EP2078163B1 - Gear pump with reduced pressure impulses on the conveyor side - Google Patents

Gear pump with reduced pressure impulses on the conveyor side Download PDF

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Publication number
EP2078163B1
EP2078163B1 EP07788028.4A EP07788028A EP2078163B1 EP 2078163 B1 EP2078163 B1 EP 2078163B1 EP 07788028 A EP07788028 A EP 07788028A EP 2078163 B1 EP2078163 B1 EP 2078163B1
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EP
European Patent Office
Prior art keywords
groove
gearwheel
angular
region
pump according
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EP07788028.4A
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German (de)
French (fr)
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EP2078163A1 (en
Inventor
Alexander Fuchs
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Robert Bosch GmbH
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Robert Bosch GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0049—Equalization of pressure pulses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/086—Carter
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms

Definitions

  • the invention relates to a gear pump, in particular for conveying fuel from a fuel tank to a high-pressure fuel pump, according to the preamble of claim 1.
  • Such a gear pump is through US 2004/0228752 A1 known.
  • This gear pump has a housing in which a pump chamber is formed, in which a pair is arranged on its outer periphery of intermeshing gears.
  • the gears promote the medium to be conveyed along between the outer periphery and adjacent peripheral walls of the pump chamber formed conveying channels of a suction chamber in a pressure chamber.
  • a tooth gap in the pressure chamber and subsequently at the other gear reaches a tooth space in the pressure chamber successively in time at a gear.
  • the angle of rotation of the gears corresponding to this distance is in each case 360 ° / 2z where z is the number of teeth of the gears.
  • Gear pumps are known in which also in the peripheral walls of the pump chamber in their extending to the pressure chamber angle ranges each provided with a pressure chamber groove is provided by the radial distance between the outer periphery of the gears and the peripheral walls is increased, wherein the radial distance between the outer circumference of the gears and the peripheral walls in the region of the grooves assumes different values.
  • the invention has for its object to provide a gear pump with further reduced amplitudes of the pressure pulsations.
  • the gear pump according to the invention with the features according to claim 1 has the advantage that a further reduction of the pressure pulsations is achieved by arranged at different angular intervals beginnings of the grooves in the peripheral walls of the pump chamber. This reduces the mechanical load on the gear pump so that it can be manufactured more cost-effectively. In addition, the degree of delivery of the gear pump is thereby improved.
  • a gear pump which is used in particular for conveying fuel from a fuel tank to a high-pressure pump of a fuel injection system of an internal combustion engine of a motor vehicle.
  • the gear pump has a multi-part housing with a housing part 10, in which a pump chamber 12 is formed.
  • a pair of gearwheels 14, 16 meshing with each other at their outer periphery are arranged, each having a spur toothing.
  • the gear 14 is rotatable about an axis 15 and the gear 16 is rotatably mounted about an axis 17.
  • gear 14 is driven in a manner not shown around its axis of rotation 15 circumferentially in a rotational direction 18 and drives via its meshing the other gear 16 about its axis of rotation 17 in a rotational direction 19 to rotate.
  • the pump chamber 12 has the outer peripheries of the gears 14, 16 facing peripheral walls 20, 22, which are correspondingly concavely curved.
  • the gears 14, 16 are located approximately in the middle of the pump chamber 12 in engagement, starting from the meshing of the gears 14, 16 on the side facing the directions of rotation 18, 19 side, a suction chamber 24 is formed in the pump chamber 12 and on the opposite Turning directions 18, 19 facing side a pressure chamber 26 is formed in the pump chamber 12. Starting from the suction chamber 24 is between the outer periphery of the respective gear 14, 16 and the adjacent peripheral wall 20, 22 of the pump chamber 12 each have a delivery channel 28, 30 is formed.
  • a groove 32 is formed through which the radial distance between the outer periphery of the gear 14 and the peripheral wall 20 is increased.
  • the first groove 32 extends in the direction of rotation 18 of the gear 14 to the beginning of the pressure chamber 26.
  • a radial distance A r1 is present in a first angular range ⁇ 1 of the first groove 32 between the peripheral wall 20 and the first gear 14.
  • a radial distance A r2 is present in a second angle range ⁇ 2 of the first groove 32, there is a radial distance A r2 between the peripheral wall 20 and the first gear 14, where A r1 is not equal to A r2 .
  • a r1 is greater than A r2 .
  • a second groove 34 is formed through which the radial distance between the outer periphery of the gear 16 and the peripheral wall 22 is increased.
  • the second groove 34 extends in the direction of rotation 19 of the gear 16 to the beginning of the pressure chamber 26.
  • a first angular range ⁇ 1 of the second groove 34 is between the peripheral wall 22 and the second gear 16, a radial distance A r1 available.
  • a second angular range ⁇ 2 of the second groove 34 there is a radial distance A r2 between the peripheral wall 22 and the first gear 14, where A r1 is not equal to A r2 .
  • a r1 is greater than A r2 .
  • the ends of the grooves 32, 34 are arranged in the pressure chamber 26 at least approximately the same and the beginnings of the grooves 32, 34 are arranged at different angular intervals ⁇ and ⁇ from the ends.
  • transition regions 36 between the first angle ranges ⁇ 1 , ⁇ 1 on the one hand and the second angle ranges ⁇ 2 , ⁇ 2 are rounded.
  • the transition regions 36 can also be shortened or even completely eliminated.
  • Fig. 2 the amplitude of the pressure pulsations in the pressure chamber 26 is shown over the rotational speed n of the gear pump.
  • a first line 38 is the amplitude of the pressure pulsations of a gear pump according to the prior art.
  • a second line 40 shows the amplitude of the pressure pulsations of a gear pump according to the invention.
  • the gear pump according to the invention can not only be made lighter and manufactured more cost-effectively, but the pressure control is improved in the low-pressure region of the fuel injection system but also on the suction side of a downstream high-pressure fuel pump.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Zahnradpumpe, insbesondere zum Fördern von Kraftstoff aus einem Kraftstoffvorratsbehälter zu einer Kraftstoffhochdruckpumpe, nach der Gattung des Anspruchs 1.The invention relates to a gear pump, in particular for conveying fuel from a fuel tank to a high-pressure fuel pump, according to the preamble of claim 1.

Eine solche Zahnradpumpe ist durch die US 2004/0228752 A1 bekannt. Diese Zahnradpumpe weist ein Gehäuse auf, in dem eine Pumpenkammer gebildet ist, in der ein Paar an ihrem Außenumfang miteinander kämmender Zahnräder angeordnet ist. Die Zahnräder fördern das zu fördernde Medium entlang zwischen deren Außenumfang und angrenzenden Umfangswänden der Pumpenkammer gebildeter Förderkanäle von einem Saugraum in einen Druckraum. Beim Betrieb der Zahnradpumpe gelangt jeweils zeitlich nacheinander beim einen Zahnrad eine Zahnlücke in den Druckraum und anschließend beim anderen Zahnrad eine Zahnlücke in den Druckraum. Der Drehwinkel der Zahnräder entsprechend diesem Abstand beträgt hierbei jeweils 360°/2z wobei z die Zähnezahl der Zahnräder ist.Such a gear pump is through US 2004/0228752 A1 known. This gear pump has a housing in which a pump chamber is formed, in which a pair is arranged on its outer periphery of intermeshing gears. The gears promote the medium to be conveyed along between the outer periphery and adjacent peripheral walls of the pump chamber formed conveying channels of a suction chamber in a pressure chamber. During operation of the gear pump, a tooth gap in the pressure chamber and subsequently at the other gear reaches a tooth space in the pressure chamber successively in time at a gear. The angle of rotation of the gears corresponding to this distance is in each case 360 ° / 2z where z is the number of teeth of the gears.

Beim Eintreten einer Zahnlücke in den Druckraum wird dessen Volumen vergrößert, wodurch der Druck im Druckraum abfällt. Beim Betrieb der Zahnradpumpe ergeben sich somit Druckpulsationen im Druckraum, die eine Periode entsprechend dem halben Zahnteilungswinkel der Zahnräder aufweisen. Bei einer Zähnezahl z = 10 beträgt die Periode somit 18° bezogen auf die jeweiligen Drehachsen der Zahnräder. Das heißt, dass nach jeweils 18° Drehwinkel der Zahnräder eine Zahnlücke in den Druckraum eintritt und dessen Volumen vergrößert wird. Die Druckpulsationen führen zu einer hohen mechanischen Belastung der Zahnradpumpe, der durch eine die erforderliche Festigkeit aufweisende, teure Konstruktion der Zahnradpumpe Rechnung getragen werden muss. Die Druckpulsationen führen außerdem zu einer Verringerung des Liefergrads der Zahnradpumpe.Upon entering a tooth gap in the pressure chamber whose volume is increased, whereby the pressure drops in the pressure chamber. During operation of the gear pump, pressure pulsations thus result in the pressure chamber, which have a period corresponding to half the tooth pitch angle of the gears. With a number of teeth z = 10, the period is thus 18 ° relative to the respective axes of rotation of the gears. That means that after each 18 ° rotation angle of the gears enters a tooth gap in the pressure chamber and its volume is increased. The pressure pulsations lead to a high mechanical load of the gear pump, which must be taken into account by having the required strength, expensive construction of the gear pump. The pressure pulsations also lead to a reduction in the degree of delivery of the gear pump.

Durch die US 2004/0228752 A1 ist es bekannt die Umfangswände der Pumpenkammer in ihren zum Druckraum hin verlaufenden Winkelbereichen jeweils mit einer mit dem Druckraum verbundenen Nut zu versehen, durch die der radiale Abstand zwischen dem Außenumfang der Zahnräder und den Umfangswänden vergrößert ist, wobei der radiale Abstand zwischen dem Außenumfang der Zahnräder und den Umfangswänden im Bereich der Nuten unterschiedliche Werte annimmt. Hierdurch können die Amplituden der Druckpulsationen reduziert werden.By the US 2004/0228752 A1 It is known to provide the circumferential walls of the pump chamber in their angle to the pressure chamber extending angle ranges each with a connected to the pressure chamber groove through which the radial distance between the outer periphery of the gears and the peripheral walls is increased, wherein the radial distance between the outer periphery of the gears and the peripheral walls in the region of the grooves assumes different values. As a result, the amplitudes of the pressure pulsations can be reduced.

Durch die JP 2002 242854 A und die JP 2000 205146 A sind Zahnradpumpen bekannt, bei denen ebenfalls in den Umfangswänden der Pumpenkammer in ihren zum Druckraum hin verlaufenden Winkelbereichen jeweils eine mit dem Druckraum verbundene Nut vorgesehen ist, durch die der radiale Abstand zwischen dem Außenumfang der Zahnräder und den Umfangswänden vergrößert ist, wobei der radiale Abstand zwischen dem Außenumfang der Zahnräder und den Umfangswänden im Bereich der Nuten unterschiedliche Werte annimmt.By the JP 2002 242854 A and the JP 2000 205146 A Gear pumps are known in which also in the peripheral walls of the pump chamber in their extending to the pressure chamber angle ranges each provided with a pressure chamber groove is provided by the radial distance between the outer periphery of the gears and the peripheral walls is increased, wherein the radial distance between the outer circumference of the gears and the peripheral walls in the region of the grooves assumes different values.

Offenbarung der ErfindungDisclosure of the invention

Der Erfindung liegt die Aufgabe zugrunde, eine Zahnradpumpe mit weiter reduzierten Amplituden der Druckpulsationen bereitzustellen.The invention has for its object to provide a gear pump with further reduced amplitudes of the pressure pulsations.

Die erfindungsgemäße Zahnradpumpe mit den Merkmalen gemäss Anspruch 1 hat den Vorteil, dass durch die in unterschiedlichen Winkelabständen angeordneten Anfänge der Nuten in den Umfangswänden der Pumpenkammer eine weitere Reduktion der Druckpulsationen erreicht wird. Dadurch werden die mechanischen Belastung der Zahnradpumpe verringert, so dass diese kostengünstiger gefertigt werden kann. Außerdem wird der Liefergrad der Zahnradpumpe hierdurch verbessert.The gear pump according to the invention with the features according to claim 1 has the advantage that a further reduction of the pressure pulsations is achieved by arranged at different angular intervals beginnings of the grooves in the peripheral walls of the pump chamber. This reduces the mechanical load on the gear pump so that it can be manufactured more cost-effectively. In addition, the degree of delivery of the gear pump is thereby improved.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Zahnradpumpe angegeben.In the dependent claims advantageous refinements and developments of the gear pump according to the invention are given.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen

Fig. 1
eine Zahnradpumpe in einem Querschnitt und
Fig. 2
den Verlauf von Druckpulsationen im Druckraum der Zahnradpumpe.
An embodiment of the invention is illustrated in the drawing and explained in more detail in the following description. Show it
Fig. 1
a gear pump in a cross section and
Fig. 2
the course of pressure pulsations in the pressure chamber of the gear pump.

Ausführungsformen der ErfindungEmbodiments of the invention

In Fig. 1 ist eine Zahnradpumpe dargestellt, die insbesondere zum Fördern von Kraftstoff aus einem Kraftstoffvorratsbehälter zu einer Hochdruckpumpe eines Kraftstoffeinspritzsystems einer Brennkraftmaschine eines Kraftfahrzeugs dient. Die Zahnradpumpe weist ein mehrteiliges Gehäuse mit einem Gehäuseteil 10 auf, in dem eine Pumpenkammer 12 gebildet ist. In der Pumpenkammer 12 ist ein Paar an ihrem Außenumfang miteinander kämmender Zahnräder 14, 16 angeordnet, die jeweils eine Stirnverzahnung aufweisen. Das Zahnrad 14 ist um eine Achse 15 drehbar und das Zahnrad 16 ist um eine Achse 17 drehbar gelagert. Eines der Zahnräder 14, 16, beispielsweise das Zahnrad 14 wird in nicht näher dargestellter Weise um seine Drehachse 15 umlaufend in einer Drehrichtung 18 angetrieben und treibt über seinen Zahneingriff das andere Zahnrad 16 um dessen Drehachse 17 in einer Drehrichtung 19 rotierend an.In Fig. 1 a gear pump is shown, which is used in particular for conveying fuel from a fuel tank to a high-pressure pump of a fuel injection system of an internal combustion engine of a motor vehicle. The gear pump has a multi-part housing with a housing part 10, in which a pump chamber 12 is formed. In the pump chamber 12, a pair of gearwheels 14, 16 meshing with each other at their outer periphery are arranged, each having a spur toothing. The gear 14 is rotatable about an axis 15 and the gear 16 is rotatably mounted about an axis 17. One of the gears 14, 16, for example, the gear 14 is driven in a manner not shown around its axis of rotation 15 circumferentially in a rotational direction 18 and drives via its meshing the other gear 16 about its axis of rotation 17 in a rotational direction 19 to rotate.

Die Pumpenkammer 12 weist den Außenumfängen der Zahnräder 14, 16 zugewandte Umfangswände 20, 22 auf, die entsprechend konkav gekrümmt sind. Die Zahnräder 14, 16 befinden sich etwa in der Mitte der Pumpenkammer 12 in Eingriff, wobei ausgehend vom Zahneingriff der Zahnräder 14, 16 auf der in die Drehrichtungen 18, 19 weisenden Seite ein Saugraum 24 in der Pumpenkammer 12 gebildet ist und auf der entgegen der Drehrichtungen 18, 19 weisenden Seite ein Druckraum 26 in der Pumpenkammer 12 gebildet ist. Ausgehend vom Saugraum 24 ist zwischen dem Außenumfang des jeweiligen Zahnrads 14, 16 und der angrenzenden Umfangswand 20, 22 der Pumpenkammer 12 jeweils ein Förderkanal 28, 30 gebildet. Beim Betrieb der Zahnradpumpe wird durch die Zahnräder 14, 16 Kraftstoff aus dem Saugraum 24 entlang der Förderkanäle 28, 30 in ihren Zahnlücken in den Druckraum 26. In den Saugraum 24 mündet ein Zulauf vom Kraftstoffvorratsbehälter her und vom Druckraum 26 führt eine Verbindung zur Kraftstoffhochdruckpumpe ab.The pump chamber 12 has the outer peripheries of the gears 14, 16 facing peripheral walls 20, 22, which are correspondingly concavely curved. The gears 14, 16 are located approximately in the middle of the pump chamber 12 in engagement, starting from the meshing of the gears 14, 16 on the side facing the directions of rotation 18, 19 side, a suction chamber 24 is formed in the pump chamber 12 and on the opposite Turning directions 18, 19 facing side a pressure chamber 26 is formed in the pump chamber 12. Starting from the suction chamber 24 is between the outer periphery of the respective gear 14, 16 and the adjacent peripheral wall 20, 22 of the pump chamber 12 each have a delivery channel 28, 30 is formed. During operation of the gear pump is through the gears 14, 16 fuel from the suction chamber 24 along the delivery channels 28, 30 in their tooth spaces in the pressure chamber 26. In the suction chamber 24 opens an inlet from the fuel tank forth and from the pressure chamber 26 performs a connection to the high-pressure fuel pump ,

In der dem Zahnrad 14 zugewandten Umfangswand 20 der Pumpenkammer 12 ist eine Nut 32 ausgebildet, durch die der radiale Abstand zwischen dem Außenumfang des Zahnrads 14 und der Umfangswand 20 vergrößert ist. Die erste Nut 32 erstreckt sich in Drehrichtung 18 des Zahnrads 14 bis zum Beginn des Druckraums 26. In einem ersten Winkelbereich α1 der ersten Nut 32 ist zwischen der Umfangswand 20 und dem ersten Zahnrad 14 ein radialer Abstand Ar1 vorhanden. In einem zweiten Winkelbereich α2 der ersten Nut 32 ist zwischen der Umfangswand 20 und dem ersten Zahnrad 14 ein radialer Abstand Ar2vorhanden, wobei Ar1 ungleich Ar2. Bei dem in Figur 1 dargestellten Ausführungsbeispiel ist Ar1 größer Ar2.In the gear wheel 14 facing peripheral wall 20 of the pump chamber 12, a groove 32 is formed through which the radial distance between the outer periphery of the gear 14 and the peripheral wall 20 is increased. The first groove 32 extends in the direction of rotation 18 of the gear 14 to the beginning of the pressure chamber 26. In a first angular range α 1 of the first groove 32 between the peripheral wall 20 and the first gear 14, a radial distance A r1 is present. In a second angle range α 2 of the first groove 32, there is a radial distance A r2 between the peripheral wall 20 and the first gear 14, where A r1 is not equal to A r2 . At the in FIG. 1 illustrated embodiment, A r1 is greater than A r2 .

In der dem Zahnrad 16 zugewandten Umfangswand 22 der Pumpenkammer 12 ist eine zweit Nut 34 ausgebildet, durch die der radiale Abstand zwischen dem Außenumfang des Zahnrads 16 und der Umfangswand 22 vergrößert ist. Die zweite Nut 34 erstreckt sich in Drehrichtung 19 des Zahnrads 16 bis zum Beginn des Druckraums 26. In einem ersten Winkelbereich β1 der zweiten Nut 34 ist zwischen der Umfangswand 22 und dem zweiten Zahnrad 16 ein radialer Abstand Ar1 vorhanden. In einem zweiten Winkelbereich β2 der zweiten Nut 34 ist zwischen der Umfangswand 22 und dem ersten Zahnrad 14 ein radialer Abstand Ar2vorhanden, wobei Ar1 ungleich Ar2. Bei dem in Figur 1 dargestellten Ausführungsbeispiel ist Ar1 größer Ar2.In the gear wheel 16 facing peripheral wall 22 of the pump chamber 12, a second groove 34 is formed through which the radial distance between the outer periphery of the gear 16 and the peripheral wall 22 is increased. The second groove 34 extends in the direction of rotation 19 of the gear 16 to the beginning of the pressure chamber 26. In a first angular range β 1 of the second groove 34 is between the peripheral wall 22 and the second gear 16, a radial distance A r1 available. In a second angular range β 2 of the second groove 34, there is a radial distance A r2 between the peripheral wall 22 and the first gear 14, where A r1 is not equal to A r2 . At the in FIG. 1 illustrated embodiment, A r1 is greater than A r2 .

Bezogen auf die Drehachse 15, 17 des jeweiligen Zahnrads 14, 16 sind die Enden der Nuten 32, 34 im Druckraum 26 zumindest annähernd gleich angeordnet und die Anfänge der Nuten 32, 34 sind in unterschiedlichen Winkelabständen α bzw. β von den Enden entfernt angeordnet.Based on the axis of rotation 15, 17 of the respective gear 14, 16, the ends of the grooves 32, 34 are arranged in the pressure chamber 26 at least approximately the same and the beginnings of the grooves 32, 34 are arranged at different angular intervals α and β from the ends.

Durch diese Ausbildung der Nuten 32, 34 wird eine weitere Reduktion der Druckpulsationen erreicht. Alternativ ist der gleiche Effekt auch durch eine gezielte Anordnung mehrerer Nuten mit jeweils konstantem Querschnitt zu erreichen. Allerdings ist diese Variante aufwändiger in der Herstellung und neigt eher zu Kavitation.By this formation of the grooves 32, 34, a further reduction of the pressure pulsations is achieved. Alternatively, the same effect can be achieved by a targeted arrangement of several grooves, each with a constant cross section. However, this variant is more complex to produce and tends to cavitation.

Um Kavitationserscheinungen zu verhindern sind die Übergangsbereiche 36 zwischen den ersten Winkelbereichen α1, β1 einerseits und den zweiten Winkelbereichen α2, β2 verrundet. In einer vereinfachten Ausführungsform können die Übergangsbereiche 36 auch verkürzt werden oder sogar ganz entfallen.In order to prevent cavitation phenomena, the transition regions 36 between the first angle ranges α 1 , β 1 on the one hand and the second angle ranges α 2 , β 2 are rounded. In a simplified embodiment, the transition regions 36 can also be shortened or even completely eliminated.

In Fig. 2 ist die Amplitude der Druckpulsationen im Druckraum 26 über der Drehzahl n der Zahnradpumpe dargestellt. Mit einer ersten Linie 38 ist die Amplitude der Druckpulsationen einer Zahnradpumpe nach dem Stand der Technik. Mit einer zweiten Linie 40 ist die Amplitude der Druckpulsationen einer erfindungsgemäßen Zahnradpumpe dargestellt.In Fig. 2 the amplitude of the pressure pulsations in the pressure chamber 26 is shown over the rotational speed n of the gear pump. With a first line 38 is the amplitude of the pressure pulsations of a gear pump according to the prior art. A second line 40 shows the amplitude of the pressure pulsations of a gear pump according to the invention.

Durch den Vergleich der ersten Linie 38 und der zweiten Linie 40 wird unmittelbar deutlich, dass die Amplituden der Druckpulsationen bei der erfindungsgemäßen Zahnradpumpe gegenüber der aus der DE 101 345 622 A1 bekannten Zahnradpumpe nochmals deutlich reduziert werden konnten. Dadurch kann die erfindungsgemäße Zahnradpumpe nicht nur leichter gebaut und kostengünstiger hergestellt werden, sondern die Druckregelung wird im Niederdruckbereich der Kraftstoffeinspritzanlage aber auch auf der Saugseite einer nachgeschalteten Kraftstoffhochdruckpumpe verbessert.By comparing the first line 38 and the second line 40 is immediately clear that the amplitudes of the pressure pulsations in the gear pump according to the invention over that of DE 101 345 622 A1 known gear pump could be significantly reduced again. As a result, the gear pump according to the invention can not only be made lighter and manufactured more cost-effectively, but the pressure control is improved in the low-pressure region of the fuel injection system but also on the suction side of a downstream high-pressure fuel pump.

Claims (10)

  1. Gearwheel pump, in particular for delivering fuel from a fuel reservoir to a high-pressure fuel pump, having a housing (10) in which there is formed a pump chamber (12) in which a pair of intermeshing gearwheels (14, 16) is arranged, which gearwheels deliver the medium for delivery from a suction chamber (24) into a pressure chamber (26) along delivery ducts (28, 30) which are formed between the outer circumferences of said gearwheels and circumferential walls (20, 22) adjoining said outer circumferences, of the pump chambers (12), wherein the circumferential walls (20, 22) of the pump chambers (12) have, in their angular regions (α, β) running toward the pressure chamber (26), in each case one groove (32, 34) which is connected to the pressure chamber (26) and by means of which the radial distance between the outer circumference of the gearwheels (14, 16) and the circumferential walls (20, 22) is enlarged, wherein the radial distance (Ar1, Ar2) between the outer circumference of the gearwheels (14, 16) and the circumferential walls (20, 22) assumes different values in the region of the grooves (32, 34), characterized in that, in relation to the axis of rotation (15, 17) of the respective gearwheel (14, 16), the end points of the grooves (32, 34) in the pressure chamber (26) are arranged at least approximately equally, and the starting points of the grooves (32, 34) are arranged so as to be spaced apart from the ends by different angular distances (α, β).
  2. Gearwheel pump according to Claim 1, characterized in that, within a first angular region (α1) of a first groove (32), the radial distance (Ar1) between the outer circumference of a first gearwheel (14) and the circumferential wall (20) in the region of the first groove (32) is greater than the radial distance (Ar2) between the outer circumference of a first gearwheel (14) and the circumferential wall (20) within a second angular region (α2) of a first groove (32).
  3. Gearwheel pump according to Claim 2, characterized in that the first angular region (α1) is arranged closer to the pressure chamber (26) than the second angular region (α2).
  4. Gearwheel pump according to one of the preceding claims, characterized in that, within a first angular region (β1) of a second groove (34), the radial distance (Ar1) between the outer circumference of a second gearwheel (16) and the circumferential wall (20) in the region of the second groove (34) is greater than the radial distance (Ar2) between the outer circumference of the second gearwheel (16) and the circumferential wall (20) within a second angular region (β2) of the second groove (34).
  5. Gearwheel pump according to Claim 4, characterized in that the first angular region (β1) is arranged closer to the pressure chamber (26) than the second angular region (β2).
  6. Gearwheel pump according to one of the preceding claims, characterized in that the transitions (36) from the first angular regions (α1, β1) to the second angular regions (α2, β2) are rounded.
  7. Gearwheel pump according to one of the preceding claims, characterized in that the first angular regions (α1, β1) and/or the second angular regions (α2, β2) are greater than or approximately equal to the pitch of the gearwheels (14, 16).
  8. Gearwheel pump according to one of the preceding claims, characterized in that the first angular region (α1) of the first groove (32) is of approximately the same size as the first angular region (β1) of the second groove (34).
  9. Gearwheel pump according to one of the preceding claims, characterized in that the second angular region (α2) of the first groove (32) is approximately the same size as the second angular region (β2) of the second groove (34).
  10. Gearwheel pump according to one of the preceding claims, characterized in that the angular regions (α, β) over which the grooves (32, 34) extend are defined such that a respective tooth gap or tooth of both gearwheels (14, 16) enters into a position of overlap with the respective groove (32, 34) at least approximately simultaneously.
EP07788028.4A 2006-09-28 2007-07-30 Gear pump with reduced pressure impulses on the conveyor side Active EP2078163B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006045932A DE102006045932A1 (en) 2006-09-28 2006-09-28 Gear pump with reduced pressure pulsations on the delivery side
PCT/EP2007/057821 WO2008037525A1 (en) 2006-09-28 2007-07-30 Gear pump with reduced pressure impulses on the conveyor side

Publications (2)

Publication Number Publication Date
EP2078163A1 EP2078163A1 (en) 2009-07-15
EP2078163B1 true EP2078163B1 (en) 2017-04-12

Family

ID=38662856

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07788028.4A Active EP2078163B1 (en) 2006-09-28 2007-07-30 Gear pump with reduced pressure impulses on the conveyor side

Country Status (6)

Country Link
US (1) US8444406B2 (en)
EP (1) EP2078163B1 (en)
JP (1) JP4909415B2 (en)
CN (1) CN101517235B (en)
DE (1) DE102006045932A1 (en)
WO (1) WO2008037525A1 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1403528B1 (en) * 2011-01-25 2013-10-31 Trw Automotive Italia S R L PUMPING GROUP TO SUPPLY OIL IN PRESSURE TO A USER
DE102012008527B3 (en) * 2012-05-02 2013-07-25 Netzsch Pumpen & Systeme Gmbh ROTARY PISTON PUMP WITH OPTIMIZED INPUTS AND OUTLETS
DE102013226852A1 (en) 2013-12-20 2015-06-25 Volkswagen Aktiengesellschaft gear pump
DE102017209022A1 (en) * 2017-05-30 2018-12-06 Robert Bosch Gmbh External gear unit
CN113002783A (en) * 2021-04-08 2021-06-22 安徽砺德特种动力科技有限公司 Electric control type pump body, driving device for unmanned aerial vehicle and fluid transmission method
CN117703748A (en) * 2024-01-05 2024-03-15 南京孚奥智能技术有限公司 Gear pump and gear pump housing

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2036217U (en) * 1988-07-28 1989-04-19 西安交通大学 Low-fluctuation and low-noise gear pump
JP2000205146A (en) * 1999-01-11 2000-07-25 Kayaba Ind Co Ltd Hydraulic unit
DE10018348A1 (en) 2000-04-13 2001-10-25 Bosch Gmbh Robert Gearwheel pump for high pressure fuel pump has housing with gear wheels and groove having first and second sections with different spacing at bottom from tooth tips producing narrow gap for better pump action
JP4061847B2 (en) * 2001-02-15 2008-03-19 株式会社ジェイテクト Gear pump
DE10134622B4 (en) * 2001-07-17 2018-09-13 Robert Bosch Gmbh Gear pump, in particular for conveying fuel from a fuel tank to a high-pressure fuel pump
DE10239558B4 (en) 2002-08-28 2005-03-17 SCHWäBISCHE HüTTENWERKE GMBH External gear pump with pressurized fluid precharge

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
US20100047102A1 (en) 2010-02-25
JP2010505059A (en) 2010-02-18
JP4909415B2 (en) 2012-04-04
DE102006045932A1 (en) 2008-04-03
EP2078163A1 (en) 2009-07-15
CN101517235B (en) 2012-10-10
CN101517235A (en) 2009-08-26
WO2008037525A1 (en) 2008-04-03
US8444406B2 (en) 2013-05-21

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