[go: up one dir, main page]
More Web Proxy on the site http://driver.im/

EP0657642B1 - Fuel injection device for internal combustion engines - Google Patents

Fuel injection device for internal combustion engines Download PDF

Info

Publication number
EP0657642B1
EP0657642B1 EP94113010A EP94113010A EP0657642B1 EP 0657642 B1 EP0657642 B1 EP 0657642B1 EP 94113010 A EP94113010 A EP 94113010A EP 94113010 A EP94113010 A EP 94113010A EP 0657642 B1 EP0657642 B1 EP 0657642B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
space
injection
injection device
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
EP94113010A
Other languages
German (de)
French (fr)
Other versions
EP0657642A2 (en
EP0657642A3 (en
Inventor
Peter Dipl.-Ing. Müller
Jaroslaw Dipl.-Ing. Hlousek
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
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0657642A2 publication Critical patent/EP0657642A2/en
Publication of EP0657642A3 publication Critical patent/EP0657642A3/en
Application granted granted Critical
Publication of EP0657642B1 publication Critical patent/EP0657642B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0007—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using electrically actuated valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the invention relates to a fuel injection device for Internal combustion engines according to the preamble of claim 1.
  • a fuel injection device known from DE-OS 37 00 687 a high pressure fuel pump delivers fuel from a Low-pressure room in a high-pressure plenum that is connected to high-pressure lines with the individual, in the combustion chamber of the to be supplied Internal combustion engine projecting injection valves is connected, wherein this common pressure storage system by a pressure control device is kept at a certain pressure.
  • a pressure control device is kept at a certain pressure.
  • To control the Injection times and injection quantities at the injection valves is on These each have an electrically controlled control valve in the high pressure lines used that with its opening and closing the High-pressure fuel injection on the injection valve controls.
  • the known fuel injection device has the disadvantage that it is very expensive to construct and also for the defined limitation of the stroke movements of the valve member additional stroke stop surfaces are provided.
  • the fuel injection device according to the invention with the characteristic Features of claim 1 contributes to simplification of the entire injector. This will be advantageous simply with a double seat valve electrically controlled control valve reached, the respective Stroke is formed by a valve seat and that the pressure application surfaces of the same size on the valve member in both stroke directions in the open and closed state is pressure balanced, so that the actuating forces of the valve member actuating solenoid valve only the force of a return spring have to overcome.
  • Another advantage is the through hole in the piston Valve element of the control valve reached, via which the under high Fuel under pressure during the injection breaks from the High pressure area within the control valve in a relief chamber flows out and via which a constant pressure equalization on both valve member faces, or the rooms adjacent to it.
  • An injection pressure curve with a slight increase in pressure at the beginning and to achieve a high injection pressure at the end is the volume of the pressure storage spaces 5 assigned to the injection valves up to 20 times larger than the maximum injection quantity at the injection valve executed, the one at the injection valve at the start of injection reflected fuel pressure in the pressure reservoir for a pressure increase is used to a value above the system pressure.
  • This Pressure increase can be done by dimensioning the high pressure line and a pressure valve in the inlet adjustable Adjust the afterflow into the pressure accumulator in such a way that towards the end of injection the highest fuel pressure is built up in the system.
  • a flow restrictor inserted into the pressure connection of the pressure accumulator prevents the pressure fluctuations from propagating into the system.
  • FIG. 1 shows a schematic illustration of the fuel injection device with a longitudinal section through the control valve and the injection valve and Figure 2 shows the design of the valve seats and sealing surfaces of the control valve in an enlarged section from FIG. 1.
  • FIG. 1 In the fuel injection device shown in FIG. 1 is a high-pressure fuel pump 1 on the suction side via a fuel supply line 3 with a fuel-filled low-pressure chamber 5 and on the pressure side via a delivery line 7 with a high-pressure plenum 9 connected, the output of High-pressure fuel pump 1 from an electrical control unit 11 is controllable.
  • High-pressure lines 13 lead from the high-pressure collecting space 9 to the individual, protruding into the combustion chamber of the internal combustion engine to be supplied Injection valves 15, whereby to control the injection process one electric control valve 17 on each injection valve 15 is inserted into the respective high pressure line 13.
  • each high-pressure line 13 there is between the high-pressure plenum 9 and control valve 17, a further pressure storage space 19 is provided, whose volume is about 5 to 20 times larger than the maximum Injection quantity at injection valve 15 per injection process is and the one via two parallel pressure connections with that to the high-pressure plenum 9 leading part of the high pressure line 13 is connected.
  • first pressure connection 21 in the direction of the pressure storage space 19 opening pressure valve 23 and designed as a check valve a second pressure port 25 to a throttle point 27, wherein about the throttle 27 an uncontrolled backflow of fuel in the part of the high-pressure line 13 leading to the high-pressure collecting space 9 and influencing the pressure in the pressure storage spaces of the remaining injectors should be avoided while the pressure valve 23 enables rapid refilling of the pressure storage space 19.
  • It can be about the design of the throttle 27 and Pressure valve 23 depending on the dimensioning of the high pressure line 13 the inflow and outflow quantity into the pressure storage space 19 adjust especially during high pressure injection, whereby Throttle 27 and pressure valve 23 also in a common pressure connection, can be arranged in series.
  • the control valve 17 is designed as a 3/2 way valve, the piston-shaped Valve member 29 from one to its one end face one between the housing 31 and a spring plate 33 on Valve member 29 supporting compression spring 35 acting electrical Actuating magnet 37 is actuated, the current supply from the control unit 11 is controlled.
  • the valve member 29 has one on its shaft Ring web 39, the lower one facing away from the actuating magnet 37 Transition surface to the piston skirt is conical and there forms a first conical sealing surface 41 on the valve member 29, which with a conical valve seat 43 cooperates.
  • This in Figure 2 enlarged conical valve seat 43 is by a conical diameter expansion of a, a guide piston part 45 on the valve member 29 receiving guide bore 49 within the housing 31 of the control valve 17 is formed.
  • the stroke movement of the valve member 29 is in each case by contact the sealing surfaces 41, 55 limited to one of the valve seats 43, 59.
  • the ring web 39 is in one of the respective valve seats 43, 59 limited, an anteroom 65 forming an annular space from which a pressure line 67 to the injection valve 15 and a relief channel 69 lead away.
  • This relief channel 69 is partially through a remaining annular gap between the piston skirt and the bore 57 formed in the intermediate piece 61, with its outer diameter formed smaller than the sealing surface 55 and so of this is lockable.
  • the bore 57 opens into the as a return spring acting compression spring 35 of the valve member 29 receiving Spring chamber 63 and is, an axial through bore 71 in the valve member 29 intersecting transverse bores 73 with one of which Setting magnet 37 facing away from the end face of the guide piston 45 of the Valve member 29 connected relief space 75.
  • This inside the relief bore 75 formed in the guide bore 49 axially in a direction away from the control magnet 37 in a spring chamber 77 of the injection valve 15, in which a valve member 79 of the injection valve 15 acting in the closing direction valve spring 81 is arranged and of which a return line 83 in discharges the low pressure chamber 5.
  • the valve member 79 of the injection valve 15 is known Way with a conical pressure shoulder 85, which in one with the pressure line 67 connected pressure chamber 87 protrudes such that the pressure in the pressure chamber 87 acts on the valve member 79 in the opening direction.
  • An injection channel 89 also leads from the pressure chamber 87 along valve member 79 to one or more of the sealing surface at the tip of the valve member 79 controlled injection openings 91 of the injection valve 15 in the not shown Combustion chamber of the internal combustion engine to be supplied.
  • the fuel injection device according to the invention works in the following Wise.
  • the high-pressure fuel pump 1 delivers the fuel from the Low pressure chamber 5 in the high pressure collection chamber 9 and builds in this high fuel pressure, which is controlled by the high pressure pump 1 is adjustable. This high fuel pressure takes over the high pressure lines 13 into the pressure chamber 51 of the individual Control valves 17 on the injection valves 15 and fills also the respective pressure storage spaces 19 via the pressure valves 23.
  • the Actuator 37 energizes and shifts the valve member 29 of the control valve 17 against the restoring force of the spring 35 to the system its flat valve sealing surface 55 to the flat valve seat 59 the connection of the anteroom 65 to the relief channel 69 is closed and opened to the pressure line 67, so that the High fuel pressure now from the pressure chamber 51 via the vestibule 65 and the Pressure line 67 continues to the pressure chamber 87 of the injection valve 15 and there about the lifting of the valve member 79 from its valve seat The injection takes place at the injection openings 91 in a known manner.
  • the actuating magnet 37 is activated again switched off and the compression spring 35 brings this even in the open Condition due to the ring shoulder 53 pressure-balanced valve member 29 of the control valve 17 again in contact with the conical valve seat 43.
  • the opening cross section at the flat valve seat 59 is opened and the high pressure fuel relaxes via the relief channel 69, the spring chamber 63, the transverse and longitudinal bores 73, 71 in valve member 29 in the relief chamber 75, from where the fuel via the spring chamber 77 and the return line 83 flows into the low pressure chamber 5, so that the valve member 79 of the injection valve 15 is depressurized under Action of the valve spring 81 goes into the closed position and the valve member 29 is pressure balanced again.

Landscapes

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

Description

Stand der TechnikState of the art

Die Erfindung geht von einer Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1 aus. Bei einer solchen aus der DE-OS 37 00 687 bekannten Kraftstoffeinspritzeinrichtung fördert eine Kraftstoffhochdruckpumpe Kraftstoff aus einem Niederdruckraum in einen Hochdrucksammelraum, der über Hochdruckleitungen mit den einzelnen, in den Brennraum der zu versorgenden Brennkraftmaschine ragenden Einspritzventilen verbunden ist, wobei dieses gemeinsame Druckspeichersystem durch eine Drucksteuereinrichtung auf einem bestimmten Druck gehalten wird. Zur Steuerung der Einspritzzeiten und Einspritzmengen an den Einspritzventilen, ist an diesen jeweils ein elektrisch gesteuertes Steuerventil in die Hochdruckleitungen eingesetzt, das mit seinem Öffnen und Schließen die Kraftstoffhochdruckeinspritzung am Einspritzventil steuert.The invention relates to a fuel injection device for Internal combustion engines according to the preamble of claim 1. At such a fuel injection device known from DE-OS 37 00 687 a high pressure fuel pump delivers fuel from a Low-pressure room in a high-pressure plenum that is connected to high-pressure lines with the individual, in the combustion chamber of the to be supplied Internal combustion engine projecting injection valves is connected, wherein this common pressure storage system by a pressure control device is kept at a certain pressure. To control the Injection times and injection quantities at the injection valves is on These each have an electrically controlled control valve in the high pressure lines used that with its opening and closing the High-pressure fuel injection on the injection valve controls.

Dabei ist bei der bekannten Kraftstoffeinspritzeinrichtung an jedem Einspritzventil ein weiterer Druckspeicherraum vorgesehen, der vom gemeinsamen Druckspeichersystem gefüllt wird und der neben der vom Hochdrucksammelraum abführenden Hochdruckleitung ebenfalls mit dem Einspritzventil verbunden ist. Durch diese Aufteilung des Speichervolumens an jedem Einspritzventil auf zwei Druckräume, die durch eine Leitung bestimmter Länge miteinander verbunden sind, kann dort in Verbindung mit einem gedrosselten Abströmen von Kraftstoff aus einem auf das Ventilglied des Einspritzventils wirkenden Druckraum der Einspritzverlauf den Erfordernissen der jeweiligen Brennkraftmaschine optimal angepaßt werden, wobei insbesondere ein langsamer Druckanstieg am Beginn und ein hoher Druckanstieg zum Ende der Einspritzung erreichbar ist. Die direkt aus dem gemeinsamen Hochdrucksammelraum dem Einspritzventil zugeführte Kraftstoffmenge wird dabei lediglich als Steuermittel zur Steuerung der Hubbewegung des Ventilgliedes des Einspritzventiles verwendet, während die Einspritzmenge vollständig dem jeweiligen kleineren Druckspeicherraum entnommen wird. It is in the known fuel injection device on everyone Injection valve another pressure storage space provided by the common pressure storage system is filled and in addition to that of High-pressure line discharging high-pressure line also with the Injector is connected. By dividing the storage volume on each injection valve to two pressure chambers, which are separated by a Line of a certain length can be connected there Connection with a throttled outflow of fuel from a pressure chamber acting on the valve member of the injection valve Injection course the requirements of the respective internal combustion engine can be optimally adapted, in particular a slow rise in pressure at the beginning and a high pressure increase at the end of the injection is achievable. The directly from the common high-pressure collection room The amount of fuel supplied to the injector is only as control means for controlling the stroke movement of the valve member of the injector used while the injection quantity completely removed from the respective smaller pressure storage space becomes.

Aus der Schrift FR-A-2 449 795 ist desweiteren eine Kraftstoffeinspritzeinrichtung bekannt, bei der das Steuerventil am Einspritzventil die Verbindung des weiteren Druckspeicherraumes mit einem, das Ventilglied des Einspritzventils in öffnungsrichtung beaufschlagenden Druckraum innerhalb des Einspritzventils während der Einspritzpausen verschließen kann. Dabei steuert dieses Steuerventil während der Einspritzpausen am zu versorgenden Einspritzventil eine Verbindung des Druckraumes des Einspritzventils mit einem Entlastungsraum auf und entlastet so den Druckraum des Einspritzventilgliedes von dem hohen im Druckspeicherraum befindlichen Kraftstoffdruck.From the document FR-A-2 449 795 there is also a fuel injection device known, in which the control valve on the injection valve the connection of the further pressure storage space with one, the valve member of the injection valve in the opening direction pressurizing pressure chamber during the injection valve during the injection breaks can close. This controls Control valve during the injection breaks on the injection valve to be supplied a connection of the pressure chamber of the injection valve with a relief chamber and thus relieves the pressure chamber of the injection valve member from the high one in the pressure storage space fuel pressure.

Dabei weist die bekannte Kraftstoffeinspritzeinrichtung jedoch den Nachteil auf, daß sie konstruktiv sehr aufwendig baut und zudem zur definierten Begrenzung der Hubbewegungen des Ventilgliedes zusätzliche Hubanschlagflächen vorgesehen sind. However, the known fuel injection device has the disadvantage that it is very expensive to construct and also for the defined limitation of the stroke movements of the valve member additional stroke stop surfaces are provided.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzeinrichtung mit den kennzeichnenden Merkmalen des Patentanspruchs 1 trägt zu einer Vereinfachung der gesamten Einspritzeinrichtung bei. Dies wird dabei in vorteilhaft einfacher Weise mit einem als Doppelsitzventil ausgebildeten elektrisch angesteuerten Steuerventil erreicht, dessen jeweiliger Hubanschlag durch einen Ventilsitz gebildet ist und das durch die jeweils gleich groß dimensionierten Druckangriffsflächen am Ventilglied in beiden Hubrichtungen in geöffnetem und geschlossenem Zustand druckausgeglichen ist, so daß die Stellkräfte des das Ventilglied betätigenden Magnetventils lediglich die Kraft einer Rückstellfeder überwinden müssen.The fuel injection device according to the invention with the characteristic Features of claim 1 contributes to simplification of the entire injector. This will be advantageous simply with a double seat valve electrically controlled control valve reached, the respective Stroke is formed by a valve seat and that the pressure application surfaces of the same size on the valve member in both stroke directions in the open and closed state is pressure balanced, so that the actuating forces of the valve member actuating solenoid valve only the force of a return spring have to overcome.

Ein weiterer Vorteil wird durch die Durchgangsbohrung im kolbenförmigen Ventilglied des Steuerventils erreicht, über die der unter hohem Druck stehende Kraftstoff während der Einspritzpausen aus dem Hochdruckbereich innerhalb des Steuerventils in einen Entlastungsraum abströmt und über die ständig ein Druckausgleich an beiden Ventilgliedstirnseiten, bzw. der an diese angrenzenden Räume erfolgt. Um einen Einspritzdruckverlauf mit zu Beginn geringem Druckanstieg und zum Ende hin einem hohen Einspritzdruck zu erreichen ist das Volumen der den Einspritzventilen zugeordneten Druckspeicherräume 5 bis 20 mal größer als die maximale Einspritzmenge am Einspritzventil ausgeführt, wobei der am Einspritzventil am Beginn der Einspritzung reflektierte Kraftstoffdruck im Druckspeicherraum für eine Druckerhöhung auf einen Wert oberhalb des Systemdrucks genutzt wird. Diese Drucküberhöhung läßt sich dabei über das durch die Dimensionierung der Hochdruckleitung und ein Druckventil im Zulauf einstellbare Nachströmen in den Druckspeicher derart abstimmen, daß gegen Einspritzende der höchste Kraftstoffdruck im System aufgebaut ist. Eine in den Druckanschluß des Druckspeichers eingesetzte Strömungsdrossel vermeidet dabei eine Fortpflanzung der Druckschwankungen in das System.Another advantage is the through hole in the piston Valve element of the control valve reached, via which the under high Fuel under pressure during the injection breaks from the High pressure area within the control valve in a relief chamber flows out and via which a constant pressure equalization on both valve member faces, or the rooms adjacent to it. An injection pressure curve with a slight increase in pressure at the beginning and to achieve a high injection pressure at the end is the volume of the pressure storage spaces 5 assigned to the injection valves up to 20 times larger than the maximum injection quantity at the injection valve executed, the one at the injection valve at the start of injection reflected fuel pressure in the pressure reservoir for a pressure increase is used to a value above the system pressure. This Pressure increase can be done by dimensioning the high pressure line and a pressure valve in the inlet adjustable Adjust the afterflow into the pressure accumulator in such a way that towards the end of injection the highest fuel pressure is built up in the system. A flow restrictor inserted into the pressure connection of the pressure accumulator prevents the pressure fluctuations from propagating into the system.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Beschreibung, der Zeichnung und den Ansprüchen entnehmbar.Further advantages and advantageous configurations of the object the invention are the description, the drawing and the claims removable.

Zeichnungdrawing

Ein Ausführungsbeispiel der erfindungsgemäßen Kraftstoffeinspritzeinrichtung ist in der Zeichnung dargestellt und wird in der nachfolgenden Beschreibung näher erläutert.An embodiment of the fuel injection device according to the invention is shown in the drawing and is shown in the following Description explained in more detail.

Es zeigen die Figur 1 eine schematische Darstellung der Kraftstoffeinspritzeinrichtung mit einem Längsschnitt durch das Steuerventil und das Einspritzventil und die Figur 2 die Ausbildung der Ventilsitze und Dichtflächen des Steuerventils in einem vergrößerten Ausschnitt aus der Figur 1.FIG. 1 shows a schematic illustration of the fuel injection device with a longitudinal section through the control valve and the injection valve and Figure 2 shows the design of the valve seats and sealing surfaces of the control valve in an enlarged section from FIG. 1.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Bei der in der Figur 1 dargestellten Kraftstoffeinspritzeinrichtung ist eine Kraftstoffhochdruckpumpe 1 saugseitig über eine Kraftstoffzuführungsleitung 3 mit einem kraftstoffgefüllten Niederdruckraum 5 und druckseitig über eine Förderleitung 7 mit einem Hochdrucksammelraum 9 verbunden, wobei die Fördermenge der Kraftstoffhochdruckpumpe 1 von einem elektrischen Steuergerät 11 steuerbar ist.In the fuel injection device shown in FIG. 1 is a high-pressure fuel pump 1 on the suction side via a fuel supply line 3 with a fuel-filled low-pressure chamber 5 and on the pressure side via a delivery line 7 with a high-pressure plenum 9 connected, the output of High-pressure fuel pump 1 from an electrical control unit 11 is controllable.

Vom Hochdrucksammelraum 9 führen Hochdruckleitungen 13 zu den einzelnen, in den Brennraum der zu versorgenden Brennkraftmaschine ragenden Einspritzventilen 15 ab, wobei zur Steuerung des Einspritzvorganges jeweils ein elektrisches Steuerventil 17 an jedem Einspritzventil 15 in die jeweilige Hochdruckleitung 13 eingesetzt ist.High-pressure lines 13 lead from the high-pressure collecting space 9 to the individual, protruding into the combustion chamber of the internal combustion engine to be supplied Injection valves 15, whereby to control the injection process one electric control valve 17 on each injection valve 15 is inserted into the respective high pressure line 13.

Des weiteren ist in jeder Hochdruckleitung 13 zwischen Hochdrucksammelraum 9 und Steuerventil 17 ein weiterer Druckspeicherraum 19 vorgesehen, dessen Volumen in etwa 5 bis 20 mal größer als die maximale Einspritzmenge am Einspritzventil 15 pro Einspritzvorgang ist und der über zwei parallele Druckanschlüsse mit dem zum Hochdrucksammelraum 9 führenden Teil der Hochdruckleitung 13 verbunden ist. Dabei weist ein erster Druckanschluß 21 ein in Richtung Druckspeicherraum 19 öffnendes, als Rückschlagventil ausgebildetes Druckventil 23 und ein zweiter Druckanschluß 25 eine Drosselstelle 27 auf, wobei über die Drossel 27 ein unkontrolliertes Rückströmen von Kraftstoff in den zum Hochdrucksammelraum 9 führenden Teil der Hochdruckleitung 13 und eine Beeinflussung des Druckes in den Druckspeicherräumen der übrigen Einspritzventile vermieden werden soll, während das Druckventil 23 ein rasches Nachfüllen des Druckspeicherraumes 19 ermöglicht. Dabei lassen sich über die Auslegung der Drossel 27 und des Druckventils 23 in Abhängigkeit von der Dimensionierung der Hochdruckleitung 13 die Zu- und Ablaufmenge in den Druckspeicherraum 19 insbesondere während der Hochdruckeinspritzung einstellen, wobei Drossel 27 und Druckventil 23 auch in einem gemeinsamen Druckanschluß, in Reihe geschaltet angeordnet sein können.Furthermore, in each high-pressure line 13 there is between the high-pressure plenum 9 and control valve 17, a further pressure storage space 19 is provided, whose volume is about 5 to 20 times larger than the maximum Injection quantity at injection valve 15 per injection process is and the one via two parallel pressure connections with that to the high-pressure plenum 9 leading part of the high pressure line 13 is connected. Here has a first pressure connection 21 in the direction of the pressure storage space 19 opening pressure valve 23 and designed as a check valve a second pressure port 25 to a throttle point 27, wherein about the throttle 27 an uncontrolled backflow of fuel in the part of the high-pressure line 13 leading to the high-pressure collecting space 9 and influencing the pressure in the pressure storage spaces of the remaining injectors should be avoided while the pressure valve 23 enables rapid refilling of the pressure storage space 19. It can be about the design of the throttle 27 and Pressure valve 23 depending on the dimensioning of the high pressure line 13 the inflow and outflow quantity into the pressure storage space 19 adjust especially during high pressure injection, whereby Throttle 27 and pressure valve 23 also in a common pressure connection, can be arranged in series.

Das Steuerventil 17 ist als 3/2 Wegeventil ausgeführt, dessen kolbenförmiges Ventilglied 29 von einem auf seine eine Stirnseite entgegen einer sich zwischen Gehäuse 31 und einem Federteller 33 am Ventilglied 29 abstützenden Druckfeder 35 wirkenden elektrischen Stellmagneten 37 betätigt wird, dessen Bestromung vom Steuergerät 11 gesteuert wird. Dabei weist das Ventilglied 29 an seinem Schaft einen Ringsteg 39 auf, dessen untere dem Stellmagneten 37 abgewandte Übergangsfläche zum Kolbenschaft konisch ausgeführt ist und dabei eine erste konische Dichtfläche 41 am Ventilglied 29 bildet, die mit einem konischen Ventilsitz 43 zusammenwirkt. Dieser in der Figur 2 vergrößert dargestellte konische Ventilsitz 43 ist dabei durch eine konische Durchmessererweiterung einer, einen Führungskolbenteil 45 am Ventilglied 29 aufnehmenden Führungsbohrung 49 innerhalb des Gehäuses 31 des Steuerventils 17 gebildet. Dabei ist zwischen dem das Ventilglied 29 auf der stellmagnetabgewandten Seite begrenzenden Führungskolbenteil 45 und der konischen Ventildichtfläche 41 eine Ringnut 47 am Ventilglied 29 vorgesehen, die mit der Wand der Führungsbohrung 49 einen Druckraum 51 bildet, der vom Führungskolbenteil 45 und der konischen Ventildichtfläche 41 am Ringsteg 39 begrenzt wird und in den ein vom Druckspeicherraum 19 abführender Teil der Hochdruckleitung 13 zum Steuerventil 17 derart mündet, daß die Mündung während der Hubbewegung des Ventilgliedes 29 nicht durch das Ventilglied 29 verschließbar ist.The control valve 17 is designed as a 3/2 way valve, the piston-shaped Valve member 29 from one to its one end face one between the housing 31 and a spring plate 33 on Valve member 29 supporting compression spring 35 acting electrical Actuating magnet 37 is actuated, the current supply from the control unit 11 is controlled. The valve member 29 has one on its shaft Ring web 39, the lower one facing away from the actuating magnet 37 Transition surface to the piston skirt is conical and there forms a first conical sealing surface 41 on the valve member 29, which with a conical valve seat 43 cooperates. This in Figure 2 enlarged conical valve seat 43 is by a conical diameter expansion of a, a guide piston part 45 on the valve member 29 receiving guide bore 49 within the housing 31 of the control valve 17 is formed. It is between that Limit valve member 29 on the side remote from the solenoid Guide piston part 45 and the conical valve sealing surface 41 a Annular groove 47 is provided on the valve member 29, which with the wall of the guide bore 49 forms a pressure chamber 51, which is from the guide piston part 45 and the conical valve sealing surface 41 on the ring web 39 limited and into a part of the pressure storage space 19 leading away the high pressure line 13 to the control valve 17 opens such that the Mouth during the lifting movement of the valve member 29 not through the Valve member 29 is closable.

Der dem Stellmagneten 37 zugewandte Übergang vom Ringsteg 39 zum Kolbenschaft erfolgt über einen Ringabsatz 53, wobei die entstandene axial gerichtete Ringfläche am Ringabsatz 53 dabei eine zweite flache Dichtfläche 55 bildet, die mit einem eine Bohrung 57 umgebenden Flachventilsitz 59 an der axialen Stirnseite eines Zwischenstückes 61 zusammenwirkt, wobei der Kolbenschaft durch die Bohrung 57 zum Stellmagneten 37 weiterführt und dabei mit seinem Ende in einen die Druckfeder 35 des Ventilgliedes 29 aufnehmenden Federaum 63 ragt. Der Außendurchmesser des die flache axiale Dichtfläche 55 tragenden Ringabsatzes 53 am Ringsteg 39 ist dabei für einen Druckausgleich am geöffneten Steuerventil 17 gleich groß dem Durchmesser des Führungskolbenteils 45.The transition from the ring web 39 to the actuating magnet 37 Piston shaft takes place via a ring shoulder 53, the resulting one axially directed ring surface on the ring shoulder 53 a second flat Sealing surface 55 forms that with a surrounding a bore 57 Flat valve seat 59 on the axial end face of an intermediate piece 61 cooperates, the piston skirt through the bore 57 to Solenoid 37 continues and with its end in one Compression spring 35 of the valve member 29 receiving spring space 63 protrudes. The outer diameter of the bearing the flat axial sealing surface 55 Ring shoulder 53 on the ring web 39 is for a pressure equalization on open control valve 17 the same size as the diameter of the guide piston part 45.

Die Hubbewegung des Ventilgliedes 29 ist dabei jeweils durch Anlage der Dichtflächen 41, 55 an einem der Ventilsitze 43, 59 begrenzt. Der Ringsteg 39 ist in einem von den jeweiligen Ventilsitzen 43, 59 begrenzten, einen Vorraum 65 bildenden Ringraum angeordnet, von dem eine Druckleitung 67 zum Einspritzventil 15 und ein Entlastungskanal 69 abführen. Dieser Entlastungskanal 69 wird dabei zum Teil durch einen verbleibenden Ringspalt zwischen dem Kolbenschaft und der Bohrung 57 im Zwischenstück 61 gebildet, der mit seinem äußeren Durchmesser kleiner als die Dichtfläche 55 ausgebildet und so von dieser verschließbar ist. Die Bohrung 57 mündet dabei in den die als Rückstellfeder wirkende Druckfeder 35 des Ventilgliedes 29 aufnehmenden Federraum 63 und ist über, eine axiale Durchgangsbohrung 71 im Ventilglied 29 schneidende Querbohrungen 73 mit einem, von der dem Stellmagneten 37 abgewandten Stirnseite des Führungskolbens 45 des Ventilgliedes 29 begrenzten Entlastungsraum 75 verbunden. Dieser innerhalb der Führungsbohrung 49 gebildete Entlastungsraum 75 setzt sich axial in vom Stellmagnet 37 abgewandter Richtung in einen Federraum 77 des Einspritzventils 15 fort, in dem eine ein Ventilglied 79 des Einspritzventils 15 in Schließrichtung beaufschlagende Ventilfeder 81 angeordnet ist und von dem eine Rücklaufleitung 83 in den Niederdruckraum 5 abführt.The stroke movement of the valve member 29 is in each case by contact the sealing surfaces 41, 55 limited to one of the valve seats 43, 59. The ring web 39 is in one of the respective valve seats 43, 59 limited, an anteroom 65 forming an annular space from which a pressure line 67 to the injection valve 15 and a relief channel 69 lead away. This relief channel 69 is partially through a remaining annular gap between the piston skirt and the bore 57 formed in the intermediate piece 61, with its outer diameter formed smaller than the sealing surface 55 and so of this is lockable. The bore 57 opens into the as a return spring acting compression spring 35 of the valve member 29 receiving Spring chamber 63 and is, an axial through bore 71 in the valve member 29 intersecting transverse bores 73 with one of which Setting magnet 37 facing away from the end face of the guide piston 45 of the Valve member 29 connected relief space 75. This inside the relief bore 75 formed in the guide bore 49 axially in a direction away from the control magnet 37 in a spring chamber 77 of the injection valve 15, in which a valve member 79 of the injection valve 15 acting in the closing direction valve spring 81 is arranged and of which a return line 83 in discharges the low pressure chamber 5.

Dabei ist das Ventilglied 79 des Einspritzventils 15 in bekannter Weise mit einer konischen Druckschulter 85 versehen, die in einen mit der Druckleitung 67 verbundenen Druckraum 87 derart ragt, daß der Druck im Druckraum 87 das Ventilglied 79 in Öffnungsrichtung beaufschlagt. Vom Druckraum 87 führt desweiteren ein Einspritzkanal 89 entlang des Ventilgliedes 79 zu einer oder mehreren von der Dichtfläche an der Spitze des Ventilgliedes 79 gesteuerten Einspritzöffnungen 91 des Einspritzventils 15 in den nicht näher dargestellten Brennraum der zu versorgenden Brennkraftmaschine.The valve member 79 of the injection valve 15 is known Way with a conical pressure shoulder 85, which in one with the pressure line 67 connected pressure chamber 87 protrudes such that the pressure in the pressure chamber 87 acts on the valve member 79 in the opening direction. An injection channel 89 also leads from the pressure chamber 87 along valve member 79 to one or more of the sealing surface at the tip of the valve member 79 controlled injection openings 91 of the injection valve 15 in the not shown Combustion chamber of the internal combustion engine to be supplied.

Die erfindungsgemäße Kraftstoffeinspritzeinrichtung arbeitet in folgender Weise.The fuel injection device according to the invention works in the following Wise.

Die Kraftstoffhochdruckpumpe 1 fördert den Kraftstoff aus dem Niederdruckraum 5 in den Hochdrucksammelraum 9 und baut so in diesem einen Kraftstoffhochdruck auf, der über die Steuerung der Hochdruckpumpe 1 einstellbar ist. Dieser Kraftstoffhochdruck setzt sich über die Hochdruckleitungen 13 bis in den Druckraum 51 der einzelnen Steuerventile 17 an den Einspritzventilen 15 fort und befüllt dabei auch die jeweiligen Druckspeicherräume 19 über die Druckventile 23.The high-pressure fuel pump 1 delivers the fuel from the Low pressure chamber 5 in the high pressure collection chamber 9 and builds in this high fuel pressure, which is controlled by the high pressure pump 1 is adjustable. This high fuel pressure takes over the high pressure lines 13 into the pressure chamber 51 of the individual Control valves 17 on the injection valves 15 and fills also the respective pressure storage spaces 19 via the pressure valves 23.

Im Ruhezustand, also bei geschlossenem Einspritzventil 15 ist der Stellmagnet 37 am Steuerventil 17 stromlos geschaltet, so daß die Druckfeder 35 das Ventilglied 29 über den Federteller 33 mit der konischen Dichtfläche 41 in Anlage am konischen Ventilsitz 43 hält, so daß die Verbindung zwischen dem unter Kraftstoffhochdruck stehenden Druckraum 51 und dem ständig mit der Druckleitung 67 zum Einspritzventil 15 verbundenen Vorraum 65 verschlossen und die Verbindung vom Vorraum 65 in den Entlastungskanal 69 geöffnet ist.In the idle state, that is, with the injector 15 closed Solenoid 37 on the control valve 17 is de-energized so that the Compression spring 35, the valve member 29 via the spring plate 33 with the conical Sealing surface 41 in contact with the conical valve seat 43 holds, so that the connection between the high fuel pressure Pressure chamber 51 and that constantly with the pressure line 67 to the injection valve 15 connected vestibule 65 closed and the connection from Anteroom 65 in the relief channel 69 is open.

Soll eine Einspritzung am Einspritzventil 15 erfolgen, wird der Stellmagnet 37 bestromt und verschiebt das Ventilglied 29 des Steuerventils 17 entgegen der Rückstellkraft der Feder 35 bis zur Anlage seiner flachen Ventildichtfläche 55 an den Flachventilsitz 59. Dabei wird die Verbindung des Vorraumes 65 zum Entlastungskanal 69 verschlossen und zur Druckleitung 67 aufgesteuert, so daß sich der Kraftstoffhochdruck nun vom Druckraum 51 über den Vorraum 65 und die Druckleitung 67 zum Druckraum 87 des Einspritzventils 15 fortsetzt und dort über das Abheben des Ventilgliedes 79 von seinem Ventilsitz in bekannter Weise die Einspritzung an den Einspritzöffnungen 91 erfolgt.If an injection is to take place at the injection valve 15, the Actuator 37 energizes and shifts the valve member 29 of the control valve 17 against the restoring force of the spring 35 to the system its flat valve sealing surface 55 to the flat valve seat 59 the connection of the anteroom 65 to the relief channel 69 is closed and opened to the pressure line 67, so that the High fuel pressure now from the pressure chamber 51 via the vestibule 65 and the Pressure line 67 continues to the pressure chamber 87 of the injection valve 15 and there about the lifting of the valve member 79 from its valve seat The injection takes place at the injection openings 91 in a known manner.

Dabei läßt sich in der Druckleitung 67 während der Einspritzphase eine Drucküberhöhung über den Systemdruck in folgender Weise erreichen. Durch die Verschiebung des Ventilgliedes 29 wird der Druckraum 51 mit dem Vorraum 65 verbunden und es setzt eine Strömung in Richtung Querbohrung 73 und Durchgangsbohrung 71 bis hin zur drucklosen Rücklaufleitung 83 ein. Diese Strömung verursacht in weiterer Folge eine Strömung in der Leitungsverbindung vom Druckspeicherraum 19 zum Druckraum 51 und in der Leitung 13 zwischen Druckspeicherraum 19 und Hochdrucksammelraum 9.It can be in the pressure line 67 during the injection phase achieve a pressure increase above the system pressure in the following way. By moving the valve member 29, the pressure chamber 51 connected to the vestibule 65 and it sets a flow in the direction Cross bore 73 and through bore 71 up to the unpressurized Return line 83 a. This flow caused in Another consequence is a flow in the line connection from the pressure storage space 19 to the pressure chamber 51 and in line 13 between Pressure accumulator 19 and high pressure accumulator 9.

Bei Beendigung des Öffnungshubes des Ventilgliedes 29 durch Anlage der Dichtfläche 55 am Ventilsitz 59 wird der Kraftstoffluß in Richtung Druckleitung 67 gelenkt. Durch den Staueffekt der in Bewegung befindlichen Kraftstoffströmung entsteht dort eine Drucküberhöhung. Diese Drucküberhöhung ist durch geeignete Wahl der Einflußgrößen Leitungslänge, Leitungsdurchmesser, Speichervolumen, Drosselquerschnitt usw. beeinflußbar.At the end of the opening stroke of the valve member 29 by contact the sealing surface 55 on the valve seat 59, the fuel flow in the direction Pressure line 67 directed. Due to the traffic jam effect in motion existing fuel flow there is a pressure increase. This pressure increase is due to a suitable choice of the influencing variables Line length, line diameter, storage volume, throttle cross-section etc. can be influenced.

Zudem läßt sich infolge der Umsetzung der Strömungsenergie eine Druckerhöhung des Einspritzdruckes über den Wert des Systemdruckes erreichen, indem die zum Einspritzventil 15 laufende Kraftstoffdruckwelle zum Teil am Einspritzventil reflektiert wird, zum Druckspeicher 19 zurückläuft und in diesem eine Druckerhöhung bewirkt, die sich durch die Strömungsenergie des vom Hochdrucksammelraum 9 nachströmenden Kraftstoffes und die Dimensionierung der Drossel 27, die einen schnellen Druckabbau verhindert, einstellen läßt. Dieser erhöhte Kraftstoffdruck gelangt dann erneut zum Einspritzventil 15 und erhöht dessen Einspritzrate gegen Ende der Einspritzung. Der Einspritzverlauf am Einspritzventil 15 läßt sich zudem über den Öffnungsquerschnitt am Ventilglied 29 (Durchmesser/Hub), das Volumen des Vorraumes 65 und der Druckleitung 67 sowie das Volumen des Druckspeichers 19 formen.In addition, due to the implementation of the flow energy Pressure increase of the injection pressure above the value of the system pressure achieve by the fuel pressure wave running to the injection valve 15 partly reflected at the injection valve, to the pressure accumulator 19 runs back and causes a pressure increase in this, which is caused by the flow energy of the high-pressure plenum 9 inflowing fuel and the dimensioning of the throttle 27, which prevents rapid pressure reduction, can be adjusted. This the increased fuel pressure then reaches the injection valve 15 again and increases its injection rate towards the end of the injection. Of the Injection course at the injection valve 15 can also be over the opening cross section on the valve member 29 (diameter / stroke), the volume of the vestibule 65 and the pressure line 67 and the volume of the Form the accumulator 19.

Soll die Einspritzung beendet werden, wird der Stellmagnet 37 erneut stromlos geschaltet und die Druckfeder 35 bringt das auch in geöffnetem Zustand durch den Ringabsatz 53 druckausgeglichene Ventilglied 29 des Steuerventils 17 wieder in Anlage an den konischen Ventilsitz 43. Dabei wird der Öffnungsquerschnitt am Flachventilsitz 59 aufgesteuert und der unter hohem Druck stehende Kraftstoff entspannt sich über den Entlastungskanal 69, den Federraum 63, die Querund Längsbohrungen 73, 71 im Ventilglied 29 in den Entlastungsraum 75, von wo der Kraftstoff über den Federraum 77 und die Rücklaufleitung 83 in den Niederdruckraum 5 abströmt, so daß das Ventilglied 79 des Einspritzventils 15 druckentlastet unter Einwirkung der Ventilfeder 81 in Schließstellung geht und das Ventilglied 29 wieder druckausgeglichen ist. Dabei ist der Querschnitt des Entlastungskanals 69 so ausgelegt, daß er einerseits einen raschen Druckabfall in der Druckleitung 67 unter den Schließdruck des Einspritzventils 15 gewährleistet, andererseits jedoch das Abströmen aus der Druckleitung 67 so drosselt, daß während der Einspritzpausen ein Restdruck in der Druckleitung 67 und dem Einspritzventil 15 verbleibt.If the injection is to be ended, the actuating magnet 37 is activated again switched off and the compression spring 35 brings this even in the open Condition due to the ring shoulder 53 pressure-balanced valve member 29 of the control valve 17 again in contact with the conical valve seat 43. The opening cross section at the flat valve seat 59 is opened and the high pressure fuel relaxes via the relief channel 69, the spring chamber 63, the transverse and longitudinal bores 73, 71 in valve member 29 in the relief chamber 75, from where the fuel via the spring chamber 77 and the return line 83 flows into the low pressure chamber 5, so that the valve member 79 of the injection valve 15 is depressurized under Action of the valve spring 81 goes into the closed position and the valve member 29 is pressure balanced again. Here is the cross section of the relief channel 69 designed so that it has a rapid one hand Pressure drop in the pressure line 67 below the closing pressure of the Injector 15 ensures, but on the other hand, the outflow throttles from the pressure line 67 so that during the injection breaks a residual pressure remains in the pressure line 67 and the injection valve 15.

Um eine Beeinflussung der einzelnen Einspritzventile 15 untereinander durch die beim Einspritzende vom geschlossenen Steuerventil 17 rücklaufende Druckwelle zu vermeiden, ist das Volumen des Druckspeicherraumes 19 und der Querschnitt der Drossel 27 im als Rücklaufleitung dienenden Druckanschluß 25 so abzustimmen, daß die Druckspitzen innerhalb des Druckspeicherraumes 19 und zum Hochdrucksammelraum 9 abgebaut werden.To influence the individual injection valves 15 with one another by the closed control valve 17 at the end of injection Avoiding a returning pressure wave is the volume of the pressure storage space 19 and the cross section of the throttle 27 in the return line serve pressure port 25 so that the Pressure peaks within the pressure storage space 19 and to the high-pressure collection space 9 are dismantled.

Claims (12)

  1. Fuel injection device for internal combustion engines, with a fuel high-pressure pump (1) which conveys fuel out of a low-pressure space (5) into a high-pressure collecting space (9) which is connected, via high-pressure conduits (13), to injection valves (15) which project into the combustion space of the internal combustion engine to be supplied and the opening and closing movement of which is controlled in each case by an electrically activated control valve (17) arranged in the high-pressure conduit (13) on the injection valve (15) and having a piston-shaped valve member (29), and with, on each injection valve (15), a further pressure accumulator space (19) which is integrated into the high-pressure conduit (13) between the high-pressure collecting space (9) and the injection valve (15), during the injection intermissions the control valve (17) on the injection valve (15) closing the connection of the further pressure accumulator space (19) to a pressure space (87) located within the injection valve (15) and acting on the valve member (79) of the injection valve (15) in the opening direction, the control valve (17) opening a connection of the pressure space (87) of the injection valve (15) to a relief space (75) during the injection intermissions of the injection valve (15), characterized in that the piston-shaped valve member (29) has an annular web (39), of which one surface of transition to the valve-member shank of smaller diameter forms a first valve sealing surface (41) cooperating with a valve seat (43) and of which the other transition to the valve-member shank of smaller diameter takes place via an annular shoulder (53) which has adjoining it, facing away from the annular web (39), a guide-piston part (45) spaced from the annular web (39) and of which the axial annular end surface facing away from the annular web (39) forms a second valve sealing surface (55) which co-operates with a valve seat (59) fixed relative to the housing.
  2. Fuel injection device according to Claim 1, characterized in that the stroke movement of the valve member (29) of the control valve (17) is limited in each case by the bearing of the valve sealing surfaces (41, 55) on one of the valve seats (43, 59).
  3. Fuel injection device according to Claim 1, characterized in that the outside diameter of the annular shoulder (53) carrying the flat valve sealing surface (55) is equal to the diameter of a guide piston (45) of the valve member (29) in a guide bore (49), the said guide piston adjoining an annular groove (47) located on the valve member (29) and emanating from the conical valve sealing surface (41), and the said guide piston, at the same time, delimiting a pressure space (51) formed between the wall of the guide bore (49) and the valve member (29) in the region of the annular groove (47).
  4. Fuel injection device according to Claim 3, characterized in that the annular web (39) is arranged in a pre-space (65) constantly connected to a pressure conduit (67) leading to the pressure space (87) of the injection valve (15).
  5. Fuel injection device according to Claim 4, characterized in that the pressure space (51) in the region of the annular groove (47) of the valve member (29) is constantly connected to a part of the high-pressure conduit (13) which leads away from the pressure accumulator space (19).
  6. Fuel injection device according to Claims 4 and 5, characterized in that the connection between the pre-space (65) and the pressure space (51) can be closed by the bearing of the conical sealing surface (41) of the valve member (29) on the conical valve seat (43).
  7. Fuel injection device according to Claim 4, characterized in that, by designing the valve-member shank adjoining the flat valve sealing surface (55) so as to have a smaller diameter than a bore (57) receiving the said shank, a relief duct (69) is formed which connects the pre-space (65) to the relief space (75) when the flat-seat valve is open.
  8. Fuel injection device according to Claim 7, characterized in that the piston-shaped valve member (29) of the control valve (17) has an axial passage bore (71) and, in the region of the relief duct (69), transverse bores (73) which lead radially away from the said passage bore and via which the fuel flowing away from the pressure conduit (67) and the pre-space (65) when the flat-seat valve is open passes from the relief duct (69) into the relief space (75).
  9. Fuel injection device according to Claim 1, characterized in that the control valve (17) is designed as a 3/2-way solenoid valve which is activated by means of an electric control unit (11).
  10. Fuel injection device according to Claim 1, characterized in that the accumulator volume of the pressure accumulator space (19) is about 5 to 20 times larger than the maximum injection quantity on the injection valve (15).
  11. Fuel injection device according to Claim 1, characterized in that the pressure accumulator space (19) is connected, via two parallel pressure connections, to that part of the high-pressure conduit (13) which leads to the high-pressure collecting space (9), of which pressure connections a first (21) has a pressure valve (23), preferably a non-return valve, opening in the direction of the pressure accumulator space (19) and a second (25) has a throttle point (27).
  12. Fuel injection device according to Claim 1, characterized in that the pressure accumulator space (19) is connected, via one pressure connection, to that part of the high-pressure conduit (13) which leads to the high-pressure collecting space (9), the said pressure connection having a pressure valve, preferably a non-return valve, opening in the direction of the pressure accumulator space (19) and a throttle point connected in series with the said valve.
EP94113010A 1993-12-07 1994-08-20 Fuel injection device for internal combustion engines Expired - Lifetime EP0657642B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4341543 1993-12-07
DE4341543A DE4341543A1 (en) 1993-12-07 1993-12-07 Fuel injection device for internal combustion engines

Publications (3)

Publication Number Publication Date
EP0657642A2 EP0657642A2 (en) 1995-06-14
EP0657642A3 EP0657642A3 (en) 1995-12-06
EP0657642B1 true EP0657642B1 (en) 1999-01-13

Family

ID=6504295

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94113010A Expired - Lifetime EP0657642B1 (en) 1993-12-07 1994-08-20 Fuel injection device for internal combustion engines

Country Status (4)

Country Link
US (1) US5497750A (en)
EP (1) EP0657642B1 (en)
JP (1) JP3655938B2 (en)
DE (2) DE4341543A1 (en)

Families Citing this family (45)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5669355A (en) * 1994-07-29 1997-09-23 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
US5687693A (en) 1994-07-29 1997-11-18 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
US5526791A (en) * 1995-06-07 1996-06-18 Diesel Technology Company High-pressure electromagnetic fuel injector
DE19701879A1 (en) 1997-01-21 1998-07-23 Bosch Gmbh Robert Fuel injection device for internal combustion engines
DE19712135C1 (en) 1997-03-22 1998-08-13 Mtu Friedrichshafen Gmbh Fuel injection system for internal combustion engine
DE19715234A1 (en) * 1997-04-12 1998-06-25 Daimler Benz Ag Valve for fuel injection system of internal combustion engine
DE19720913C1 (en) * 1997-05-16 1998-08-20 Mtu Friedrichshafen Gmbh Diesel engine fuel injection system with common controller reservoir
DE19732070C2 (en) * 1997-07-25 2001-02-01 Daimler Chrysler Ag Direct-injection fuel injector with solenoid valve control for a multi-cylinder internal combustion engine
DE19742073A1 (en) 1997-09-24 1999-03-25 Bosch Gmbh Robert Fuel injection arrangement for internal combustion engines
DE19748999C2 (en) * 1997-11-06 2002-11-07 Daimler Chrysler Ag Solenoid valve controlled injector for a storage system of a multi-cylinder internal combustion engine
DE19753072C2 (en) * 1997-11-29 1999-11-18 Bosch Gmbh Robert Fuel supply system for an internal combustion engine, in particular of a motor vehicle
US6026785A (en) * 1998-05-08 2000-02-22 Caterpillar Inc. Hydraulically-actuated fuel injector with hydraulically assisted closure of needle valve
US6364282B1 (en) 1998-12-04 2002-04-02 Caterpillar Inc. Hydraulically actuated fuel injector with seated pin actuator
DE19859175A1 (en) * 1998-12-21 2000-06-29 Siemens Ag Fuel supply system venting method for diesel engine common rail systems
DE19860678A1 (en) * 1998-12-29 2000-07-06 Bosch Gmbh Robert Fuel injection device for internal combustion engines
DE19910970A1 (en) * 1999-03-12 2000-09-28 Bosch Gmbh Robert Fuel injector
DE19919665A1 (en) * 1999-04-29 2000-11-02 Volkswagen Ag Fuel injector
DE19928846A1 (en) * 1999-06-24 2001-03-08 Bosch Gmbh Robert Common rail injector
DE19928906A1 (en) * 1999-06-24 2001-01-11 Bosch Gmbh Robert Common rail injector
DE19939428A1 (en) * 1999-08-20 2001-03-01 Bosch Gmbh Robert Method and device for performing a fuel injection
DE19942990A1 (en) 1999-09-09 2001-03-22 Bosch Gmbh Robert Common rail injector
DE19951554A1 (en) * 1999-10-26 2001-05-10 Bosch Gmbh Robert Fuel injector with integrated flow limitation
DE10032923A1 (en) * 2000-07-06 2002-01-24 Bosch Gmbh Robert Fuel injection device for internal combustion engines
DE10046829C2 (en) * 2000-09-20 2003-01-09 Orange Gmbh Control valve for injection injectors of internal combustion engines
DE10054991A1 (en) 2000-11-07 2002-05-29 Bosch Gmbh Robert Pressure controlled injector for injecting fuel with double valve
DE10055268A1 (en) 2000-11-08 2002-05-23 Bosch Gmbh Robert Pressure controlled injector of a high pressure accumulator injection system
DE10055269B4 (en) * 2000-11-08 2005-10-27 Robert Bosch Gmbh Pressure-controlled injector with pressure boost
DE10056165C2 (en) 2000-11-13 2003-06-12 Bosch Gmbh Robert Sammelraumbeaufschlagter injector with a cascade control arrangement
DE10059124B4 (en) * 2000-11-29 2005-09-15 Robert Bosch Gmbh Pressure-controlled injector for injection systems with high-pressure collecting space
DE10059423A1 (en) 2000-11-30 2002-06-13 Bosch Gmbh Robert Device for conveying liquids, in particular fuel
DE10060811A1 (en) * 2000-12-07 2002-06-13 Bosch Gmbh Robert Fuel injection system for internal combustion engines
DE10060836C1 (en) * 2000-12-07 2002-07-25 Bosch Gmbh Robert Pressure-controlled CR injector with stepped opening and closing behavior
DE10105031A1 (en) * 2001-02-05 2002-08-14 Bosch Gmbh Robert Device for damping pressure pulsations in high-pressure injection systems
DE10114252C2 (en) * 2001-03-22 2003-01-30 Mtu Friedrichshafen Gmbh Method for injecting fuel into the combustion chambers of an internal combustion engine, and fuel injection system for such
DE10143423A1 (en) * 2001-09-05 2003-05-08 Bosch Gmbh Robert Fuel injection system with injector hydraulically decoupled from the supply line
DE10149868C1 (en) * 2001-10-10 2002-12-05 Orange Gmbh Fuel injector for diesel engine has fuel return line coupled to injection jet provided with high pressure region coupled to low pressure region via venting valve
DE10151955A1 (en) 2001-10-22 2003-05-08 Bosch Gmbh Robert Reduced-mass solenoid carrier
US7124746B2 (en) 2002-07-16 2006-10-24 Brocco Douglas S Method and apparatus for controlling a fuel injector
US7021565B2 (en) * 2004-02-10 2006-04-04 Caterpillar Inc. Pressure modulated common rail injector and system
EP1584815A1 (en) * 2004-04-05 2005-10-12 Tiby M. Martin Common rail fuel injector
ATE488690T1 (en) * 2005-07-18 2010-12-15 Ganser Hydromag STORAGE INJECTION SYSTEM FOR INTERNAL COMBUSTION ENGINE
ATE530761T1 (en) * 2007-09-13 2011-11-15 Ganser Hydromag FUEL INJECTION DEVICE
US20110297125A1 (en) * 2010-06-03 2011-12-08 Caterpillar Inc. Reverse Flow Check Valve For Common Rail Fuel System
CH712276B1 (en) * 2016-03-18 2020-03-13 Ganser Hydromag Accumulator injection system for internal combustion engines.
DE102021200154A1 (en) * 2021-01-11 2022-07-14 Robert Bosch Gesellschaft mit beschränkter Haftung fuel injector

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS51101628A (en) * 1975-01-24 1976-09-08 Diesel Kiki Co
GB2045347B (en) * 1979-02-24 1983-04-20 Huber Motorenbau Inst I c engine fuel injection system
US4360163A (en) * 1981-01-19 1982-11-23 General Motors Corporation Electromagnetic diesel fuel injector
JPS5939963A (en) * 1982-08-27 1984-03-05 Nippon Denso Co Ltd Fuel injector
JPS5941658A (en) * 1982-08-31 1984-03-07 Yanmar Diesel Engine Co Ltd Fuel injection unit
USRE33270E (en) * 1982-09-16 1990-07-24 Bkm, Inc. Pressure-controlled fuel injection for internal combustion engines
JPS6111447A (en) * 1984-06-27 1986-01-18 Nippon Denso Co Ltd Fuel injection valve
DE3788406T2 (en) * 1986-09-25 1994-04-14 Ganser Hydromag Zuerich Electronically controlled injection system.
JP2712760B2 (en) * 1990-05-29 1998-02-16 トヨタ自動車株式会社 Fuel injection valve
US5191867A (en) * 1991-10-11 1993-03-09 Caterpillar Inc. Hydraulically-actuated electronically-controlled unit injector fuel system having variable control of actuating fluid pressure
US5245970A (en) * 1992-09-04 1993-09-21 Navistar International Transportation Corp. Priming reservoir and volume compensation device for hydraulic unit injector fuel system

Also Published As

Publication number Publication date
US5497750A (en) 1996-03-12
EP0657642A2 (en) 1995-06-14
DE59407645D1 (en) 1999-02-25
EP0657642A3 (en) 1995-12-06
JP3655938B2 (en) 2005-06-02
JPH07189849A (en) 1995-07-28
DE4341543A1 (en) 1995-06-08

Similar Documents

Publication Publication Date Title
EP0657642B1 (en) Fuel injection device for internal combustion engines
DE4311627B4 (en) Fuel injection device for internal combustion engines
EP0898650B1 (en) Fuel injection device for internal combustion engines
EP1485609B1 (en) Device for injecting fuel to stationary internal combustion engines
EP0779949B1 (en) Fuel injection device for internal combustion engines
DE4332119A1 (en) Fuel injection device for internal combustion engines
DE4341546A1 (en) Fuel injection device for internal combustion engines
DE19910589C2 (en) Injection valve for an internal combustion engine
WO2002084106A1 (en) Valve for controlling liquids
WO2000019089A1 (en) Fuel injection valve for internal combustion engines
EP1910663B1 (en) Fuel injection device for an internal combustion engine using direct fuel injection
DE19634933B4 (en) Fuel injection valve for internal combustion engines
DE102009000181A1 (en) Fuel injector
DE102004024527A1 (en) Fuel injection system
EP1045975B1 (en) Control unit for controlling the build-up of pressure in a pump unit
EP2743493B1 (en) Fuel injector
EP2011995A2 (en) Injector with a valve element which opens to the outside
AT501914A4 (en) DEVICE FOR INJECTING FUEL IN THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE
DE10131642A1 (en) Fuel injector with variable control room pressurization
DE19623211A1 (en) Fuel injection valve for internal combustion engines
WO2008122521A1 (en) Valve and injection system for an internal combustion engine comprising a valve
DE29814934U1 (en) Fuel injection valve for internal combustion engines
DE102006050033A1 (en) Injector, in particular common rail injector
DE10160490B4 (en) Fuel injection device, fuel system and internal combustion engine
EP1415082A1 (en) Fuel injector having two-way valve control

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE FR GB IT

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE FR GB IT

17P Request for examination filed

Effective date: 19960607

17Q First examination report despatched

Effective date: 19971007

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

REF Corresponds to:

Ref document number: 59407645

Country of ref document: DE

Date of ref document: 19990225

ET Fr: translation filed
ITF It: translation for a ep patent filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19990318

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20071024

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20080826

Year of fee payment: 15

Ref country code: FR

Payment date: 20080818

Year of fee payment: 15

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20080822

Year of fee payment: 15

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090303

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20090820

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20100430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090820

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090820