EP1317619B1 - Common rail system - Google Patents

Common rail system Download PDF

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Publication number
EP1317619B1
EP1317619B1 EP01971670A EP01971670A EP1317619B1 EP 1317619 B1 EP1317619 B1 EP 1317619B1 EP 01971670 A EP01971670 A EP 01971670A EP 01971670 A EP01971670 A EP 01971670A EP 1317619 B1 EP1317619 B1 EP 1317619B1
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EP
European Patent Office
Prior art keywords
valve
control valve
pressure
common rail
control
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
EP01971670A
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German (de)
French (fr)
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EP1317619A1 (en
Inventor
Friedrich Boecking
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • F02D41/3809—Common rail control systems
    • F02D41/3836—Controlling the fuel pressure
    • F02D41/3863—Controlling the fuel pressure by controlling the flow out of the common rail, e.g. using pressure relief valves
    • F02D41/3872—Controlling the fuel pressure by controlling the flow out of the common rail, e.g. using pressure relief valves characterised by leakage flow in injectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/20—Output circuits, e.g. for controlling currents in command coils
    • F02D41/2096—Output circuits, e.g. for controlling currents in command coils for controlling piezoelectric injectors
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/005—Fuel-injectors combined or associated with other devices the devices being sensors
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167—Means for compensating clearance or thermal expansion
    • 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
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2200/00—Input parameters for engine control
    • F02D2200/02—Input parameters for engine control the parameters being related to the engine
    • F02D2200/06—Fuel or fuel supply system parameters
    • F02D2200/0602—Fuel pressure
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/24—Fuel-injection apparatus with sensors
    • F02M2200/244—Force sensors
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/24—Fuel-injection apparatus with sensors
    • F02M2200/247—Pressure sensors
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/704—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with actuator and actuated element moving in different directions, e.g. in opposite directions
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. for compensating clearance or thermal expansion

Definitions

  • the invention is based on a control valve for controlling a fluid according to the manner defined in more detail in claim 1.
  • a nozzle needle of a fuel injection valve is opened or closed depending on the pressure prevailing in a control chamber.
  • the control chamber is permanently connected to a common rail high-pressure accumulator and can be connected by means of the control valve to the low pressure side and thereby relieved of pressure, so that the nozzle needle opens.
  • the control valve is a 2/2-way solenoid valve whose axially displaceable valve closure member lifts in the magnetic field of a coil from its valve seat.
  • control valve which can be actuated via a special piezoelectric actuator.
  • control valve described therein has an arrangement for acting in the stroke direction path transformer of the piezoelectric actuator, wherein the deflection is transmitted via a hydraulic chamber.
  • This hydraulic chamber serves as a translation and tolerance compensation element.
  • the transmission ratio determined by the different diameter of two pistons, between which the hydraulic chamber is arranged.
  • settling effects and tolerances can be compensated, which occur, for example, due to different coefficients of thermal expansion of the materials used in the valve.
  • pressure relief valves are used to protect against overpressure, which usually are arranged in the region of the common fuel tank for all injectors.
  • Such a pressure limiting valve limits the pressure in the fuel or pressure accumulator by releasing a drain opening for the fuel at too high a load. It may, for example, at a normal working pressure of up to 1350 bar in the accumulator briefly 'allow a maximum pressure of up to 1500 bar.
  • pressure relief valves are mechanically working components with a housing with external thread for screwing to the rail, a connection to a return line to a fuel tank, a movable piston and a spring.
  • the housing has on the connection side to the rail a bore which is closed by a conical end of the piston at the sealing seat inside the housing.
  • the spring presses at normal working pressure of the fuel force the piston tight in its sealing seat, so that the pressure accumulator on the connection side, where the pressure relief valve is connected, remains closed. Only when the maximum working or injection pressure is exceeded, the piston is pressed by the pressure prevailing in the pressure accumulator overpressure against the spring, so that the high-pressure fuel can escape. The escaping fuel is then ducted into a cylindrical bore of the piston and returned to the fuel tank via a manifold.
  • a high-pressure fuel injection device which has a control valve without pressure-limiting function.
  • the control valve proposed there has a valve closing member which opens in the direction of the control chamber. If an overpressure arises in the control chamber, then it can not automatically escape via the control valve, since the valve closing member then blocks the valve opening.
  • the common rail system according to the invention with the features of claim 1 advantageously requires no known from the prior art separate pressure relief valve to the common rail pressure accumulator, since its function of the already existing control valves, by means of which the injection behavior is controlled in the injectors, is adopted.
  • an inventive valve for controlling a fluid having the features of claim 3 is used.
  • Such a valve which of course can also be used in other areas, offers the advantage that the pending pressure is sensed via an optionally already existing actuator unit, and the pressure limiting function is essentially realized by a simple software.
  • valve according to the invention for controlling a fluid is shown in the drawing and will be explained in more detail in the following description.
  • the embodiment shown in the figure shows a use of the valve 1 according to the invention in a common rail injector or an injection device 2 for the injection of preferably diesel fuel for internal combustion engines of motor vehicles.
  • the fuel injection via the pressure level in a valve control chamber 3, which is connected to a high-pressure supply 4.
  • a high pressure or injection pressure p_R prevails, which defines the high pressure region.
  • the high pressure supply 4 connects the valve control chamber 3 with a common rail pressure accumulator 5, in which the fuel is also present under high pressure p_R.
  • a valve member 6 is actuated in the valve 1 via a trained as a piezoelectric actuator actuator unit 7, on the valve control chamber 3 and the combustion chamber side facing away from the valve member 6 is arranged.
  • the piezoelectric actuator 7 is constructed in the usual way of several layers and has on its the valve member 6 facing side an actuator head 9 and on its side facing away from the valve member 7 an actuator foot 8, which is supported on a wall of a valve body 9 of the valve 1. Via a support 11, a first piston 12 connects to a hydraulic transmission device 13 of the valve member 6.
  • the valve member 6 is arranged axially displaceably in a corresponding longitudinal bore of the valve body 10 and has a second piston 14 which actuates a valve closing member 15.
  • first piston 12 and the second piston 14 are configured such that they are arranged axially displaceably in a chamber 16 of the hydraulic transmission device 13 in the valve body 10, wherein the second piston 14 in turn in a sleeve-like end piece 17 of first piston 12 is guided.
  • the first piston 12 and the second piston 14 include a first hydraulic chamber 18 with the valve body 9. Between the side of the second piston 14 facing away from the first hydraulic chamber 18 and the first piston 12, a second hydraulic chamber 19 is formed in the recess provided in the first piston 12 for guiding the second piston 14.
  • the pistons 12 and 14 in the hydraulic transmission device 13 are coupled together so that the deflection of the piezoelectric actuator 7 is transmitted by the second piston 14 is raised by a certain distance corresponding to the transmission ratio of the piston diameter.
  • the spherical valve closure member 15 cooperates with a formed on the valve body 10 valve seat 23, wherein the valve closure member 15 is a low-pressure region 24 with a prevailing low pressure of the fluid from an outlet throttle 30 and the valve control chamber 3, which is acted upon by the injection or high pressure p_R of the fluid separates.
  • a leakage compensation channel 25 branches off.
  • the valve control chamber 3 of the injector 2 is only partially indicated in the figure.
  • a movable nozzle needle 26 is arranged, which closes and opens an injection opening in a combustion chamber of a 'nes motor.
  • the injection behavior of the injectors 2 is controlled in a manner known per se, the fuel in the valve control chamber 3 being supplied via the high-pressure supply 4 from the pressure accumulator 5 common to several injectors 2, and the valve control chamber 3 being injected via the outlet throttle 30 and the valve 1 according to the invention is relieved.
  • a sealing spring 27 is arranged, which surrounds the second piston 14 and is supported in the valve body 10 such that by the spring force of the sealing spring 27, the second piston 14 is pressed down, so that the valve closing member 15 comes to rest in the resting state of the valve 1 against the valve seat 23 sealingly.
  • the actuator unit 7 designed here with piezoceramic not only serves as a lifting element, but also as a force sensor, because the force changes acting on the piezoelectric unit are registered as changes in voltage.
  • the piezoelectric actuator 7 is connected to a control unit 28 via a single line, which functions as a sensor and control line.
  • This control unit 28 serves both the Meßability when the piezoelectric actuator 7 acts as Kraftmeßsensor, and at the same time as a drive device when the piezoelectric actuator 7 is to be deflected. Within the controller 28, these functions can be shared via a accomplish appropriate electronic circuit or software.
  • the valve 1 assumes the function of a pressure relief valve for a possibly occurring in the high pressure region 3 overpressure, which is above the injection pressure p_R.
  • the diameter of the valve seat 23 determines the sealing force when the spring force of the sealing spring 27 is fixed. If this sealing force is exceeded, the valve 1 opens without activation by the piezoelectric actuator 7 on its own if the counterforce resulting from the overpressure in the high-pressure region 3 exceeds the sealing force. In this case, a force is transmitted to the piezoelectric actuator 7 by the stroke of the second piston 14 and the hydraulic transmission device 13, which measures this and passes it on to the control unit 28. Thus, the control unit 28 can recognize that a malfunction is present in the high-pressure area 3.
  • the opening for purposes of reducing the overpressure is clocked so short that it can come to any control of the nozzle needle 26 itself.
  • the opening of the valve 1 is carried out in such short periods of time that due to the inertia of the nozzle needle 26, this in its closed position remains with the effect that the injector 2 does not open and there is no injection of fuel.
  • the invention can not only be used in the common rail systems described here as a preferred application, but generally in fuel injection valves or in other areas, such as pumps, can be realized where a sudden degradation of a short-term overpressure is to be ensured.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Physics & Mathematics (AREA)
  • Analytical Chemistry (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Train Traffic Observation, Control, And Security (AREA)
  • Automatic Cycles, And Cycles In General (AREA)
  • Vehicle Body Suspensions (AREA)
  • Fluid-Driven Valves (AREA)

Abstract

Disclosed is a valve which is used to control a fluid, comprising an actuator unit (7) which is used to actuate an axially displaceable valve member (6) with an associated valve closing member (15), cooperating with a valve seat (23) in order to open and close the valve (1) and separating a high pressure area (3) from the valve (1). The fluid to be controlled is located in the high pressure area (3) at a working pressure (p-R). Said working pressure (p-R) and an over pressure occurring in specific circumstances are recorded by the actuator unit (7) which is embodied as a force measuring sensor.Said valve (1) is especially used as a pressure limiting valve in a common rail system.

Description

Stand der TechnikState of the art

Die Erfindung geht von einem Steuerventil zum Ansteuern eines Fluids gemäß der in Patentanspruch 1 näher definierten Art aus.The invention is based on a control valve for controlling a fluid according to the manner defined in more detail in claim 1.

Bei einem solchen, z.B. aus der EP 0 971 119 A bekannten Steuerventil wird eine Düsennadel eines Kraftstoffeinspritzventils abhängig von dem in einem Steuerraum herrschenden Druck geöffnet oder geschlossen. Der Steuerraum ist permanent an einen Common-Rail-Hochdruckspeicher angeschlossen und kann mittels des Steuerventils mit der Niederdruckseite verbunden und dadurch druckentlastet werden, so dass die Düsennadel öffnet. Das Steuerventil ist ein 2/2-Wege-Magnetventil, dessen axial verschiebbares Ventilschließglied im Magnetfeld einer Spule von seinem Ventilsitz abhebt.In such, e.g. From EP 0 971 119 A known control valve, a nozzle needle of a fuel injection valve is opened or closed depending on the pressure prevailing in a control chamber. The control chamber is permanently connected to a common rail high-pressure accumulator and can be connected by means of the control valve to the low pressure side and thereby relieved of pressure, so that the nozzle needle opens. The control valve is a 2/2-way solenoid valve whose axially displaceable valve closure member lifts in the magnetic field of a coil from its valve seat.

Weiterhin ist aus der EP 0 477 400 A1 ein Steuerventil bekannt, das über einen speziellen piezoelektrischen Aktuator betätigbar ist. Darüber hinaus weist das darin beschriebene Steuerventil eine Anordnung für einen in Hubrichtung wirkenden Wegtransformator des piezoelektrischen Aktuators auf, wobei dessen Auslenkung über eine Hydraulikkammer übertragen wird. Diese Hydraulikkammer dient als Übersetzungs- und Toleranzausgleichselement. Hierbei bestimmt sich das Übersetzungsverhältnis über die unterschiedlichen Durchmesser zweier Kolben, zwischen denen die Hydraulikkammer angeordnet ist. Daneben können über das Arbeitsvolumen der Hydraulikkammer unter Umständen auftretende Setzeffekte sowie Toleranzen ausgeglichen werden, die beispielsweise aufgrund von unterschiedlichen Temperaturausdehnungskoeffizienten der in dem Ventil zur Anwendung kommenden Materialien auftreten.Furthermore, from EP 0 477 400 A1 a control valve is known which can be actuated via a special piezoelectric actuator. In addition, the control valve described therein has an arrangement for acting in the stroke direction path transformer of the piezoelectric actuator, wherein the deflection is transmitted via a hydraulic chamber. This hydraulic chamber serves as a translation and tolerance compensation element. Here, the transmission ratio determined by the different diameter of two pistons, between which the hydraulic chamber is arranged. In addition, over the working volume of the hydraulic chamber under certain circumstances occurring settling effects and tolerances can be compensated, which occur, for example, due to different coefficients of thermal expansion of the materials used in the valve.

Aus dem Stand der Technik sind auch Common-Rail-Systeme mit Magnetventilen bekannt, bei denen eine Feder ein entsprechendes Ventilschließglied zu Dichtungszwecken gegen einen Ventilsitz drückt.Common rail systems with solenoid valves are known from the prior art, in which a spring presses a corresponding valve closure member against a valve seat for sealing purposes.

Bei gängigen Common-Rail-Systemen, bei denen der Einspritzdruck unabhängig von der Motordrehzahl und der Einspritzmenge erzeugt wird und in einem gemeinsamen Kraftstoffspeicher (Common Rail) zur Einspritzung über ventilgesteuerte Injektoren bereitgehalten wird, werden Druckbegrenzungsventile zur Sicherung gegen Überdruck eingesetzt, die in der Regel in dem Bereich des für alle Einspritzventile gemeinsamen Kraftstoffspeichers angeordnet sind. Ein solches Druckbegrenzungsventil begrenzt den Druck in dem Kraftstoff- bzw. Druckspeicher, indem es bei zu hoher Beanspruchung eine Ablauföffnung für den Kraftstoff freigibt. Dabei kann es z.B. bei einem normalen Arbeitsdruck von bis 1350 bar in dem Druckspeicher kurzzeitig' einen maximalen Druck von bis zu 1500 bar zulassen.In common rail systems in which the injection pressure is generated independently of the engine speed and the injection quantity and in a common fuel storage (common rail) for injection via valve-controlled injectors is used, pressure relief valves are used to protect against overpressure, which usually are arranged in the region of the common fuel tank for all injectors. Such a pressure limiting valve limits the pressure in the fuel or pressure accumulator by releasing a drain opening for the fuel at too high a load. It may, for example, at a normal working pressure of up to 1350 bar in the accumulator briefly 'allow a maximum pressure of up to 1500 bar.

Bei aus der Praxis bekannten Druckbegrenzungsventilen handelt es sich um mechanisch arbeitende Komponenten mit einem Gehäuse mit Außengewinde zum Anschrauben an den Rail, einem Anschluß an eine Rücklaufleitung zu einem Kraftstoffbehälter, einem beweglichen Kolben und einer Feder. Das Gehäuse hat auf der Anschlußseite zu dem Rail eine Bohrung, die durch ein kegelförmiges Ende des Kolbens am Dichtsitz im Gehäuseinneren verschlossen wird.In known from practice pressure relief valves are mechanically working components with a housing with external thread for screwing to the rail, a connection to a return line to a fuel tank, a movable piston and a spring. The housing has on the connection side to the rail a bore which is closed by a conical end of the piston at the sealing seat inside the housing.

Die Feder drückt bei normalem Arbeitsdruck des Kraft stoffs den Kolben dicht in seinen Dichtsitz, so daß der Druckspeicher auf der Anschlußseite, an der das Druckbegrenzungsventil angeschlossen ist, geschlossen bleibt. Erst beim Überschreiten des maximalen Arbeits- bzw. Einspritzdruckes wird der Kolben durch den in dem Druckspeicher vorherrschenden Überdruck gegen die Feder aufgedrückt, so daß der unter Hochdruck stehende Kraftstoff entweichen kann. Der entweichende Kraftstoff wird dann.über Kanäle in eine zylindrische Bohrung des Kolbens geleitet und über eine Sammelleitung zu dem Kraftstoffbehälter zurückgeführt.The spring presses at normal working pressure of the fuel force the piston tight in its sealing seat, so that the pressure accumulator on the connection side, where the pressure relief valve is connected, remains closed. Only when the maximum working or injection pressure is exceeded, the piston is pressed by the pressure prevailing in the pressure accumulator overpressure against the spring, so that the high-pressure fuel can escape. The escaping fuel is then ducted into a cylindrical bore of the piston and returned to the fuel tank via a manifold.

Aus der DE 199 54 023 A1 ist eine Hochdruckkraftstoffeinspritzvorrichtung bekannt, die ein Steuerventil ohne Druckbegrenzungsfunktion aufweist. Das dort vorgeschlagene Steuerventil weist ein in Richtung auf die Steuerkammer öffnendes Ventilschliessglied auf. Entsteht in der Steuerkammer ein Überdruck, so vermag dieser nicht selbsttätig über das Steuerventil entweichen, da das Ventilschliessglied dann die Ventilöffnung sperrt.From DE 199 54 023 A1 a high-pressure fuel injection device is known which has a control valve without pressure-limiting function. The control valve proposed there has a valve closing member which opens in the direction of the control chamber. If an overpressure arises in the control chamber, then it can not automatically escape via the control valve, since the valve closing member then blocks the valve opening.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Common-Rail-System mit den Merkmalen des Patentanspruchs 1 benötigt vorteilhafterweise kein aus dem Stand der Technik bekanntes separates Überdruckventil an dem Common-Rail-Druckspeicher, da dessen Funktion von den ohnehin vorhandenen Steuerventilen, mittels denen das Einspritzverhalten in den Einspritzeinrichtungen gesteuert wird, übernommen wird.The common rail system according to the invention with the features of claim 1 advantageously requires no known from the prior art separate pressure relief valve to the common rail pressure accumulator, since its function of the already existing control valves, by means of which the injection behavior is controlled in the injectors, is adopted.

Besonders vorteilhaft ist es dabei, wenn ein erfindungsgemäßes Ventil zur Steuerung eines Fluids mit den Merkmalen des Patentanspruchs 3 zum Einsatz kommt. Ein solches Ventil, welches selbstverständlich auch in anderen Bereichen Verwendung finden kann, bietet den Vorteil, daß der anstehende Druck über eine gegebenenfalls bereits vorhandene Aktuator-Einheit sensiert wird, und die Druckbegrenzungsfunktion im wesentlichen über eine einfache Software realisierbar ist.It is particularly advantageous if an inventive valve for controlling a fluid having the features of claim 3 is used. Such a valve, which of course can also be used in other areas, offers the advantage that the pending pressure is sensed via an optionally already existing actuator unit, and the pressure limiting function is essentially realized by a simple software.

Damit werden nicht nur Druckbegrenzungsventile als zusätzliche Komponenten überflüssig, sondern es entsteht auch kein nennenswerter mechanischer Mehraufwand bei den Ventilen, so daß sich hierdurch eine erhebliche Kosteneinsparung erzielen läßt.This not only pressure relief valves are unnecessary as additional components, but there is no appreciable mechanical overhead in the valves, so that this can achieve a significant cost savings.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstands der Erfindung sind der Beschreibung, der Zeichnung und den Patentansprüchen entnehmbar.Further advantages and advantageous embodiments of the subject invention are the description, the drawings and the claims removed.

Zeichnungdrawing

Ein Ausführungsbeispiel des erfindungsgemäßen Ventils zur Ansteuerung eines Fluids ist in der Zeichnung dargestellt und wird in der folgenden Beschreibung näher erläutert.An embodiment of the valve according to the invention for controlling a fluid is shown in the drawing and will be explained in more detail in the following description.

Es zeigt die einzige Figur der Zeichnung eine schematische, ausschnittsweise Darstellung eines Ausführungsbeispiels der Erfindung für eine Einspritzeinrichtung eines Common-Rail-Systems im Längsschnitt.It shows the sole figure of the drawing is a schematic, partial view of an embodiment of the invention for an injection device of a common rail system in longitudinal section.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Das in der Figur dargestellte Ausführungsbeispiel zeigt eine Verwendung des erfindungsgemäßen Ventils 1 bei einem Common-Rail-Injektor bzw. einer Einspritzeinrichtung 2 zur Einspritzung von vorzugsweise Dieselkraftstoff für Brennkraftmaschinen von Kraftfahrzeugen. In der vorliegenden Ausführung erfolgt die Kraftstoffeinspritzung über das Druckniveau in einem Ventilsteuerraum 3, der mit einer Hochdruckversorgung 4 verbunden ist. In diesem Ventilsteuerraum 3 herrscht ein Hochdruck bzw. Einspritzdruck p_R vor, welcher den Hochdruckbereich definiert. Die Hochdruckversorgung 4 verbindet den Ventilsteuerraum 3 mit einem Common-Rail-Druckspeicher 5, in dem der Kraftstoff ebenfalls unter Hochdruck p_R vorliegt.The embodiment shown in the figure shows a use of the valve 1 according to the invention in a common rail injector or an injection device 2 for the injection of preferably diesel fuel for internal combustion engines of motor vehicles. In the present embodiment, the fuel injection via the pressure level in a valve control chamber 3, which is connected to a high-pressure supply 4. In this valve control chamber 3, a high pressure or injection pressure p_R prevails, which defines the high pressure region. The high pressure supply 4 connects the valve control chamber 3 with a common rail pressure accumulator 5, in which the fuel is also present under high pressure p_R.

Zur Einstellung eines Einspritzbeginns, einer Einspritzdauer und einer Einspritzmenge über bestimmte Kräfteverhältnisse in der Einspritzeinrichtung 2 wird ein Ventilglied 6 in dem Ventil 1 über eine als piezoelektrischer Aktor 7 ausgebildete Aktuator-Einheit angesteuert, die auf der dem Ventilsteuerraum 3 und dem Brennraum abgewandten Seite des Ventilglieds 6 angeordnet ist.To set an injection start, an injection duration and an injection quantity over certain balance of forces in the injector 2, a valve member 6 is actuated in the valve 1 via a trained as a piezoelectric actuator actuator unit 7, on the valve control chamber 3 and the combustion chamber side facing away from the valve member 6 is arranged.

Der piezoelektrische Aktor 7 ist in üblicher Weise aus mehreren Schichten aufgebaut und weist auf seiner dem ventilglied 6 zugewandten Seite einen Aktorkopf 9 und auf seiner dem Ventilglied 7 abgewandten Seite einen Aktorfuß 8 auf, der sich an einer Wand eines Ventilkörpers 9 des Ventils 1 abstützt. Über ein Auflager 11 schließt ein erster Kolben 12 einer hydraulischen Übersetzungseinrichtung 13 des Ventilglieds 6 an. Das Ventilglied 6 ist in einer entsprechenden Längsbohrung des Ventilkörpers 10 axial verschiebbar angeordnet und weist einen zweiten Kolben 14 auf, der ein Ventilschließglied 15 betätigt.The piezoelectric actuator 7 is constructed in the usual way of several layers and has on its the valve member 6 facing side an actuator head 9 and on its side facing away from the valve member 7 an actuator foot 8, which is supported on a wall of a valve body 9 of the valve 1. Via a support 11, a first piston 12 connects to a hydraulic transmission device 13 of the valve member 6. The valve member 6 is arranged axially displaceably in a corresponding longitudinal bore of the valve body 10 and has a second piston 14 which actuates a valve closing member 15.

Innerhalb der hydraulischen Übersetzungseinrichtung 13 sind der erste Kolben 12 und der zweite Kolben 14 derart ausgestaltet, daß sie in einer Kammer 16 der hydraulischen Übersetzungseinrichtung 13 in dem Ventilkörper 10 axial verschiebbar angeordnet sind, wobei der zweite Kolben 14 wiederum in einem muffenartig ausgebildeten Endstück 17 des ersten Kolbens 12 geführt ist.Within the hydraulic transmission device 13, the first piston 12 and the second piston 14 are configured such that they are arranged axially displaceably in a chamber 16 of the hydraulic transmission device 13 in the valve body 10, wherein the second piston 14 in turn in a sleeve-like end piece 17 of first piston 12 is guided.

Der erste Kolben 12 und der zweite Kolben 14 schließen mit dem Ventilkörper 9 eine erste Hydraulikkammer 18 ein. Zwischen der der ersten Hydraulikkammer 18 abgewandten Seite des zweiten Kolbens 14 und dem ersten Kolben 12 ist in der für die Führung des zweiten Kolbens 14 in dem ersten Kolben 12 vorgesehenen Ausnehmung eine zweite Hydraulikkammer 19 ausgebildet.The first piston 12 and the second piston 14 include a first hydraulic chamber 18 with the valve body 9. Between the side of the second piston 14 facing away from the first hydraulic chamber 18 and the first piston 12, a second hydraulic chamber 19 is formed in the recess provided in the first piston 12 for guiding the second piston 14.

Es ist zu erkennen, daß durch die spezielle Anordnung der Hydraulikkammern 18 und 19 eine Bewegungsumkehr zwischen beiden Kolben 12 und 14 bewerkstelligt wird. Wird der erste Kolben 12 infolge einer Auslenkung des piezoelektrischen Aktors 7 nach unten gedrückt, führt dies gleichzeitig zu einer Hubbewegung des zweiten Kolbens 14 in entgegengesetzter Richtung. Dieser zweite Kolben 14 verdrängt das in der zweiten Hydraulikkammer 19 befindliche Arbeitsfluid über einen Ausgleichskanal 20 in eine Ausgleichskammer 21. Die Ausgleichskammer 21 steht zu Zwecken der Abführung des Arbeitsfluids mit einem Leckageausgleichskanal 22 in Verbindung und ist durch eine Membran 29 gegenüber dem piezoelektrischen Aktor 7 abgedichtet.It can be seen that by the special arrangement of the hydraulic chambers 18 and 19, a movement reversal between the two pistons 12 and 14 is accomplished. If the first piston 12 is pressed down as a result of a deflection of the piezoelectric actuator 7, this leads to the same time a lifting movement of the second piston 14 in the opposite direction. This second piston 14 displaces the working fluid contained in the second hydraulic chamber 19 via a compensation channel 20 into a compensation chamber 21. The compensation chamber 21 communicates with a leakage compensation channel 22 for purposes of discharging the working fluid and is sealed off from the piezoelectric actuator 7 by a diaphragm 29 ,

Mit anderen Worten sind die Kolben 12 und 14 in der hydraulischen Übersetzungseinrichtung 13 so miteinander gekoppelt, daß die Auslenkung des piezoelektrischen Aktors 7 übertragen wird, indem der zweite Kolben 14 entsprechend dem Übersetzungsverhältnis der Kolbendurchmesser um eine bestimmte Wegstrecke angehoben wird.In other words, the pistons 12 and 14 in the hydraulic transmission device 13 are coupled together so that the deflection of the piezoelectric actuator 7 is transmitted by the second piston 14 is raised by a certain distance corresponding to the transmission ratio of the piston diameter.

An dem dem Ventilsteuerraum 3 zugewandten Ende des Ventilglieds 6 wirkt das kugelartige Ventilschließglied 15 mit einem an dem Ventilkörper 10 ausgebildeten Ventilsitz 23 zusammen, wobei das Ventilschließglied 15 einen Niederdruckbereich 24 mit einem darin vorherrschenden Niederdruck des Fluids von einer Ablaufdrossel 30 und dem Ventil steuerraum 3, welcher mit dem Hoch- bzw. Einspritzdruck p_R des Fluids beaufschlagbar ist, trennt.At the valve control chamber 3 facing the end of the valve member 6, the spherical valve closure member 15 cooperates with a formed on the valve body 10 valve seat 23, wherein the valve closure member 15 is a low-pressure region 24 with a prevailing low pressure of the fluid from an outlet throttle 30 and the valve control chamber 3, which is acted upon by the injection or high pressure p_R of the fluid separates.

Von dem Niederdruckbereich 24 zweigt ein Leckageausgleichskanal 25 ab. Der Ventilsteuerraum 3 der Einspritzeinrichtung 2 ist in der Figur lediglich ausschnittsweise angedeutet. In dieser ist eine bewegliche Düsennadel 26 angeordnet, die eine Einspritzöffnung in eine Brennkammer ei-' nes Motors schließt und öffnet. Durch deren axialer Bewegung wird das Einspritzverhalten der Einspritzeinrichtungen 2 auf an sich bekannte Art und Weise gesteuert, wobei der Kraftstoff in dem Ventilsteuerraum 3 über die Hochdruckversorgung 4 aus dem mit dem für mehrere Einspritzeinrichtungen 2 gemeinsamen Druckspeicher 5 zugeführt wird, und der Ventilsteuerraum 3 zur Einspritzung über die Ablaufdrossel 30 und das erfindungsgemäße Ventil 1 entlastet wird.From the low-pressure region 24, a leakage compensation channel 25 branches off. The valve control chamber 3 of the injector 2 is only partially indicated in the figure. In this, a movable nozzle needle 26 is arranged, which closes and opens an injection opening in a combustion chamber of a 'nes motor. By their axial movement the injection behavior of the injectors 2 is controlled in a manner known per se, the fuel in the valve control chamber 3 being supplied via the high-pressure supply 4 from the pressure accumulator 5 common to several injectors 2, and the valve control chamber 3 being injected via the outlet throttle 30 and the valve 1 according to the invention is relieved.

Zwischen der hydraulischen Übersetzungseinrichtung 13 und dem Ventilschließglied 15 ist eine Dichtfeder 27 angeordnet, die den zweiten Kolben 14 umschließt und in dem Ventilkörper 10 derart abgestützt ist, daß durch die Federkraft der Dichtfeder 27 der zweite Kolben 14 nach unten gepreßt wird, so daß das Ventilschließglied 15 im Ruhezustand des Ventils 1 gegen den Ventilsitz 23 dichtend zum Anliegen kommt.Between the hydraulic transmission device 13 and the valve closing member 15, a sealing spring 27 is arranged, which surrounds the second piston 14 and is supported in the valve body 10 such that by the spring force of the sealing spring 27, the second piston 14 is pressed down, so that the valve closing member 15 comes to rest in the resting state of the valve 1 against the valve seat 23 sealingly.

Der hier mit Piezokeramik ausgebildete Aktuator-Einheit 7 dient erfindungsgemäß nicht nur als Huborgan, sondern auch als Kraftsensor, denn die auf die piezoelektrische Einheit wirkenden Kraftänderungen werden als Spannungsänderungen registriert. Hierzu steht der piezoelektrische Aktor 7 über eine einzige Leitung, welche als Sensor- und Steuerleitung fungiert, mit einem Steuergerät 28 in Verbindung.According to the invention, the actuator unit 7 designed here with piezoceramic not only serves as a lifting element, but also as a force sensor, because the force changes acting on the piezoelectric unit are registered as changes in voltage. For this purpose, the piezoelectric actuator 7 is connected to a control unit 28 via a single line, which functions as a sensor and control line.

Dieses Steuergerät 28 dient sowohl der Meßaufnahme, wenn der piezoelektrische Aktor 7 als Kraftmeßsensor wirkt, als auch gleichzeitig als Ansteuergerät, wenn der piezoelektrische Aktor 7 ausgelenkt werden soll. Innerhalb des Steuergeräts 28 lassen sich diese Funktionen gemeinsam über eine entsprechende elektronische Schaltung bzw. Software bewerkstelligen.This control unit 28 serves both the Meßaufnahme when the piezoelectric actuator 7 acts as Kraftmeßsensor, and at the same time as a drive device when the piezoelectric actuator 7 is to be deflected. Within the controller 28, these functions can be shared via a accomplish appropriate electronic circuit or software.

Das erfindungsgemäße Ventil 1 übernimmt die Funktion eines Druckbegrenzungsventils für einen in dem Hochdruckbereich 3 gegebenenfalls auftretenden Überdruck, der über dem Einspritzdruck p_R liegt. Der Durchmesser des Ventilsitzes 23 bestimmt bei festgelegter Federkraft der Dichtfeder 27 die Dichtkraft. Wird diese Dichtkraft überschritten, öffnet das Ventil 1 ohne Ansteuerung durch den piezoelektrischen Aktor 7 von sich aus, wenn die aus dem Überdruck in dem Hochdruckbereich 3 resultierende Gegenkraft die Dichtkraft übersteigt. In diesem Fall wird durch den Hub des zweiten Kolbens 14 und der hydraulischen Übersetzungseinrichtung 13 eine Kraft auf den piezoelektrischen Aktor 7 übertragen, der diese mißt und an das Steuergerät 28 weitergibt. So kann das Steuergerät 28 erkennen, daß eine Fehlfunktion in dem Hochdruckbereich 3 vorliegt.The valve 1 according to the invention assumes the function of a pressure relief valve for a possibly occurring in the high pressure region 3 overpressure, which is above the injection pressure p_R. The diameter of the valve seat 23 determines the sealing force when the spring force of the sealing spring 27 is fixed. If this sealing force is exceeded, the valve 1 opens without activation by the piezoelectric actuator 7 on its own if the counterforce resulting from the overpressure in the high-pressure region 3 exceeds the sealing force. In this case, a force is transmitted to the piezoelectric actuator 7 by the stroke of the second piston 14 and the hydraulic transmission device 13, which measures this and passes it on to the control unit 28. Thus, the control unit 28 can recognize that a malfunction is present in the high-pressure area 3.

Durch eine daraufhin folgende gezielte Auslenkung des piezoelektrischen Aktors 7. läßt sich dann der Hub des zweiten Kolbens 14 und damit das Ventilschließglied 15 gezielt öffnen, so daß sich der Überdruck, der in dem Hochdruckbereich 3 vorherrscht, über den Leckageausgleichskanal 25 abbauen kann.By a subsequent targeted deflection of the piezoelectric actuator 7 can then be the stroke of the second piston 14 and thus the valve closure member 15 selectively open, so that the overpressure that prevails in the high pressure region 3, can degrade through the leakage compensation channel 25.

Die Öffnung zu Zwecken des Abbaus des Überdrucks wird dabei so kurz getaktet, daß es zu keiner Ansteuerung der Düsennadel 26 selbst kommen kann. Mit anderen Worten erfolgt die Öffnung des Ventils 1 in so kurzen Zeiträumen, daß infolge der Trägheit der Düsennadel 26 diese in ihrer Schließstellung verharrt mit dem Effekt, daß die Einspritzeinrichtung 2 nicht öffnet und es zu keiner Einspritzung von Kraftstoff kommt.The opening for purposes of reducing the overpressure is clocked so short that it can come to any control of the nozzle needle 26 itself. In other words, the opening of the valve 1 is carried out in such short periods of time that due to the inertia of the nozzle needle 26, this in its closed position remains with the effect that the injector 2 does not open and there is no injection of fuel.

Es versteht sich auch, daß die Erfindung nicht nur bei den hier als bevorzugtes Einsatzgebiet beschriebenen Common-Rail-Systemen Verwendung finden kann, sondern generell bei Kraftstoffeinspritzventilen oder auch in anderen Bereichen, wie beispielsweise bei Pumpen, verwirklicht werden kann, wo ein schlagartiger Abbau eines kurzfristig auftretenden Überdrucks sichergestellt werden soll.It is also understood that the invention can not only be used in the common rail systems described here as a preferred application, but generally in fuel injection valves or in other areas, such as pumps, can be realized where a sudden degradation of a short-term overpressure is to be ensured.

Claims (10)

  1. Control valve (1) for a common rail system for controlling a fluid, having an actuator unit (7) for activating an axially displaceable valve element (6) to which a valve closing element (15) is assigned, said valve closing element (15) interacting with a value seat (23) in order to open and close the control valve (1) and disconnecting a control space (3), in which the fluid to be controlled is located at a high pressure (p_R), from the control valve (1), characterized in that, in order to measure the high pressure (p_R) which is present, the actuator unit (7) is simultaneously embodied as a force-measuring sensor and can be actuated as a function of the detected force acting on it.
  2. Control valve according to Claim 1, characterized in that the actuator unit (7) is embodied as a piezoelectric unit.
  3. Control valve according to Claim 1 or 2, characterized in that the valve element (6) is coupled to a sealing spring (27) which forces the valve closing element (15) against the valve seat (23) under the effect of a specific sealing force.
  4. Control valve according to one of the preceding claims, characterized in that the valve closing element (15) is arranged in a low pressure region (24) in which the fluid is under a low pressure when the control valve (1) is closed.
  5. Control valve according to Claim 4, characterized in that the low pressure region (24) is connected to a leakage compensating duct (25).
  6. Control valve according to one of the preceding claims, characterized in that the valve element (6) has a hydraulic transmission device (13).
  7. Control valve according to Claim 6, characterized in that the hydraulic transmission device (13) is embodied in such a way that the valve element (6) can be displaced counter to a deflection direction of the piezoelectric unit (7).
  8. Control valve according to Claim 7, characterized in that the hydraulic transmission device (13) has a first piston (12) in which a second piston (14) of the valve element (6) is guided in such a way that a hydraulic chamber (18) and (19) is arranged on each of the two sides of the second piston (14).
  9. Common rail system having a common rail pressure accumulator (5) and a plurality of injection devices (2) which can be actuated by means of one control valve (1) each in order to inject fuel from the common rail pressure accumulator (5) into the combustion chamber of an internal combustion engine, with at least one of the control valves (1) being embodied according to one of the preceding claims, and being embodied in particular at the same time as a pressure-limiting valve for the common rail pressure accumulator (5).
  10. Common rail system according to Claim 9, characterized in that the control valve (1) can be actuated by a control unit (28) in such a way that when an excess pressure is detected in the common rail pressure accumulator (5) said control valve (1) remains opened until the excess pressure is reduced via the control valve (1) without a nozzle needle (26) of the injection device (2) being actuated in the process.
EP01971670A 2000-09-07 2001-08-29 Common rail system Expired - Lifetime EP1317619B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10044120A DE10044120A1 (en) 2000-09-07 2000-09-07 Common Rail System
DE10044120 2000-09-07
PCT/DE2001/003303 WO2002020976A1 (en) 2000-09-07 2001-08-29 Common rail system

Publications (2)

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EP1317619A1 EP1317619A1 (en) 2003-06-11
EP1317619B1 true EP1317619B1 (en) 2006-03-29

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EP01971670A Expired - Lifetime EP1317619B1 (en) 2000-09-07 2001-08-29 Common rail system

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EP (1) EP1317619B1 (en)
JP (1) JP2004508494A (en)
AT (1) ATE321945T1 (en)
CZ (1) CZ20021537A3 (en)
DE (2) DE10044120A1 (en)
WO (1) WO2002020976A1 (en)

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DE10216154A1 (en) * 2002-04-12 2003-10-23 Hydraulik Ring Gmbh Pressure relief valve, in particular for high-pressure diesel pumps for injectors in motor vehicles
DE10307816A1 (en) * 2003-02-24 2004-09-02 Robert Bosch Gmbh Fuel injector
DE10333695A1 (en) * 2003-07-24 2005-03-03 Robert Bosch Gmbh Fuel injector
DE10333697A1 (en) 2003-07-24 2005-02-24 Robert Bosch Gmbh Fuel injector
DE10333696A1 (en) * 2003-07-24 2005-02-24 Robert Bosch Gmbh Fuel injector
DE10358864A1 (en) * 2003-12-16 2005-07-14 Volkswagen Ag Fuel supply device for an internal combustion engine and method for operating this
DE102007017126A1 (en) * 2007-04-11 2008-10-16 Robert Bosch Gmbh Injection Module
DE102008040629A1 (en) * 2008-07-23 2010-01-28 Robert Bosch Gmbh Method for controlling a fuel injector in the event of overpressure or failure and associated injection system
DE102012204252B3 (en) 2012-03-19 2013-08-29 Continental Automotive Gmbh Method for operating a pressure-reducing fuel-injection system and fuel-injection system with servo-valve
DE102015205114B4 (en) 2015-03-20 2022-08-04 Volkswagen Aktiengesellschaft Procedure for avoiding excessive system pressures in common rail systems

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EP0790402A2 (en) * 1996-02-13 1997-08-20 Isuzu Motors Limited Fuel injector for internal combustion engines
EP0971119A2 (en) * 1998-07-08 2000-01-12 Isuzu Motors Limited Common-rail fuel-injection system
DE19954023A1 (en) * 1998-11-30 2000-05-31 Denso Corp High pressure fuel injection system has device for controlling stroke of piezoelectric actuator in steps to control degree of opening of bleed valve feeding low pressure fuel reservoir

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EP0477400B1 (en) 1990-09-25 2000-04-26 Siemens Aktiengesellschaft Device for compensating the tolerance in the lift direction of the displacement transformer of a piezoelectric actuator
GB9610819D0 (en) * 1996-05-22 1996-07-31 Lucas Ind Plc Valve arrangement
DE29708369U1 (en) * 1997-05-09 1997-07-10 FEV Motorentechnik GmbH & Co. KG, 52078 Aachen Controllable injection valve for fuel injection on internal combustion engines
DE19917711C2 (en) * 1999-04-20 2001-06-07 Bosch Gmbh Robert Method and device for controlling an internal combustion engine

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EP0790402A2 (en) * 1996-02-13 1997-08-20 Isuzu Motors Limited Fuel injector for internal combustion engines
EP0971119A2 (en) * 1998-07-08 2000-01-12 Isuzu Motors Limited Common-rail fuel-injection system
DE19954023A1 (en) * 1998-11-30 2000-05-31 Denso Corp High pressure fuel injection system has device for controlling stroke of piezoelectric actuator in steps to control degree of opening of bleed valve feeding low pressure fuel reservoir

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CZ20021537A3 (en) 2003-10-15
DE50109392D1 (en) 2006-05-18
WO2002020976A1 (en) 2002-03-14
DE10044120A1 (en) 2002-04-04
EP1317619A1 (en) 2003-06-11
ATE321945T1 (en) 2006-04-15
JP2004508494A (en) 2004-03-18

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