EP1651855B1 - Fuel injection device - Google Patents

Fuel injection device Download PDF

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Publication number
EP1651855B1
EP1651855B1 EP04738649A EP04738649A EP1651855B1 EP 1651855 B1 EP1651855 B1 EP 1651855B1 EP 04738649 A EP04738649 A EP 04738649A EP 04738649 A EP04738649 A EP 04738649A EP 1651855 B1 EP1651855 B1 EP 1651855B1
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EP
European Patent Office
Prior art keywords
valve
pressure
piston
actuator
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 - Lifetime
Application number
EP04738649A
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German (de)
French (fr)
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EP1651855A1 (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
    • 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
    • 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
    • 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
    • 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
    • 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
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0043—Two-way valves

Definitions

  • the invention relates to a fuel injection device according to the preamble of patent claim 1.
  • Such a fuel injection device is, for example, by the DE 100 44 120 A known.
  • the aforementioned DE 100 44 120 A discloses a fuel injector including an injector, a high pressure fuel injecting line to the injector under high pressure, and a pilot valve controlling the pressure in a control chamber of the injector connected to the high pressure line, the movable valve member of which is actuatable by an actuator via a hydraulic coupler having two a piston of the coupler having cooperating pistons, wherein the seat of the movable valve member having a clear cross-sectional area f3, wherein the pistons are arranged parallel to each other, wherein the outer piston is mechanically coupled with a piston surface f4 to the actuator via a rod with a cross-sectional area f5 , and wherein the inner piston, which has a piston surface f2, actuates the control valve via a rod with a smaller cross-sectional area f1 than f2.
  • the associated hydraulic chambers are connected via a compensation chamber to the leakage line, ie at low pressure. Low pressure acts on the inner piston in the second hydraulic chamber and high
  • a control valve is known in which the direction of closing movement of a movable valve member coincides with the direction of fuel flowing out of a control chamber, so that the control valve is at least partially force balanced because of the high pressure on the second piston.
  • the fuel injection device according to the invention for internal combustion engines with the characterizing features of claim 1 has the opposite advantage that a CR injector is provided with piezoelectric actuator, in which a large valve cross-section is possible. As a result, the opening and closing of the injection valve can be done faster.
  • the integrated coupler allows a short overall length of the device. The coupler is supported by CR printing.
  • FIG. 1 An embodiment of the fuel injection device according to the invention is shown in the drawing and will be explained in more detail in the following description. It shows the single figure the essential components of a fuel injection device according to the invention with an injection valve and a control valve and a hydraulic coupler.
  • the fuel injection device 1 is supplied from a pressure accumulator (common rail) 3 with fuel at high pressure via a high-pressure line 5, from which fuel passes via an injection line 6 to an injection valve 9.
  • An internal combustion engine normally has a plurality of such injectors, and for the sake of simplicity only one is shown.
  • the injection valve 9 has a valve needle (valve piston, nozzle needle) 11, which closes with a conical valve sealing surface 12 in its closed position injection openings 13, is to be injected through the fuel into the interior of a combustion chamber of the internal combustion engine.
  • the fuel enters the area of the nozzle needle via an annular nozzle chamber 14, from which it allows to exert a pressure in the opening direction of the nozzle needle via a control surface 15 formed as a pressure shoulder. When said pressure exerts a force in the opening direction on the valve needle, which overcomes this opening counteracting forces, so the valve opens.
  • An actuator 31 serves to control the opening and closing of the injection openings. It generates a deflection and a force for actuating further elements as a function of an activation at a mechanical output.
  • it is an electrically actuated actuator.
  • it is an actuator which has a piezoelectric element, namely a piezoelectric actuator.
  • the actuator assumes a lengthy configuration or a shortened configuration depending on an electrical drive in the vertical direction of the drawing and thus in its longitudinal direction.
  • an actuator is provided with such a construction, which assumes a patentede configuration when energized (connected to a DC power supply), without energization occupies a shortened configuration.
  • the actuator forms a capacitive load and absorbs no power loss during continuous power.
  • the piezoelectric actuator by a clamping device, for. As spring so pretension that contained in the actuator piezoelectric elements are always subjected to pressure. This is known to those skilled in the art and therefore will not be referred to hereinafter. While the upper end of the piezoelectric actuator is anchored in the injection device in a manner not visible in the drawing, the lower end of the piezoelectric actuator is used to ultimately use its force and movement to open and close the injection ports.
  • a hydraulic coupler 38 is provided for its coupling, which has a piston 39 coupled to the piezoelectric actuator and a further piston 40. In the present application is generally by the coupler, an enlargement of the path of the further piston 40 in comparison to the path of the piston 39 (by appropriate choice of the hydraulically effective piston surfaces) necessary. The construction and operation of the hydraulic coupler will be described below.
  • the sink If the not directly connected to the piezoelectric actuator piston 40 of the hydraulic coupler opens a control valve 41 (or exhaust valve), the sinks Pressure in a fuel-filled control chamber 43, in which engages the upper end portion of the nozzle needle.
  • the control chamber 43 is filled with fuel under pressure via an inlet throttle 47, and when the control valve 41 is open, fuel flows out of the control chamber 43 via an outlet throttle 49.
  • the outflow of fuel is assisted by forces that tend to move the nozzle needle 11 to its open position.
  • a movable valve piece 51 sealingly abuts a valve seat 53 when the control valve 41 is closed and is mechanically coupled to the piston 40.
  • the outflowing with the valve piece 51 open from the control chamber control amount is discharged through a leakage channel 55.
  • the pistons 39 and 40 are in the example parallel to each other and into each other, manufacturing technology advantageous coaxial with each other (integrated coupler). The way in which they are coupled together is explained below.
  • an arrow is shown, which indicates the movement of this piston when the actuator performs a movement in the drawing down.
  • an arrow is shown, which indicates the movement of this piston when the piston 39 carries out the movement indicated by its arrow.
  • the movable valve piece 51 is formed substantially conically with a cylindrical extension. In particular, it rests against the valve seat 53 with the conical part in the closed state.
  • the valve piece 51 is biased by a guided by the cylindrical extension compression spring 54 in the direction of its valve seat 53. In its blocking position, it has been moved "out", namely in the direction of high pressure in the control chamber 43 to a region of lower pressure (leakage pressure).
  • the exhaust valve is therefore referred to in this case as an A-valve.
  • the valve seat 53 facing side of the Valve piece 51 is rigidly connected to an actuating part which is connected to the hydraulic coupler.
  • the connection with the piston 37 is advantageous tensile strength for a particularly fast closing.
  • the actuator 31 is connected to the piston 39 by a rod 61 having a diameter d5.
  • the piston 40 is connected to the movable valve member 51 to be actuated by a rod 63 having a diameter d1.
  • the outer piston 39 has an annular piston surface with an area size f4, the inner piston 40 has a diameter d2 (and therefore an area size 0.25 x ⁇ x d2 2 ).
  • the clear diameter of the valve seat 53 where the movable valve member abuts against it is d3.
  • Guide gaps 65 and 67 which serve to slide the pistons and through which a coupler volume is filled with fuel, are formed in the area of the outer cylindrical surface of the outer piston (opposite to a housing, not shown) and in the area of mutual sliding of the two pistons.
  • the other end region of the inner piston 40 projects into a filling space 71-2, which is filled with CR pressure via an annular groove 71 'via a channel 71 "in the piston 39.
  • the booster chamber 72 is filled 72 is penetrated by the rod 63.
  • the filling space 71-1 is penetrated by the rod 61.
  • the pistons 39 and 40 move in opposite directions and because of the desired path ratio from the actuator to the control valve at different speeds.
  • CR pressure pressure of the pressure accumulator or common rail
  • the valve member 51 is closed by the pressure in the booster chamber 72 with a proportional to (d2 2 - d1 2 ) force.
  • the filling space 71-2 is filled with CR pressure, as a result of which the seat diameter d3 of the valve part 51 can be selected to be very large, since the piston 40 largely compensates for this surface with its rear side located in the filling space 71-2.
  • the invention provides an advantageous A-valve servo-injector with CR pressure assist for very fast opening and closing of the injector.
  • the coupler ensures a short overall length.
  • An important feature of the invention is that at the rear (as opposed to the side of the booster chamber) of the piston directly connected to the control valve 40 rail pressure is applied, which supports the actuation of the control valve and the valve member 51 in the locked state of the control chamber 43rd counteracts acting pressure.
  • the force to be supplied by the actuator for closing the valve is therefore smaller than the known one.
  • a valve 51 is provided with a larger diameter d3 than the known one, which permits faster opening and closing allows the injection valve, because the flow increase and decrease in this is greater than in the known smaller A-valve.
  • a compression spring 75 in the filling chamber 71-2 pushes the pistons apart and ensures good contact of the coupler on the actuator 31 and with the valve closed 51 of the valve seat 53.
  • the invention also covers embodiments in which the high pressure fuel is not supplied by a high pressure accumulator but by a pump (e.g., unit injector) associated with the injector which also feeds the charge space.
  • a pump e.g., unit injector

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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)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The invention concerns a fuel injection device (1) comprising an injection valve (9); a conduit (5) transporting high pressure fuel to the injection valve (9), when the device is operational; and a regulating valve (41) which regulates the pressure in a control chamber (43) of the injection valve, communicating with said conduit (5). The mobile part (51) of said regulating valve can be actuated by an actuator (31) via a hydraulic coupler (39). The pistons (39, 40) are nested in parallel. A multiplying chamber (72) is located at the ends of the pistons facing the actuator (31). A filling chamber (71-2) is located inside the outer piston (39) and communicates with said conduit (5). The direction of the closing movement of the mobile part (51) of the valve coincides with the direction in which the fuel exits from the control chamber (43), such that the force exerted on the regulating valve is at least partly compensated due to the pressure exerted on the other piston (40) in the filling chamber (71-2).

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Kraftstoffeinspritzvorrichtung nach der Gattung des Patentanspruchs 1.The invention relates to a fuel injection device according to the preamble of patent claim 1.

Eine derartige Kraftstoffeinspritzvorrichtung ist beispielsweise durch die DE 100 44 120 A bekannt geworden.Such a fuel injection device is, for example, by the DE 100 44 120 A known.

Ein CR-Injektor (CR = Common Rail) mit Piezoaktor (= Piezosteller) und Übersetzung durch hydraulischen Koppler bekannt. Ebenfalls bekannt sind integrierte Koppler mit koaxial ineinander angeordneten Kolben. Die bekannte Vorrichtung verwendet ein A-Ventil als Steuerventil. Dieses kann nur mit relativ kleinem Durchmesser ausgebildet werden, da sonst die Kräfte am Ventil zu hoch werden und es nicht durch einen Piezoaktor betätigbar ist.A CR injector (CR = Common Rail) with piezo actuator (= piezo actuator) and translation through hydraulic coupler known. Also known are integrated couplers with coaxially arranged pistons. The known device uses an A-valve as a control valve. This can only be formed with a relatively small diameter, otherwise the forces on the valve are too high and it is not actuated by a piezoelectric actuator.

Die eingangs genannte DE 100 44 120 A offenbart eine Kraftstoffeinspritzvorrichtung mit einem Einspritzventil, einer dem Einspritzventil bei Betrieb Kraftstoff unter hohem Druck zuführenden Hochdruckleitung und einem den Druck in einer mit der Hochdruckleitung verbundenen Steuerkammer des Einspritzventils steuernden Steuerventil, dessen bewegliches Ventilteil von einem Aktor über einen hydraulischen Koppler betätigbar ist, der zwei mit einem Kopplervolumen des Kopplers zusammenwirkende Kolben aufweist, wobei der Sitz des beweglichen Ventilteils eine lichte Querschnittsfläche f3 aufweist, wobei die Kolben parallel zueinander ineinander angeordnet sind, wobei der äußere Kolben mit einer Kolbenfläche f4 mit dem Aktor über eine Stange mit einer Querschnittsfläche f5 mechanisch gekoppelt ist, und wobei der innere Kolben, der eine Kolbenfläche f2 aufweist, über eine Stange mit einer gegenüber f2 kleineren Querschnittsfläche f1 das Steuerventil betätigt. Die zugehörigen Hydraulikkammern sind über eine Ausgleichkammer an die Leckageleitung, also an Niederdruck, angeschlossen. Auf den inneren Kolben wirkt in der zweiten Hydraulikkammer Niederdruck und bei geschlossenem Ventilschließglied Hochdruck, so dass das Steuerventil nicht kraftausgeglichen ist.The aforementioned DE 100 44 120 A discloses a fuel injector including an injector, a high pressure fuel injecting line to the injector under high pressure, and a pilot valve controlling the pressure in a control chamber of the injector connected to the high pressure line, the movable valve member of which is actuatable by an actuator via a hydraulic coupler having two a piston of the coupler having cooperating pistons, wherein the seat of the movable valve member having a clear cross-sectional area f3, wherein the pistons are arranged parallel to each other, wherein the outer piston is mechanically coupled with a piston surface f4 to the actuator via a rod with a cross-sectional area f5 , and wherein the inner piston, which has a piston surface f2, actuates the control valve via a rod with a smaller cross-sectional area f1 than f2. The associated hydraulic chambers are connected via a compensation chamber to the leakage line, ie at low pressure. Low pressure acts on the inner piston in the second hydraulic chamber and high pressure with the valve closing element closed so that the control valve is not balanced with force.

Aus der WO 01/31192 A ist ein Steuerventil bekannt, bei dem die Richtung der Schließbewegung eines beweglichen Ventilteils mit der Richtung von aus einer Steuerkammer ausströmendem Kraftstoff übereinstimmt, so dass das Steuerventil wegen des auf den zweiten Kolben Hochdrucks mindestens teilweise kraftausgeglichen ist.From the WO 01/31192 A a control valve is known in which the direction of closing movement of a movable valve member coincides with the direction of fuel flowing out of a control chamber, so that the control valve is at least partially force balanced because of the high pressure on the second piston.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat dem gegenüber den Vorteil, dass ein CR-Injektor mit Piezosteller geschaffen wird, bei dem ein großer Ventilquerschnitt möglich ist. Dadurch kann das Öffnen und Schließen des Einspritzventils schneller erfolgen. Der integrierte Koppler ermöglicht eine kurze Baulänge der Vorrichtung. Der Koppler ist durch CR-Druck unterstützt.The fuel injection device according to the invention for internal combustion engines with the characterizing features of claim 1 has the opposite advantage that a CR injector is provided with piezoelectric actuator, in which a large valve cross-section is possible. As a result, the opening and closing of the injection valve can be done faster. The integrated coupler allows a short overall length of the device. The coupler is supported by CR printing.

Zeichnungdrawing

Ein Ausführungsbeispiel der erfindungsgemäßen Kraftstoffeinspritzvorrichtung ist in der Zeichnung dargestellt und wird in der nachfolgenden Beschreibung näher erläutert. Es zeigt
die einzige Figur die wesentlichen Komponenten einer erfindungsgemäßen Kraftstoffeinspritzvorrichtung mit einem Einspritzventil und einem Steuerventil sowie einem hydraulischen Koppler.An embodiment of the fuel injection device according to the invention is shown in the drawing and will be explained in more detail in the following description. It shows
the single figure the essential components of a fuel injection device according to the invention with an injection valve and a control valve and a hydraulic coupler.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Die erfindungsgemäße Kraftstoffeinspritzvorrichtung 1 wird von einem Druckspeicher (Common Rail) 3 mit Kraftstoff unter hohem Druck über eine Hochdruckleitung 5 versorgt, von der aus Kraftstoff über eine Einspritzleitung 6 zu einem Einspritzventil 9 gelangt. Eine Brennkraftmaschine hat normalerweise mehrere derartige Einspritzventile, und der Einfachheit halber ist lediglich eines dargestellt. Das Einspritzventil 9 weist eine Ventilnadel (Ventilkolben, Düsennadel) 11 auf, die mit einer konischen Ventildichtfläche 12 in ihrer Schließstellung Einspritzöffnungen 13, durch die Kraftstoff ins Innere eines Verbrennungsraums des Verbrennungsmotors eingespritzt werden soll, verschließt. Der Kraftstoff gelangt in den Bereich der Düsennadel über einen ringförmigen Düsenraum 14, von dem aus er über eine als Druckschulter ausgebildete Steuerfläche 15 einen Druck in Öffnungsrichtung der Düsennadel auszuüben gestattet. Wenn der genannte Druck eine Kraft in Öffnungsrichtung auf die Ventilnadel ausübt, die diesem Öffnen entgegen wirkende Kräfte überwindet, so öffnet sich das Ventil.The fuel injection device 1 according to the invention is supplied from a pressure accumulator (common rail) 3 with fuel at high pressure via a high-pressure line 5, from which fuel passes via an injection line 6 to an injection valve 9. An internal combustion engine normally has a plurality of such injectors, and for the sake of simplicity only one is shown. The injection valve 9 has a valve needle (valve piston, nozzle needle) 11, which closes with a conical valve sealing surface 12 in its closed position injection openings 13, is to be injected through the fuel into the interior of a combustion chamber of the internal combustion engine. The fuel enters the area of the nozzle needle via an annular nozzle chamber 14, from which it allows to exert a pressure in the opening direction of the nozzle needle via a control surface 15 formed as a pressure shoulder. When said pressure exerts a force in the opening direction on the valve needle, which overcomes this opening counteracting forces, so the valve opens.

Zum Steuern des Öffnens und Schließens der Einspritzöffnungen dient ein Aktor 31. Dieser erzeugt in Abhängigkeit von einer Ansteuerung an einem mechanischen Ausgang eine Auslenkung und eine Kraft zum Betätigen weiterer Elemente. Im Beispiel handelt es sich um einen elektrisch betätigten Aktor. Im Beispiel ist es ein Aktor, der ein piezoelektrisches Element aufweist, nämlich ein Piezoaktor. Der Aktor nimmt in Abhängigkeit von einer elektrischen Ansteuerung in Vertikalrichtung der Zeichnung und somit in seiner Längsrichtung eine gelängte Konfiguration oder eine verkürzte Konfiguration ein. Im Beispiel ist ein Aktor mit einer derartigen Konstruktion vorgesehen, der bei Bestromung (Anschluss an eine Gleichstromversorgung) eine gelängte Konfiguration einnimmt, ohne Bestromung eine verkürzte Konfiguration einnimmt. Der Aktor bildet eine kapazitive Last und nimmt bei Dauerbestromung keine Verlustleistung auf. Es kann vorteilhaft oder erforderlich sein, den Piezoaktor durch eine Spannvorrichtung, z. B. Feder, so vorzuspannen, dass im Aktor enthaltene piezoelektrische Elemente stets auf Druck beansprucht sind. Dies ist den Fachleuten bekannt, und deshalb wird hierauf im Folgenden nicht hingewiesen. Während das obere Ende des Piezoaktors in einer in der Zeichnung nicht sichtbaren Weise in der Einspritzvorrichtung verankert ist, dient das untere Ende des Piezoaktors dazu, dessen Kraft und Bewegung letztendlich zum Öffnen und Schließen der Einspritzöffnungen zu verwenden. Hierzu ist für seine Ankopplung ein hydraulischer Koppler 38 vorgesehen, der einen mit dem Piezoaktor gekoppelten Kolben 39 und einen weiteren Kolben 40 aufweist. Im vorliegenden Anwendungsfall ist im allgemeinen durch den Koppler eine Vergrößerung des Wegs des weiteren Kolbens 40 im Vergleich zum Weg des Kolbens 39 (durch passende Wahl der hydraulisch wirksamen Kolbenflächen) nötig. Die Konstruktion und Wirkungsweise des hydraulischen Kopplers wird weiter unten beschrieben.An actuator 31 serves to control the opening and closing of the injection openings. It generates a deflection and a force for actuating further elements as a function of an activation at a mechanical output. In the example, it is an electrically actuated actuator. In the example, it is an actuator which has a piezoelectric element, namely a piezoelectric actuator. The actuator assumes a lengthy configuration or a shortened configuration depending on an electrical drive in the vertical direction of the drawing and thus in its longitudinal direction. In the example, an actuator is provided with such a construction, which assumes a gelangte configuration when energized (connected to a DC power supply), without energization occupies a shortened configuration. The actuator forms a capacitive load and absorbs no power loss during continuous power. It may be advantageous or necessary, the piezoelectric actuator by a clamping device, for. As spring so pretension that contained in the actuator piezoelectric elements are always subjected to pressure. This is known to those skilled in the art and therefore will not be referred to hereinafter. While the upper end of the piezoelectric actuator is anchored in the injection device in a manner not visible in the drawing, the lower end of the piezoelectric actuator is used to ultimately use its force and movement to open and close the injection ports. For this purpose, a hydraulic coupler 38 is provided for its coupling, which has a piston 39 coupled to the piezoelectric actuator and a further piston 40. In the present application is generally by the coupler, an enlargement of the path of the further piston 40 in comparison to the path of the piston 39 (by appropriate choice of the hydraulically effective piston surfaces) necessary. The construction and operation of the hydraulic coupler will be described below.

Wenn der mit dem Piezoaktor nicht unmittelbar verbundene Kolben 40 des hydraulischen Kopplers ein Steuerventil 41 (oder Auslassventil) öffnet, sinkt der Druck in einer mit Kraftstoff gefüllten Steuerkammer 43, in die der obere Endabschnitt der Düsennadel eingreift. Die Steuerkammer 43 wird mit Kraftstoff unter Druck über eine Zulaufdrossel 47 gefüllt, und bei geöffnetem Steuerventil 41 fließt Kraftstoff über eine Ablaufdrossel 49 aus der Steuerkammer 43 aus. Das Ausfließen von Kraftstoff wird durch Kräfte unterstützt, die die Düsennadel 11 in ihre offene Stellung zu bewegen bestrebt sind. Ein bewegliches Ventilstück 51 liegt bei geschlossenem Steuerventil 41 an einem Ventilsitz 53 dichtend an und ist mit dem Kolben 40 mechanisch gekoppelt. Die bei geöffnetem Ventilstück 51 aus der Steuerkammer ausströmende Steuermenge wird durch einen Leckagekanal 55 abgeführt. Bei geschlossenem Ventilstück 51 wird dieses von der Steuerkammer her mit Raildruck (= Druck in der Leitung 5) beaufschlagt, wobei der Druck auf die Fläche mit dem Durchmesser d3 wirkt.If the not directly connected to the piezoelectric actuator piston 40 of the hydraulic coupler opens a control valve 41 (or exhaust valve), the sinks Pressure in a fuel-filled control chamber 43, in which engages the upper end portion of the nozzle needle. The control chamber 43 is filled with fuel under pressure via an inlet throttle 47, and when the control valve 41 is open, fuel flows out of the control chamber 43 via an outlet throttle 49. The outflow of fuel is assisted by forces that tend to move the nozzle needle 11 to its open position. A movable valve piece 51 sealingly abuts a valve seat 53 when the control valve 41 is closed and is mechanically coupled to the piston 40. The outflowing with the valve piece 51 open from the control chamber control amount is discharged through a leakage channel 55. When the valve piece 51 is closed, it is acted upon by the control chamber with rail pressure (= pressure in the line 5), the pressure acting on the surface with the diameter d3.

Die Kolben 39 und 40 sind im Beispiel parallel zueinander und ineinander, fertigungstechnisch vorteilhaft koaxial ineinander angeordnet (integrierter Koppler). Die Art, in der sie miteinander gekoppelt sind, wird unten erläutert. Im Kolben 39 ist ein Pfeil eingezeichnet, der die Bewegung dieses Kolbens anzeigt, wenn der Aktor eine Bewegung in der Zeichnung nach unten ausführt. Im Kolben 40 ist ein Pfeil eingezeichnet, der die Bewegung dieses Kolbens anzeigt, wenn der Kolben 39 die durch seinen Pfeil bezeichnete Bewegung ausführt. Durch Vergleich des Pfeil des Kolbens 40 mit der Richtung, in der das bewegliche Ventilelement des vom hydraulischen Wandler 38 zu betätigenden Ventils zum Öffnen bzw. zum Schließen bewegt werden muss, ist aus der Zeichnung unmittelbar ersichtlich, ob die in der Zeichnung eingezeichnete Richtung der genannten Pfeile einem Öffnungsvorgang oder einem Schließvorgang des genannten Ventils entspricht.The pistons 39 and 40 are in the example parallel to each other and into each other, manufacturing technology advantageous coaxial with each other (integrated coupler). The way in which they are coupled together is explained below. In the piston 39, an arrow is shown, which indicates the movement of this piston when the actuator performs a movement in the drawing down. In the piston 40, an arrow is shown, which indicates the movement of this piston when the piston 39 carries out the movement indicated by its arrow. By comparing the arrow of the piston 40 with the direction in which the movable valve element of the valve to be actuated by the hydraulic converter 38 has to be moved to open or close, it can be seen directly from the drawing whether the direction indicated in the drawing is that of FIG Arrows corresponds to an opening operation or a closing operation of said valve.

Das bewegliche Ventilstück 51 ist im wesentlichen kegelförmig mit einem zylindrischen Fortsatz ausgebildet. Insbesondere liegt es mit dem kegelförmigen Teil im geschlossenen Zustand an dem Ventilsitz 53 an. Das Ventilstück 51 ist durch eine von dem zylindrischen Fortsatz geführte Druckfeder 54 in Richtung auf seinen Ventilsitz 53 vorgespannt. In seiner Sperrstellung ist es nach "außen" bewegt worden, nämlich in Richtung vom hohen Druck in der Steuerkammer 43 zu einem Bereich niedrigeren Drucks (Leckagedruck). Das Auslassventil wird in diesem Fall daher als A-Ventil bezeichnet. Die dem Ventilsitz 53 zugewandte Seite des Ventilstücks 51 ist mit einem Betätigungsteil starr verbunden, das mit dem hydraulischen Koppler verbunden ist. Die Verbindung mit dem Kolben 37 ist vorteilhaft zugfest für ein besonders schnelles Schließen.The movable valve piece 51 is formed substantially conically with a cylindrical extension. In particular, it rests against the valve seat 53 with the conical part in the closed state. The valve piece 51 is biased by a guided by the cylindrical extension compression spring 54 in the direction of its valve seat 53. In its blocking position, it has been moved "out", namely in the direction of high pressure in the control chamber 43 to a region of lower pressure (leakage pressure). The exhaust valve is therefore referred to in this case as an A-valve. The valve seat 53 facing side of the Valve piece 51 is rigidly connected to an actuating part which is connected to the hydraulic coupler. The connection with the piston 37 is advantageous tensile strength for a particularly fast closing.

Der Aktor 31 ist mit dem Kolben 39 durch eine Stange 61 mit einem Durchmesser d5 verbunden. Der Kolben 40 ist mit dem von ihm zu betätigenden beweglichen Ventilteil 51 durch eine Stange 63 mit einem Durchmesser d1 verbunden. Der äußere Kolben 39 hat eine kreisringförmige Kolbenfläche mit einer Flächengröße f4 , der innere Kolben 40 hat einen Durchmesser d2 (und daher eine Flächengröße 0,25 x π x d22). Der lichte Durchmesser des Ventilsitzes 53 dort, wo das bewegliche Ventilteil an ihm anliegt, ist d3.The actuator 31 is connected to the piston 39 by a rod 61 having a diameter d5. The piston 40 is connected to the movable valve member 51 to be actuated by a rod 63 having a diameter d1. The outer piston 39 has an annular piston surface with an area size f4, the inner piston 40 has a diameter d2 (and therefore an area size 0.25 x π x d2 2 ). The clear diameter of the valve seat 53 where the movable valve member abuts against it is d3.

Führungsspalte 65 und 67, die der Gleitführung der Kolben dienen und durch die hindurch ein Kopplervolumen mit Treibstoff gefüllt wird, sind im Bereich der zylindrischen Außenfläche des äußeren Kolbens (gegenüber einem nicht gezeigten Gehäuse) und im Bereich der gegenseitigen Gleitführung der beiden Kolben gebildet.Guide gaps 65 and 67, which serve to slide the pistons and through which a coupler volume is filled with fuel, are formed in the area of the outer cylindrical surface of the outer piston (opposite to a housing, not shown) and in the area of mutual sliding of the two pistons.

Maßgeblich für die Funktion sind die den oben genannten Durchmessern d1 bis d3 und d5 (für kreisförmige Querschnitte) entsprechenden Flächen f1 bis f3 und f5 sowie die genannte Fläche f4. Kreisförmige Querschnitte sind zwar für die Herstellung zweckmäßig, die Erfindung ist jedoch hierauf nicht beschränkt.Decisive for the function are the areas f1 to f3 and f5 corresponding to the above-mentioned diameters d1 to d3 and d5 (for circular cross sections) as well as the mentioned area f4. Although circular cross sections are useful for the production, but the invention is not limited thereto.

Die dem Aktor 31 abgewandten Endbereiche der Kolben 39 und 40 greifen in einen gemeinsamen Übersetzerraum 72 ein. Der andere Endbereich des Kolbens 39 greift in einen Füllraum 71-1 ein, der mit der Leitung 5 verbunden ist. Der andere Endbereich des inneren Kolbens 40 ragt in einen Füllraum 71-2, der über eine Ringnut 71' über einen Kanal 71" im Kolben 39 mit CR-Druck befüllt wird. Über die Führungsspalte 65 und 67 wird der Übersetzerraum 72 gefüllt. Der Übersetzerraum 72 wird von der Stange 63 durchdrungen. Der Füllraum 71-1 wird von der Stange 61 durchdrungen. Die Kolben 39 und 40 bewegen sich gegensinnig und wegen der gewünschten Weg-Übersetzung vom Aktor zum Steuerventil mit unterschiedlicher Geschwindigkeit.The actuator 31 facing away from the end portions of the pistons 39 and 40 engage in a common translator 72 a space. The other end portion of the piston 39 engages in a filling space 71-1 which is connected to the conduit 5. The other end region of the inner piston 40 projects into a filling space 71-2, which is filled with CR pressure via an annular groove 71 'via a channel 71 "in the piston 39. Via the guide gaps 65 and 67, the booster chamber 72 is filled 72 is penetrated by the rod 63. The filling space 71-1 is penetrated by the rod 61. The pistons 39 and 40 move in opposite directions and because of the desired path ratio from the actuator to the control valve at different speeds.

Der Aktor 31 (Piezosteller) ist im geschlossenen Zustand des Einspritzventils . 9 mit Strom und gelängt. Zum Öffnen des Steuerventils 41 wird der elektrische Strom zum Aktor 31 abgeschaltet und der Aktor wird kürzer. Dadurch wird der Kolben 39 (erster Übersetzerkolben) in der Figur nach oben bewegt, unterstützt von der Feder 75. In dem Übersetzerraum 72 ist im Ruhezustand CR-Druck (= Druck des Druckspeichers bzw. Common Rail) als Systemdruck. Im Übersetzerraum 72 sinkt durch das Bewegen des Kolbens 39 nach oben der Druck. Diese Druckabnahme bewegt den Kolben 40 (zweiter Übersetzerkolben) nach unten und öffnet durch gleich gerichtete Bewegung des Ventilteils 51 das Steuerventil 41, das ein A-Ventil ist. Zum schnellen Schließen des Ventilteils 51 ist dieses fest mit der Stange 63 und somit mit dem Kolben 40 verbunden. Das Ventilteil 51 wird durch den Druck in dem Übersetzerraum 72 mit einer zu (d22 - d12) proportionalen Kraft geschlossen. Der Füllraum 71-2 ist mit CR-Druck befüllt, dadurch ist der Sitzdurchmesser d3 des Ventilteils 51 sehr groß wählbar, da der Kolben 40 diese Fläche mit seiner im Füllraum 71-2 befindlichen Rückseite weitgehend ausgleicht. Somit schafft die Erfindung einen vorteilhaften A-Ventil-Servo-Injektor mit CR-Druckunterstützung für sehr schnelles Öffnen und Schließen des Einspritzventils. Der Koppler sorgt für eine kurze Baulänge.The actuator 31 (piezo actuator) is in the closed state of the injection valve. 9 with electricity and lengthened. To open the control valve 41, the electric current to the actuator 31 is turned off and the actuator is shorter. As a result, the piston 39 (first booster piston) is moved upward in the figure, assisted by the spring 75. In the booster chamber 72, CR pressure (= pressure of the pressure accumulator or common rail) is at rest as system pressure. In the interpreter room 72, by moving the piston 39 upward, the pressure decreases. This pressure decrease moves the piston 40 (second booster piston) downwards and opens by the same direction movement of the valve member 51, the control valve 41, which is an A-valve. For fast closing of the valve member 51, this is firmly connected to the rod 63 and thus to the piston 40. The valve member 51 is closed by the pressure in the booster chamber 72 with a proportional to (d2 2 - d1 2 ) force. The filling space 71-2 is filled with CR pressure, as a result of which the seat diameter d3 of the valve part 51 can be selected to be very large, since the piston 40 largely compensates for this surface with its rear side located in the filling space 71-2. Thus, the invention provides an advantageous A-valve servo-injector with CR pressure assist for very fast opening and closing of the injector. The coupler ensures a short overall length.

Ein wichtiges Merkmal der Erfindung besteht darin, dass an der Rückseite (im Gegensatz zu der Seite am Übersetzerraum) des mit dem Steuerventil direkt verbundenen Kolbens 40 Raildruck anliegt, der die Betätigung des Steuerventils unterstützt und dem auf das Ventilteil 51 im Sperrzustand von der Steuerkammer 43 her wirkenden Druck entgegen wirkt.An important feature of the invention is that at the rear (as opposed to the side of the booster chamber) of the piston directly connected to the control valve 40 rail pressure is applied, which supports the actuation of the control valve and the valve member 51 in the locked state of the control chamber 43rd counteracts acting pressure.

Wegen des Raildrucks in der Füllkammer 71-2 ist d3 weitgehend kraftausgeglichen. Es steht daher im Vergleich zum Stand der Technik ein größerer Überschuss an Kraft, die vom Aktor geliefert wird, zur Beschleunigung der Masse des beweglichen Ventilteils zur Verfügung. Die Erfindung schafft somit eine Variante mit teilausgeglichenem (= bezüglich der Kraft teilweise ausgeglichenem) Steuerventil, wobei das Ventil ein A-Ventil ist. Die vom Aktor zum Schließen des Ventils zu liefernde Kraft ist daher gegenüber dem Bekannten kleiner. Stattdessen ist bei einer Ausführungsform ein Ventil 51 mit einem gegenüber dem Bekannten größeren Durchmesser d3 vorgesehen, der ein schnelleres Öffnen und Schließen des Einspritzventils ermöglicht, weil die Strömungszunahme und -Abnahme in diesem größer ist als bei dem bekannten kleineren A-Ventil.Because of the rail pressure in the filling chamber 71-2, d 3 is largely force-balanced. Therefore, compared with the prior art, there is a greater surplus of force supplied by the actuator for accelerating the mass of the movable valve member. The invention thus provides a variant with partially balanced (= partially balanced with respect to the force) control valve, wherein the valve is an A-valve. The force to be supplied by the actuator for closing the valve is therefore smaller than the known one. Instead, in one embodiment, a valve 51 is provided with a larger diameter d3 than the known one, which permits faster opening and closing allows the injection valve, because the flow increase and decrease in this is greater than in the known smaller A-valve.

Eine Druckfeder 75 im Füllraum 71-2 drückt die Kolben auseinander und sorgt für gute Anlage des Kopplers am Aktor 31 und bei geschlossenem Ventil des Ventilteils 51 am Ventilsitz 53.A compression spring 75 in the filling chamber 71-2 pushes the pistons apart and ensures good contact of the coupler on the actuator 31 and with the valve closed 51 of the valve seat 53.

Die Erfindung erfasst auch Ausführungsformen, bei denen der unter hohem Druck stehende Kraftstoff nicht von einem Hochdruckspeicher zugeführt wird, sondern von einer dem Einspritzventil zugeordneten Pumpe (z.B. Pumpe-Düse-Einheit, Unit Injector), die auch den Füllraum speist.The invention also covers embodiments in which the high pressure fuel is not supplied by a high pressure accumulator but by a pump (e.g., unit injector) associated with the injector which also feeds the charge space.

Claims (1)

  1. Fuel injection device (1) having an injection valve (9), having a high-pressure line (5) which supplies highly pressurized fuel to the injection valve (9) during operation, and having a control valve (41) which controls the pressure in a control chamber (43), which is connected to the high-pressure line (5), of the injection valve, the movable valve part (51) of which control valve (41) can be actuated by an actuator (31) via a hydraulic coupler (38) which has two pistons (39, 40) which interact with a coupler volume of the coupler, the seat (53) of the movable valve part (51) having a clear cross-sectional area f3, the pistons (39, 40) being arranged parallel to one another and one inside the other, the outer piston (39) being mechanically coupled with a piston surface f4 to the actuator (31) via a rod (61) with a cross-sectional area f5, and the inner piston (40), which has a piston surface f2, actuating the control valve (41) via a rod (63) with a cross-sectional area f1 which is smaller than f2,
    characterized
    in that the outer piston (39) delimits, with its end facing towards the actuator (31), a first high-pressure filling chamber (71-1) which is connected to the high-pressure line (5),
    in that a second high-pressure filling chamber (71-2), which is connected to the high-pressure line (5), is provided in the interior of the outer piston (39),
    in that a booster chamber (72) is arranged at those ends of the pistons (39, 40) which face away from the actuator (31), which booster chamber (72) is connected to the two high-pressure filling chambers (71-1, 71-2) via guide gaps (65, 67),
    and in that the direction of the closing movement of the movable valve part (51) corresponds to the direction of fuel flowing out of the control chamber (43), such that the control valve (41) is at least partially force-balanced on account of the high pressure acting on the inner piston (40) in the second high-pressure filling chamber (71-2).
EP04738649A 2003-07-24 2004-06-09 Fuel injection device Expired - Lifetime EP1651855B1 (en)

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DE10333697A DE10333697A1 (en) 2003-07-24 2003-07-24 Fuel injector
PCT/DE2004/001197 WO2005010340A1 (en) 2003-07-24 2004-06-09 Fuel injection device

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EP1651855A1 EP1651855A1 (en) 2006-05-03
EP1651855B1 true EP1651855B1 (en) 2010-01-27

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JP6017690B2 (en) * 2012-08-08 2016-11-02 ボルボ ラストバグナー アーベー Flow control system
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US7275520B2 (en) 2007-10-02
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DE502004010708D1 (en) 2010-03-18
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TW200504281A (en) 2005-02-01
JP2007506888A (en) 2007-03-22

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