EP2399031B1 - Fuel pump - Google Patents

Fuel pump Download PDF

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Publication number
EP2399031B1
EP2399031B1 EP09801210.7A EP09801210A EP2399031B1 EP 2399031 B1 EP2399031 B1 EP 2399031B1 EP 09801210 A EP09801210 A EP 09801210A EP 2399031 B1 EP2399031 B1 EP 2399031B1
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EP
European Patent Office
Prior art keywords
throttle
pump
fuel pump
duct
fuel
Prior art date
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.)
Active
Application number
EP09801210.7A
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German (de)
French (fr)
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EP2399031A1 (en
Inventor
Marcus Kristen
Armin Merz
Markus Grieb
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2399031A1 publication Critical patent/EP2399031A1/en
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Publication of EP2399031B1 publication Critical patent/EP2399031B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/12—Combinations of two or more pumps the pumps being of different types at least one pump being of the rotary-piston positive-displacement type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
    • F04B23/103—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type being a radial piston pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections

Definitions

  • the invention relates to a fuel pump, in particular a low-pressure pump of a pump arrangement with a low-pressure pump and a high-pressure pump. Specifically, the invention relates to the field of fuel injection systems of air compressing, self-igniting internal combustion engines.
  • the known pump arrangement is particularly suitable for a common rail injection system.
  • the known pump arrangement comprises a radial piston pump with a drive shaft mounted in a pump housing and a low pressure pump upstream of the radial piston pump.
  • the supply of a fuel from the low-pressure pump to the high pressure pump via a running through an intake manifold inlet channel and a connecting channel, which are located in the pump housing.
  • the inlet channel extends in a first direction and the connecting channel extends in a direction which deviates from the direction of the inlet channel.
  • the inlet channel opens laterally into the blind channel configured as a connecting channel.
  • the fuel pump according to the invention with the features of claim 1 has the advantage that an operation is improved. Specifically, a fuel pump can be created, which has a throttle for limiting flow, with an advantageous mode of operation of the throttle and at the same time a deflection for a fuel is realized.
  • a throttle may be designed as a diaphragm or nozzle.
  • the length is much larger than a throttle diameter.
  • the throttle is not configured as such a laminar throttle.
  • a ratio of a length of the throttle to a diameter of the throttle is less than about 1.5.
  • the ratio of the length of the throttle to the diameter of the throttle may also be greater than 1.5, in particular slightly greater than 1.5.
  • the throttle may be arranged in the extension of the inlet channel. This allows the design of the inlet channel together with the throttle by means of a step tool.
  • a configuration can be realized in which a flow separation in the region of the throttle is prevented or at least reduced, whereby the full throttle diameter is effective. Together with a subsequent large connection channel or the like. This can be achieved a good throttle effect.
  • the inlet channel has a conical end section and that the throttle adjoins the conical end section.
  • the throttle is at least approximately aligned with an axis of the inlet channel.
  • the throttle is designed as a throttle bore.
  • an advantageous positioning of the throttle is given.
  • a simple configuration by means of a step tool is possible.
  • the inlet channel can be configured in an advantageous manner as an inlet bore, which extends at least in sections through an inlet connection.
  • the inlet channel can be configured in a housing part of the high-pressure pump, wherein the inlet nozzle can be an integral part of the housing part.
  • the throttle and the connecting channel can be integrated in an advantageous manner in a housing part of an external gear pump.
  • Fig. 1 shows a fuel pump 1 in a side view according to an embodiment of the invention.
  • the fuel pump 1 can in particular be configured as a pump arrangement with a low-pressure pump, for example an external gear pump 2, and a high-pressure pump 3 for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • the fuel pump 1 can also be designed as another gear pump, in particular internal gear pump, or as a vane pump.
  • a preferred use of the fuel pump 1 is for a fuel injection system having a fuel rail which stores diesel fuel under high pressure.
  • the fuel pump 1 according to the invention is also suitable for other applications.
  • the fuel pump 1 of the exemplary embodiment has a first pump part 2, which is designed as an external gear pump 2, and a second pump part 3, which is designed as a high-pressure pump 3, on.
  • the second pump part 3 lies behind the first pump part 2 and is partially covered by the first pump part 2.
  • a feed or intake 4 is provided, can be supplied via the fuel from a tank or the like. From the inlet nozzle 4, the fuel passes through the housing of the second pump part 3 to the gear pump forming the first pump part 2, that of the second pump part 3 forming high-pressure pump is connected upstream.
  • the first pump part 2 therefore has the function of a low-pressure pump, while the second pump part 3 has the function of a high-pressure pump.
  • the high-pressure pump of the second pump part 3 can be designed in particular as a radial piston pump.
  • the first pump part 2 has gears 5, 6, whose position in the Fig. 1 represented by broken lines.
  • the gears 5, 6 are covered by a housing part 7 of the external gear pump 2, which is designed as a housing 7 of the external gear pump 2.
  • the housing part 7 is connected to fixed points 8A, 8B, 8C, 8D with a housing part 9 of the second pump part 3.
  • the housing part 9 is designed as a high-pressure pump housing 9.
  • the inlet nozzle 4 is part of the housing part 9.
  • the housing part 7 at four fixed points 8 A, 8 B, 8 C, 8 D is connected to the housing part 9 of the second pump part 3.
  • different arrangements for the fixed points 8A, 8B, 8C, 8D are possible.
  • a different number of fixed points may be provided, in particular, three fixed points may be provided to connect the housing parts 7, 9 with each other.
  • Fig. 2 shows an excerpted section through the housing part 9 of FIG Fig. 1 shown fuel pump 1 along the designated II cutting line according to a conventional embodiment.
  • an inlet channel 15 is formed, which is designed as a blind hole.
  • the inlet channel 15 extends in sections through the inlet nozzle 4, wherein the inlet channel 15, in particular in the region of the inlet nozzle 4, can be configured as a stepped bore.
  • the inlet channel 15 extends in a direction 16 through the housing part 9.
  • the inlet channel 15 has an axis 17 along which the inlet channel 15 extends in the direction 16.
  • the inlet channel 15 has a bore bottom 18, on which the inlet channel 15 designed as a blind hole ends.
  • the bore bottom 18 is designed conical.
  • a connecting channel 19 is also formed, which is configured by a bore.
  • the connecting channel 19 opens into the inlet channel 15 at the bore bottom 18.
  • the connecting channel 19 has an axis 21 along which the connecting channel 19 extends in one direction 22.
  • fuel is fed via the inlet channel 15 and the connecting channel 19 to the external gear pump 2.
  • the fuel flows in the direction 16 through the inlet channel 15 and in the direction 22 through the connecting channel 19.
  • the direction 16 of the inlet channel 15 includes with the direction 22 of the connecting channel 19 an angle 23 of about 90 °. That is, the axis 17 of the inlet channel 15 closes with the axis 21 of the connecting channel 19, the angle 23 of about 90 °.
  • the external gear pump 2 is preferably operated in suction-throttled operation in order to limit a flow rate.
  • the throttle effect required for this purpose is achieved through the connecting channel 19.
  • a cross section of the connecting channel 19 is set relatively small, so that the connecting channel 19 as a throttle acts.
  • acting as a throttle connection channel 19 is seated at an angle of approximately 90 ° to the inlet channel 15.
  • the flow from the wall of the connecting channel 19 comes off in a region 24 of the connecting channel 19.
  • the full cross section of the connecting channel 19 no longer acts as a throttle. The effect of the throttle is thereby changed and possibly undetermined.
  • the throttling action of the connecting channel 19 is dependent on the transition of the inlet channel 15 in the connecting channel 19 at the bottom of the hole 18.
  • the transition depending on the configuration of the intersection between the channels 15, 19 vary. Possible reasons for varying transitions between the inlet channel 15 and the connecting channel 19 are, for example:
  • the connecting channel 19 meets in the bore bottom 18 or in a cylindrical part 25 of the inlet channel 15.
  • the angle 23 between the inlet channel 15 and the connecting channel 19 may vary, for example due to interference contours.
  • the diameter or cross section of the inlet channel 15 at the transition to the connecting channel 19 may vary due to interference contours.
  • the throttle effect of the throttle formed by the connecting channel 19 can vary. As a result, the throttle behavior of the connection channel 19 is not determined, so that no ideal throttle behavior is present.
  • the above points may also result in that for each variant of the high-pressure pump, in particular for legal and Linksmoortagen, a separate throttle diameter for the connecting channel 19 must be specified and votes are required.
  • Fig. 3 shows the in Fig. 2 shown section of the housing part 9 of the fuel pump 1 according to the embodiment of the invention.
  • the connecting channel 19 extends in a direction 22 which deviates from a direction 16 of the inlet channel 15. However, adjoining the inlet channel 15 in the direction 16, a throttle 30, which is aligned in this embodiment of the axis 17, the inlet channel 15.
  • the connecting channel 19 is configured in the form of a blind bore, which has a bore base 31.
  • the connecting channel 19 has a cylindrical portion 32.
  • the throttle 30 opens laterally into the connecting channel 19 and indeed into the cylindrical portion 32 of the connecting channel 19.
  • the inlet channel 15 has a conical end portion 33.
  • the conical end portion 33 connects in the direction 16 to the cylindrical part 25 of the inlet channel 15.
  • the throttle 30 connects.
  • a transition from the cylindrical part 25 of the inlet channel 15 is formed in the throttle 30.
  • the connecting channel 19 has a diameter or cross section which is relatively large compared to a diameter or cross section of the throttle 30. This results in a favorable intersection between the throttle 30 and the connecting channel 19, wherein a reproducible in the production of the intersection line 34, which preferably deviates only slightly from a circular intersection line.
  • Both the Inlet channel 15 and the connecting channel 19 have essentially no throttle effect.
  • a specific throttle effect of the throttle 30 is predetermined.
  • the effective length of the throttle 30 is therefore obtained uniformly along the circumference of the throttle 30. Thereby, a defined throttle effect of the throttle 30 is given.
  • the effect of the throttle 30 can be specified in a simple manner.
  • the diameter or cross section of the throttle 30 can be specified. Since the throttle 30 directly adjoins the inlet channel 15 in the direction 16, the inlet channel 15 can be produced together with the throttle 30 by means of a stepping tool.
  • the throttle 30 can also be integrated into the housing part 7 of the external gear pump 2. In this case, defined ratios for the throttle 30 can also be created.
  • the angle 23 between the inlet channel 15 and the connecting channel 19 is preferably equal to 90 °. This is production technology advantageous. However, a beneficial throttling effect can also be applied to other angles 23 not equal to 90 ° are reached. It is particularly advantageous if the angle 23 is equal to or greater than 90 °, for example equal to 110 °. This is Strömsstochnisch advantageous.

Description

Stand der TechnikState of the art

Die Erfindung betrifft eine Brennstoffpumpe, insbesondere eine Niederdruckpumpe einer Pumpenanordnung mit einer Niederdruckpumpe und einer Hochdruckpumpe. Speziell betrifft die Erfindung das Gebiet der Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen.The invention relates to a fuel pump, in particular a low-pressure pump of a pump arrangement with a low-pressure pump and a high-pressure pump. Specifically, the invention relates to the field of fuel injection systems of air compressing, self-igniting internal combustion engines.

Aus der DE197 36 160 A1 ist eine Pumpenanordnung zur Brennstoffhochdruckversorgung bei Brennstoffeinspritzsystemen von Brennkraftmaschinen bekannt. Die bekannte Pumpenanordnung eignet sich besonders für ein Common-Rail-Einspritzsystem. Die bekannte Pumpenanordnung umfasst eine Radialkolbenpumpe mit einer in einem Pumpengehäuse gelagerten Antriebswelle und eine der Radialkolbenpumpe vorgeschaltete Niederdruckpumpe. Die Zuführung eines Brennstoffs von der Niederdruckpumpe zur Hochdruckpumpe erfolgt über einen durch einen Ansaugstutzen verlaufenden Zulaufkanal und einen Verbindungskanal, die sich im Pumpengehäuse befinden. Der Zulaufkanal verläuft in einer ersten Richtung und der Verbindungskanal verläuft in einer Richtung, die von der Richtung des Zulaufkanals abweicht. Der Zulaufkanal mündet seitlich in den als Sacklochbohrung ausgestalteten Verbindungskanal.From the DE197 36 160 A1 a pump arrangement for high-pressure fuel supply in fuel injection systems of internal combustion engines is known. The known pump arrangement is particularly suitable for a common rail injection system. The known pump arrangement comprises a radial piston pump with a drive shaft mounted in a pump housing and a low pressure pump upstream of the radial piston pump. The supply of a fuel from the low-pressure pump to the high pressure pump via a running through an intake manifold inlet channel and a connecting channel, which are located in the pump housing. The inlet channel extends in a first direction and the connecting channel extends in a direction which deviates from the direction of the inlet channel. The inlet channel opens laterally into the blind channel configured as a connecting channel.

Es ist denkbar, dass bei einer Pumpenanordnung eine Drossel im Zulauf der Niederdruckpumpe vorgesehen ist, um einen sauggedrosselten Betrieb der Niederdruckpumpe mit begrenzter Fördermenge zu ermöglichen. Dabei ergibt sich allerdings dasIt is conceivable that in a pump arrangement, a throttle is provided in the inlet of the low-pressure pump in order to allow a suction-throttled operation of the low-pressure pump with a limited flow rate. However, this results in the

Problem, dass zum einen eine kompakte Ausgestaltung wünschenswert ist und zum anderen ungünstige Strömungsverhältnisse auftreten können.Problem that on the one hand a compact design is desirable and on the other unfavorable flow conditions can occur.

Offenbarung der ErfindungDisclosure of the invention

Die erfindungsgemäße Brennstoffpumpe mit den Merkmalen des Anspruchs 1 hat den Vorteil, dass eine Funktionsweise verbessert ist. Speziell kann eine Brennstoffpumpe geschaffen werden, die zur Fördermengenbegrenzung eine Drossel aufweist, wobei eine vorteilhafte Funktionsweise der Drossel und zugleich eine Umlenkung für einen Brennstoff realisiert ist.The fuel pump according to the invention with the features of claim 1 has the advantage that an operation is improved. Specifically, a fuel pump can be created, which has a throttle for limiting flow, with an advantageous mode of operation of the throttle and at the same time a deflection for a fuel is realized.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen der im Anspruch 1 angegebenen Brennstoffpumpe möglich.The measures listed in the dependent claims advantageous developments of the fuel pump specified in claim 1 are possible.

Im Allgemeinen kann eine Drossel als Blende oder Düse ausgestaltet sein. Speziell bei einer Laminardrossel ist die Länge sehr viel größer als ein Drosseldurchmesser. Vorzugsweise ist die Drossel nicht als solch eine Laminardrossel ausgestaltet. Insbesondere ist es vorteilhaft, dass ein Verhältnis einer Länge der Drossel zu einem Durchmesser der Drossel kleiner als etwa 1,5 ist. Allerdings kann das Verhältnis der Länge der Drossel zu dem Durchmesser der Drossel auch größer als 1,5, insbesondere etwas größer als 1,5, sein. In vorteilhafter Weise kann die Drossel in der Verlängerung des Zulaufkanals angeordnet sein. Dies ermöglicht die Ausgestaltung des Zulaufkanals zusammen mit der Drossel mittels eines Stufenwerkzeugs. Ferner kann in vorteilhafter Weise eine Ausgestaltung realisiert werden, bei der eine Strömungsablösung im Bereich der Drossel verhindert oder zumindest verringert ist, wodurch der volle Drosseldurchmesser wirksam ist. Zusammen mit einem sich anschließenden großen Verbindungskanal oder dgl. kann dadurch eine gute Drosselwirkung erzielt werden.In general, a throttle may be designed as a diaphragm or nozzle. Especially with a laminar throttle, the length is much larger than a throttle diameter. Preferably, the throttle is not configured as such a laminar throttle. In particular, it is advantageous that a ratio of a length of the throttle to a diameter of the throttle is less than about 1.5. However, the ratio of the length of the throttle to the diameter of the throttle may also be greater than 1.5, in particular slightly greater than 1.5. Advantageously, the throttle may be arranged in the extension of the inlet channel. This allows the design of the inlet channel together with the throttle by means of a step tool. Furthermore, in Advantageously, a configuration can be realized in which a flow separation in the region of the throttle is prevented or at least reduced, whereby the full throttle diameter is effective. Together with a subsequent large connection channel or the like. This can be achieved a good throttle effect.

Vorteilhaft ist es auch, dass der Zulaufkanal einen konischen Endabschnitt aufweist und dass sich die Drossel an den konischen Endabschnitt anschließt.It is also advantageous that the inlet channel has a conical end section and that the throttle adjoins the conical end section.

In vorteilhafter Weise ist die Drossel zumindest näherungsweise an einer Achse des Zulaufkanals ausgerichtet. Hierbei ist es ferner vorteilhaft, dass die Drossel als Drosselbohrung ausgestaltet ist. Dadurch ist eine vorteilhafte Positionierung der Drossel gegeben. Außerdem ist eine einfache Ausgestaltung mittels eines Stufenwerkzeugs möglich.Advantageously, the throttle is at least approximately aligned with an axis of the inlet channel. Here, it is also advantageous that the throttle is designed as a throttle bore. As a result, an advantageous positioning of the throttle is given. In addition, a simple configuration by means of a step tool is possible.

Der Zulaufkanal kann in vorteilhafter Weise als Zulaufbohrung ausgestaltet sein, der sich zumindest abschnittsweise durch einen Zulaufstutzen erstreckt. Hierbei kann der Zulaufkanal in einem Gehäuseteil der Hochdruckpumpe ausgestaltet sein, wobei der Zulaufstutzen integraler Bestandteil des Gehäuseteils sein kann.The inlet channel can be configured in an advantageous manner as an inlet bore, which extends at least in sections through an inlet connection. Here, the inlet channel can be configured in a housing part of the high-pressure pump, wherein the inlet nozzle can be an integral part of the housing part.

Allerdings können die Drossel und der Verbindungskanal in vorteilhafter Weise auch in ein Gehäuseteil einer Außenzahnradpumpe integriert sein. Beispielsweise kann eine Integration in ein als Gehäuse der Außenzahnradpumpe ausgestaltetes Gehäuseteil der Außenzahnradpumpe erfolgen.However, the throttle and the connecting channel can be integrated in an advantageous manner in a housing part of an external gear pump. For example, an integration into a designed as a housing of the external gear pump housing part of the external gear pump.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Bevorzugte Ausführungsbeispiele der Erfindung sind in der nachfolgenden Beschreibung anhand der beigefügten Zeichnungen, in denen sich entsprechende Elemente mit übereinstimmenden Bezugszeichen versehen sind, näher erläutert. Es zeigt:

  • Fig. 1 eine Seitenansicht einer Brennstoffpumpe entsprechend einem Ausführungsbeispiel der Erfindung;
  • Fig. 2 einen auszugsweisen Schnitt durch die in Fig. 1 gezeigte Brennstoffpumpe entlang der mit II bezeichneten Schnittlinie entsprechend einer herkömmlichen Ausgestaltung;
  • Fig. 3 den in Fig. 2 dargestellten Schnitt durch die Brennstoffpumpe entsprechend dem Ausführungsbeispiel der Erfindung.
Preferred embodiments of the invention are explained in more detail in the following description with reference to the accompanying drawings, in which corresponding elements are provided with corresponding reference numerals. It shows:
  • Fig. 1 a side view of a fuel pump according to an embodiment of the invention;
  • Fig. 2 an excerpted section through the in Fig. 1 shown fuel pump along the designated II cutting line according to a conventional embodiment;
  • Fig. 3 the in Fig. 2 illustrated section through the fuel pump according to the embodiment of the invention.

Ausführungsformen der ErfindungEmbodiments of the invention

Fig. 1 zeigt eine Brennstoffpumpe 1 in einer seitlichen Ansicht entsprechend einem Ausführungsbeispiel der Erfindung. Die Brennstoffpumpe 1 kann insbesondere als Pumpenanordnung mit einer Niederdruckpumpe, beispielsweise einer Außenzahnradpumpe 2, und einer Hochdruckpumpe 3 für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen ausgestaltet sein. Die Brennstoffpumpe 1 kann auch als andere Zahnradpumpe, insbesondere Innenzahnradpumpe, oder als Flügelzellenpumpe ausgebildet sein. Ein bevorzugter Einsatz der Brennstoffpumpe 1 besteht für eine Brennstoffeinspritzanlage mit einer Brennstoffverteilerleiste, die Dieselbrennstoff unter hohem Druck speichert. Die erfindungsgemäße Brennstoffpumpe 1 eignet sich jedoch auch für andere Anwendungsfälle. Fig. 1 shows a fuel pump 1 in a side view according to an embodiment of the invention. The fuel pump 1 can in particular be configured as a pump arrangement with a low-pressure pump, for example an external gear pump 2, and a high-pressure pump 3 for fuel injection systems of air-compressing, self-igniting internal combustion engines. The fuel pump 1 can also be designed as another gear pump, in particular internal gear pump, or as a vane pump. A preferred use of the fuel pump 1 is for a fuel injection system having a fuel rail which stores diesel fuel under high pressure. However, the fuel pump 1 according to the invention is also suitable for other applications.

Die Brennstoffpumpe 1 des Ausführungsbeispiels weist einen ersten Pumpenteil 2, der als Außenzahnradpumpe 2 ausgestaltet ist, und einen zweiten Pumpenteil 3, der als Hochdruckpumpe 3 ausgestaltet ist, auf. Dabei liegt in der dargestellten Seitenansicht der zweite Pumpenteil 3 hinter dem ersten Pumpenteil 2 und ist teilweise von dem ersten Pumpenteil 2 verdeckt. An einem Gehäuse des zweiten Pumpenteils 3 ist ein Zulauf- oder Ansaugstutzen 4 vorgesehen, über den Brennstoff aus einem Tank oder dergleichen zugeführt werden kann. Von dem Zulaufstutzen 4 gelangt der Brennstoff durch das Gehäuse des zweiten Pumpenteils 3 zu der den ersten Pumpenteil 2 bildenden Zahnradpumpe, die der den zweiten Pumpenteil 3 bildenden Hochdruckpumpe vorgeschaltet ist. Das erste Pumpenteil 2 hat deshalb die Funktion einer Niederdruckpumpe, während das zweite Pumpenteil 3 die Funktion einer Hochdruckpumpe hat. Die Hochdruckpumpe des zweiten Pumpenteils 3 kann insbesondere als Radialkolbenpumpe ausgestaltet sein.The fuel pump 1 of the exemplary embodiment has a first pump part 2, which is designed as an external gear pump 2, and a second pump part 3, which is designed as a high-pressure pump 3, on. In the illustrated side view, the second pump part 3 lies behind the first pump part 2 and is partially covered by the first pump part 2. On a housing of the second pump part 3, a feed or intake 4 is provided, can be supplied via the fuel from a tank or the like. From the inlet nozzle 4, the fuel passes through the housing of the second pump part 3 to the gear pump forming the first pump part 2, that of the second pump part 3 forming high-pressure pump is connected upstream. The first pump part 2 therefore has the function of a low-pressure pump, while the second pump part 3 has the function of a high-pressure pump. The high-pressure pump of the second pump part 3 can be designed in particular as a radial piston pump.

Der erste Pumpenteil 2 weist Zahnräder 5, 6 auf, deren Position in der Fig. 1 durch unterbrochen dargestellte Linien dargestellt ist. Dabei sind die Zahnräder 5, 6 von einem Gehäuseteil 7 der Außenzahnradpumpe 2 abgedeckt, das als Gehäuse 7 der Außenzahnradpumpe 2 ausgestaltet ist. Das Gehäuseteil 7 ist dabei an Fixpunkten 8A, 8B, 8C, 8D mit einem Gehäuseteil 9 des zweiten Pumpenteils 3 verbunden. Das Gehäuseteil 9 ist dabei als Hochdruckpumpengehäuse 9 ausgestaltet. Der Zulaufstutzen 4 ist Bestandteil des Gehäuseteils 9. In diesem Ausführungsbeispiel ist das Gehäuseteil 7 an vier Fixpunkten 8A, 8B, 8C, 8D mit dem Gehäuseteil 9 des zweiten Pumpenteils 3 verbunden. Hierbei sind unterschiedliche Anordnungen für die Fixpunkte 8A, 8B, 8C, 8D möglich. Außerdem kann auch eine andere Anzahl an Fixpunkten vorgesehen sein, insbesondere können drei Fixpunkte vorgesehen sein, um die Gehäuseteile 7, 9 miteinander zu verbinden.The first pump part 2 has gears 5, 6, whose position in the Fig. 1 represented by broken lines. The gears 5, 6 are covered by a housing part 7 of the external gear pump 2, which is designed as a housing 7 of the external gear pump 2. The housing part 7 is connected to fixed points 8A, 8B, 8C, 8D with a housing part 9 of the second pump part 3. The housing part 9 is designed as a high-pressure pump housing 9. The inlet nozzle 4 is part of the housing part 9. In this embodiment, the housing part 7 at four fixed points 8 A, 8 B, 8 C, 8 D is connected to the housing part 9 of the second pump part 3. Here, different arrangements for the fixed points 8A, 8B, 8C, 8D are possible. In addition, a different number of fixed points may be provided, in particular, three fixed points may be provided to connect the housing parts 7, 9 with each other.

Fig. 2 zeigt einen auszugsweisen Schnitt durch das Gehäuseteil 9 der in Fig. 1 dargestellten Brennstoffpumpe- 1 entlang der mit II bezeichneten Schnittlinie entsprechend einer herkömmlichen Ausgestaltung. In dem Gehäuseteil 9 ist ein Zulaufkanal 15 ausgebildet, der als Sackbohrung ausgestaltet ist. Der Zulaufkanal 15 erstreckt sich dabei abschnittsweise durch den Zulaufstutzen 4, wobei der Zulaufkanal 15, insbesondere im Bereich des Zulaufstutzens 4, als Stufenbohrung ausgestaltet sein kann. Der Zulaufkanal 15 erstreckt sich in einer Richtung 16 durch das Gehäuseteil 9. Der Zulaufkanal 15 weist eine Achse 17 auf, entlang der sich der Zulaufkanal 15 in der Richtung 16 erstreckt. Der Zulaufkanal 15 weist einen Bohrungsgrund 18 auf, an dem der als Sacklochbohrung ausgestaltete Zulaufkanal 15 endet. Der Bohrungsgrund 18 ist kegelförmig ausgestaltet. Fig. 2 shows an excerpted section through the housing part 9 of FIG Fig. 1 shown fuel pump 1 along the designated II cutting line according to a conventional embodiment. In the housing part 9, an inlet channel 15 is formed, which is designed as a blind hole. The inlet channel 15 extends in sections through the inlet nozzle 4, wherein the inlet channel 15, in particular in the region of the inlet nozzle 4, can be configured as a stepped bore. The inlet channel 15 extends in a direction 16 through the housing part 9. The inlet channel 15 has an axis 17 along which the inlet channel 15 extends in the direction 16. The inlet channel 15 has a bore bottom 18, on which the inlet channel 15 designed as a blind hole ends. The bore bottom 18 is designed conical.

In dem Gehäuseteil 9 ist außerdem ein Verbindungskanal 19 ausgebildet, der durch eine Bohrung ausgestaltet ist. Der Verbindungskanal 19 mündet einerseits an einer Außenfläche 20 des Gehäuseteils 9. Andererseits mündet der Verbindungskanal 19 am Bohrungsgrund 18 in den Zulaufkanal 15. Der Verbindungskanal 19 weist eine Achse 21 auf, entlang der sich der Verbindungskanal 19 in einer Richtung 22 erstreckt.In the housing part 9, a connecting channel 19 is also formed, which is configured by a bore. On the one hand, the connecting channel 19 opens into the inlet channel 15 at the bore bottom 18. The connecting channel 19 has an axis 21 along which the connecting channel 19 extends in one direction 22.

Im Betrieb der Brennstoffpumpe 1 wird Brennstoff über den Zulaufkanal 15 und den Verbindungskanal 19 zu der Außenzahnradpumpe 2 geführt. Dabei strömt der Brennstoff in der Richtung 16 durch den Zulaufkanal 15 und in der Richtung 22 durch den Verbindungskanal 19. Die Richtung 16 des Zulaufkanals 15 schließt mit der Richtung 22 des Verbindungskanals 19 einen Winkel 23 von etwa 90° ein. Das heißt, die Achse 17 des Zulaufkanals 15 schließt mit der Achse 21 des Verbindungskanals 19 den Winkel 23 von etwa 90° ein.During operation of the fuel pump 1, fuel is fed via the inlet channel 15 and the connecting channel 19 to the external gear pump 2. In this case, the fuel flows in the direction 16 through the inlet channel 15 and in the direction 22 through the connecting channel 19. The direction 16 of the inlet channel 15 includes with the direction 22 of the connecting channel 19 an angle 23 of about 90 °. That is, the axis 17 of the inlet channel 15 closes with the axis 21 of the connecting channel 19, the angle 23 of about 90 °.

Im Betrieb der Brennstoffpumpe 1 wird die Außenzahnradpumpe 2 vorzugsweise im sauggedrosselten Betrieb betrieben, um eine Fördermenge zu begrenzen. Die hierfür erforderliche Drosselwirkung wird durch den Verbindungskanal 19 erreicht. Hierfür ist ein Querschnitt des Verbindungskanals 19 relativ klein vorgegeben, so dass der Verbindungskanal 19 als Drossel wirkt. Dies bedeutet, dass der als Drossel wirkende Verbindungskanal 19 in einem Winkel von etwa 90° zum Zulaufkanal 15 sitzt. Durch diese starke Umlenkung der Strömung von dem Zulaufkanal 15 in den Verbindungskanal 19 kommt es in einem Bereich 24 des Verbindungskanal 19 zu einer Ablösung der Strömung von der Wand des Verbindungskanals 19. Hierdurch wirkt nicht mehr der volle Querschnitt des Verbindungskanals 19 als Drossel. Die Wirkung der Drossel ist hierdurch verändert und gegebenenfalls unbestimmt.During operation of the fuel pump 1, the external gear pump 2 is preferably operated in suction-throttled operation in order to limit a flow rate. The throttle effect required for this purpose is achieved through the connecting channel 19. For this purpose, a cross section of the connecting channel 19 is set relatively small, so that the connecting channel 19 as a throttle acts. This means that acting as a throttle connection channel 19 is seated at an angle of approximately 90 ° to the inlet channel 15. As a result of this strong deflection of the flow from the inlet channel 15 into the connecting channel 19, the flow from the wall of the connecting channel 19 comes off in a region 24 of the connecting channel 19. As a result, the full cross section of the connecting channel 19 no longer acts as a throttle. The effect of the throttle is thereby changed and possibly undetermined.

Außerdem ist die Drosselwirkung des Verbindungskanals 19 abhängig von dem Übergang des Zulaufkanals 15 in den Verbindungskanal 19 am Bohrungsgrund 18. Hierbei kann der Übergang je nach Ausgestaltung der Verschneidung zwischen den Kanälen 15, 19 variieren. Mögliche Gründe für variierende Übergänge zwischen dem Zulaufkanal 15 und dem Verbindungskanal 19 sind beispielsweise:In addition, the throttling action of the connecting channel 19 is dependent on the transition of the inlet channel 15 in the connecting channel 19 at the bottom of the hole 18. Here, the transition depending on the configuration of the intersection between the channels 15, 19 vary. Possible reasons for varying transitions between the inlet channel 15 and the connecting channel 19 are, for example:

Erstens, der Verbindungskanal 19 trifft in den Bohrungsgrund 18 oder in einen zylindrischen Teil 25 des Zulaufkanals 15. Zweitens kann der Winkel 23 zwischen dem Zulaufkanal 15 und dem Verbindungskanal 19 variieren, beispielsweise aufgrund von Störkonturen. Drittens kann der Durchmesser oder Querschnitt des Zulaufkanals 15 am Übergang zum Verbindungskanal 19 auf Grund von Störkonturen variieren.First, the connecting channel 19 meets in the bore bottom 18 or in a cylindrical part 25 of the inlet channel 15. Second, the angle 23 between the inlet channel 15 and the connecting channel 19 may vary, for example due to interference contours. Third, the diameter or cross section of the inlet channel 15 at the transition to the connecting channel 19 may vary due to interference contours.

Durch diese Einflüsse kann unter anderem die Drosselwirkung der durch den Verbindungskanal 19 gebildeten Drossel variieren. Dadurch ist das Drosselverhalten des Verbindungskanals 19 nicht bestimmt, so dass kein ideales Drosselverhalten vorliegt. Die genannten Punkte haben gegebenenfalls auch zur Folge, dass für jede Variante der Hochdruckpumpe, insbesondere für Rechts- und Linkslaufvarianten, ein eigener Drosseldurchmesser für den Verbindungskanal 19 vorgegeben werden muss und Abstimmungen erforderlich sind.Due to these influences, among other things, the throttle effect of the throttle formed by the connecting channel 19 can vary. As a result, the throttle behavior of the connection channel 19 is not determined, so that no ideal throttle behavior is present. The above points may also result in that for each variant of the high-pressure pump, in particular for legal and Linkslaufvarianten, a separate throttle diameter for the connecting channel 19 must be specified and votes are required.

Fig. 3 zeigt den in Fig. 2 dargestellten Ausschnitt des Gehäuseteils 9 der Brennstoffpumpe 1 entsprechend dem Ausführungsbeispiel der Erfindung. Der Verbindungskanal 19 verläuft dabei in einer Richtung 22, die von einer Richtung 16 des Zulaufkanals 15 abweicht. Allerdings schließt sich an den Zulaufkanal 15 in der Richtung 16 eine Drossel 30 an, die in diesem Ausführungsbeispiel an der Achse 17,des Zulaufkanals 15 ausgerichtet ist. Der Verbindungskanal 19 ist in Form einer Sackbohrung ausgestaltet, die einen Bohrungsgrund 31 aufweist. Ferner weist der Verbindungskanal 19 einen zylindrischen Abschnitt 32 auf. Die Drossel 30 mündet seitlich in den Verbindungskanals 19 und zwar in den zylindrischen Abschnitt 32 des Verbindungskanal 19. Ferner weist der Zulaufkanal 15 einen konischen Endabschnitt 33 auf. Der konische Endabschnitt 33 schließt sich in der Richtung 16 an den zylindrischen Teil 25 des Zulaufkanals 15 an. An den konischen Endabschnitt 33 schließt sich dann die Drossel 30 an. Dadurch ist ein Übergang von dem zylindrischen Teil 25 des Zulaufkanals 15 in die Drossel 30 gebildet. Dies wirkt sich günstig auf das Strömungsverhalten im Bereich des Übergangs von dem Zulaufkanal 15 in die Drossel 30 aus. Der Verbindungskanal 19 weist einen Durchmesser oder Querschnitt auf, der im Vergleich zu einem Durchmesser oder Querschnitt der Drossel 30 relativ groß ist. Dadurch ergibt sich eine günstige Verschneidung zwischen der Drossel 30 und dem Verbindungskanal 19, wobei eine bei der Herstellung reproduzierbare Verschneidungslinie 34 besteht, die vorzugsweise nur relativ geringfügig von einer kreisförmigen Verschneidungslinie abweicht. Sowohl der Zulaufkanal 15 als auch der Verbindungskanal 19 haben im Wesentlichen keine Drosselwirkung. Fig. 3 shows the in Fig. 2 shown section of the housing part 9 of the fuel pump 1 according to the embodiment of the invention. The connecting channel 19 extends in a direction 22 which deviates from a direction 16 of the inlet channel 15. However, adjoining the inlet channel 15 in the direction 16, a throttle 30, which is aligned in this embodiment of the axis 17, the inlet channel 15. The connecting channel 19 is configured in the form of a blind bore, which has a bore base 31. Furthermore, the connecting channel 19 has a cylindrical portion 32. The throttle 30 opens laterally into the connecting channel 19 and indeed into the cylindrical portion 32 of the connecting channel 19. Further, the inlet channel 15 has a conical end portion 33. The conical end portion 33 connects in the direction 16 to the cylindrical part 25 of the inlet channel 15. At the conical end portion 33, then the throttle 30 connects. As a result, a transition from the cylindrical part 25 of the inlet channel 15 is formed in the throttle 30. This has a favorable effect on the flow behavior in the region of the transition from the inlet channel 15 into the throttle 30. The connecting channel 19 has a diameter or cross section which is relatively large compared to a diameter or cross section of the throttle 30. This results in a favorable intersection between the throttle 30 and the connecting channel 19, wherein a reproducible in the production of the intersection line 34, which preferably deviates only slightly from a circular intersection line. Both the Inlet channel 15 and the connecting channel 19 have essentially no throttle effect.

Durch die Ausgestaltung des Zulaufkanals 15, der Drossel 30 und des Verbindungskanals 19 entsprechend dem Ausführungsbeispiel ist eine bestimmte Drosselwirkung der Drossel 30 vorgegeben. Außerdem ergibt sich ein vorteilhafter Strömungsverlauf des zunächst in der Richtung 16 und dann in der Richtung 22 strömenden Brennstoffs, insbesondere im Umlenkbereich in die Drossel 30 und von der Drossel 30 in den Verbindungskanal 19. Strömungsablösungen innerhalb der Drossel 30 sind dabei verhindert. Die wirksame Länge der Drossel 30 ergibt sich daher gleichmäßig entlang des Umfangs der Drossel 30. Dadurch ist eine definierte Drosselwirkung der Drossel 30 gegeben.Due to the design of the inlet channel 15, the throttle 30 and the connecting channel 19 according to the embodiment, a specific throttle effect of the throttle 30 is predetermined. In addition, there is an advantageous flow pattern of the fuel flowing initially in the direction 16 and then in the direction 22, in particular in the deflection in the throttle 30 and the throttle 30 in the connecting channel 19. Flow separation within the throttle 30 are prevented. The effective length of the throttle 30 is therefore obtained uniformly along the circumference of the throttle 30. Thereby, a defined throttle effect of the throttle 30 is given.

Außerdem kann die Wirkung der Drossel 30 in einfacher Weise vorgegeben werden. Hierbei kann insbesondere der Durchmesser oder Querschnitt der Drossel 30 vorgegeben werden. Da sich die Drossel 30 in der Richtung 16 an den Zulaufkanal 15 unmittelbar anschließt, kann der Zulaufkanal 15 zusammen mit der Drossel 30 mittels eines Stufenwerkzeugs hergestellt sein.In addition, the effect of the throttle 30 can be specified in a simple manner. In this case, in particular, the diameter or cross section of the throttle 30 can be specified. Since the throttle 30 directly adjoins the inlet channel 15 in the direction 16, the inlet channel 15 can be produced together with the throttle 30 by means of a stepping tool.

Die Drossel 30 kann auch in das Gehäuseteil 7 der Außenzahnradpumpe 2 integriert werden. In diesem Fall können ebenfalls definierte Verhältnisse für die Drossel 30 geschaffen werden.The throttle 30 can also be integrated into the housing part 7 of the external gear pump 2. In this case, defined ratios for the throttle 30 can also be created.

Der Winkel 23 zwischen dem Zulaufkanal 15 und dem Verbindungskanal 19 ist vorzugsweise gleich 90°. Dies ist fertigungstechnisch von Vorteil. Allerdings kann eine vorteilhafte Drosselwirkung auch für andere Winkel 23, die ungleich 90° sind, erreicht werden. Vorteilhaft ist es insbesondere, wenn der Winkel 23 gleich oder großer als 90°, beispielsweise gleich 110°, ist. Dies ist strömungstochnisch von Vorteil.The angle 23 between the inlet channel 15 and the connecting channel 19 is preferably equal to 90 °. This is production technology advantageous. However, a beneficial throttling effect can also be applied to other angles 23 not equal to 90 ° are reached. It is particularly advantageous if the angle 23 is equal to or greater than 90 °, for example equal to 110 °. This is Strömsstochnisch advantageous.

Claims (8)

  1. Fuel pump (1) for a pump arrangement having a low-pressure pump and a high-pressure pump for fuel injection systems of air-compressing, autoignition internal combustion engines, having a supply duct (15) and a connecting duct (19) on the suction side of the fuel pump, wherein the connecting duct (19) runs in a direction (22) which differs from a direction (16) of the supply duct (15), wherein the supply duct (15) opens laterally into the connecting duct (19) which is in the form of a blind bore, characterized in that a throttle (30) is provided which adjoins the supply duct (15) in the direction (16) of the supply duct (15) and which opens laterally into the connecting duct (19) and which opens perpendicularly into a cylindrical section (32) of the connecting duct (19), and in that a cross section of the connecting duct (19) is larger than a cross section of the throttle (30).
  2. Fuel pump according to Claim 1, characterized in that the supply duct (15) has a conical end section (33), and in that the throttle (30) adjoins the conical end section (33).
  3. Fuel pump according to either of Claims 1 and 2, characterized in that the supply duct (15) has an axis (17), and in that the throttle (30) is aligned with the axis (17) of the supply duct (15).
  4. Fuel pump according to one of Claims 1 to 3, characterized in that the throttle (30) is in the form of a throttle bore.
  5. Fuel pump according to one of Claims 1 to 4, characterized in that the connecting duct (19) is in the form of an unthrottled connecting duct (19).
  6. Fuel pump according to one of Claims 1 to 5, characterized in that the supply duct (15) is in the form of a supply bore which extends in sections through a supply connector (4).
  7. Fuel pump according to one of Claims 1 to 6, characterized in that the supply duct (15), the throttle (30) and the connecting duct (19) are formed in a housing part (9) of a high-pressure pump (3).
  8. Fuel pump according to one of Claims 1 to 5, characterized in that the throttle (30) and the connecting duct (19) are integrated into a housing part (7) of a low-pressure pump (2), and/or in that the housing part (7) of the low-pressure pump (2) is in the form of a housing (7) of the external gear pump (2).
EP09801210.7A 2009-02-18 2009-12-22 Fuel pump Active EP2399031B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009000945A DE102009000945A1 (en) 2009-02-18 2009-02-18 fuel pump
PCT/EP2009/067745 WO2010094366A1 (en) 2009-02-18 2009-12-22 Fuel pump

Publications (2)

Publication Number Publication Date
EP2399031A1 EP2399031A1 (en) 2011-12-28
EP2399031B1 true EP2399031B1 (en) 2015-08-05

Family

ID=41632302

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09801210.7A Active EP2399031B1 (en) 2009-02-18 2009-12-22 Fuel pump

Country Status (4)

Country Link
EP (1) EP2399031B1 (en)
CN (1) CN102325997B (en)
DE (1) DE102009000945A1 (en)
WO (1) WO2010094366A1 (en)

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19719265A1 (en) * 1997-05-07 1998-11-12 Deutz Ag Internal combustion engine with fuel pump in the crankcase
DE19736160A1 (en) 1997-08-20 1999-02-25 Bosch Gmbh Robert High pressure fuel pump for IC engine in common rail systems
JP2001214829A (en) * 2000-01-31 2001-08-10 Bosch Automotive Systems Corp Fuel injection pump
JP3861835B2 (en) * 2003-03-31 2006-12-27 株式会社デンソー Fuel injection pump
DE10357612A1 (en) * 2003-12-10 2005-07-07 Robert Bosch Gmbh Valve arrangement, in particular inlet valve of a high-pressure fuel pump
DE102004037132A1 (en) * 2004-07-30 2006-03-23 Robert Bosch Gmbh High-pressure line inside fuel injectors and suchlike has sections in which flow direction is reversed and in these sections has recirculation areas connected to flow restriction of determined width

Also Published As

Publication number Publication date
CN102325997B (en) 2015-05-20
CN102325997A (en) 2012-01-18
WO2010094366A1 (en) 2010-08-26
DE102009000945A1 (en) 2010-08-19
EP2399031A1 (en) 2011-12-28

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