EP1651857B1 - Fuel injection device - Google Patents

Fuel injection device Download PDF

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Publication number
EP1651857B1
EP1651857B1 EP04738652A EP04738652A EP1651857B1 EP 1651857 B1 EP1651857 B1 EP 1651857B1 EP 04738652 A EP04738652 A EP 04738652A EP 04738652 A EP04738652 A EP 04738652A EP 1651857 B1 EP1651857 B1 EP 1651857B1
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EP
European Patent Office
Prior art keywords
valve
actuator
piston
coupler
space
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
EP04738652A
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German (de)
French (fr)
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EP1651857A1 (en
Inventor
Friedrich Boecking
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP1651857A1 publication Critical patent/EP1651857A1/en
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Publication of EP1651857B1 publication Critical patent/EP1651857B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0073—Pressure balanced valves
    • 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
    • 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
    • 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
    • F02M63/0031—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
    • 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

Definitions

  • the invention relates to a fuel injection device according to the preamble of claim 1.
  • a fuel injection device is, for example by the DE 101 01 802 A known.
  • 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, so that it is not actuated by a piezoelectric actuator.
  • a booster chamber of the hydraulic coupler is formed within the outer piston between the inner and the outer piston.
  • the actuator acts directly on the outer piston, while the inner piston actuates the control valve via a rod.
  • the fuel injection device according to the invention for internal combustion engines with the features of the independent claim 1 has the opposite advantage that a CR injector is provided with piezoelectric actuator, in which a large cross-section of the valve 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.
  • 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 passes into the region 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 designed 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 gelangete configuration when energized (connected to a DC power supply), without energization takes a shortened configuration.
  • the actuator forms a capacitive load and does not dissipate power 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.
  • 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 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 member 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 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 inner piston 39 has a diameter d4, the outer piston 40 has an annular piston surface of size f2.
  • 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 actuator 31 facing 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 71-2; this is connected via bores in the lower end wall of the piston 40, which is connected to the conduit 5.
  • the other end portion of the inner piston 40 projects into the filling space 71-2.
  • the translator space 72 is filled via the guide gaps 65 and 67.
  • the translator space 72 is penetrated by the rod 61.
  • the filling space 71-1 is penetrated by the rod 63.
  • the pistons 39 and 40 move in opposite directions and because of the desired path translation from the actuator to the control valve at different speeds.
  • the valve member 51 For fast closing of the valve member 51, this is preferably fixedly connected to the rod 63 and thus to the piston 40. Because of the CR pressure in the booster chamber 72, 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 side located in the booster chamber 72.
  • 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 on the side of the piston 39 (in the booster chamber), which faces away from the control valve, rail pressure is applied, which supports the actuation of the control valve and the pressure acting on the valve member 51 in the locked state from the control chamber 43 forth counteracts.
  • d3 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 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 diameter larger than the known diameter d3, which allows a faster opening and closing of the injection valve, because the flow increase and decrease is greater in this 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.
  • a further filling space 90 which is connected to the line 5, is present at a distance from the space of the coupler closest to the actuator 31.
  • the additional filling space 90 surrounds the actuator 31 in its lower end region. Preferably, it surrounds the entire actuator 31.
  • a guide gap 94 of the rod 61 is dimensioned for additional filling of the adjacent space of the coupler with pressurized fuel.
  • the additional filling space 90 does not exist or is not connected to the line 5 and does not have the function of a filling space. In this case, it may be appropriate to have a hole in which the Rod 61 is guided in a housing, not shown, of the entire device to dimension for the smallest possible outflow of fuel from the coupler.
  • 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 relates to a fuel injection device (1) comprising an injection valve (9), a line (5), which supplies fuel under high pressure to the injection valve (9) during operation, a control valve (41), which controls the pressure in a control chamber (43) of the injection valve, this control chamber being connected to said line (5), and the moving valve part (51) of the control valve can be actuated by an actuator (31) via a hydraulic coupler (38), which has two plungers (39, 40) that interact with a coupler volume of the coupler. The injection valve also comprises means for filling the coupler volume with pressurized fuel via guide gaps (65, 67) of the plungers (39, 40), whereby the plungers (39, 40) are placed inside one another while being parallel to one another. A translator space (72) is placed at the ends of the plungers (39, 20, 40), said ends facing the actuator (31). A filling space (71-2) is provided inside the outer plunger (39) and is connected to said line (5). One of the plungers (39) is mechanically coupled to the actuator (31) via a rod (61), and the other plunger (40) actuates the control valve (41) via a rod (63), whereby the direction of the closing movement of the moving valve part (51) matches the direction of fuel flowing out of the control chamber (43) so that the control valve is subjected, at least in part, to an equilibrium of forces due to the force acting upon the other plunger (40) inside the translator space (72).

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Kraftstoffeinspritzvorrichtung nach dem Oberbegriff des Anspruchs 1. Eine derartige Kraftstoffeinspritzvorrichtung ist beispielsweise durch die DE 101 01 802 A bekannt.The invention relates to a fuel injection device according to the preamble of claim 1. Such a fuel injection device is, for example by the DE 101 01 802 A known.

Ein CR-Injektor (CR = Common Rail) mit Piezoaktor (= Piezosteller) und Übersetzung durch hydraulischen Koppler ist 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, so dass es nicht durch einen Piezoaktor betätigbar ist.A CR injector (CR = common rail) with piezo actuator (= piezo actuator) and transmission by hydraulic coupler is 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, so that it is not actuated by a piezoelectric actuator.

Bei der aus der eingangs genannten DE 101 01 802 A bekannten Kraftstoffeinspritzvorrichtung ist ein Übersetzerraum des hydraulischen Kopplers innerhalb des äußeren Kolbens zwischen dem innerem und dem äußeren Kolben gebildet. Der Aktor wirkt direkt auf den äußeren Kolben, während der innere Kolben über eine Stange das Steuerventil betätigt.When from the aforementioned DE 101 01 802 A known fuel injector, a booster chamber of the hydraulic coupler is formed within the outer piston between the inner and the outer piston. The actuator acts directly on the outer piston, while the inner piston actuates the control valve via a rod.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen mit den Merkmalen des unabhängigen Anspruchs 1 hat dem gegenüber den Vorteil, dass ein CR-Injektor mit Piezosteller geschaffen wird, bei dem ein großer Querschnitt des Ventils 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 features of the independent claim 1 has the opposite advantage that a CR injector is provided with piezoelectric actuator, in which a large cross-section of the valve 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 become more apparent in the following description explained. 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 passes into the region 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 designed 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 gelangete configuration when energized (connected to a DC power supply), without energization takes a shortened configuration. The actuator forms a capacitive load and does not dissipate power 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.When the piston 40 of the hydraulic coupler not directly connected to the piezoactuator opens a control valve 41 (or exhaust valve), the pressure in a fuel-filled control chamber 43 into which the upper end portion of the nozzle needle engages decreases. 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 must be moved to open or close, it can be seen directly from the drawing, whether the drawn in the drawing direction of said 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 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 member 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 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 innere Kolben 39 hat einen Durchmesser d4, der äußere Kolben 40 hat eine kreisringförmige Kolbenfläche der Größe f2. 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 inner piston 39 has a diameter d4, the outer piston 40 has an annular piston surface of size f2. 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, d3 bis d5 (für kreisförmige Querschnitte) entsprechenden Flächen f1, f3 bis f5 und die genannte Fläche f2. Kreisförmige Querschnitte sind zwar für die Herstellung zweckmäßig, die Erfindung ist jedoch hierauf nicht beschränkt.Decisive for the function are the surfaces f1, f3 to f5 corresponding to the above-mentioned diameters d1, d3 to d5 (for circular cross sections) and the said surface f2. Although circular cross sections are useful for the production, but the invention is not limited thereto.

Die dem Aktor 31 zu gewandten Endbereiche der Kolben 39 und 40 greifen in einen gemeinsamen Übersetzerraum 72 ein. Der andere Endbereich des Kolbens 39 greift in einen Füllraum 71-2 ein; dieser ist über Bohrungen in der unteren Endwand des Kolbens 40 verbunden, der mit der Leitung 5 verbunden ist. Der andere Endbereich des inneren Kolbens 40 ragt in den Füllraum 71-2. Über die Führungsspalte 65 und 67 wird der Übersetzerraum 72 gefüllt. Der Übersetzerraum 72 wird von der Stange 61 durchdrungen. Der Füllraum 71-1 wird von der Stange 63 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 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 71-2; this is connected via bores in the lower end wall of the piston 40, which is connected to the conduit 5. The other end portion of the inner piston 40 projects into the filling space 71-2. The translator space 72 is filled via the guide gaps 65 and 67. The translator space 72 is penetrated by the rod 61. The filling space 71-1 is penetrated by the rod 63. The pistons 39 and 40 move in opposite directions and because of the desired path translation from the actuator to the control valve at different speeds.

Der Aktor 31 (Piezosteller) ist im geschlossenen Zustand des Einspritzventils 9 mit Strom versorgt 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 und vom Druck im Füllraum 71-2. Im Übersetzerraum 72 und im Füllraum 71-2 ist im Ruhezustand CR-Druck (= Druck des Druckspeichers bzw. Common Rail) als Systemdruck. Im Übersetzerraum 72 steigt durch das Bewegen des Kolbens 39 nach oben der Druck. Diese Druckzunahme 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 vorzugsweise fest mit der Stange 63 und somit mit dem Kolben 40 verbunden. Wegen des CR-Drucks im Übersetzerraum 72 ist der Sitzdurchmesser d3 des Ventilteils 51 sehr groß wählbar, da der Kolben 40 diese Fläche mit seiner im Übersetzerraum 72 befindlichen Seite 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 supplied with power in the closed state of the injection valve 9 and lengthened. To open the control valve 41, the electric current to the actuator 31 is turned off and the actuator is shorter. Thereby, the piston 39 (first booster piston) in the figure is moved upwards, supported by the spring 75 and the pressure in the filling space 71-2. In the booster chamber 72 and in the filling chamber 71-2 is at rest CR pressure (= pressure of the accumulator or common rail) as a system pressure. In the interpreter room 72, by moving the piston 39 upward, the pressure increases. This pressure increase 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 preferably fixedly connected to the rod 63 and thus to the piston 40. Because of the CR pressure in the booster chamber 72, 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 side located in the booster chamber 72. 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 Seite des Kolbens 39 (im Übersetzerraum), die dem Steuerventil abgewandt ist, 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 on the side of the piston 39 (in the booster chamber), which faces away from the control valve, rail pressure is applied, which supports the actuation of the control valve and the pressure acting on the valve member 51 in the locked state from the control chamber 43 forth counteracts.

Wegen des Raildrucks im Übersetzerraum 72 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 translator 72, d3 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 diameter larger than the known diameter d3, which allows a faster opening and closing of the injection valve, because the flow increase and decrease is greater in this 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 gezeigte Vorrichtung weist noch weitere Merkmale auf. Zumindest in einem Bereich der den Aktor 31 mit dem hydraulischen Koppler verbindenden Stange 61 ist in einem Abstand von dem dem Aktor 31 am nächsten liegenden Raum des Kopplers ein weiterer Füllraum 90 vorhanden, der mit der Leitung 5 verbunden ist. Im Beispiel umgibt der weitere Füllraum 90 den Aktor 31 in dessen unterem Endbereich. Vorzugsweise umgibt er den ganzen Aktor 31. Ein Führungsspalt 94 der Stange 61 ist für eine zusätzliche Füllung des benachbarten Raums des Kopplers mit unter Druck stehendem Kraftstoff dimensioniert. Ein Vorteil besteht in der zusätzlichen Befüllung des Kopplers mit unter hohem Druck stehenden Kraftstoff.The device shown has even more features. At least in a region of the rod 61 connecting the actuator 31 to the hydraulic coupler, a further filling space 90, which is connected to the line 5, is present at a distance from the space of the coupler closest to the actuator 31. In the example, the additional filling space 90 surrounds the actuator 31 in its lower end region. Preferably, it surrounds the entire actuator 31. A guide gap 94 of the rod 61 is dimensioned for additional filling of the adjacent space of the coupler with pressurized fuel. An advantage is the additional filling of the coupler with high pressure fuel.

Bei Ausführungsformen der Erfindung ist der weitere Füllraum 90 nicht vorhanden oder ist nicht mit der Leitung 5 verbunden und hat nicht die Funktion eines Füllraums. In diesem Fall mag es zweckmäßig sein, eine Bohrung, in der die Stange 61 in einem nicht gezeigten Gehäuse der ganzen Vorrichtung geführt ist, für einen möglichst kleinen Abfluss von Kraftstoff aus dem Koppler zu dimensionieren.In embodiments of the invention, the additional filling space 90 does not exist or is not connected to the line 5 and does not have the function of a filling space. In this case, it may be appropriate to have a hole in which the Rod 61 is guided in a housing, not shown, of the entire device to dimension for the smallest possible outflow of fuel from the coupler.

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 (2)

  1. Fuel injection device (1) having an injection valve (9), having a line (5) which supplies highly pressurized fuel to the injection valve (9) during operation, having a control valve (41) which controls the pressure in a control chamber (43), which is connected to said line (5), of the injection valve (9), 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 booster space (72) of the coupler (38), with the seat (53) of the movable valve part (51) having a clear cross-sectional area f3, and having means for filling the booster space (72) with pressurized fuel via guide gaps (65, 67) of the pistons (39, 40), with the pistons (39, 40) being arranged one inside the other in parallel, with a filling space (71-2) being provided in the interior of the outer piston (40), which filling space (71-2) is connected to said line (5), with one of the two pistons (39, 40), which piston has a piston area f2, actuating the control valve (41) by means of a rod (63) with a smaller cross-sectional area f1 than f2, and with the direction of the closing movement of the movable valve part (51) corresponding to the direction of fuel flowing out of the control chamber (43), so that the control valve (41) is at least partially compensated in terms of force on account of the pressure acting on the one piston in the booster space (72),
    characterized
    in that the booster space (72) is arranged on those end sides of the pistons (39, 40) which face towards the actuator (31),
    in that the outer piston (40) actuates the control valve (41) by means of the rod (63),
    and in that the inner piston (39) with a cross-sectional area f4 is mechanically coupled to the actuator (31) by means of a further rod (61) with a smaller cross-sectional area f5 than f4.
  2. Fuel injection device according to Claim 1, characterized in that, at least in one region of the rod (61) which connects the actuator (31) to the hydraulic coupler (38), a further filling space (90) is provided at a distance from that space of the coupler (38) which is situated closest to the actuator (31), which further filling space (90) is connected to said line (5) and is connected by means of a guide gap (94) of the rod (61) to the coupler (38).
EP04738652A 2003-07-24 2004-06-09 Fuel injection device Expired - Lifetime EP1651857B1 (en)

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DE10333696A DE10333696A1 (en) 2003-07-24 2003-07-24 Fuel injector
PCT/DE2004/001200 WO2005010342A1 (en) 2003-07-24 2004-06-09 Fuel injection device

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EP1651857A1 EP1651857A1 (en) 2006-05-03
EP1651857B1 true EP1651857B1 (en) 2008-02-20

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102016285A (en) * 2008-04-23 2011-04-13 罗伯特·博世有限公司 Fuel injection valve for internal combustion engines

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090118019A1 (en) * 2002-12-10 2009-05-07 Onlive, Inc. System for streaming databases serving real-time applications used through streaming interactive video
DE102004015744A1 (en) 2004-03-31 2005-10-13 Robert Bosch Gmbh Common rail injector
DE102004044462A1 (en) * 2004-09-15 2006-03-30 Robert Bosch Gmbh Control valve for an injector
JP4003770B2 (en) * 2004-10-01 2007-11-07 トヨタ自動車株式会社 Fuel injection device
DE102005007543A1 (en) * 2005-02-18 2006-08-24 Robert Bosch Gmbh Fuel injector with direct needle control for an internal combustion engine
DE102005024721B4 (en) * 2005-05-30 2017-06-08 Robert Bosch Gmbh Common rail injector
DE102006049050A1 (en) * 2006-10-18 2008-04-30 Robert Bosch Gmbh Injector for injecting fuel
US7665445B2 (en) * 2008-04-18 2010-02-23 Caterpillar Inc. Motion coupler for a piezoelectric actuator
JP4614189B2 (en) * 2008-05-12 2011-01-19 株式会社デンソー Fuel injection device
DE102009024595A1 (en) 2009-06-10 2011-03-24 Continental Automotive Gmbh Injection valve with transmission unit
DE102009024596A1 (en) * 2009-06-10 2011-04-07 Continental Automotive Gmbh Injection valve with transmission unit
DE102011006202A1 (en) * 2011-03-28 2012-10-04 Robert Bosch Gmbh Valve for metering a medium
DE102012212266B4 (en) * 2012-07-13 2015-01-22 Continental Automotive Gmbh fluid injector
DE102012212264B4 (en) 2012-07-13 2014-02-13 Continental Automotive Gmbh Method for producing a solid state actuator
DE102013222506A1 (en) * 2012-12-06 2014-06-12 Robert Bosch Gmbh Method and device for mounting and filling a hydraulic coupler module
DE102013210843A1 (en) * 2013-06-11 2014-12-11 Continental Automotive Gmbh injector
DE102014211334B3 (en) * 2014-06-13 2015-08-27 Continental Automotive Gmbh Method for characterizing a hydraulic coupling element of a piezo injector
GB201414669D0 (en) * 2014-08-19 2014-10-01 Delphi International Operations Luxembourg S.�.R.L. Control valve arrangement
DE102014220779A1 (en) * 2014-10-14 2016-04-14 Continental Automotive Gmbh Injection valve for injecting fluid into a combustion chamber of an internal combustion engine
CN106640453B (en) * 2017-01-18 2023-01-03 哈尔滨工程大学 Micro-dynamic oil return electric control oil injector with hydraulic feedback

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19742073A1 (en) * 1997-09-24 1999-03-25 Bosch Gmbh Robert Fuel injection arrangement for internal combustion engines
DE19856617A1 (en) * 1998-12-08 2000-06-21 Siemens Ag Element for transmitting a movement and injection valve with such an element
DE19860678A1 (en) * 1998-12-29 2000-07-06 Bosch Gmbh Robert Fuel injection device for internal combustion engines
GB9905896D0 (en) * 1999-03-16 1999-05-05 Lucas Ind Plc Fuel injector arrangement
DE19949528A1 (en) * 1999-10-14 2001-04-19 Bosch Gmbh Robert Double-switching control valve for an injector of a fuel injection system for internal combustion engines with hydraulic amplification of the actuator
DE19951004A1 (en) 1999-10-22 2001-04-26 Bosch Gmbh Robert Hydraulic regulator esp. for fuel injector for motor vehicles has hydraulic converter between actor and valve member, to reverse actor movement
DE19951144A1 (en) * 1999-10-23 2001-04-26 Bosch Gmbh Robert Injector for fuel injection system in IC engines has guide bore in hydraulic connection with leakage oil return, to create pressure differential between pressure chamber and leakage oil return
DE10019764B4 (en) * 2000-04-20 2004-09-23 Robert Bosch Gmbh Length measuring device for measuring dimensions of bodies, particularly inner- and outer diameters, used in mechanical drive- and transmission elements and in circular body, has carrier element, which is adapted to body to be measured
DE10019765B4 (en) * 2000-04-20 2004-12-09 Robert Bosch Gmbh Valve for controlling liquids
US6260541B1 (en) * 2000-04-26 2001-07-17 Delphi Technologies, Inc. Hydraulic lash adjuster
DE10029629A1 (en) * 2000-06-15 2002-01-03 Bosch Gmbh Robert Fuel injection device for internal combustion engines
DE10031580A1 (en) * 2000-06-29 2002-01-17 Bosch Gmbh Robert Pressure-controlled control part for common rail injectors
DE10044120A1 (en) * 2000-09-07 2002-04-04 Bosch Gmbh Robert Common Rail System
DE10101802A1 (en) 2001-01-17 2002-07-18 Bosch Gmbh Robert Valve for controlling liquids e.g. fuel injection valve in IC engine, has actuating piston movably arranged in control piston blind bore to bound hydraulic chamber, with actuating piston and valve closure element made in one piece
DE10145622B4 (en) * 2001-09-15 2009-09-10 Robert Bosch Gmbh Valve for controlling fluids
DE10157411A1 (en) * 2001-11-23 2003-06-26 Bosch Gmbh Robert High pressure fuel injector
DE10337574A1 (en) * 2003-08-14 2005-03-10 Bosch Gmbh Robert Fuel injection device for internal combustion engines

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102016285A (en) * 2008-04-23 2011-04-13 罗伯特·博世有限公司 Fuel injection valve for internal combustion engines

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JP2006513369A (en) 2006-04-20
US7290530B2 (en) 2007-11-06
US20070001032A1 (en) 2007-01-04
WO2005010342A1 (en) 2005-02-03
CN1829858A (en) 2006-09-06
DE10333696A1 (en) 2005-02-24
JP4154425B2 (en) 2008-09-24
EP1651857A1 (en) 2006-05-03
CN100416082C (en) 2008-09-03
DE502004006265D1 (en) 2008-04-03

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