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EP0171667B1 - Control valve for a fuel injection device - Google Patents

Control valve for a fuel injection device Download PDF

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Publication number
EP0171667B1
EP0171667B1 EP85109245A EP85109245A EP0171667B1 EP 0171667 B1 EP0171667 B1 EP 0171667B1 EP 85109245 A EP85109245 A EP 85109245A EP 85109245 A EP85109245 A EP 85109245A EP 0171667 B1 EP0171667 B1 EP 0171667B1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
chamber
low
pressure chamber
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
Application number
EP85109245A
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German (de)
French (fr)
Other versions
EP0171667A1 (en
Inventor
Reda R. Rizk
Hans-Gottfried Michels
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.)
Kloeckner Humboldt Deutz AG
Original Assignee
Kloeckner Humboldt Deutz AG
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Application filed by Kloeckner Humboldt Deutz AG filed Critical Kloeckner Humboldt Deutz AG
Priority to AT85109245T priority Critical patent/ATE41042T1/en
Publication of EP0171667A1 publication Critical patent/EP0171667A1/en
Application granted granted Critical
Publication of EP0171667B1 publication Critical patent/EP0171667B1/en
Expired 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves

Definitions

  • the invention relates to an electromagnetically actuated control valve for a high-pressure fuel injection device on an air-compressing, self-igniting internal combustion engine according to the preamble of claim 1.
  • a generic control valve for a fuel injector is such. B. from GB-A-2 041 577 or the subsequently published EP-A-0 114 375.
  • Such a control valve for a high-pressure fuel injection device is connected between a fuel injection pump and an injection nozzle.
  • the piston slide sliding in a housing space has a section designed as a seat valve, to which a corresponding valve seat in the housing of the control valve is assigned.
  • the valve seat separates a high pressure chamber from a low pressure chamber and is arranged in the flow connection between the two chambers.
  • the low pressure chamber is connected to a relief line, while the high pressure connection is connected to the pump chamber.
  • the seat valve In its closed position, the seat valve lies sealingly on the valve seat and blocks the flow connection between the high-pressure chamber and the low-pressure chamber.
  • the high pressure fuel in the high pressure chamber flows through a check valve to the injection nozzle.
  • the valve blocking the flow connection between the high-pressure chamber and the low-pressure chamber has to withstand considerable pressure loads. If the spool is accelerated from its open position - in which the high-pressure chamber is relieved via the low-pressure chamber - to its closed position, the poppet valve impinges at high speed on the valve seat assigned to it in the housing of the control valve. Due to the applicable impulse laws, the poppet valve lifts again after the first impact in order to hit the valve seat in the housing again. The consequence of this valve bounce is that the fuel pressure is built up only hesitantly at the beginning of an injection, since the high-pressure chamber and thus the injection nozzle are repeatedly relieved for a short time via the low-pressure chamber due to the valve bounce.
  • a control valve of similar construction is also known from FR-A-2 465 085.
  • the piston valve designed with a seat valve blocks the injection line to the injection nozzle in its closed position. Valve impacts will also occur during the closing process, which is why the end of injection cannot be precisely adjusted by uncontrolled spraying.
  • the invention has for its object to eliminate the valve bounce when increasing the service life of the control valve in order to enable precise control of the injection.
  • control valve With the control valve according to the invention, precise control of the start of injection is thus possible without pressure drops caused by valve impacts and, moreover, a control valve is created which, in addition to the precise control of the start of injection, also shows significantly longer service lives due to less wear.
  • the piston slide area on the low-pressure side is preferably smaller overall Diameter formed as the high-pressure piston spool area. This ensures that in the high pressure phase there is basically a resulting pressure force in the closing direction during an injection process. This includes the decisive advantage of the absolute tightness of the control valve in the high-pressure phase for the operating result, particularly in the case of the very high injection pressures of 1000 to 2000 bar which are aimed at in air-compressing, self-igniting internal combustion engines.
  • the valve seat of the valve housing space preferably has an undercut covering the piston slide in the closed position, as a result of which the space required in terms of production technology for machining the valve seat is created.
  • control valve according to the invention which in particular an improvement of the control valve with regard to z. B. low spool actuator forces, optimization of any z. B. to pressure discontinuities or pressure differences in pressure compensation lines to be attributed to disturbances on the control valve and representation of a closing pressure force acting on the spool.
  • the figure shows in section the control valve 1 according to the invention without its electromagnetic actuation devices.
  • This control valve 1 is intended to be used in a high-pressure fuel injection device by a multi-cylinder, self-igniting, air-compressing internal combustion engine.
  • the control valve 1 is associated with a fuel injection pump (not shown) which is driven via a cam and a spring-loaded tappet.
  • the control valve 1 is connected via the high-pressure connection 2 to the fuel injection pump, not shown.
  • the high pressure channel 3 leads to a fuel injector, not shown.
  • the high-pressure connection 2 and the high-pressure channel 3 leading to the fuel injection nozzle open into the valve housing space 7 into a high-pressure chamber 9, which in turn communicates via a flow connection with a low-pressure chamber 10 arranged in the valve housing space 7.
  • the low-pressure chamber 10 is to be depressurized into a fuel tank via a relief line 11.
  • the flow connection between the high-pressure chamber 9 and the low-pressure chamber 10 is controlled by a valve body designed as a spool 4, the high-pressure side spool area 5 of which is delimited by a seat edge 6.
  • the seat edge 6 interacts with a valve seat 8 incorporated in the valve housing space 6 and blocks the flow connection to the low-pressure chamber 10, so that in the closed position of the spool 4 via the high-pressure connection 2 entering fuel can flow via the high-pressure channel 3 to the fuel injection nozzle.
  • the high-pressure connection 2 in the open position of the spool 4 is connected to the relief line 11 leading into the fuel tank, so that the opening or closing of the control valve 1 in the high-pressure phase of the fuel injection pump
  • the start of injection or the end of injection is adjustable.
  • the piston slide is preferably acted upon by compression springs and actuated by an electromagnetic actuating device which is controlled by an electrically operating measured value processing device.
  • the electromagnetic actuating device acts on the end face of the low-pressure piston valve region 12 and a compression spring on the end surface of the high-pressure piston valve region 5.
  • EP-A-0 114 375 for the actuating device of the piston slide 4.
  • the movement stroke of the spool 4 is provided in the area of the valve housing space 7 on the high-pressure side.
  • the valve housing space 7 has between its valve seat 8 and the high-pressure connection or the high-pressure channel 3 a housing section 13 which is designed with the same diameter as the high-pressure side piston slide region 5.
  • the diameter of the valve housing-side housing section 13 is designed with a fit allowance such that the Axial movement of the spool 4 is not affected.
  • the piston valve region 12 on the low pressure side is overall smaller in diameter than the high pressure side piston slide area 5 formed.
  • the valve housing chamber 7 has a housing chamber end chamber 15 on the high pressure side and a housing chamber end chamber 16 on the low pressure side, which are respectively assigned to the end faces 14 (high pressure side) and 17 (low pressure side).
  • the housing chamber end chamber 15 on the high pressure side and the housing chamber end chamber 16 on the low pressure side are connected to one another via a bore 18 running within the piston slide 4.

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

Abstract

A control valve for a fuel injector, especially of an air-compressing, spontaneous-ignition, internal combustion engine. The control valve includes a valve body in the form of a piston valve which is axially movable in a housing chamber into a closure position and an open position, with the closure position being determined by a valve seat on the housing, and a seating surface edge on the piston valve. The housing chamber includes at least one high pressure connection, and a low pressure connection. The basic problem with a control valve of this general type is that when the piston valve strikes the valve seat, rebound movements are carried out by the piston valve, so that the closure position can only be reliably assumed after a certain time delay, thus negatively influencing the injection process. In order to avoid these drawbacks, it is possible to have the valve housing chamber, either between its valve seat and the high pressure connection on the one hand, as well as the high-pressure side of the piston valve adjacent the seating surface edge on the other hand, or between its valve seat and the low pressure connection on the one hand as well as the low-pressure side of the piston valve adjacent the seating surface edge, each being provided with a portion having the same diameter. Alternatively, an attenuation mass, especially an attenuation piston element, can be provided on and/or within the piston valve, with this attenuation mass being movable relative to the piston valve.

Description

Die Erfindung bezieht sich auf ein elektromagnetisch betätigtes Steuerventil für eine Hochdruckkraftstoffeinspritzvorrichtung an einer luftverdichtenden, selbstzündenden Brennkraftmaschine nach dem Oberbegriff des Anspruchs 1.The invention relates to an electromagnetically actuated control valve for a high-pressure fuel injection device on an air-compressing, self-igniting internal combustion engine according to the preamble of claim 1.

Ein gattungsgemäßes Steuerventil für eine Kraftstoffeinspritzvorrichtung ist z. B. aus der GB-A-2 041 577 oder der nachveröffentlichten EP-A-0 114 375 zu entnehmen. Ein derartiges Steuerventil für eine Hochdruckkraftstoffeinspritzvorrichtung ist zwischen eine Kraftstoff-Einspritzpumpe und eine Einspritzdüse geschaltet. Der in einem Gehäuseraum gleitende Kolbenschieber weist einen als Sitzventil ausgebildeten Abschnitt auf, dem ein entsprechender Ventilsitz im Gehäuse des Steuerventils zugeordnet ist. Der Ventilsitz trennt eine Hochdruckkammer von einer Niederdruckkammer und ist in der Strömungsverbindung zwischen den beiden Kammern angeordnet. Die Niederdruckkammer ist mit einer Entlastungsleitung verbunden, während der Hochdruckanschluß mit der Pumpenkammer in Verbindung steht.A generic control valve for a fuel injector is such. B. from GB-A-2 041 577 or the subsequently published EP-A-0 114 375. Such a control valve for a high-pressure fuel injection device is connected between a fuel injection pump and an injection nozzle. The piston slide sliding in a housing space has a section designed as a seat valve, to which a corresponding valve seat in the housing of the control valve is assigned. The valve seat separates a high pressure chamber from a low pressure chamber and is arranged in the flow connection between the two chambers. The low pressure chamber is connected to a relief line, while the high pressure connection is connected to the pump chamber.

In seiner Schließstellung liegt das Sitzventil dichtend am Ventilsitz an und sperrt die Strömungsverbindung zwischen Hochdruckkammer und Niederdruckkammer. Der in der Hochdruckkammer anstehende, unter hohen Druck gesetzte Kraftstoff fließt über ein Rückschlagventil zur Einspritzdüse.In its closed position, the seat valve lies sealingly on the valve seat and blocks the flow connection between the high-pressure chamber and the low-pressure chamber. The high pressure fuel in the high pressure chamber flows through a check valve to the injection nozzle.

In der Öffnungsstellung des Steuerventils ist die Strömungsverbindung zwischen Hochdruckkammer und Niederdruckkammer hergestellt, so daß der Kraftstoff aus der Hochdruckkammer über die Entlastungsleitung abgesteuert ist.In the open position of the control valve, the flow connection between the high pressure chamber and the low pressure chamber is established, so that the fuel from the high pressure chamber is diverted via the relief line.

Bei einer derartigen Hochdruckkraftstoffeinspritzvorrichtung hat das die Strömungsverbindung zwischen der Hochdruckkammer und der Niederdruckkammer sperrende Ventil erhebliche Druckbelastungen auszuhalten. Wird der Kolbenschieber von seiner Öffnungsstellung - in der die Hochdruckkammer über die Niederdruckkammer entlastet ist - in seine Schließstellung beschleunigt, so prallt das Sitzventil mit hoher Geschwindigkeit auf den ihm zugeordneten Ventilsitz im Gehäuse des Steuerventils. Aufgrund der geltenden Impulsgesetze hebt das Sitzventil nach dem ersten Aufschlag wieder ab, um erneut auf den Ventilsitz im Gehäuse aufzuschlagen. Dieses Ventilprallen hat zur Folge, daß zu Beginn einer Einspritzung der Kraftstoffdruck nur zögernd aufgebaut wird, da die Hochdruckkammer und damit die Einspritzdüse aufgrund des Ventilprallens immer wieder kurzzeitig über die Niederdruckkammer entlastet wird. Dieses Ventilprallen verzögert den Einspritzbeginn unkontrolliert, so daß die Einspritzung zu ungenau einsetzt. Ferner mußte festgestellt werden, daß bereits nach wenigen Betriebsstunden das Ventil bzw. der ihm zugeordnete Ventilsitz mechanisch erheblich -beschädigt war, so daß das Steuerventil in seiner geschlossenen Stellung große Undichtigkeiten zeigte. Das Steuerventil war zur Verwendung bei hohen Einspritzdrücken nicht mehr geeignet. Auch traten aufgrund der herrschenden hohen Drücke im Hochdruckraum Kavitationserscheinungen auf.In such a high-pressure fuel injection device, the valve blocking the flow connection between the high-pressure chamber and the low-pressure chamber has to withstand considerable pressure loads. If the spool is accelerated from its open position - in which the high-pressure chamber is relieved via the low-pressure chamber - to its closed position, the poppet valve impinges at high speed on the valve seat assigned to it in the housing of the control valve. Due to the applicable impulse laws, the poppet valve lifts again after the first impact in order to hit the valve seat in the housing again. The consequence of this valve bounce is that the fuel pressure is built up only hesitantly at the beginning of an injection, since the high-pressure chamber and thus the injection nozzle are repeatedly relieved for a short time via the low-pressure chamber due to the valve bounce. This valve bouncing delays the start of injection in an uncontrolled manner, so that the injection starts too imprecisely. Furthermore, it had to be found that after a few hours of operation the valve or the valve seat assigned to it was mechanically considerably damaged, so that the control valve showed large leaks in its closed position. The control valve was no longer suitable for use at high injection pressures. Cavitation phenomena also occurred due to the high pressures in the high-pressure room.

Die Summe all dieser Nachteile führt in der Praxis dazu, daß das bekannte Steuerventil - wurde es in einer Hochdruckkraftstoffeinspritzvorrichtung verwendet - nach kurzer Zeit unbrauchbar wurde.In practice, the sum of all these disadvantages means that the known control valve - if it was used in a high-pressure fuel injector - became unusable after a short time.

Ein im Aufbau ähnliches Steuerventil geht auch aus der FR-A-2 465 085 als bekannt hervor. Der mit Sitzventil ausgebildete Kolbenschieber sperrt in seiner Schließstellung die Einspritzleitung zur Einspritzdüse. Beim Schließvorgang wird ebenfalls Ventilprallen auftreten, weshalb das Einspritzende durch unkontrollierte Nachspritzer nicht genau eingestellt werden kann.A control valve of similar construction is also known from FR-A-2 465 085. The piston valve designed with a seat valve blocks the injection line to the injection nozzle in its closed position. Valve impacts will also occur during the closing process, which is why the end of injection cannot be precisely adjusted by uncontrolled spraying.

Der Erfindung liegt die Aufgabe zugrunde, bei Erhöhung der Standzeit des Steuerventils das Ventilprallen zu beseitigen, um eine genaue Steuerung der Einspritzung zu ermöglichen.The invention has for its object to eliminate the valve bounce when increasing the service life of the control valve in order to enable precise control of the injection.

Diese Aufgabe wird nach den kennzeichnenden Merkmalen des ersten Anspruchs gelöst. Da bei der Schließbewegung des Kolbenschiebers vor Auftreffen der Sitzflächenkante auf den Ventilsitz der Gehäuseabschnitt vom hochdruckseitigen Kolbenschieberbereich überfahren wird, erfolgt bereits in dieser Kolbenschieberstellung eine Unterbrechung der Strömungsverbindung zwischen der Hochdruckkammer und der Niederdruckkammer. Beim Auftreffen der Sitzflächenkante auf den Ventilsitz tritt zwar ein Ventilprallen auf, das nun jedoch aufgrund der Sperrwirkung des Kolbenschiebers in Verbindung mit dem Gehäuseabschnitt nicht zu einer Entlastung der Hochdruckkammer führt. Mit dem Überfahren des Gehäuseabschnitts durch die Sitzflächenkante wird somit bereits in der Hochdruckkammer Druck aufgebaut, so daß eine zeitgenaue Einspritzung - ohne nachteilige Druckabfälle - möglich ist.This object is achieved according to the characterizing features of the first claim. Since the housing section is run over by the high-pressure side of the piston slide area during the closing movement of the piston valve before the seat surface edge hits the valve seat, the flow connection between the high-pressure chamber and the low-pressure chamber is already interrupted in this piston valve position. When the seat surface edge hits the valve seat, valve collision occurs, but this does not relieve the high-pressure chamber due to the locking action of the piston slide in conjunction with the housing section. When the housing section is passed over by the edge of the seat surface, pressure is thus built up in the high-pressure chamber, so that a timely injection - without disadvantageous pressure drops - is possible.

Ist der Druck in der Hochdruckkammer auf Werte gestiegen, die zu Leckageströmen längs des Kolbenschieberbereichs durch den Gehäuseabschnitt führen, so sind diese durch das inzwischen dicht aufsitzende Sitzventil in Strömungsrichtung zur Niederdruckkammer unterbrochen, so daß keine Volumenverminderung in der Hochdruckkammer und somit auch kein Druckabfall in dieser Kammer auftreten kann.If the pressure in the high-pressure chamber has risen to values that lead to leakage flows along the piston slide area through the housing section, then these are interrupted in the flow direction to the low-pressure chamber by the seat valve, which is now tightly seated, so that there is no volume reduction in the high-pressure chamber and therefore no pressure drop in it Chamber can occur.

Es hat sich überraschend gezeigt, daß bei einem mit den Merkmalen des Anspruchs 1 ausgebildeten Steuerventil die mechanischen Verschleiß- und Kavitationserscheinungen am Sitzventil nicht in dem Maße ausgebildet werden, wie bei bekannten Steuerventilen. Vielmehr konnte festgestellt werden, daß die Standzeit des erfindungsgemäßen Steuerventils um Faktoren höher ist als die des bekannten Steuerventils.It has surprisingly been found that in a control valve designed with the features of claim 1, the mechanical wear and cavitation phenomena on the poppet valve are not designed to the same extent as in known control valves. Rather, it was found that the service life of the control valve according to the invention is longer by factors than that of the known control valve.

Mit dem erfindungsgemäßen Steuerventil ist somit eine genaue Steuerung des Einspritzbeginns ohne durch Ventilprallen bedingte Druckabfälle möglich und im übrigen ein Steuerventil geschaffen, das neben der genauen Steuerung des Einspritzbeginns auch deutlich höhere Standzeiten aufgrund eines geringeren Verschleißes zeigt.With the control valve according to the invention, precise control of the start of injection is thus possible without pressure drops caused by valve impacts and, moreover, a control valve is created which, in addition to the precise control of the start of injection, also shows significantly longer service lives due to less wear.

Bevorzugt ist der niederdruckseitige Kolbenschieberbereich insgesamt mit einem kleineren Durchmesser als der hochdruckseitige Kolbenschieberbereich ausgebildet. Hierdurch ist sichergestellt, daß in der Hochdruckphase während eines Einspritzvorganges grundsätzlich eine resultierende Druckkraft in Schließrichtung vorhanden ist. Dies beinhaltet den für das Betriebsergebnis insbesondere bei den bei luftverdichtenden, selbstzündenden Brennkraftmaschinen angestrebten sehr hohen Einspritzdrücken von 1000 bis 2000 bar entscheidenden Vorteil der absoluten Dichtheit des Steuerventils in der Hochdruckphase.The piston slide area on the low-pressure side is preferably smaller overall Diameter formed as the high-pressure piston spool area. This ensures that in the high pressure phase there is basically a resulting pressure force in the closing direction during an injection process. This includes the decisive advantage of the absolute tightness of the control valve in the high-pressure phase for the operating result, particularly in the case of the very high injection pressures of 1000 to 2000 bar which are aimed at in air-compressing, self-igniting internal combustion engines.

Bevorzugt weist der Ventilsitz des Ventilgehäuseraums eine den Kolbenschieber in der Schließstellung überdeckende Hinterschneidung auf, wodurch der fertigungstechnisch notwendige Raum zur Bearbeitung des Ventilsitzes geschaffen ist.The valve seat of the valve housing space preferably has an undercut covering the piston slide in the closed position, as a result of which the space required in terms of production technology for machining the valve seat is created.

Die weiteren Ansprüche geben vorteilhafte Ausgestaltungen des erfindungsgemäßen Steuerventils an, die insbesondere eine Verbesserung des Steuerventils im Hinblick auf z. B. geringe Kolbenschieberbetätigungskräfte, Optimierung etwaiger z. B. auf Druckunstetigkeiten bzw. Druckdifferenzen in Druckausgleichsleitungen zurückzuführender Störeinflüsse auf das Steuerventil und Darstellung einer auf den Kolbenschieber wirkenden Schließdruckkraft zum Gegenstand haben.The further claims indicate advantageous embodiments of the control valve according to the invention, which in particular an improvement of the control valve with regard to z. B. low spool actuator forces, optimization of any z. B. to pressure discontinuities or pressure differences in pressure compensation lines to be attributed to disturbances on the control valve and representation of a closing pressure force acting on the spool.

Zur Erläuterung der Erfindung ist nachfolgend ein in der Zeichnung dargestelltes Ausführungsbeispiel im einzelnen beschrieben.To explain the invention, an embodiment shown in the drawing is described in detail below.

Die Figur zeigt im Schnitt das erfindungsgemäße Steuerventil 1 ohne dessen elektromagnetische Betätigungsvorrichtungen. Dieses Steuerventil 1 soll in einer Hochdruckkraftstoffeinspritzvorrichtung von einer mehrzylindrigen, selbstzündenden, luftverdichtenden Brennkraftmaschine eingesetzt sein. Das Steuerventil 1 ist einer - nicht dargestellten - Kraftstoffeinspritzpumpe zugeordnet, die über einen Nocken und einen federbelasteten Stößel angetrieben ist. Das Steuerventil 1 ist über den Hochdruckanschluß 2 mit der nicht gezeigten Kraftstoffeinspritzpumpe verbunden. Der Hochdruckkanal 3 führt zu einer nicht dargestellten Kraftstoffeinspritzdüse.The figure shows in section the control valve 1 according to the invention without its electromagnetic actuation devices. This control valve 1 is intended to be used in a high-pressure fuel injection device by a multi-cylinder, self-igniting, air-compressing internal combustion engine. The control valve 1 is associated with a fuel injection pump (not shown) which is driven via a cam and a spring-loaded tappet. The control valve 1 is connected via the high-pressure connection 2 to the fuel injection pump, not shown. The high pressure channel 3 leads to a fuel injector, not shown.

Der Hochdruckanschluß 2 und der zur Kraftstoffeinspritzdüse führende Hochdruckkanal 3 münden im Ventilgehäuseraum 7 in eine Hochdruckkammer 9, die ihrerseits über eine Strömungsverbindung mit einer im Ventilgehäuseraum 7 angeordneten Niederdruckkammer 10 kommuniziert. Die Niederdruckkammer 10 ist über eine Entlastungsleitung 11 drucklos in einen Kraftstoffbehälter zu entlasten. Die Strömungsverbindung zwischen Hochdruckkammer 9 und Niederdruckkammer 10 ist von einem als Kolbenschieber 4 ausgebildeten Ventilkörper beherrscht, dessen hochdruckseitiger Kolbenschieberbereich 5 von einer Sitzflächenkante 6 begrenzt wird. Die Sitzflächenkante 6 wirkt mit einem im Ventilgehäuseraum 6 eingearbeiteten Ventilsitz 8 zusammen und sperrt die Strömungsverbindung zur Niederdruckkammer 10, so daß in der Schließstellung des Kolbenschiebers 4 über den Hochdruckanschluß 2 eintretender Kraftstoff über den Hochdruckkanal 3 zur Kraftstoffeinspritzdüse fließen kann.The high-pressure connection 2 and the high-pressure channel 3 leading to the fuel injection nozzle open into the valve housing space 7 into a high-pressure chamber 9, which in turn communicates via a flow connection with a low-pressure chamber 10 arranged in the valve housing space 7. The low-pressure chamber 10 is to be depressurized into a fuel tank via a relief line 11. The flow connection between the high-pressure chamber 9 and the low-pressure chamber 10 is controlled by a valve body designed as a spool 4, the high-pressure side spool area 5 of which is delimited by a seat edge 6. The seat edge 6 interacts with a valve seat 8 incorporated in the valve housing space 6 and blocks the flow connection to the low-pressure chamber 10, so that in the closed position of the spool 4 via the high-pressure connection 2 entering fuel can flow via the high-pressure channel 3 to the fuel injection nozzle.

Zur grundsätzlichen Funktionsweise des Steuerventils 1 ist anzumerken, daß über die Strömungsverbindung der Hochdruckanschluß 2 in der Öffnungsstellung des Kolbenschiebers 4 mit der in den Kraftstoffbehälter führenden Entlastungsleitung 11 verbunden ist, so daß durch das Öffnen bzw. Schließen des Steuerventils 1 in der Hochdruckphase der Kraftstoffeinspritzpumpe der Einspritzbeginn bzw. das Einspritzende regelbar ist.Regarding the basic functioning of the control valve 1, it should be noted that, via the flow connection, the high-pressure connection 2 in the open position of the spool 4 is connected to the relief line 11 leading into the fuel tank, so that the opening or closing of the control valve 1 in the high-pressure phase of the fuel injection pump The start of injection or the end of injection is adjustable.

Aus Übersichtsgründen wurde auf die Darstellung der Betätigungsvorrichtungen des Steuerventils verzichtet. Bevorzugt ist der Kolbenschieber druckfederbeaufschlagt und von einer elektromagnetischen Stellvorrichtung, die von einer elektrisch arbeitenden Meßwertverarbeitungseinrichtung gesteuert ist, betätigt. Dabei greift die nicht gezeigte elektromagnetische Stellvorrichtung an der Stirnseite des niederdruckseitigen Kolbenschieberbereichs 12 und eine Druckfeder an der Stirnfläche des hochdruckseitigen Kolbenschieberbereiches 5 an. Zur Betätigungsvorrichtung des Kolbenschiebers 4 wird ergänzend auf die EP-A-0 114 375 hingewiesen.For reasons of clarity, the actuators of the control valve have not been shown. The piston slide is preferably acted upon by compression springs and actuated by an electromagnetic actuating device which is controlled by an electrically operating measured value processing device. The electromagnetic actuating device, not shown, acts on the end face of the low-pressure piston valve region 12 and a compression spring on the end surface of the high-pressure piston valve region 5. Reference is also made to EP-A-0 114 375 for the actuating device of the piston slide 4.

Im gezeigten Ausführungsbeispiel ist der Bewegungshub des Kolbenschiebers 4 im hochdruckseitigen Bereich des Ventilgehäuseraumes 7 vorgesehen. Der Ventilgehäuseraum 7 weist zwischen seinem Ventilsitz 8 und dem Hochdruckanschluß bzw. dem Hochdruckkanal 3 einen Gehäuseabschnitt 13 auf, der mit dem gleichen Durchmesser ausgebildet ist, wie der hochdruckseitige Kolbenschieberbereich 5. Der Durchmesser des ventilgehäuseseitigen Gehäuseabschnittes 13 ist mit einer derartigen Passungszugabe ausgebildet, daß die Axialbewegung des Kolbenschiebers 4 nicht beeinträchtigt ist.In the exemplary embodiment shown, the movement stroke of the spool 4 is provided in the area of the valve housing space 7 on the high-pressure side. The valve housing space 7 has between its valve seat 8 and the high-pressure connection or the high-pressure channel 3 a housing section 13 which is designed with the same diameter as the high-pressure side piston slide region 5. The diameter of the valve housing-side housing section 13 is designed with a fit allowance such that the Axial movement of the spool 4 is not affected.

Sobald sich der Kolbenschieber aus der Öffnungsstellung, in der die Stirnfläche 14 des hochdruckseitigen Kolbenschieberbereiches 5 weitgehend an der Stirnfläche der hochdruckseitigen Gehäuseraumendkammer 15 anliegt, in Richtung des Ventilsitzes bewegt, überfährt die Sitzflächenkante 6 den Gehäuseabschnitt 13 mit der Hinterschneidung 8a, bevor sie am Ventilsitz 8 des Ventilgehäuseraumes 7 aufschlägt und sperrt so die Verbindung zwischen der Hochdruckkammer 9 und der Niederdruckkammer 10. Soweit nach dem Ausschlagen der Sitzflächenkante 6 am Ventilsitz 8 der Kolbenschieber 4 Rückprallbewegungen ausführt, bleiben diese Rückprallbewegungen ohne Einfluß auf das Dichtverhalten des Steuerventils 1, so daß eine gleichbleibende Hochdruckverbindung zwischen dem Hochdruckanschluß 2 und dem Hochdruckkanal 3 zur Einspritzdüse sichergestellt ist. Bei Einsatz des erfindungsgemäßen Steuerventils in einer Kraftstoffeinspritzvorrichtung von mehrzylindrigen Brennkraftmaschinen ist somit eine Gleichförderung bei den jeweiligen Zylindereinheiten sichergestellt.As soon as the spool moves in the direction of the valve seat from the open position, in which the end face 14 of the high-pressure spool region 5 largely abuts the end face of the high-pressure side chamber end chamber 15, the seat surface edge 6 runs over the housing section 13 with the undercut 8a before it touches the valve seat 8 of the valve housing space 7 opens and thus blocks the connection between the high-pressure chamber 9 and the low-pressure chamber 10. As far as after the knocking out of the seat edge 6 on the valve seat 8 of the piston slide 4 makes rebound movements, these rebound movements remain without influencing the sealing behavior of the control valve 1, so that a constant High-pressure connection between the high-pressure connection 2 and the high-pressure channel 3 to the injection nozzle is ensured. When using the control valve according to the invention in a fuel injection device of multi-cylinder internal combustion engines, equal delivery is thus ensured in the respective cylinder units.

Im Ausführungsbeispiel ist der niederdruckseitige Kolbenschieberbereich 12 insgesamt mit einem kleineren Durchmesser als der hochdruckseitige Kolbenschieberbereich 5 ausgebildet. Zudem weist der Ventilgehäuseraum 7 eine hochdruckseitige Gehäuseraumendkammer 15 und eine niederdruckseitige Gehäuseraumendkammer 16 auf, die jeweils den Stirnflächen 14 (hochdruckseitig) und 17 (niederdruckseitig) zugeordnet sind. Die hochdruckseitige Gehäuseraumendkammer 15 und die niederdruckseitige Gehäuseraumendkammer 16 sind über eine innerhalb des Kolbenschiebers 4 verlaufende Bohrung 18 miteinander verbunden. Durch diese Ausgestaltungen des Steuerventils sind weitere Vorteile erzielt. Durch die hochdruckseitige Kolbenschieberauslegung mit glattem Übergang in die Sitzflächenkante 6 fehlt jegliche Druckangriffsfläche für den sehr hohen Kraftstoffdruck, so daß etwaige ungleichmäßige Druckverteilungen auf den Kolbenschieber 4 in der für den regelbaren Einspritzvorgang entscheidenden Schließstellung keinerlei Einfluß ausüben können. Während der Hochdruckphase der Kraftstoffeinspritzpumpe wird der Kraftstoff über den Hochdruckanschluß 2, die Hochdruckkammer 9 und den Hochdruckkanal 3 zu der nicht gezeigten Kraftstoffeinspritzdüse gefördert. Hierbei besteht über den Dichtspalt 19 im hochdruckseitigen Kolbenschieberbereich 5 zu der hochdruckseitigen Gehäuseraumendkammer 15 und über die Bohrung 18 somit auch zu der niederdruckseitigen Gehäuseraumendkammer 16 ein Druckgefälle, das stets dafür sorgt, daß das Kammersystem mit Kraftstoff gefüllt ist. Durch die Öffnungsbewegung des Kolbenschiebers 4 wird aus der hochdruckseitigen Gehäuseraumendkammer 15 Kraftstoff in die niederdruckseitige Gehäuseraumendkammer 16 verdrängt, wobei aufgrund der Durchmesserdifferenz der Stirnflächen 14 bzw. 17 des Kolbenschiebers 4 der Kraftstoff in den Gehäuseraumendkammern komprimiert wird. Dieser Überdruck wird in der Öffnungsstellung des Kolbenschiebers 4 durch über die niederdruckseitigen Dichtspalte 20 abfließenden Kraftstoff abgebaut. Diese abgeflossene Kraftstoffmenge wird in der Schließstellung des Kolbenschiebers 4 aufgrund des Druckgefälles über die hochdruckseitigen Dichtspalte 19 wieder aufgefüllt, wobei der Füllvorgang während der Hochdruckphase eine weitere die Dichtheit des Steuerventils 1 unterstützende, resultierende Druckschließkraft auf den Kolbenschieber 4 ausübt, so daß das Steuerventil in vorteilhafter Weise neben den bereits erläuterten Vorteilen hinsichtlich der Rückprallbewegungen im Sinne einer absoluten Dichtheit in der Schließstellung optimiert ist.In the exemplary embodiment, the piston valve region 12 on the low pressure side is overall smaller in diameter than the high pressure side piston slide area 5 formed. In addition, the valve housing chamber 7 has a housing chamber end chamber 15 on the high pressure side and a housing chamber end chamber 16 on the low pressure side, which are respectively assigned to the end faces 14 (high pressure side) and 17 (low pressure side). The housing chamber end chamber 15 on the high pressure side and the housing chamber end chamber 16 on the low pressure side are connected to one another via a bore 18 running within the piston slide 4. These advantages of the control valve provide further advantages. Due to the high-pressure piston valve design with a smooth transition into the seat edge 6, there is no pressure application surface for the very high fuel pressure, so that any uneven pressure distributions on the piston valve 4 cannot exert any influence in the closed position, which is decisive for the controllable injection process. During the high pressure phase of the fuel injection pump, the fuel is conveyed via the high pressure connection 2, the high pressure chamber 9 and the high pressure channel 3 to the fuel injection nozzle, not shown. Here there is a pressure drop across the sealing gap 19 in the high-pressure side spool area 5 to the high-pressure side housing chamber end chamber 15 and thus via the bore 18 also to the low-pressure side housing chamber end chamber 16, which always ensures that the chamber system is filled with fuel. Due to the opening movement of the piston valve 4, fuel is displaced from the high-pressure-side housing chamber end chamber 15 into the low-pressure-side housing chamber end chamber 16, the fuel in the housing chamber end chambers being compressed due to the difference in diameter of the end faces 14 and 17 of the piston valve 4. This excess pressure is reduced in the open position of the spool 4 by fuel flowing out through the low-pressure sealing gaps 20. This flow of fuel is refilled in the closed position of the spool 4 due to the pressure drop across the high-pressure sealing gaps 19, the filling process during the high-pressure phase exerting a further pressure-closing force on the spool 4, which supports the tightness of the control valve 1, so that the control valve is more advantageous In addition to the advantages already explained with regard to the rebound movements in the sense of an absolute tightness in the closed position is optimized.

Claims (6)

1. An electromagnetically operable pilot valve (1) for a high-pressure fuel injection system of an air-compressing, auto-ignition internal combustion engine, in which the pilot valve (1), which is connectable between a fuel injection pump and an injection nozzle, includes a valve body constructed as a piston slide (4) which is axially displaceably mounted in the casing interior (7), in which the casing interior (7) includes a high-pressure chamber (9) and a low-pressure chamber (10) communicating via a flow link with one another, in which the high-pressure chamber (9) is provided with at least one high-pressure terminal (2) and the low-pressure chamber is connected to a discharge duct (11), in which the injection nozzle is in communication with the high-pressure chamber (9), in which a valve seat (8) provided in the casing interior in the region of the flow link is arranged to cooperate with a seating edge (6) on the piston slide (4), in which the piston slide (4) rests, when in its closing position, against the valve seat (8) and blocks the flow link between the high-pressure chamber (9) and the low-pressure chamber (10) and, when in its opening position, clears the flow link so as to relieve the high-pressure chamber (9), characterized in that the diameter of the piston slide's section (5) disposed at the high-pressure side is uniform and the same as that of the seating edge (6), that the casing interior (7) is provided between the valve seat (8) and the high-pressure chamber (9) with an internal section (13) of a diameter equal to that of the piston slide's section (5) at the high-pressure side, and in that the piston slide (4), when being axially displaced from its opening position into its closing position, blocks - prior to the seating edge (6) coming to rest against the valve seat (8) - the flow link between the high-pressure chamber (9) and the low-pressure chamber (10) by traversing the internal section (13).
2. A pilot valve according to claim 1, characterized in that the diameter of the piston slide's section (12) at the low-pressure side is smaller than that of the slide's section (5) at the high-pressure side.
3. A pilot valve according to claim 1 or claim 2, characterized in that the valve seat (8) in the valve casing's interior (7) is provided with an undercut (8a) which overlaps the piston slide (4) when the latter is in its closing position.
4. A pilot valve according to any of the claims 1 to 3, characterized in that the valve casing's interior (7) includes one inner end chamber (15) disposed at the high-pressure side and another inner end chamber (16) disposed at the low-pressure side, and in that the one chamber is associated with the piston slide's one end face (14) and the other chamber with the slide's other end face (17).
5. A pilot valve according to claim 4, characterized in that the inner end chambers (15, 16) at the high-pressure and, respectively, the low-pressure sides are connectable by at least one bore (18) provided in the piston slide (4).
6. A pilot valve according to any of the claims 1 to 5, characterized in that the valve casing's interior (7), excepting the terminals at the high-pressure side (2, 3, 9) and those at the low-pressure side (10, 11), is pressure-tightly sealed.
EP85109245A 1984-07-25 1985-07-24 Control valve for a fuel injection device Expired EP0171667B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85109245T ATE41042T1 (en) 1984-07-25 1985-07-24 CONTROL VALVE FOR A FUEL INJECTOR.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843427421 DE3427421A1 (en) 1984-07-25 1984-07-25 CONTROL VALVE FOR A FUEL INJECTION DEVICE
DE3427421 1984-07-25

Publications (2)

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EP0171667A1 EP0171667A1 (en) 1986-02-19
EP0171667B1 true EP0171667B1 (en) 1989-03-01

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EP85109245A Expired EP0171667B1 (en) 1984-07-25 1985-07-24 Control valve for a fuel injection device

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US (2) US4653723A (en)
EP (1) EP0171667B1 (en)
JP (1) JPS6138158A (en)
AT (1) ATE41042T1 (en)
DE (2) DE3427421A1 (en)

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Also Published As

Publication number Publication date
DE3427421A1 (en) 1986-01-30
DE3568468D1 (en) 1989-04-06
ATE41042T1 (en) 1989-03-15
EP0171667A1 (en) 1986-02-19
US4653723A (en) 1987-03-31
US4757973A (en) 1988-07-19
JPS6138158A (en) 1986-02-24

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