EP1119704B1 - Pump arrangement for providing fuel at high pressure - Google Patents

Pump arrangement for providing fuel at high pressure Download PDF

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Publication number
EP1119704B1
EP1119704B1 EP99936424A EP99936424A EP1119704B1 EP 1119704 B1 EP1119704 B1 EP 1119704B1 EP 99936424 A EP99936424 A EP 99936424A EP 99936424 A EP99936424 A EP 99936424A EP 1119704 B1 EP1119704 B1 EP 1119704B1
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EP
European Patent Office
Prior art keywords
pump
pressure
valve
fuel
pressure pump
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.)
Expired - Lifetime
Application number
EP99936424A
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German (de)
French (fr)
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EP1119704A1 (en
Inventor
Gerhard Geyer
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Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1119704A1 publication Critical patent/EP1119704A1/en
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Publication of EP1119704B1 publication Critical patent/EP1119704B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing
    • F04B49/246—Bypassing by keeping open the outlet valve

Definitions

  • the invention relates to a pump arrangement according to the Genus of claim 1.
  • the pump arrangement according to the invention with the features of Claim 1 has the advantage that the High-pressure pump in the "zero delivery" operating state Fuel delivers because the differential pressure valve from Leakage current of the flow control valve is not overcome.
  • the suction valves of the high pressure pump can open what a very low opening pressure can be set again the even filling of the pump elements with Ensures fuel in the "partial filling" operating state. Opening pressure tolerances and changes over the service life suction valves set in this way have only a small number Influence on the equal delivery of the pump elements.
  • An embodiment of the invention is in the drawing based on a hydraulic circuit diagram for a pump arrangement schematically simplified for high-pressure fuel generation shown and in the following description explained.
  • the pump arrangement shown for High pressure fuel generation is for one in Fuel injection system used in internal combustion engines, in particular common rail injection system.
  • the Pump arrangement has a low-pressure pump 1, which on the suction side of a diesel fuel, for example containing fuel tank 2 is connected. Of the Low-pressure pump 1 goes to a delivery line 3 on the pressure side off, in which downstream one on Flow control valve 4 and a differential pressure valve 5 arranged are. Between the flow control valve 4 and the Differential pressure valve 5 goes from the delivery line 3 to Return tank 6 leading fuel tank 2 out. In the Return line 6, a throttle 7 is arranged.
  • the pump assembly also includes a high pressure pump 10 with three pump elements 11. These each have one Pump piston 12 and a to a displacement space 13 of the Pump element 11 connected suction valve 14 and Pressure valve 15 on.
  • the on a cam ring 16 by spring force supported pump pistons 12 are from an eccentric shaft 17 drivable, which like the low pressure pump 1 with the Internal combustion engine, not shown, is coupled.
  • the Delivery line 3 is on the downstream side Differential pressure valve 5 following branching to the Suction valves 14 of the pump elements 11 connected.
  • Of the Pressure valves 15 of the pump elements 11 go line branches a high-pressure fuel line 18, which leads to a High pressure fuel reservoir, not shown Fuel injection system leads.
  • the low pressure pump 1 and the high pressure pump 10 of the pump arrangement are each through Pressure relief valves, not shown, before overload protected.
  • the low pressure pump 1 from the fuel tank 2 Intake fuel is used by the Proportional solenoid valve designed flow control valve 4 quantified and by the open Differential pressure valve 5 delivered to the high pressure pump 10. This raises the pressure of the fuel delivered relatively high pressure level and gives this through the High-pressure fuel line 18 into the fuel accumulator, on the fuel injectors of the internal combustion engine are connected. A small part of the flow of the Low pressure pump 1 passes through the flow control valve 4 the throttled return line 6 back into the Fuel tank 2.
  • the fuel consumption of the Internal combustion dependent delivery of the high pressure pump 10 is set as with the flow control valve 4 Flow control referred to as suction throttling.
  • the low pressure pump 1 and the are of the type High pressure pump 10 constant pumps.
  • the suction valves 14 of the pump elements 11 of the high pressure pump 10 are, as shown schematically in simplified form, as unloaded check valve. Deviating from the representation of the suction valves 14 also as spring-loaded check valves. Essential to the invention, however, is that the suction valves 14 have a very low opening pressure.
  • the differential pressure valve 5 in the Delivery line 3 has an opening pressure that is greater than that of the suction valves 14.
  • the upstream of the Differential pressure valve 5 arranged in the delivery line 3 Flow control valve 4 is designed and has a slide type consequently, in its closed position, a fuel leakage flow, which after the flow control valve in the throttled return line 6 is derived without that Switch differential pressure valve to its open position.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Pumpenanordnung nach der Gattung des Patentanspruchs 1.The invention relates to a pump arrangement according to the Genus of claim 1.

Es ist schon eine solche Pumpenanordnung bekannt (DE 195 49 108 A1), bei welcher das Stromregelventil in seiner den Förderstrom zur Hochdruckpumpe absperrenden Stellung den von der Niederdruckpumpe herangeführten Kraftstoff zum Kraftstoffbehälter absteuert. Ein in Schieberbauart ausgebildetes Stromregelventil hat bauartbedingt einen mehr oder weniger großen Leckstrom. Im Betriebszustand "Nullförderung" der Hochdruckpumpe soll jedoch das Ansaugen des Leckstroms durch eines oder mehrere der Pumpenelemente der Hochdruckpumpe vermieden werden. Dies erfordert das Einstellen der Saugventile der Hochdruckpumpe auf einen relativ hohen Öffnungsdruck mit der nachteiligen Folge, daß im Betriebszustand "Teilfüllung" Öffnungsdruckund Durchflußtoleranzen eine ungleichmäßige Füllung der Pumpenelemente und damit eine ungleichförmige Förderung der Hochdruckpumpe bewirken. Unterschiedliches Verschleißverhalten der Saugventile über die Lebensdauer der Pumpe kann zu einer weiteren Verschlechterung der Gleichförderung führen. Such a pump arrangement is already known (DE 195 49 108 A1), in which the flow control valve in its shutting off the flow to the high pressure pump Position brought up by the low pressure pump Fuel to the fuel tank. An in Flow control valve designed slide valve type a more or less large leakage current due to the design. in the Operating state "zero delivery" of the high pressure pump should however, the leakage current is drawn in by one or more the pump elements of the high pressure pump can be avoided. This requires the suction valves of the high pressure pump to be set to a relatively high opening pressure with the disadvantageous Consequence that in the operating state "partial filling" opening pressure and Flow tolerances an uneven filling of the Pump elements and thus a non-uniform promotion of Effect high pressure pump. different Wear behavior of the suction valves over the life of the Pump can further worsen the Lead equal promotion.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Pumpenanordnung mit den Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß die Hochdruckpumpe im Betriebszustand "Null-Förderung" keinen Kraftstoff fördert, weil das Differenzdruckventil vom Leckstrom des Stromregelventils nicht überwunden wird. Demzufolge können die Saugventile der Hochdruckpumpe auf einen sehr niedrigen Öffnungsdruck eingestellt werden, was wiederum die gleichmäßige Füllung der Pumpenelemente mit Kraftstoff im Betriebszustand "Teilfüllung" sicherstellt. Öffnungsdrucktoleranzen und -änderungen über die Lebensdauer derart eingestellter Saugventile haben nur einen geringen Einfluß auf die Gleichförderung der Pumpenelemente.The pump arrangement according to the invention with the features of Claim 1 has the advantage that the High-pressure pump in the "zero delivery" operating state Fuel delivers because the differential pressure valve from Leakage current of the flow control valve is not overcome. As a result, the suction valves of the high pressure pump can open what a very low opening pressure can be set again the even filling of the pump elements with Ensures fuel in the "partial filling" operating state. Opening pressure tolerances and changes over the service life suction valves set in this way have only a small number Influence on the equal delivery of the pump elements.

Eine vorteilhafte Weiterbildung der erfindungsgemäßen Pumpenanordnung ist im Anspruch 2 angegeben.An advantageous development of the invention Pump arrangement is specified in claim 2.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung anhand eines Hydraulikschaltplans für eine Pumpenanordnung zur Kraftstoffhochdruckerzeugung schematisch vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert.An embodiment of the invention is in the drawing based on a hydraulic circuit diagram for a pump arrangement schematically simplified for high-pressure fuel generation shown and in the following description explained.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Die dargestellte Pumpenanordnung zur Kraftstoffhochdruckerzeugung ist für ein in Brennkraftmaschinen eingesetztes Kraftstoffeinspritzsystem, insbesondere Common-Rail-Einspritzsystem, bestimmt. Die Pumpenanordnung weist eine Niederdruckpumpe 1 auf, welche saugseitig an einen beispielsweise Dieselkraftstoff enthaltenden Kraftstoffbehälter 2 angeschlossen ist. Von der Niederdruckpumpe 1 geht druckseitig eine Förderleitung 3 aus, in welcher stromabwärts aufeinanderfolgend ein Stromregelventil 4 und ein Differenzdruckventil 5 angeordnet sind. Zwischen dem Stromregelventil 4 und dem Differenzdruckventil 5 geht von der Förderleitung 3 eine zum Kraftstoffbehälter 2 führende Rücklaufleitung 6 aus. In der Rücklaufleitung 6 ist eine Drossel 7 angeordnet.The pump arrangement shown for High pressure fuel generation is for one in Fuel injection system used in internal combustion engines, in particular common rail injection system. The Pump arrangement has a low-pressure pump 1, which on the suction side of a diesel fuel, for example containing fuel tank 2 is connected. Of the Low-pressure pump 1 goes to a delivery line 3 on the pressure side off, in which downstream one on Flow control valve 4 and a differential pressure valve 5 arranged are. Between the flow control valve 4 and the Differential pressure valve 5 goes from the delivery line 3 to Return tank 6 leading fuel tank 2 out. In the Return line 6, a throttle 7 is arranged.

Zu der Pumpenanordnung gehört außerdem eine Hochdruckpumpe 10 mit drei Pumpenelementen 11. Diese weisen jeweils einen Pumpenkolben 12 und ein an einen Verdrängerraum 13 des Pumpenelements 11 angeschlossenes Saugventil 14 und Druckventil 15 auf. Die an einem Hubring 16 durch Federkraft abgestützten Pumpenkolben 12 sind von einer Exzenterwelle 17 antreibbar, welche ebenso wie die Niederdruckpumpe 1 mit der nicht dargestellten Brennkraftmaschine gekoppelt ist. Die Förderleitung 3 ist nach einer abströmseitig auf das Differenzdruckventil 5 folgenden Verzweigung an die Saugventile 14 der Pumpenelemente 11 angeschlossen. Von den Druckventilen 15 der Pumpenelemente 11 gehen Leitungszweige einer Kraftstoffhochdruckleitung 18 aus, welche zu einem nicht dargestellten Kraftstoffhochdruckspeicher des Kraftstoffeinspritzsystems führt. Die Niederdruckpumpe 1 und die Hochdruckpumpe 10 der Pumpenanordnung sind jeweils durch nicht dargestellte Druckbegrenzungsventile vor Überlastung geschützt.The pump assembly also includes a high pressure pump 10 with three pump elements 11. These each have one Pump piston 12 and a to a displacement space 13 of the Pump element 11 connected suction valve 14 and Pressure valve 15 on. The on a cam ring 16 by spring force supported pump pistons 12 are from an eccentric shaft 17 drivable, which like the low pressure pump 1 with the Internal combustion engine, not shown, is coupled. The Delivery line 3 is on the downstream side Differential pressure valve 5 following branching to the Suction valves 14 of the pump elements 11 connected. Of the Pressure valves 15 of the pump elements 11 go line branches a high-pressure fuel line 18, which leads to a High pressure fuel reservoir, not shown Fuel injection system leads. The low pressure pump 1 and the high pressure pump 10 of the pump arrangement are each through Pressure relief valves, not shown, before overload protected.

Der von der Niederdruckpumpe 1 aus dem Kraftstoffbehälter 2 angesaugte Kraftstoff wird von dem als Proportionalmagnetventil ausgebildeten Stromregelventil 4 mengenmäßig bemessen und durch das geöffnete Differenzdruckventil 5 an die Hochdruckpumpe 10 abgegeben. Diese hebt den Druck des geförderten Kraftstoffes auf ein relativ hohes Druckniveau an und gibt diesen durch die Kraftstoffhochdruckleitung 18 in den Kraftstoffspeicher ab, an den Kraftstoffinjektoren der Brennkraftmaschine angeschlossen sind. Ein geringer Teil des Förderstroms der Niederdruckpumpe 1 gelangt nach dem Stromregelventil 4 durch die gedrosselte Rücklaufleitung 6 zurück in den Kraftstoffbehälter 2. Die vom Kraftstoffbedarf der Brennkraftmaschine abhängige Förderung der Hochdruckpumpe 10 wird als mit dem Stromregelventil 4 eingestellte Mengenregelung durch Saugdrosselung bezeichnet.The low pressure pump 1 from the fuel tank 2 Intake fuel is used by the Proportional solenoid valve designed flow control valve 4 quantified and by the open Differential pressure valve 5 delivered to the high pressure pump 10. This raises the pressure of the fuel delivered relatively high pressure level and gives this through the High-pressure fuel line 18 into the fuel accumulator, on the fuel injectors of the internal combustion engine are connected. A small part of the flow of the Low pressure pump 1 passes through the flow control valve 4 the throttled return line 6 back into the Fuel tank 2. The fuel consumption of the Internal combustion dependent delivery of the high pressure pump 10 is set as with the flow control valve 4 Flow control referred to as suction throttling.

Von der Bauart her sind die Niederdruckpumpe 1 und die Hochdruckpumpe 10 Konstantpumpen.The low pressure pump 1 and the are of the type High pressure pump 10 constant pumps.

Die Saugventile 14 der Pumpenelemente 11 der Hochdruckpumpe 10 sind, wie schematisch vereinfacht dargestellt, als unbelastetes Rückschlagventil ausgebildet. Abweichend von der Darstellung können die Saugventile 14 auch als federbelastete Rückschlagventile ausgebildet sein. Erfindungswesentlich ist jedoch, daß die Saugventile 14 auf einen sehr niedrigen Öffnungsdruck eingestellt sind. Demgegenüber hat das Differenzdruckventil 5 in der Förderleitung 3 einen Öffnungsdruck, der größer ist als derjenige der Saugventile 14. Das stromaufwärts des Differenzdruckventils 5 in der Förderleitung 3 angeordnete Stromregelventil 4 ist in Schieberbauart ausgeführt und hat demzufolge in seiner Schließstellung einen Kraftstoff-Leckstrom, welcher nach dem Stromregelventil in die gedrosselte Rücklaufleitung 6 abgeleitet wird, ohne das Differenzdruckventil in seine Durchlaßstellung zu schalten.The suction valves 14 of the pump elements 11 of the high pressure pump 10 are, as shown schematically in simplified form, as unloaded check valve. Deviating from the representation of the suction valves 14 also as spring-loaded check valves. Essential to the invention, however, is that the suction valves 14 have a very low opening pressure. In contrast, the differential pressure valve 5 in the Delivery line 3 has an opening pressure that is greater than that of the suction valves 14. The upstream of the Differential pressure valve 5 arranged in the delivery line 3 Flow control valve 4 is designed and has a slide type consequently, in its closed position, a fuel leakage flow, which after the flow control valve in the throttled return line 6 is derived without that Switch differential pressure valve to its open position.

In der Sperrstellung des Stromregelventils 4 wird daher mittels des Differenzdruckventils 5 sichergestellt, daß die Pumpenelemente 11 keinen Kraftstoff ansaugen können und die Hochdruckpumpe 10 im Betriebszustand "Null-Förderung" arbeitet. Für einen Betriebszustand "Teil-Förderung" wird mittels des Stromregelventils 4 ein Kraftstoff-Förderstrom eingestellt, dessen Druck das Differenzdruckventil 5 umschaltet, so daß die Pumpenelemente 11 Kraftstoff ansaugen und in die Kraftstoffhochdruckleitung 18 abgeben können. Dabei ist durch den niedrigen Öffnungsdruck der Saugventile 14 eine gleichmäßige Füllung der Pumpenelemente 11 erzielt. Mit der Gleichförderung der Pumpenelemente 11 werden Druckschwankungen im Kraftstoffhochdruckbehälter weitgehend vermieden.In the locked position of the flow control valve 4 is therefore by means of the differential pressure valve 5 ensures that the Pump elements 11 can not draw fuel and the High pressure pump 10 in the "zero delivery" operating state is working. For an operating state "partial funding" will a fuel delivery flow by means of the flow control valve 4 set, the pressure of the differential pressure valve 5 switches so that the pump elements 11 suck in fuel and can deliver into the high-pressure fuel line 18. This is due to the low opening pressure of the suction valves 14 achieves a uniform filling of the pump elements 11. With the same promotion of the pump elements 11 Pressure fluctuations in the high-pressure fuel tank largely avoided.

Claims (2)

  1. Pump arrangement for producing fuel at high pressure for a fuel injection system used in internal combustion engines, in particular a common-rail injection system, having a low-pressure pump (1) which sucks up fuel from a fuel tank (2), having a high-pressure pump (10) with a plurality of pump elements (11), having a feed line (3) which leads from the low-pressure pump (1) to the high-pressure pump (10) and to which a suction valve (14) of the respective pump element (11) is connected, having a flow-regulating valve (4) of slide-type construction in the feed line (3), and having a return line (6) which is connected on the output side of the flow-regulating valve (4), characterized in that the return line (6) is connected between the flow-regulating valve (4) and the high-pressure pump (10) to the feed line (3), and in that a differential pressure valve (5) is arranged in the feed line (3) between the connection of the return line (6) and the suction valves (14) of the high-pressure pump (10), the opening pressure of which differential pressure valve is greater than that of the suction valves (14).
  2. Pump arrangement according to Claim 1, characterized in that the suction valve (14) of the pump elements (11) is an unloaded or spring-loaded nonreturn valve.
EP99936424A 1998-10-07 1999-06-08 Pump arrangement for providing fuel at high pressure Expired - Lifetime EP1119704B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19846157A DE19846157A1 (en) 1998-10-07 1998-10-07 Pump arrangement for high-pressure fuel generation
DE19846157 1998-10-07
PCT/DE1999/001664 WO2000020753A1 (en) 1998-10-07 1999-06-08 Pump arrangement for providing fuel at high pressure

Publications (2)

Publication Number Publication Date
EP1119704A1 EP1119704A1 (en) 2001-08-01
EP1119704B1 true EP1119704B1 (en) 2002-12-18

Family

ID=7883677

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99936424A Expired - Lifetime EP1119704B1 (en) 1998-10-07 1999-06-08 Pump arrangement for providing fuel at high pressure

Country Status (5)

Country Link
US (1) US6581577B1 (en)
EP (1) EP1119704B1 (en)
JP (1) JP2002526716A (en)
DE (2) DE19846157A1 (en)
WO (1) WO2000020753A1 (en)

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DE19954695A1 (en) * 1999-11-13 2001-05-23 Bosch Gmbh Robert Fuel injection system
IT1310753B1 (en) * 1999-11-30 2002-02-22 Elasis Sistema Ricerca Fiat CAPACITY ADJUSTMENT SYSTEM OF A HIGH PRESSURE PUMP FOR THE FUEL SUPPLY TO AN INJECTION ENGINE.
JP2001221118A (en) * 2000-02-07 2001-08-17 Bosch Automotive Systems Corp Fuel injection device
DE10057244A1 (en) * 2000-11-18 2002-06-06 Bosch Gmbh Robert Fuel injection system for internal combustion engines with improved starting behavior
DE10100700C1 (en) * 2001-01-10 2002-08-01 Bosch Gmbh Robert Fuel injection system with pressure control in the return line
DE10139054C1 (en) * 2001-08-08 2003-01-30 Bosch Gmbh Robert Operating method for direct fuel injection engine has controlled inlet valve with variable opening duration controlling fuel quantity supplied to common-rail for fuel injection valves
DE10154133C1 (en) * 2001-11-03 2003-02-13 Bosch Gmbh Robert Common-rail fuel system for IC engine has fuel fed from between fuel metering device and high pressure fuel pump fed to low pressure region with pressure reduction device
JP2005299683A (en) * 2001-11-27 2005-10-27 Bosch Corp Liquid flow control valve and needle anchor
DE10205187A1 (en) * 2002-02-08 2003-08-21 Bosch Gmbh Robert Fuel injection device for an internal combustion engine
DE10218022A1 (en) 2002-04-23 2003-11-06 Bosch Gmbh Robert Fuel injection device for an internal combustion engine
DE10237586A1 (en) * 2002-08-16 2004-02-26 Robert Bosch Gmbh Fuel injection installation for IC engine, such as diesel engine with high pressure pump for fuel delivery to buffer container, whose piston is driven from engine camshaft
US6755625B2 (en) * 2002-10-07 2004-06-29 Robert H. Breeden Inlet throttle valve
DE10247564A1 (en) * 2002-10-11 2004-04-22 Robert Bosch Gmbh Operating common rail fuel injection system for combustion engine involves driving pressure regulating valve if fuel quantity less than threshold so defined leakage occurs at pressure regulating valve
US20040101420A1 (en) * 2002-11-18 2004-05-27 Breeden Robert H. Solenoid regulated pump assembly
JP2005188432A (en) * 2003-12-26 2005-07-14 Bosch Automotive Systems Corp Fuel supply device
DE602004005051T2 (en) * 2004-11-12 2007-11-22 C.R.F. S.C.P.A. High-pressure pump with a device for controlling the flow for a fuel injection system
ATE491885T1 (en) * 2004-12-23 2011-01-15 Fiat Ricerche FUEL INJECTION DEVICE WITH VARIABLE FLOW HIGH PRESSURE FUEL PUMP
DE102005033638A1 (en) * 2005-07-19 2007-01-25 Robert Bosch Gmbh Fuel conveyor, in particular for an internal combustion engine
CN1786457B (en) * 2005-09-19 2011-06-22 童维友 Preset high pressure distributing type fuel oil injecting pump
DE602006017981D1 (en) * 2006-06-09 2010-12-16 Fiat Ricerche Fuel injection device for an internal combustion engine
DE102006037174A1 (en) * 2006-08-09 2008-02-14 Robert Bosch Gmbh Apparatus and method for controlling a fuel flow rate in a low pressure circuit system for an internal combustion engine
DE102010043439A1 (en) * 2010-11-05 2012-05-10 Robert Bosch Gmbh Fuel injection system of an internal combustion engine
JP5664539B2 (en) * 2011-12-21 2015-02-04 株式会社デンソー Control device for fuel supply system
DE102012107764A1 (en) 2012-08-23 2014-04-10 Kendrion (Villingen) Gmbh Common Rail System

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DE3310049A1 (en) * 1983-03-19 1984-09-20 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION DEVICE FOR INJECTING A FUEL MIXTURE MADE OF AT LEAST TWO COMPONENTS
CN1082143C (en) * 1993-11-08 2002-04-03 Crt公共铁路技术公司 Control device for a variable volume pump
DE19549108A1 (en) * 1995-12-29 1997-07-03 Bosch Gmbh Robert High-pressure fuel generation system for a fuel injection system used in internal combustion engines
DE19612412B4 (en) * 1996-03-28 2006-07-06 Siemens Ag Control for a pressurized fluid supply system, in particular for the high pressure in a fuel injection system
DE19630938C5 (en) * 1996-07-31 2008-02-14 Siemens Ag Fuel supply with a flow control valve and flow control valve

Also Published As

Publication number Publication date
DE59903863D1 (en) 2003-01-30
EP1119704A1 (en) 2001-08-01
DE19846157A1 (en) 2000-04-13
WO2000020753A1 (en) 2000-04-13
JP2002526716A (en) 2002-08-20
US6581577B1 (en) 2003-06-24

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