abgewandten Seite geringfügig größer ist als der Winkel α(r). Durch diese Gestaltung verdicken sich die Laufschaufeln mit zunehmendem Abstand von ihrer nächsten Stirnseite geringfügig. Das zur Fertigung der Schaufelkammern vorgesehene Werkzeugformteil kann daher sich verjüngende Vorsprünge zur Erzeugung der Schaufelkammern aufweisen, so dass sich das Laufrad nach dem Lösen aus dem Werkzeugformteil einfach entnehmen lässt.To further simplify the demoulding of the impeller it according to another advantageous development of the invention at when the angle β of the blades at the distance r on their in the intended direction of rotation of the impeller Side is slightly larger than the angle α (r). With this design, the blades also thicken increasing distance from their next face slightly. The mold part intended for the manufacture of the blade chambers can therefore produce tapered projections of the blade chambers, so that the impeller simply remove from the mold after loosening leaves.

Strömungsverluste innerhalb des Förderkanals oder der Schaufelkammern lassen sich gemäß einer anderen vorteilhaften Weiterbildung der Erfindung besonders gering halten, wenn die Laufschaufeln einen Winkel α(r) von 10° bis 50° aufweisen. Der Bereich des Winkels α(r) lässt sich bei vorgesehenem Abstand der entsprechenden Kränze der Laufschaufeln von dem Mittelpunkt des Laufrades einfach durch eine Auswahl des vorzugebenden Winkels α(ra) festlegen. According to another advantageous development of the invention, flow losses within the delivery channel or the vane chambers can be kept particularly low if the rotor blades have an angle α (r) of 10 ° to 50 °. The range of the angle α (r) can be in the intended distance between the corresponding rings of the rotor blades from the center of the impeller simply by selection of the presettable angle α (r a) set.

Zur weiteren Verringerung der Strömungsverluste in dem Förderkanal oder den Schaufelkammern trägt es gemäß einer anderen vorteilhaften Weiterbildung der Erfindung bei, wenn der Winkel α(r) zwischen 15° und 38° liegt.To further reduce the flow losses in the delivery channel or it carries the bucket chambers according to another advantageous development of the invention when the Angle α (r) is between 15 ° and 38 °.

Zur weiteren Erhöhung des Wirkungsgrades der erfindungsgemäßen Förderpumpe trägt es bei, wenn die Schaufelkammern das Laufrad durchdringen und an den Stirnseiten des Laufrades jeweils eine Laufschaufel haben und dass die Laufschaufeln zu den Stirnseiten in der vorgesehenen Drehrichtung des Laufrades weisend ausgerichtet sind. Hierdurch kann die Förderpumpe axial durchströmt werden und daher in radialer Richtung sehr kompakt aufgebaut sein.To further increase the efficiency of the invention Feed pump helps when the vane chambers do that Penetrate the impeller and on the end faces of the impeller in each case have a moving blade and that the moving blades too the end faces in the intended direction of rotation of the impeller are oriented. As a result, the feed pump are flowed through axially and therefore very much in the radial direction be compact.

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 Schnittdarstellung durch die Förderpumpe aus Figur 1 entlang der Linie II - II,
Figur 3
eine vergrößerte Schnittdarstellung durch ein Laufrad aus Figur 2 entlang der Linie III - III,
Figur 4
ein Diagramm über die Abhängigkeit eines Winkels von Laufschaufeln in Abhängigkeit von dem Abstand von dem Mittelpunkt des Laufrades der Förderpumpe aus Figur 1.
The invention permits numerous embodiments. To further clarify its basic principle, one of these is shown in the drawing and is described below. This shows in
Figure 1
2 shows a sectional view through a feed pump according to the invention,
Figure 2
2 shows a sectional view through the feed pump from FIG. 1 along the line II-II,
Figure 3
3 shows an enlarged sectional view through an impeller from FIG. 2 along the line III-III,
Figure 4
1 shows a diagram of the dependency of an angle of rotor blades as a function of the distance from the center point of the impeller of the feed pump from FIG. 1.

Figur 1 zeigt eine Schnittdarstellung durch eine als Seitenkanalpumpe ausgebildete Förderpumpe. Die Förderpumpe weist ein auf einer Welle 1 befestigtes, sich zwischen zwei feststehenden Gehäuseteilen 2, 3 drehbares Laufrad 4 auf. Die Förderpumpe hat zwei sich konzentrisch umschließende Förderkammern 5, 6. Die Förderkammern 5, 6 erstrecken sich jeweils von einem Einlasskanal 7, 8 bis zu einem Auslasskanal 9, 10 und setzen sich jeweils in aus in den Gehäuseteilen 2, 3 angeordneten Förderkanälen 11, 12 und aus in dem Laufrad 4 angeordneten und von Laufschaufeln 13, 14 begrenzten Schaufelkammern 15, 16 zusammen. Die Schaufelkammern 15, 16 sind jeweils als Vertiefung in einer der Stirnseiten angeordnet. Einander gegenüberstehende Schaufelkammern 15, 16 sind untereinander verbunden. Bei einer Drehung des Laufrades 4 entstehen in den Förderkammern 5, 6 von den Einlasskanälen 7, 8 zu den Auslasskanälen 9, 10 führende Zirkulationsströmungen.Figure 1 shows a sectional view through a side channel pump trained feed pump. The feed pump has a fixed on a shaft 1, between two fixed Housing parts 2, 3 rotatable impeller 4. The Delivery pump has two concentrically surrounding delivery chambers 5, 6. The delivery chambers 5, 6 each extend from an inlet duct 7, 8 to an outlet duct 9, 10 and are each arranged in the housing parts 2, 3 Delivery channels 11, 12 and arranged in the impeller 4 and blade chambers delimited by rotor blades 13, 14 15, 16 together. The blade chambers 15, 16 are each arranged as a depression in one of the end faces. Opposing vane chambers 15, 16 are one below the other connected. When the impeller 4 rotates in the delivery chambers 5, 6 from the inlet channels 7, 8 to the outlet channels 9, 10 leading circulation flows.

Figur 2 zeigt in einer Schnittdarstellung durch die Förderpumpe aus Figur 1 entlang der Linie II - II eine Draufsicht auf eine der Stirnseiten des Laufrades 4. Hierbei ist zu erkennen, dass insgesamt zwei Kränze der Schaufelkammern 15, 16 in dem Laufrad 4 angeordnet sind. Die Kränze der Schaufelkammern 15, 16 umschließen sich konzentrisch. Weiterhin sind in Figur 3 die die Schaufelkammern 15, 16 begrenzenden Laufschaufeln 13, 14, 14', 14'', 14''' zu erkennen.Figure 2 shows a sectional view through the feed pump from Figure 1 along the line II - II a plan view on one of the end faces of the impeller 4. Here you can see that a total of two rings of the blade chambers 15, 16 are arranged in the impeller 4. The wreaths of the vane chambers 15, 16 surround each other concentrically. Furthermore, in Figure 3 shows the blade chambers 15, 16 delimiting blades 13, 14, 14 ', 14' ', 14' ''.

Figur 3 zeigt in einer Schnittdarstellung durch das Laufrad 4 aus Figur 2 beispielhaft mehrere Laufschaufeln 14', 14'', 14''' 13 mit Winkeln α1 - α4, mit denen ihre der vorgesehenen Drehrichtung des Laufrades 4 zugewandte Seite zur Senkrechten und damit zu einer Parallelen der Drehachse des Laufrades 4 geneigt ist. Hierbei ist zu erkennen, dass der Winkel α1 der Laufschaufel 13 des inneren Kranzes der in Figur 2 dargestellten Schaufelkammern 15 kleiner ist als die Winkel α2 - α4 der Laufschaufeln 14', 14'', 14''' des äußeren Kranzes der Schaufelkammern 16. Weiterhin sind die Winkel α2 - α4 abhängig von dem Abstand des Schnittpunktes der Laufschaufel 14', 14'', 14''' von der Drehachse des Laufrades 4. Die Neigung der Laufschaufel 14', 14", 14''' zu einer Parallelen der Drehachse des Laufrades 4 steigt mit zunehmendem Abstand von der Drehachse des Laufrades 4 an. Der Winkel α4 ist damit größer als der Winkel α2. Die der vorgesehenen Drehrichtung des Laufrades 4 abgewandte Seite hat einen Winkel β. Dieser Winkel β ist geringfügig größer als der Winkel α der der Drehrichtung des Laufrades 4 zugewandten Seite. Beispielhaft ist der Winkel β3 dargestellt, der geringfügig größer sein soll als der Winkel α3. Dies trägt zur einfachen Entformbarkeit des im Spritzgussverfahren gefertigten Laufrades 4 aus der nicht dargestellten Werkzeugform bei.FIG. 3 shows a sectional view through the impeller 4 from FIG. 2, by way of example, a plurality of moving blades 14 ′, 14 ″, 14 '' '13 with angles α1 - α4, with which their the intended Direction of rotation of the impeller 4 side facing the vertical and thus to a parallel of the axis of rotation of the impeller 4 is inclined. It can be seen here that the angle α1 of Blade 13 of the inner ring of that shown in Figure 2 Blade chambers 15 is smaller than the angle α2 - α4 of the blades 14 ', 14' ', 14' '' of the outer ring of the Blade chambers 16. Furthermore, the angles α2 - α4 are dependent from the distance of the intersection of the blade 14 ', 14 '', 14 '' 'from the axis of rotation of the impeller 4. The inclination the blade 14 ', 14 ", 14"' to a parallel of the The axis of rotation of the impeller 4 increases with increasing distance from the axis of rotation of the impeller 4. The angle α4 is thus larger than the angle α2. The intended direction of rotation the side facing away from the impeller 4 has an angle β. This Angle β is slightly larger than the angle α Direction of rotation of the impeller 4 side. exemplary the angle β3 is shown to be slightly larger is said to be the angle α3. This contributes to easy demoldability the impeller 4 made by injection molding the tool shape, not shown.

Figur 4 zeigt ein Diagramm des Schaufelwinkels α(r) mit r = 1, 2, 3... über den Abstand des Schnittpunktes der Laufschaufeln 13, 14 von der Drehachse des Laufrades 4. der Winkel α(r) der Laufschaufeln zur Senkrechten verhält sich nach der Beziehung

Figure 00070001
Bei einem an der Stelle ra = 10 mm vorgegebenen Winkel α(ra) = 22° ergibt sich für den Winkelverlauf der in den Figuren 1 bis 3 dargestellten Laufschaufeln 13, 14 eine Kurve. Mit zunehmendem Abstand r von der Drehachse steigt der Winkel α(r) an. Die Vergrößerung des Winkels α(r) verringert sich jedoch mit größer werdendem Abstand r von der Drehachse des Laufrades 4.Figure 4 shows a diagram of the blade angle α (r) with r = 1, 2, 3 ... over the distance of the intersection of the blades 13, 14 from the axis of rotation of the impeller 4. the angle α (r) of the blades relates to the vertical yourself after the relationship
Figure 00070001
With an angle α (ra) = 22 ° predetermined at the point ra = 10 mm, a curve results for the angular profile of the rotor blades 13, 14 shown in FIGS. 1 to 3. The angle α (r) increases with increasing distance r from the axis of rotation. However, the increase in the angle α (r) decreases with increasing distance r from the axis of rotation of the impeller 4.

Claims (6)

  1. Feed pump with a driven impeller (4) rotating in a pump casing (2, 3) and having a plurality of rings of blade chambers (15, 16), the said rings being arranged on one end face of the impeller (4) and concentrically surrounding one another, with feed channels (11, 12) arranged opposite the rings of blade chambers (15, 16) in the wall of the pump casing (2, 3) and with moving blades (13, 14) which delimit the blade chambers (15, 16) in each case tangentially to the impeller (4) and which are arranged so as to be inclined at an angle to a line parallel to the axis of rotation of the impeller (4) on their side pointing in the intended direction of rotation of the impeller (4), that the angle α1 - α4 of the moving blades (13, 14) increases proportionally, along the radial extent of the moving blades (13, 14), with increasing distance from the centre of the impeller (4), and that the angles α1 - α4 of a plurality of rings of moving blades (13, 14), the said rings being arranged on one of the end faces, have the same proportional dependence.
  2. Feed pump according to Claim 1, characterized in that the angle α1 - α4 of the moving blades (13, 14) has a profile according to the formula
    Figure 00100001
    r being any distance of an intended point of the moving blades (13, 14) from the centre of the impeller (4), and α(ra) being a predetermined angle.
  3. Feed pump according to Claim 1, characterized in that the moving blades (13, 14) have an angle α(r) of 10° to 50°.
  4. Feed pump according to at least one of the preceding claims, characterized in that the angle β of the moving blades (13, 14) at the distance r, on their side facing away in the intended direction of rotation of the impeller (4), is slightly larger than the angle α(r).
  5. Feed pump according to at least one of the preceding claims, characterized in that the angle α(r) is between 15° and 38°.
  6. Feed pump according to at least one of the preceding claims, characterized in that the blade chambers (15, 16) pass through the impeller (4) and have a moving blade (13, 14) on each of the end faces of the impeller (4), and in that the moving blades (13, 14) are oriented so as to point toward the end faces in the intended direction of rotation of the impeller (4).
EP01915233A 2000-03-21 2001-02-13 Feed pump Expired - Lifetime EP1192358B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10013908 2000-03-21
DE10013908A DE10013908A1 (en) 2000-03-21 2000-03-21 Fuel or washing fluid supply pump for vehicle has angles of blades in their radial extend increasing proportionally from center point with decrease in spacing
PCT/EP2001/001550 WO2001071192A1 (en) 2000-03-21 2001-02-13 Feed pump

Publications (2)

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EP1192358A1 EP1192358A1 (en) 2002-04-03
EP1192358B1 true EP1192358B1 (en) 2004-09-22

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EP (1) EP1192358B1 (en)
JP (1) JP4741155B2 (en)
KR (1) KR100760053B1 (en)
CN (1) CN1247900C (en)
AU (1) AU4238701A (en)
BR (1) BR0105550B1 (en)
DE (2) DE10013908A1 (en)
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WO (1) WO2001071192A1 (en)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4552221B2 (en) * 2000-04-14 2010-09-29 株式会社デンソー Fuel pump
US6932562B2 (en) * 2002-06-18 2005-08-23 Ti Group Automotive Systems, L.L.C. Single stage, dual channel turbine fuel pump
US7037066B2 (en) 2002-06-18 2006-05-02 Ti Group Automotive Systems, L.L.C. Turbine fuel pump impeller
US6890144B2 (en) 2002-09-27 2005-05-10 Visteon Global Technologies, Inc. Low noise fuel pump design
DE10246694B4 (en) * 2002-10-07 2016-02-11 Continental Automotive Gmbh Side channel pump
DE10341837B3 (en) * 2003-09-09 2005-03-10 Siemens Ag Fuel pump for fuel tank of motor vehicle has two running wheels on common shaft, spaced apart from each other by dividing wall
KR100581903B1 (en) 2004-03-09 2006-05-22 삼성에스디아이 주식회사 Electroluminescence display device
JP4252507B2 (en) * 2004-07-09 2009-04-08 愛三工業株式会社 Fuel pump
US7165932B2 (en) * 2005-01-24 2007-01-23 Visteon Global Technologies, Inc. Fuel pump having dual single sided impeller
US7632060B2 (en) * 2005-01-24 2009-12-15 Ford Global Technologies, Llc Fuel pump having dual flow channel
US20080056886A1 (en) * 2006-08-31 2008-03-06 Varian, S.P.A. Vacuum pumps with improved pumping channel cross sections
DE102007026533A1 (en) * 2007-06-08 2008-12-11 Continental Automotive Gmbh Fuel pump
DE102007038144A1 (en) * 2007-08-13 2009-02-19 Continental Automotive Gmbh Side channel pump for conveying fuel in a motor vehicle
JP5627217B2 (en) * 2009-11-11 2014-11-19 愛三工業株式会社 Fuel pump
US9249806B2 (en) 2011-02-04 2016-02-02 Ti Group Automotive Systems, L.L.C. Impeller and fluid pump
DE102013220717B4 (en) * 2013-10-14 2016-04-07 Continental Automotive Gmbh pump
US12000411B2 (en) * 2022-01-07 2024-06-04 Phinia Delphi Luxembourg Sarl Fluid pump impeller including blades extending from a hub to an outer ring and having a draft angle between adjacent blades that varies between the hub and the outer ring

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3951567A (en) * 1971-12-18 1976-04-20 Ulrich Rohs Side channel compressor
US3782851A (en) * 1973-01-02 1974-01-01 Outboard Marine Corp Die castable centrifugal fan
JPS5525555A (en) * 1978-08-12 1980-02-23 Hitachi Ltd Impeller
JPS58135397A (en) * 1982-02-05 1983-08-11 Mitsubishi Heavy Ind Ltd Centrifugal pump
GB2253010B (en) * 1990-12-15 1994-04-20 Dowty Defence & Air Syst Regenerative pump
US5310308A (en) * 1993-10-04 1994-05-10 Ford Motor Company Automotive fuel pump housing with rotary pumping element
DE19504079B4 (en) * 1995-02-08 2004-11-04 Robert Bosch Gmbh Flow pump for delivering fuel from a reservoir to the internal combustion engine of a motor vehicle
DE19615322A1 (en) * 1996-04-18 1997-10-23 Vdo Schindling Peripheral pump
US5702229A (en) * 1996-10-08 1997-12-30 Walbro Corporation Regenerative fuel pump
US5762469A (en) * 1996-10-16 1998-06-09 Ford Motor Company Impeller for a regenerative turbine fuel pump
DE19643728A1 (en) * 1996-10-23 1998-04-30 Mannesmann Vdo Ag Feed pump
DE19725249C2 (en) * 1997-06-14 2002-05-02 Siemens Ag feed pump
DE19826902C2 (en) * 1998-06-17 2000-05-04 Mannesmann Vdo Ag Feed pump
DE19912314C2 (en) * 1999-03-19 2002-10-10 Siemens Ag feed pump

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JP4741155B2 (en) 2011-08-03
US20010026757A1 (en) 2001-10-04
BR0105550B1 (en) 2009-08-11
EP1192358A1 (en) 2002-04-03
JP2003528256A (en) 2003-09-24
CN1365434A (en) 2002-08-21
ES2228828T3 (en) 2005-04-16
BR0105550A (en) 2002-03-05
CN1247900C (en) 2006-03-29
DE10013908A1 (en) 2001-09-27
US6517310B2 (en) 2003-02-11
DE50103731D1 (en) 2004-10-28
WO2001071192A1 (en) 2001-09-27
KR20020025870A (en) 2002-04-04
KR100760053B1 (en) 2007-09-18
AU4238701A (en) 2001-10-03

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